Liquid pump

Abstract

This application discloses a liquid pump, including a housing, within which are: a pump liquid chamber with an inlet and an outlet; a motor chamber located on one side of the pump liquid chamber; a heat dissipation chamber located on the outer periphery of the motor chamber for heat dissipation; and a liquid channel located between the pump liquid chamber and the heat dissipation chamber, with the heat dissipation chamber connected to the pump liquid chamber via the liquid channel; wherein, heat dissipation fins are provided in the heat dissipation chamber and / or the motor chamber. Under pressure difference, the liquid in the pump liquid chamber can flow into the heat dissipation chamber through the liquid channel for heat exchange, and the heat-exchanged liquid flows back from the heat dissipation chamber to the pump liquid chamber through the liquid channel, causing the liquid to circulate repeatedly from high pressure to low pressure to remove heat from the heat dissipation chamber. This application eliminates the piping structure, making manufacturing simpler and reducing costs. In addition, by providing heat dissipation fins in the heat dissipation chamber and / or the motor chamber to increase the heat exchange area, the heat transfer area between the heat dissipation chamber and the motor chamber is increased, thereby increasing the heat transfer rate and further improving the heat dissipation efficiency and performance of the liquid pump.

Description

Technical Field

[0001] This application relates to the field of liquid pump technology, and more particularly to liquid pumps. Background Technology

[0002] A liquid pump typically includes a stator, a rotor, a shaft, and a pump chamber for housing the axial end impeller of the shaft. The liquid flowing into the pump chamber is increased to a preset pressure by the impeller and then discharged from the pump chamber to the next stage, thereby realizing the liquid delivery of the liquid cooling system.

[0003] In the process of developing this application, the inventors discovered at least the following problems in the prior art:

[0004] 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, liquid pumps using this method are more complex to manufacture, their heat dissipation efficiency needs improvement, and their overall heat dissipation performance is relatively poor. Summary of the Invention

[0005] This application proposes a liquid pump designed to improve upon the technical problems of existing liquid pumps, such as complex manufacturing processes and relatively poor heat dissipation performance.

[0006] This application provides a liquid pump, including a housing, wherein the housing contains:

[0007] A pump fluid chamber, wherein the pump fluid chamber is provided with an inlet and an outlet;

[0008] The motor cavity is located on one side of the pump liquid cavity;

[0009] A heat dissipation cavity is disposed on the outer periphery of the motor cavity for dissipating heat from the motor cavity;

[0010] A liquid channel is disposed between the pump liquid chamber and the heat dissipation chamber, and the heat dissipation chamber is connected to the pump liquid chamber through the liquid channel;

[0011] The heat dissipation cavity and / or the motor cavity are provided with heat dissipation fins to increase the heat exchange area.

[0012] In some embodiments, it also includes:

[0013] The drive mechanism is located in the motor cavity;

[0014] An impeller assembly is disposed in the pump liquid chamber and located in the flow path between the liquid inlet and the liquid outlet;

[0015] Wherein: the impeller assembly is connected to the drive mechanism; a spiral flow channel is formed in the pump liquid chamber on the radially outer side of the impeller assembly, and the liquid inlet, the spiral flow channel, the liquid channel and the heat dissipation chamber are connected in sequence.

[0016] In some embodiments, a first heat dissipation fin is provided on the cavity wall of the heat dissipation cavity near the motor cavity, and the first heat dissipation fin extends spirally around the rotation axis of the drive mechanism; or

[0017] The heat dissipation cavity has a first heat dissipation fin on the cavity wall near the motor cavity, and the first heat dissipation fin extends along the axial direction of the drive mechanism's shaft.

[0018] In some embodiments, a second heat dissipation fin is provided on the cavity wall of the motor cavity near the heat dissipation cavity, and the second heat dissipation fin extends along the axial direction of the drive mechanism's shaft.

[0019] In some embodiments, the number of the first heat dissipation fins and the number of the second heat dissipation fins are both multiple.

[0020] In some embodiments, the impeller assembly includes multiple stages of impellers and guide vanes arranged coaxially, with adjacent stages of the impellers connected through the guide vanes. The number of helical flow channels is multiple, and the multiple helical flow channels are arranged sequentially along the impeller axis and connected to each other through the impeller. The helical flow channels are configured in one-to-one correspondence with the impellers.

[0021] In some embodiments, the plurality of spiral flow channels include a first flow channel, the guide vane includes a main body and a stop portion, the main body is disposed between two adjacent impellers, and the stop portion is formed by extending the outer periphery of the main body away from the liquid inlet along the impeller axis toward the end closer to the liquid inlet, and the first flow channel is formed between the stop portion and the impeller and the main body portion corresponding to it.

[0022] In some embodiments, the plurality of flow channels include a second flow channel. A convex ring is provided on the cavity wall of the pump liquid chamber near the heat dissipation cavity. The convex ring is correspondingly provided with the impeller near the liquid outlet in the multi-stage impeller. The convex ring extends in a spiral shape along the circumference of the impeller corresponding to it. The second flow channel is formed between the convex ring and the impeller corresponding to it. The liquid inlet, the first flow channel, the second flow channel, the liquid channel and the heat dissipation cavity are sequentially connected.

[0023] In some embodiments, the second flow channel has a head and a tail, and the radial width of the second flow channel gradually increases from the head toward the tail.

[0024] In some embodiments, the pump liquid chamber is provided with a first through hole on the side of the chamber facing the heat dissipation chamber, the liquid channel is formed by the first through hole, and there are multiple first through holes, which are arranged in a spiral interval around the rotating shaft of the drive mechanism.

[0025] The diameter of the plurality of first through holes gradually increases from the head to the tail.

[0026] Compared with the prior art, this technical solution has at least the following technical advantages:

[0027] The heat generated during the operation of a liquid pump mainly originates from the drive mechanism. By setting a heat dissipation chamber connected to the pump liquid chamber on the outer periphery of the motor cavity, the heat in the motor cavity can be continuously dissipated by the fluid in the pump liquid chamber. This means the heat generated during the operation of the liquid pump can be continuously absorbed and transferred without the need for a separate liquid cooling circulation system. Specifically, the pump liquid chamber can form a high-pressure zone and a low-pressure zone, with the liquid pressure in the high-pressure zone being greater than that in the low-pressure zone. Since the heat dissipation chamber connects the high-pressure and low-pressure zones of the pump liquid chamber through a liquid channel, during operation, under the action of the pressure difference, the liquid in the pump liquid chamber can flow from the liquid channel into the heat dissipation chamber for heat exchange. After heat exchange, the liquid flows back from the heat dissipation chamber to the pump liquid chamber through the liquid channel, causing the liquid to circulate repeatedly from high pressure to low pressure, thus carrying away the heat from the heat dissipation chamber. This achieves self-circulation of the liquid flow, reducing the need for an external power source, eliminating the need for additional piping structures, simplifying manufacturing, and reducing costs. In addition, by setting heat dissipation fins in the heat dissipation cavity and / or motor cavity to increase the heat exchange area, the heat transfer area between the heat dissipation cavity and the motor cavity is increased, thereby increasing the heat transfer rate between the heat dissipation cavity and the motor cavity, further improving the heat dissipation efficiency of the liquid pump, and achieving better heat dissipation performance. Attached Figure Description

[0028] The present invention will be further described below with reference to the accompanying drawings and embodiments.

