Electronic water pump, thermal management system, and vehicle

Abstract

The utility model discloses an electronic water pump, heat management system and vehicle. Electronic water pump includes: pump shell is equipped with liquid inlet and liquid outlet, and the inner wall surface of pump shell includes cooperation circumference surface and the annular sealing surface that is connected with the axial one end of cooperation circumference surface, and cooperation circumference surface extends along the periphery of liquid inlet, impeller subassembly, axial one end is equipped with liquid inlet cylinder section, and liquid inlet cylinder section is at least partially located in the region surrounded by cooperation circumference surface, and the outer periphery between cooperation circumference surface and liquid inlet cylinder section is equipped with floating mouth ring, and floating mouth ring can axially float to abut and seal with annular sealing surface under the state that impeller subassembly rotates, and the inner diameter of cooperation circumference surface is M, and the outer diameter of liquid inlet cylinder section is N, and the outer diameter of floating mouth ring is P and the inner diameter is L, and M-P is greater than L-N. The hydraulic efficiency of the electronic water pump according to the utility model embodiment is improved obviously, and the required motor efficiency is lower to reduce the volume and weight of motor, realizes light weight and reduces cost, and the floating mouth ring structure is simple, and the part quantity is few and easy to assemble.

Description

Technical Field

[0001] This utility model relates to the field of water pump technology, and more specifically, to an electronic water pump, a thermal management system, and a vehicle. Background Technology

[0002] In related technologies, the impeller of an electronic water pump is located inside the pump casing and is used to drive the water flow within the casing. However, the assembly gap between the impeller and the pump casing results in significant hydraulic losses, leading to low pump efficiency. Utility Model Content

[0003] The present invention aims to at least solve one of the technical problems existing in the prior art. Therefore, one object of the present invention is to provide an electronic water pump that improves hydraulic efficiency.

[0004] This utility model also proposes a thermal management system having the above-mentioned electronic water pump.

[0005] This utility model also proposes a vehicle having the above-mentioned thermal management system.

[0006] An electronic water pump according to an embodiment of the present invention includes: a pump housing, wherein the pump housing has an inlet and an outlet, the inner wall surface of the pump housing includes an annular sealing surface and a mating circumferential surface, the annular sealing surface is connected to one axial end of the mating circumferential surface, and the annular sealing surface and the mating circumferential surface extend circumferentially along the inlet; an impeller assembly, the impeller assembly is rotatably disposed within the pump housing, and one axial end of the impeller assembly has an inlet cylinder section, the inlet cylinder section being at least partially located within the area enclosed by the mating circumferential surface; and a floating port ring, the floating port ring being disposed between the mating circumferential surface and the outer circumferential surface of the inlet cylinder section, wherein the floating port ring is axially floating to abut against and seal with the annular sealing surface when the impeller assembly is rotating, the inner diameter of the mating circumferential surface is M, the outer diameter of the inlet cylinder section is N, the outer diameter of the floating port ring is P and the inner diameter is L, MP is greater than LN.

[0007] According to the embodiment of the present invention, the electronic water pump is axially movable between the mating circumferential surface of the pump casing and the liquid inlet section of the impeller assembly via a floating port ring. This allows the floating port ring to abut against the annular sealing surface and seal during the working state of the impeller assembly. A small gap fit is formed between the floating port ring and the liquid inlet section, achieving effective sealing. This greatly improves the volumetric efficiency of the electronic water pump, significantly increases the overall hydraulic efficiency of the pump, and requires a lower motor efficiency to reduce the size and weight of the motor, achieving lightweighting and reducing motor costs. Furthermore, the floating port ring has advantages such as simple structure, few parts, and easy assembly.

[0008] In addition, the electronic water pump according to the above embodiments of this utility model may also have the following additional technical features:

[0009] According to some embodiments of the present invention, LN is greater than or equal to 0.2 mm and less than or equal to 0.4 mm; and / or, MP is greater than or equal to 0.6 mm and less than or equal to 1 mm.

[0010] According to some embodiments of this utility model, when the floating port ring is in contact with the annular sealing surface, the axial distance between the end face of the floating port ring away from the liquid inlet and the end face of the liquid inlet cylinder section near the liquid inlet is J, where J is greater than or equal to 0.1L and less than or equal to 0.2L.

[0011] According to some embodiments of the present invention, the distance between the inner and outer circumferential surfaces of the floating ring is G, where G is greater than or equal to 1.5 mm and less than or equal to 4 mm.

[0012] According to some embodiments of the present invention, the floating port ring has a boss on its axial end face facing away from the annular sealing surface. The boss extends circumferentially along the floating port ring, and the distance between the boss and the outer circumferential surface of the floating port ring is less than the distance between the boss and the inner circumferential surface of the floating port ring.

[0013] According to some embodiments of this utility model, the axial height of the boss is H, where H is greater than or equal to 0.3 mm and less than or equal to 1 mm.

[0014] According to some embodiments of the present invention, the distance between the inner and outer circumferential surfaces of the floating ring is G, and the radial width of the boss is K, where K is greater than or equal to 0.2G and less than or equal to 0.3G.

[0015] According to some embodiments of the present invention, the outer peripheral surface of the liquid inlet cylinder section is provided with a support protrusion. When the impeller assembly stops rotating, the floating port ring is supported on the support protrusion and spaced apart from the annular sealing surface. The support area of ​​the support protrusion is smaller than the end face area of ​​the floating port ring at the end away from the liquid inlet.