[0029] Figure 1 This is a schematic diagram of the structure of the hydraulic motor in one embodiment of the present application;

[0030] Figure 2 for Figure 1 The main view;

[0031] Figure 3 for Figure 2 Sectional view along axis AA;

[0032] Figure 4 Figure 2 A cross-sectional view from another direction;

[0033] Figure 5 This is a schematic diagram of the internal structure of the housing in one embodiment;

[0034] Figure 6 This is a schematic diagram of the internal structure of the housing in another embodiment;

[0035] Figure 7 for Figure 6 A schematic diagram of the structure of the first heat dissipation fin;

[0036] Figure 8 This is a schematic diagram of the internal structure of the housing at the end away from the pump fluid chamber in one embodiment;

[0037] Figure 9 This is a schematic diagram of the internal structure of the housing near the pump fluid chamber in one embodiment;

[0038] Figure 10 for Figure 9 Assembly diagram of the middle casing and impeller assembly;

[0039] Figure 11 This is a schematic diagram of the structure of the hydraulic motor in another embodiment of this application.

[0040] Figure label:

[0041] Detailed Implementation

[0042] To better understand the technical solution of the present invention, the embodiments of the present invention will be described in detail below with reference to the accompanying drawings.

[0043] It should be understood that the described embodiments are merely some, not all, of the embodiments of the present invention. All other embodiments obtained by those skilled in the art based on the embodiments of the present invention without inventive effort are within the scope of protection of the present invention.

[0044] The terminology used in the embodiments of this invention is for the purpose of describing particular embodiments only and is not intended to limit the invention. The singular forms “a,” “the,” and “the” as used in the embodiments of this invention and the appended claims are also intended to include the plural forms unless the context clearly indicates otherwise.

[0045] It should be understood that the term "and / or" used in this article is merely a description of the relationship between related objects, indicating that three relationships can exist. For example, A and / or B can represent: A existing alone, A and B existing simultaneously, and B existing alone. Additionally, the character " / " in this article generally indicates that the preceding and following related objects have an "or" relationship.

[0046] It should be noted that if the embodiments of this application involve directional indicators (such as up, down, left, right, front, back, etc.), the directional indicators are only used to explain the relative positional relationship and movement of the components in a certain specific posture (as shown in the figure). If the specific posture changes, the directional indicators will also change accordingly.

[0047] This application proposes a liquid pump.

[0048] Please see Figures 1-6 The liquid pump includes a housing 110, a drive mechanism 130, and an impeller assembly 150; wherein the housing 110 has a pump liquid chamber 110a, a heat dissipation chamber 110c and a motor chamber 110b adjacent to one side of the pump liquid chamber 110a, and a liquid passage 110c disposed between the pump liquid chamber 110a and the heat dissipation chamber 110c. 11 The pump liquid chamber 110a is provided with an inlet 110a1 and an outlet 110a2. The end of the pump liquid chamber 110a near the outlet 110a2 is connected to the heat dissipation chamber 110c, that is, the heat dissipation chamber 110c can be connected to the heat dissipation chamber 110c through the liquid channel 110c. 11 The high-pressure zone and low-pressure zone of the pump liquid chamber 110a are connected, with the liquid pressure in the high-pressure zone being greater than that in the low-pressure zone. A heat dissipation chamber 110c is located on the outer periphery of the motor chamber 110b for heat dissipation. A drive mechanism 130 is located in the motor chamber 110b. An impeller assembly 150 is connected to the drive mechanism 130 and is disposed in the pump liquid chamber 110a, located on the flow path between the inlet 110a1 and the outlet 110a2. A spiral flow channel 110d1 / 110d2 is formed radially outside the impeller assembly 150 in the pump liquid chamber 110a. The inlet 110a1, the spiral flow channel 110d1 / 110d2, and the liquid channel 110c are also present. 11 The heat dissipation cavity 110c is connected in sequence with the heat dissipation cavity 110c. Heat dissipation fins are provided on the cavity wall between the heat dissipation cavity 110c and the motor cavity 110b. Specifically, multiple heat dissipation fins are provided on the cavity wall of the heat dissipation cavity 110c near the motor cavity 110b, and / or multiple heat dissipation fins are provided on the cavity wall of the motor cavity 110b near the heat dissipation cavity 110c. That is, heat dissipation fins for increasing the heat exchange area are provided in the heat dissipation cavity 110c and / or the motor cavity 110b. For easy distinction, the heat dissipation fins provided on the cavity wall of the heat dissipation cavity 110c are referred to as the first heat dissipation fin 191, and the heat dissipation fins provided on the cavity wall of the motor cavity 110b are referred to as the second heat dissipation fin 192.

[0049] That is, in one embodiment, the liquid pump 100 includes a housing 110, and the housing 110 is provided with: a pump liquid chamber 110a, the pump liquid chamber 110a having an inlet 110a1 and an outlet 110a2; a motor chamber 110b, disposed on one side of the pump liquid chamber 110a; a heat dissipation chamber 110c, disposed on the outer periphery of the motor chamber 110b, for dissipating heat from the motor chamber 110b; and a liquid channel 110c. 11 It is disposed between the pump liquid chamber 110a and the heat dissipation chamber 110c, and the heat dissipation chamber 110c is connected to the liquid channel 110c. 11 The high-pressure zone and low-pressure zone of the pump liquid chamber 110a are connected; wherein, the heat dissipation chamber 110c and / or the motor chamber 110b are provided with heat dissipation fins to increase the heat exchange area. The liquid pump 100 also includes: a drive mechanism 130, disposed in the motor chamber 110b; and an impeller assembly 150, disposed in the pump liquid chamber 110a and located on the flow path between the inlet 110a1 and the outlet 110a2; wherein: the impeller assembly 150 is drivenly connected to the drive mechanism 130, and a spiral flow channel 110d1 / 110d2 is formed on the radially outer side of the impeller assembly 150 in the pump liquid chamber 110a, the axial direction of the spiral flow channel 110d1 / 110d2 is consistent with the axial direction of the impeller assembly 150, and the inlet 110a1, the spiral flow channel 110d1 / 110d2, and the liquid channel 110c are connected. 11 It is connected in sequence with the heat dissipation cavity 110c.

[0050] 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 150. The principle of pressure difference refers to the difference in water pressure along the flow direction. When the impeller assembly 150 rotates, the rotational motion causes water flow. The area near the center line of the impeller assembly 150 is subject to low water pressure, while the area near the outer diameter of the impeller assembly 150 is affected by the water pressure of the high-pressure turbulent zone, resulting in a pressure difference. Furthermore, the interaction between the impeller assembly 150 and the inner wall of the pump liquid chamber 110a generates a vortex effect, making the liquid flow in the entire pump liquid chamber 110a consistent with the characteristics of the centrifugal force of the impeller assembly 150's rotation. This allows the liquid to flow from the high-pressure zone to the low-pressure zone and to flow into and out of the heat dissipation chamber 110c, 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 150 and the structure of the pump liquid chamber 110a. 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.

[0051] Please see Figure 3 and Figure 4In this embodiment, the drive mechanism 130 includes a stator 135, a rotor 133, and a shaft 131. The rotor 133 and the stator 135 are arranged sequentially from the inside to the outside, that is, the rotor 133 is located at the center of the stator 135. One end of the shaft 131 is connected to the impeller assembly 150 for transmission, and the other end is connected to the rotor 133. When the stator 135 is energized, it generates electromagnetic force to drive the rotor 133 to rotate the shaft 131. During this process, the drive mechanism 130 inevitably generates iron loss and copper loss. These energy losses are mainly manifested as heat. If this heat is not effectively dissipated, it will adversely affect the performance and service life of the liquid pump 100.

[0052] In this embodiment, the heat generated by the drive mechanism 130 is transferred to the heat dissipation chamber 110c through the wall of the motor cavity 110b. During the operation of the liquid pump, the drive mechanism 130 drives the impeller assembly 150 to rotate, so that external fluid is continuously introduced into the pump liquid chamber 110a from the inlet 110a1. Part of the fluid in the pump liquid chamber 110a is directly discharged from the outlet 110a2, and the other part is discharged through the liquid channel 110c. 11 The fluid enters the heat dissipation chamber 110c to absorb the heat transferred from the drive mechanism 130, and then returns to the pump fluid chamber 110a to mix with the fluid in the pump fluid chamber 110a. This cycle continues, continuously removing the heat generated by the drive mechanism 130.

[0053] In this application's technical solution, the heat generated during the operation of the liquid pump 100 mainly originates from the drive mechanism 130. By providing a heat dissipation cavity 110c connected to the pump liquid cavity 110a on the outer periphery of the motor cavity 110b, the heat in the motor cavity 110b can be continuously dissipated by the fluid in the pump liquid cavity 110a. This means the heat generated during the operation of the liquid pump can be continuously absorbed and transferred without the need for an additional liquid cooling circulation system. Specifically, the pump liquid cavity 110a can form a high-pressure zone and a low-pressure zone, with the liquid pressure in the high-pressure zone being greater than that in the low-pressure zone. Since the heat dissipation cavity 110c can be connected to the liquid channel 110c... 11 The high-pressure zone and low-pressure zone of the pump liquid chamber 110a are connected. Therefore, when the liquid pump 100 is working, under the action of pressure difference, the liquid in the pump liquid chamber 110a can flow from the liquid channel 110c. 11 The liquid flows into the heat dissipation chamber for heat exchange, and the heat-exchanged liquid flows through liquid channel 110c. 11The liquid flows back from the heat dissipation chamber 110c to the pump liquid chamber 110a, allowing the liquid to circulate repeatedly from high pressure to low pressure, thus carrying away heat from the heat dissipation chamber. This achieves self-circulation of the liquid flow, reducing the need for an external power source, eliminating the need for additional piping structures, simplifying manufacturing, and lowering costs. Furthermore, by incorporating heat dissipation fins within the heat dissipation chamber 110c and / or the motor chamber 110b to increase the heat exchange area, the heat transfer area between the heat dissipation chamber 110c and the motor chamber 110b is increased. This enhances the heat transfer rate between the heat dissipation chamber 110c and the motor chamber 110b, further improving the heat dissipation efficiency of the drive mechanism 130 / liquid pump 100 and resulting in better heat dissipation performance. Furthermore, by setting spiral flow channels 110d1 / 110d2 in the pump liquid chamber 110a, the vortex motion of the fluid can be enhanced, turbulence can be promoted, the boundary layer can be further broken, and the convective heat transfer coefficient between the fluid and the cavity wall of the heat dissipation cavity 110c can be increased. In addition, the spiral flow channels 110d1 / 110d2 can also help to guide the fluid in the pump liquid chamber 110a to the heat dissipation cavity 110c, which can increase the circulation flow rate of the fluid between the pump liquid chamber 110a and the heat dissipation cavity 110c, and further improve the heat dissipation efficiency of the liquid pump 100.

[0054] In this embodiment, during operation, the impeller assembly 150 rotates, driving the fluid in the pump chamber 110a to undergo vortex motion. This process generates a pressure drop, which not only drives the fluid to continuously enter the pump chamber 110a from the inlet 110a1 and exit from the outlet 110a2 into downstream equipment, but also drives the fluid to circulate between the pump chamber 110a and the heat dissipation chamber 110c. Specifically, when the impeller assembly 150 rotates, it guides the fluid flow through rotational motion. The fluid pressure is low near the center (shaft) of the impeller assembly 150, while the fluid pressure is high near the outer diameter of the impeller assembly 150. That is, there is a pressure difference in different areas of the impeller assembly 150. This pressure difference drives the fluid to continuously enter the downstream equipment and continuously circulate between the pump chamber 110a and the heat dissipation chamber 110c.

[0055] In this embodiment of the application, it should be noted that, generally speaking, the liquid flow rate of the pump liquid chamber 110a is significantly greater than the inlet and outlet flow rate of the heat dissipation chamber 110c. Therefore, the higher-temperature fluid discharged from the heat dissipation chamber 110c, after entering the pump liquid chamber 110a, undergoes preliminary mixing with the higher-temperature fluid from the liquid inlet. The temperature of the preliminary mixed fluid is basically the same as the temperature of the fluid from the liquid inlet and lower than the temperature of the fluid discharged from the heat dissipation chamber 110c. Then, under the action of the impeller assembly 150, a small portion of the aforementioned preliminary mixed fluid is diverted into the heat dissipation chamber 110c, while the remaining portion of the fluid is discharged from the pump liquid chamber 110a through the liquid outlet 110a2. The aforementioned fluid movement is cyclical, continuously dissipating the heat from the heat dissipation chamber 110c.

[0056] Please see Figure 6 In some embodiments, a first heat dissipation fin 191 is provided on the cavity wall of the heat dissipation cavity 110c near the motor cavity 110b. The first heat dissipation fin 191 extends spirally around the rotating shaft 131 of the drive mechanism 130. By setting the first heat dissipation fin 191 in a spiral shape, the surface area of ​​the first fin can be increased, enhancing its heat exchange potential. Furthermore, it can guide the fluid to move along a specific path within the heat dissipation cavity 110c, enabling more efficient heat exchange within a smaller space. In addition, compared to conventional heat dissipation fins, such as straight fins, spiral heat dissipation fins can enhance the vortex motion of the fluid in the heat dissipation cavity 110c, promote turbulence, further break the boundary layer, and increase the heat transfer coefficient between the fluid and the cavity wall of the heat dissipation cavity 110c, thereby further improving the heat dissipation efficiency of the drive mechanism 130 / liquid pump 100. Multiple first heat dissipation fins 191 may be provided.

[0057] Please see Figure 7 Based on the above embodiments, in some embodiments, the first heat dissipation fin 191 has a first end close to the pump liquid chamber 110a and a second end away from the pump liquid chamber 110a. The distance between the first end and the second end is b. Along the extension direction of the first heat dissipation fin 191, the angle between the tangent direction of the first end and the cross section direction of the rotating shaft 131 is β1, and the angle between the tangent direction of the second end and the cross section direction of the rotating shaft 131 is β2. The specific values ​​of b, β1 and β2 can be adjusted according to different application scenarios to meet the heat dissipation requirements.

[0058] Please see Figure 8 In some embodiments, a first heat dissipation fin 191 is provided on the cavity wall of the heat dissipation cavity 110c near the motor cavity 110b, and the first heat dissipation fin 191 extends along the axial direction of the rotating shaft 131 of the drive mechanism 130. Multiple first heat dissipation fins 191 may be provided.

[0059] A first through hole 110c is provided on the cavity wall of the pump fluid chamber 110a near the heat dissipation chamber 110c. 11 First through hole 110c 11 Connect the pump liquid chamber 110a to the heat dissipation chamber 110c, that is, connect the liquid channel 110c. 11 From the first through hole 110c 11 Formed, and having a first through hole 110c 11 It is offset from the first heat dissipation fin 191. Specifically, along the circumferential direction of the rotating shaft 131, the first through hole 110c 11 The first through hole 110b is offset from part of the first heat dissipation fin 191, or, along the radial direction of the rotating shaft 131, the first through hole 110b 11It is offset from part of the first heat dissipation fin 191. This is achieved by interpolating the first through hole 110c. 11 The offset arrangement with the first heat dissipation fin 191 helps to reduce the flow resistance of the fluid in the heat dissipation cavity 110c and facilitates the flow of the fluid along a preset path in the heat dissipation cavity 110c, so that the fluid can achieve more efficient heat exchange in the heat dissipation cavity 110c.

[0060] Please continue reading. Figure 8 In some embodiments, the first through hole 110c 11 The first heat dissipation fins 191 are offset from each other in the radial direction of the rotating shaft 131. This arrangement helps to evenly guide the fluid into each area of ​​the heat dissipation cavity 110c, and improves the heat dissipation uniformity of each area of ​​the drive mechanism 130.

[0061] In the above embodiments, the first heat dissipation fin 191 may extend from the cavity wall of the heat dissipation cavity 110c toward the pumping cavity 110a, and there may also be a gap between the first heat dissipation fin 191 and the cavity wall of the heat dissipation cavity 110c toward the pumping cavity 110a. When there is a gap between the first heat dissipation fin 191 and the cavity wall of the heat dissipation cavity 110c toward the pumping cavity 110a, the projection of a portion of the first heat dissipation fin 191 near the pumping cavity 110a onto the cavity wall of the heat dissipation cavity 110c near the pumping cavity 110a coincides with the first through hole 110c. 11 It is offset in the radial direction of the rotating shaft 131.

[0062] Please see Figure 8 and Figure 9 In some embodiments, the first through hole 110c 11 The quantity is multiple, multiple first through holes 110c 11 The fluid is arranged in a spiral pattern around the rotating shaft 131. This arrangement helps to enhance the vortex motion of the fluid in the heat dissipation chamber 110c, promotes turbulence, and increases the circulation flow rate of the fluid between the pump fluid chamber 110a and the heat dissipation chamber 110c.

[0063] In some embodiments, further, a plurality of first through holes 110c 11 The aperture of the first through hole 110c gradually decreases, with the aperture decreasing as the hole gets closer to the rotating shaft 131. 11 The larger the aperture, the better the fluid flow path, allowing the fluid to better form vortices in the heat dissipation cavity 110c. This results in more thorough stirring of the fluid in the heat dissipation cavity 110c, enabling the fluid to more efficiently absorb heat from the motor cavity 110b after entering the heat dissipation cavity 110c. This also leads to more uniform liquid circulation and heat distribution in the heat dissipation cavity 110c.

[0064] In the above embodiment, the first through hole 110c 11The specific quantity and each first through hole 110c 11 The specific size and shape can be adjusted according to the actual heat dissipation requirements of the liquid pump, and this application does not impose any special limitations on this.

[0065] In some embodiments, the first through hole 110c corresponding to the end of the first heat dissipation fin 191 near the pump fluid chamber 110a 11 The greater the distance from the rotating shaft 131 and the smaller the aperture, the greater the width of the first heat dissipation fin 191 in the radial direction of the rotating shaft 131.

[0066] In some embodiments, a second heat dissipation fin 192 is provided on the cavity wall of the motor cavity 110b near the heat dissipation cavity 110c, and the second heat dissipation fin 192 extends along the rotation axis 131 of the drive mechanism 130. Multiple second heat dissipation fins 192 may be provided.

[0067] In the above embodiments, the second heat dissipation fin 192 can be a straight heat dissipation fin or a spiral heat dissipation fin. Preferably, the second heat dissipation fin 192 is a spiral heat dissipation fin. The spiral fin has a larger surface area and higher heat exchange potential, enabling more efficient heat exchange. In addition, when the motor cavity 110b is filled with insulating coolant, the spiral heat dissipation fin can also enhance the vortex motion of the fluid in the motor cavity 110b, promote the turbulence of the fluid in the motor cavity 110b, further break the boundary layer, increase the heat transfer coefficient between the fluid and the cavity wall of the motor cavity 110b, and improve the heat dissipation efficiency of the drive mechanism 130 / liquid pump 100.

[0068] In the above embodiments, the number, shape, and size of the first heat dissipation fins 191 and the second heat dissipation fins 192 can be adjusted according to the heat dissipation requirements of the liquid pump. In some embodiments, there are multiple first heat dissipation fins 191 and multiple second heat dissipation fins 192.

[0069] Please see Figure 11 In some embodiments, a third heat dissipation fin 193 is provided on the outer side of the housing 110. The third heat dissipation fin 193 is located on the outer periphery of the heat dissipation cavity 110c, and / or, the third heat dissipation fin 193 is located at the end of the motor cavity 110b / heat dissipation cavity 110c facing away from the pump liquid cavity 110a. By providing the third heat dissipation fin 193 on the outside of the housing 110, the convective heat transfer rate between the external air and the cavity wall of the heat dissipation cavity 110c / motor cavity 110b can be increased, further improving the heat dissipation efficiency of the liquid pump 100.

[0070] Please see Figure 3 , Figure 9 and Figure 10In some embodiments, a helical flow channel 110d1 / 110d2 is formed in the pump liquid chamber 110a on the radially outer side of the impeller assembly 150. The axial direction of the helical flow channel 110d1 / 110d2 is aligned with the axial direction of the impeller assembly 150. The inlet 110a1, the helical flow channel 110d1 / 110d2, and the liquid passage 110c are also included. 11 (that is, the first through hole 110c) 11 ) and heat dissipation cavity 110c are connected in sequence.

[0071] By setting spiral flow channels 110d1 / 110d2 in the pump liquid chamber 110a, the vortex motion of the fluid can be enhanced, turbulence can be promoted, the boundary layer can be further broken, and the convective heat transfer coefficient between the fluid and the cavity wall of the heat dissipation cavity 110c can be increased. Furthermore, the spiral flow channels 110d1 / 110d2 can also help to guide the fluid in the pump liquid chamber 110a to the heat dissipation cavity 110c, which can increase the circulation flow rate of the fluid between the pump liquid chamber 110a and the heat dissipation cavity 110c, thereby effectively improving the heat dissipation efficiency of the liquid pump 100.

[0072] In the above embodiment, the impeller assembly 150 includes a multi-stage impeller 151 and guide vanes 153 arranged coaxially. Adjacent impellers 151 are connected through the guide vanes 153. The primary impeller 151 in the multi-stage impeller 151 is the impeller 151 closest to the liquid inlet 110a1, and the last impeller 151 in the multi-stage impeller 151 is the impeller 151 closest to the liquid outlet 110a2 / heat dissipation chamber 110c. During operation, the liquid inlet 110a1 of the liquid pump is connected to a water source (fluid supply source). After the water (fluid) enters the pump liquid chamber 110a, it is first driven to rotate by the primary impeller 151. The rotation of the primary impeller 151 generates centrifugal force to throw the water out of it, and then it enters the guide vanes 153 and the next stage impeller 151 in sequence, circulating until it enters the last stage impeller 151, thus increasing the pressure of the water (fluid) to the expected range. During operation, the area near the center of impeller 151 is a low-pressure zone, and the area near the outer periphery of impeller 151 is a high-pressure zone. The low-pressure zone of the primary impeller 151 is connected to the inlet 110a1, and the high-pressure zone of the final impeller 151 is connected to the outlet 110a2 and the heat dissipation chamber 110c. Under the pressure difference between the high-pressure and low-pressure zones, water (fluid) is continuously drawn into the pump liquid chamber 110a from the inlet 110a1, and then guided to the outlet 110a2 and the heat dissipation chamber 110c. It should be noted that multi-stage impeller 151 refers to impellers with two or more stages.

[0073] In the above embodiments, the number of spiral flow channels 110d1 / 110d2 can be one or more. In some preferred embodiments, the number of spiral flow channels 110d1 / 110d2 is multiple. The multiple spiral flow channels 110d1 / 110d2 are arranged sequentially along the axial direction of the impeller 151 and are interconnected through the impeller 151. The spiral flow channels 110d1 / 110d2 are arranged in a one-to-one correspondence with the impeller 151.

[0074] In the preferred embodiment described above, the impeller 151, the spiral flow channels 110d1 / 110d2, and the guide vane 153 are sequentially and alternately connected. For example, when the number of impellers 151 is 2, that is, when there are 2 impellers 151, there is 1 guide vane 153 and 2 spiral flow channels 110d1 / 110d2. During operation, the fluid flows through the following path: inlet 110a1 → primary impeller 151 → spiral flow channels 110d1 / 110d2 → guide vane 153 → second-stage impeller 151 → spiral flow channels 110d1 / 110d2 → outlet 110a2 / heat dissipation chamber 110c.

[0075] By providing spiral flow channels 110d1 / 110d2 on the outer periphery of each impeller 151, the vortex motion of the fluid in the pump liquid chamber 110a can be enhanced step by step, which is beneficial to improving the circulation flow rate of the fluid between the pump liquid chamber 110a and the heat dissipation chamber 110c, and thus beneficial to improving the heat dissipation efficiency of the liquid pump 100.

[0076] Please see Figure 10 In the above embodiment, specifically, the plurality of spiral flow channels 110d1 / 110d2 include a first flow channel 110d1, and the guide vane 153 includes a main body 1531 and a stop part 1533. The main body 1531 is disposed between two adjacent impellers 151, and the stop part 1533 is formed by extending the outer periphery of the main body 1531 away from the liquid inlet 110a1 along the axial direction of the impeller 151 toward the end close to the liquid inlet 110a1. The first flow channel 110d1 is formed between the stop part 1533 and the impeller 151 and the main body 1531 correspondingly disposed therebetween. The first flow channel 110d1 is located in the flow path between the impeller 151 and the guide vane 153. The spiral flow channels 110d1 / 110d2 on the outer periphery of the impeller 151 (except for the last stage impeller 151) are all the first flow channels 110d1. After the fluid is thrown out from the impeller 151 (other impellers 151 except for the last stage impeller 151), it enters the first flow channel 110d1 and spirally guided into the guide vane 153 along the first flow channel 110d1. This process is repeated until the fluid enters the last stage impeller 151. The fluid is continuously pressurized throughout the process.

[0077] In the above embodiments, more specifically, the rotating shaft 131 is disposed in the rotor cavity 110b. 2，One end of the rotating shaft 131 is connected to the rotor 133, and the other end extends out of the rotor cavity 110b2 and connects to the impeller 151 located in the pump liquid cavity 110a, so as to drive the impeller 151 to rotate. The impeller 151 includes a wheel seat and multiple blades. The wheel seat is sleeved on the rotating shaft 131, and a flow guide channel is formed inside the wheel seat. The blades are located in the flow guide channel. The middle and periphery of the wheel seat have openings that communicate with the flow guide channel. The inner wall surface of the stop portion 1533 extends spirally around the rotating shaft 131. The first flow channel 110d1 is formed between the inner wall surface of the stop portion 1533 and the corresponding impeller 151 and the main body portion 1531. Alternatively, the inner wall surface of the stop portion 1533 is provided with a protrusion 15331 that extends spirally around the rotating shaft 131. The first flow channel 110d1 is formed between the protrusion 15331 and the outer periphery of the corresponding impeller 151 and the main body portion 1531. The main body 1531 of the guide vane 153 is sleeved on the rotating shaft 131 and forms a pressurization channel. The middle and periphery of the main body 1531 of the guide vane 153 have openings that communicate with the pressurization channel, so as to communicate with the first flow channel 110d1 upstream and the flow channel of the impeller 151 downstream, respectively.

[0078] In some embodiments, the impeller assembly 150 may also have a rotating shaft. That is, in addition to including multi-stage impellers 151 and guide vanes 153 arranged coaxially, the impeller assembly 150 also includes a rotating shaft. The multi-stage impellers 151 are sequentially arranged on the impeller rotating shaft 1535 along the axial direction of the shaft. The impeller rotating shaft 1535 is coaxially arranged with the rotating shaft 131 and connected to the end of the rotating shaft 131 facing the pump liquid chamber 110a. The impeller rotating shaft 1535 can be integrally formed with the rotating shaft 131 or formed separately. The impeller 151 includes a wheel seat and multiple blades. The wheel seat is sleeved on the impeller rotating shaft 1535. A flow guiding channel is formed inside the wheel seat. The blades are located in the flow guiding channel. The center and periphery of the wheel seat have openings communicating with the flow guiding channel. The inner wall of the stop portion 1533 extends spirally around the impeller shaft 1535. The first flow channel 110d1 is formed between the inner wall of the stop portion 1533 and the corresponding impeller 151 and main body portion 1531. Alternatively, the inner wall of the stop portion 1533 is provided with a protrusion 15331 extending spirally around the impeller shaft 1535, and the first flow channel 110d1 is formed between the protrusion 15331 and the outer periphery of the corresponding impeller 151 and main body portion 1531. The main body portion 1531 of the guide vane 153 is sleeved on the impeller shaft 1535 and forms a pressurization channel. The middle and periphery of the main body portion 1531 of the guide vane 153 have openings communicating with the pressurization channel, so as to communicate with the first flow channel 110d1 upstream and the guide channel of the impeller 151 downstream, respectively.

[0079] Please see Figure 9In the above embodiment, the plurality of flow channels also includes a second flow channel 110d2, which passes through the first through hole 110c. 11 It is connected to the heat dissipation cavity 110c, and the fluid passes through the first through hole 110c. 11 The liquid circulates between the second flow channel 110d2, the pump liquid chamber 110a, and the heat dissipation chamber 110c. A convex ring 1111 is provided on the wall of the pump liquid chamber 110a near the heat dissipation chamber 110c. The convex ring 1111 corresponds to the impeller 151 near the outlet 110a2 in the multi-stage impeller 151. The convex ring 1111 extends spirally along the circumference of its corresponding impeller 151. The second flow channel 110d2 is formed between the convex ring 1111 and its corresponding impeller 151. The system includes the inlet 110a1, the first flow channel 110d1, the second flow channel 110d2, and the liquid passage 110c. 11 (that is, the first through hole 110c) 11 The impeller 151 and the heat dissipation cavity 110c are connected in sequence. Specifically, for example, when the number of impellers 151 is 2, that is, when there are 2 impellers 151, the number of guide vanes 153 is 1, and the number of spiral flow channels 110d1 / 110d2 is 2. During operation, the flow path of the fluid is: inlet 110a1 → primary impeller 151 → first flow channel 110d1 → guide vane 153 → second-stage impeller 151 → second flow channel 110d2 → outlet 110a2 / heat dissipation cavity 110c.

[0080] In the above embodiment, the distance between the end of the last stage impeller 151 away from the heat dissipation cavity 110c and the cavity wall of the pumping cavity 110a near the heat dissipation cavity 110c is d. Preferably, the extension width of the convex ring 1111 along the rotation axis is d. That is, the convex ring 1111 extends from the cavity wall of the pumping cavity 110a near the heat dissipation cavity 110c to the corresponding position on the periphery of the last stage impeller 151. This arrangement allows the fluid to flow along a spiral direction after exiting the impeller assembly 150 until it is pumped into the heat dissipation cavity 110c. Conversely, the fluid can flow along a spiral direction after exiting the heat dissipation cavity 110c until it leaves from the outlet 110a2. This is beneficial for enhancing the vortex motion of the fluid, promoting turbulence, and enhancing the heat dissipation efficiency of the liquid pump 100.

[0081] In the above embodiments, by setting the first flow channel 110d1 and the second flow channel 110d2, the flow path of the fluid in the pump liquid chamber 110a is optimized, so that the fluid can continue to be pressurized after being thrown out from the impeller 151 (before entering the guide vane 153), which further promotes the circulation of the fluid between the pump liquid chamber 110a and the heat dissipation chamber 110c.

[0082] The second flow channel 110d2 has a head and a tail, and the radial width of the second flow channel 110d2 gradually increases from the head to the tail. In some embodiments, the outlet 110a2 is located at the corresponding position at the tail of the second flow channel 110d2. This arrangement allows the fluid in the pump chamber 110a to be directly discharged from the pump chamber 110a along the second flow channel 110d2, which can promote the vortex motion of the fluid and improve the working efficiency of the liquid pump 100.

[0083] In this embodiment, a first through hole 110c is provided in the cavity wall of the heat dissipation cavity 110c facing the pump liquid cavity 110a. 11 First through hole 110c 11 The second flow channel 110d2 is connected to the heat dissipation cavity 110c, that is, the liquid channel 110c. 11 From the first through hole 110c 11 Formation. Fluid passes through the first through-hole 110c 11 It circulates between the second flow channel 110d2 and the heat dissipation cavity 110c.

[0084] In some embodiments, the first through hole 110c 11 The quantity is multiple, multiple first through holes 110c 11 Multiple first through holes 110c are arranged sequentially at intervals along the circumferential extension direction of the second flow channel 110d2. 11 Multiple first through holes 110c are arranged sequentially at intervals along the spiral direction. 11 The spiral arrangement path corresponds to the spiral extension path of the second flow channel 110d2. This arrangement helps to enhance the vortex motion of the fluid in the second flow channel 110d2 and the heat dissipation cavity 110c, promotes turbulence, and increases the circulation flow rate of the fluid between the pump chamber 110a and the heat dissipation cavity 110c. In this embodiment, multiple first through holes 110c 11 They can be arranged sequentially at intervals along the Archimedean spiral 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.

[0085] Furthermore, multiple first through holes 110c 11 The orifice diameter gradually increases from the head to the tail of the second flow channel 110d2. This arrangement helps optimize the fluid flow path, ensuring that the fluid flows smoothly from the head (start of the helix), tail (end of the helix), and first through-hole 110c of the second flow channel 110d2. 11 The path can better form vortices, so that the fluid in the second flow channel 110d2 is more fully stirred and the fluid can more efficiently absorb the heat in the motor cavity 110b after entering the heat dissipation cavity 110c, thereby achieving a more uniform liquid circulation and heat distribution in the heat dissipation cavity 110c.

[0086] In the above embodiment, the first through hole 110c 11 The specific quantity and each first through hole 110c 11 The specific dimensions can be adjusted according to the actual heat dissipation requirements of the liquid pump, and this application does not impose any special limitations on them.

[0087] Please see Figure 1 In some embodiments, the housing 110 is further provided with an oil inlet 181, which communicates with the motor cavity 110b to inject insulating coolant into the motor cavity 110b. During the operation of the drive mechanism 130, the insulating coolant can circulate naturally within the motor cavity 110b, rapidly absorbing and transferring the heat generated by the drive mechanism 130 to the heat dissipation cavity 110c, thereby further improving the heat dissipation efficiency of the drive mechanism 130; and by immersing the drive mechanism 130 in the insulating coolant, it is also beneficial to improve the heat dissipation uniformity of the drive mechanism 130.

[0088] Please see Figure 3 In the above embodiment, the motor cavity 110b further includes a stator cavity 110b1 and a rotor cavity 110b2. The drive mechanism 130 includes a rotating shaft 131 and a rotor 133 and a stator 135 arranged sequentially from the inside to the outside. The stator 135 is located in the stator cavity 110b1, and the rotor 133 and the rotating shaft 131 are located in the rotor cavity 110b2. A shielding sleeve 113 is provided between the stator 135 and the rotor 133 to separate the stator cavity 110b1 and the rotor cavity 110b2. The oil injection nozzle 181 is connected to the stator cavity 110b1, and the insulating coolant is injected into the stator cavity 110b1 through the oil injection nozzle 181. By separating the stator cavity 110b1 and the rotor cavity 110b2, and using the shielding sleeve 113 to effectively ensure the sealing of the rotor 133, the contact between the insulating coolant and the rotor 133 is reduced, thus reducing the risk of corrosion of the rotor 133. This effectively ensures the normal operation of the rotor 133 and extends its service life. Furthermore, the shielding sleeve 113 absorbs the heat generated by the rotor 133 during operation and transfers the heat to the insulating coolant through its material, thereby achieving heat dissipation. It should be noted that the rotor cavity 110b2 needs to be filled with refrigerant oil, which serves two purposes: firstly, to ensure lubrication between the rotor 133 and the shaft 131, and secondly, to transfer heat to the shielding sleeve 113 through the refrigerant oil.

[0089] Please continue reading. Figure 3 In some embodiments, the housing 110 includes a main housing 111, a first cover plate 117, and a second cover plate 119. A rotor cavity 110b2, a stator cavity 110b1, a pumping fluid cavity 110a, and a heat dissipation cavity 110c are disposed in the main housing 111. A second through hole 110b21 is provided in the cavity wall of the rotor cavity 110b2 facing the pumping fluid cavity 110a for the shaft 131 to pass through and drive the impeller assembly 150; that is, the shaft 131 passes through the second through hole 110b21.21 Connected to the impeller assembly 150, a first cover plate 117 and a second cover plate 119 are respectively disposed at opposite ends of the main housing 111. The first cover plate 117 is used to cover the pump liquid chamber 110a, and the second cover plate 119 is used to cover the motor chamber 110b. By dividing the housing 110 into the main housing 111, the first cover plate 117, and the second cover plate 119, the assembly convenience of the liquid pump 100 is improved. Specifically, an oil inlet 181 is disposed on the main housing 111 and communicates with the stator chamber 110b to fill the stator chamber 110b with insulating coolant.

[0090] When assembling the liquid pump 100, the impeller assembly 150 or the drive mechanism 130 can be assembled in the first or second cylinder section, the impeller assembly 150 and the shaft 131 of the drive mechanism 130 can be fixed, and then the first cover plate 117 and the second cover plate 119 can be assembled with the main housing 111.

[0091] In the above embodiments, the main housing 111 is made of a material with high thermal conductivity to quickly conduct heat away from the liquid pump. In one specific embodiment, the main housing 111 is made of aluminum alloy, which has low density and high thermal conductivity.

[0092] In the above embodiments, the main housing 111 may include a first cylindrical section and a second cylindrical section arranged front to back. A pump fluid chamber 110a is formed in the first cylindrical section, and a motor chamber 110b and a heat dissipation chamber 110c are formed in the second cylindrical section. A first heat dissipation fin 191 is disposed on the outer wall of the second cylindrical section, and a second heat dissipation fin 192 is disposed on the inner wall of the second cylindrical section. The front end of the first cylindrical section is open, and a first cover plate 117 is disposed at the front end of the first cylindrical section to cover the pump fluid chamber 110a. The rear end of the second cylindrical section is open, and a second cover plate 119 is disposed at the rear end of the second cylindrical section to cover the motor chamber 110b. The first and second cylindrical sections may be integrally formed or separately formed. Preferably, the first and second cylindrical sections are separately formed. The following describes the liquid pump of this application in more detail using the example of the first and second cylindrical sections being integrally formed.

[0093] In some embodiments, the second cylindrical section includes an inner cylinder and an outer cylinder. The inner cylinder is integrally formed with the first cylindrical section, and the outer cylinder is sleeved around the outer periphery of the inner cylinder. The motor cavity 110b is formed in the inner cylinder, and the heat dissipation cavity 110c is formed between the inner cylinder and the outer cylinder. The inner cylinder and the outer cylinder can be integrally formed or formed separately.

[0094] In some embodiments, the stator cavity 110b1 and the rotor cavity 110b2 are separated by a shielding sleeve 113, which is separately formed from the main housing 111. Specifically, a first limiting ring is provided on the cavity wall of the motor cavity 110b near the pump fluid cavity 110a, a second limiting ring is provided on the inner side of the second cover plate 119, and the two ends of the shielding sleeve 113 are respectively fitted onto the first limiting ring and the second limiting ring.

[0095] In the above embodiments, a sealing ring is provided between the first cover plate 117 and the first cylinder section to prevent liquid in the pump fluid chamber 110a from overflowing from the connection between the first cover plate 117 and the first cylinder section; a sealing ring 171 is provided between the second cover plate 119 and the second cylinder section to prevent liquid in the motor chamber 110b from overflowing from the connection between the second cylinder section and the second cover plate 119; a sealing ring 171 is provided between the shielding sleeve 113 and the ring platform to prevent coolant in the stator chamber 110b1 from entering the rotor chamber 110b2.

[0096] In the above embodiments, the outlet 110a2 of the pump liquid chamber 110a is located at the rear end of the first cylinder section, and the inlet 110a1 can be opened in the first cylinder section or the first cover plate 117, which can be selected as needed. In some embodiments, the inlet 110a1 is opened in the first cover plate 117, and the outlet 110a2 is opened at the top of the rear end of the first cylinder section.

[0097] In the above embodiment, the impeller assembly 150 is rotatably connected to the main housing 111 via a shaft seal 173. A limiting groove is provided on the wall of the pumping chamber 110a near the rotor chamber 110b2, and the shaft seal 173 is disposed in the limiting groove. On one hand, the shaft seal 173 serves a sealing function, preventing liquid in the pumping chamber 110a from passing through the gap between the rotating shaft 131 and the wall of the second through hole 110b21; on the other hand, the shaft seal 173 also reduces friction between the impeller assembly 150, the main housing 111, and the rotating shaft 131 during operation.

[0098] In some embodiments, the drive mechanism 130 further includes a bearing 137 sleeved on the rotating shaft 131. The bearing 137 and the rotor 133 are arranged axially along the rotating shaft 131, and the rotating shaft 131 is rotatably connected to the cavity wall of the rotor cavity 110b2 through the bearing 137. Specifically, bearings 137 are provided at both the front and rear ends of the rotor 133. The bearing 137 includes an inner ring and an outer ring sleeved on the inner ring. The inner ring abuts against the side wall of the rotating shaft 131, and the outer ring abuts against the cavity wall of the rotor cavity 110b2. The inner ring and the outer ring are slidably connected. By providing the bearing 137, the friction between the drive mechanism 130 and the main housing 111 during operation can be reduced.

[0099] In some embodiments, a stop platform 1311 protrudes from the side wall of the rotating shaft 131, and the drive mechanism 130 further includes a limiter 139. The limiter 139 is sleeved on the rotating shaft 131, and the rotor 133 is clamped between the stop platform 1311 and the limiter 139 to limit the axial movement of the rotor 133 and prevent the rotor 133 from being displaced during rotation.

[0100] In the above embodiments, preferably, the limiter 139 is located at the end of the rotor 133 away from the pump liquid chamber 110a, so as to facilitate the assembly between the housing 110, the impeller assembly 150 and the drive mechanism 130.

[0101] Please see Figure 1 In some embodiments, the housing 110 is further provided with a cable interface 183 for inserting a control cable, which communicates with the stator cavity 110b1. The cable interface 183 connects to the stator 135 in the stator cavity 110b1 to transmit external electrical signals to the drive mechanism 130. In the above embodiments, the cable interface 183 may be located on the main housing 111 or on the second cover plate 119.

[0102] The above are merely preferred embodiments of the present invention and are not intended to limit the present invention. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A liquid pump characterized by, Includes a housing, wherein the housing contains: A pump fluid chamber, wherein the pump fluid chamber is provided with an inlet and an outlet; The motor cavity is located on one side of the pump liquid cavity; A heat dissipation cavity is disposed on the outer periphery of the motor cavity for dissipating heat from the motor cavity; A liquid channel is disposed between the pump liquid chamber and the heat dissipation chamber, and the heat dissipation chamber is connected to the pump liquid chamber through the liquid channel; The heat dissipation cavity and / or the motor cavity are provided with heat dissipation fins to increase the heat exchange area.

2. The liquid pump as claimed in claim 1, characterized in that, Also includes: The drive mechanism is located in the motor cavity; An impeller assembly is disposed in the pump liquid chamber and located in the flow path between the liquid inlet and the liquid outlet; Wherein: the impeller assembly is connected to the drive mechanism; a spiral flow channel is formed in the pump liquid chamber on the radially outer side of the impeller assembly, and the liquid inlet, the spiral flow channel, the liquid channel and the heat dissipation chamber are connected in sequence.

3. The liquid pump as described in claim 2, characterized in that, A first heat dissipation fin is provided on the cavity wall of the heat dissipation cavity near the motor cavity, and the first heat dissipation fin extends spirally around the rotation axis of the drive mechanism; or, The heat dissipation cavity has a first heat dissipation fin on the cavity wall near the motor cavity, and the first heat dissipation fin extends along the axial direction of the drive mechanism's shaft.

4. The liquid pump as described in claim 3, characterized in that, A second heat dissipation fin is provided on the cavity wall of the motor cavity near the heat dissipation cavity, and the second heat dissipation fin extends along the axial direction of the drive mechanism's shaft.

5. The liquid pump as described in claim 4, characterized in that, There are multiple first heat dissipation fins and multiple second heat dissipation fins.

6. The liquid pump according to any one of claims 1-5, characterized in that, The impeller assembly includes multiple stages of impellers and guide vanes arranged coaxially. Adjacent stages of the impellers are connected through the guide vanes. There are multiple spiral flow channels, which are arranged sequentially along the impeller axis and connected to each other through the impellers. Each spiral flow channel corresponds to one impeller.

7. The liquid pump as claimed in claim 6, characterized in that, The plurality of spiral flow channels include a first flow channel. The guide vane includes a main body and a stop portion. The main body is disposed between two adjacent impellers. The stop portion is formed by extending the outer periphery of the main body away from the liquid inlet along the impeller axis toward the end closer to the liquid inlet. The first flow channel is formed between the stop portion and the impeller and the main body corresponding to it.

8. The liquid pump as claimed in claim 7, characterized in that, The plurality of flow channels include a second flow channel. A convex ring is provided on the cavity wall of the pump liquid chamber near the heat dissipation cavity. The convex ring is correspondingly provided with the impeller near the liquid outlet in the multi-stage impeller. The convex ring extends in a spiral shape along the circumference of the impeller corresponding to it. The second flow channel is formed between the convex ring and the impeller corresponding to it. The liquid inlet, the first flow channel, the second flow channel, the liquid channel and the heat dissipation cavity are connected in sequence.

9. The liquid pump as claimed in claim 8, characterized in that, The second flow channel has a head and a tail, and the radial width of the second flow channel gradually increases from the head toward the tail.

10. The liquid pump as claimed in claim 9, characterized in that, The pump liquid chamber is provided with a first through hole on the side of the chamber facing the heat dissipation chamber. The liquid channel is formed by the first through hole. There are multiple first through holes, and the multiple first through holes are arranged in a spiral interval around the rotating shaft of the drive mechanism. The diameter of the plurality of first through holes gradually increases from the head to the tail.

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