[0016] According to some embodiments of the present invention, there are multiple supporting protrusions, and the multiple supporting protrusions are spaced apart along the circumference of the liquid inlet cylinder section.

[0017] According to some embodiments of the present invention, the axial height of the supporting protrusion is F, and the axial height of the boss is H, where FH is greater than or equal to 0.6 mm and less than or equal to 1 mm.

[0018] According to some embodiments of this utility model, the dimension of the supporting protrusion along the circumferential direction of the liquid inlet cylinder section is Q, where Q is greater than or equal to 1 mm and less than or equal to 1.5 mm.

[0019] According to some embodiments of the present invention, the radial dimension of the supporting protrusion is R, where R-(LN) is greater than or equal to 0.1 mm and less than or equal to 0.3 mm.

[0020] According to some embodiments of the present invention, the impeller assembly includes a thrust fitting portion, and the electronic water pump further includes a thrust portion, which stops the thrust fitting portion on the side near the liquid inlet, wherein the thrust portion is disposed in the pump housing; or, the electronic water pump further includes a mounting shaft and a rotor assembly, the rotor assembly being rotatably mounted on the mounting shaft, the impeller assembly being connected to the rotor assembly, and the thrust portion being disposed on the mounting shaft.

[0021] The thermal management system according to an embodiment of the present invention includes an electronic water pump according to an embodiment of the present invention.

[0022] The vehicle according to an embodiment of the present invention includes a thermal management system according to an embodiment of the present invention.

[0023] Additional aspects and advantages of this invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

[0024] The above and / or additional aspects and advantages of this utility model will become apparent and readily understood from the description of the embodiments taken in conjunction with the following drawings, in which:

[0025] Figure 1 This is a partial structural schematic diagram of an electronic water pump according to an embodiment of the present utility model;

[0026] Figure 2 yes Figure 1 The illustrated embodiment is a cross-sectional view along line AA with the impeller assembly stopped rotating.

[0027] Figure 3 yes Figure 2 The enlarged structural diagram at point B is shown in the middle circle.

[0028] Figure 4 yes Figure 1 The illustrated embodiment is a cross-sectional view along line AA with the impeller assembly in a rotating state.

[0029] Figure 5 yes Figure 4 The enlarged structural diagram at point C is shown in the middle circle.

[0030] Figure 6 This is a schematic diagram of the structure of the floating mouth ring according to an embodiment of the present utility model;

[0031] Figure 7 yes Figure 6 A cross-sectional view along the direction indicated by line DD;

[0032] Figure 8 This is a schematic diagram of the impeller assembly according to an embodiment of the present utility model;

[0033] Figure 9 yes Figure 8 A magnified structural diagram of point E in the middle circle;

[0034] Figure 10 This is a structural schematic diagram of the impeller assembly and part of the rotor assembly according to an embodiment of the present utility model;

[0035] Figure 11 This is a schematic diagram of a vehicle according to an embodiment of the present utility model.

[0036] Figure label:

[0037] 100 electronic water pumps; 200 thermal management systems; 300 vehicles;

[0038] Pump casing 10; liquid inlet 101; pump chamber 102; annular sealing surface 11; mating circumferential surface 12;

[0039] Impeller assembly 20; Inlet cylinder section 21; Support protrusion 22; Thrust mating part 23;

[0040] Floating ring 30; Boss 31;

[0041] Thrust section 40; mounting shaft 50; rotor assembly 60. Detailed Implementation

[0042] The embodiments of this utility model are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain this utility model, and should not be construed as limiting this utility model.

[0043] In the description of this utility model, it should be understood that the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc., indicating the orientation or positional relationship are based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this utility model and simplifying the description, and are not intended to indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this utility model.

[0044] In the description of this utility model, "first feature" and "second feature" may include one or more of the features, "multiple" means two or more, "first feature above" or "below" the second feature may include the first and second features being in direct contact, or the first and second features being in contact through another feature between them, and "first feature above", "above" and "over" the second feature may include the first feature being directly above or diagonally above the second feature, or simply indicate that the first feature is at a higher horizontal level than the second feature.

[0045] An electric water pump consists of a pump casing and an impeller. The impeller is located inside the pump casing and is used to drive the water flow within the casing. However, to prevent the impeller's rotational efficiency from being affected by friction between the impeller and the pump casing, or due to the influence of machining precision, there is an assembly gap between the impeller and the pump casing.

[0046] In some related technologies, the lack of a sealing structure at the assembly gap causes fluid at the pump casing outlet to flow through the assembly gap to the inlet, resulting in significant hydraulic losses and low pump efficiency. Therefore, it is necessary to improve the efficiency of the motor to achieve higher overall pump efficiency, which leads to an increase in motor size, weight, and cost.

[0047] In other related technologies, sealing the gap between the pump casing and the impeller using a complex sealing structure not only introduces rotational resistance to the impeller but also results in high costs and difficult assembly.

[0048] Based on this, this application proposes an electronic water pump 100, which greatly improves the volumetric efficiency of the electronic water pump 100, significantly improves the overall hydraulic efficiency of the pump, and requires a lower motor efficiency to reduce the size and weight of the motor, achieve weight reduction, and reduce motor cost. In addition, the floating port ring 30 has the advantages of simple structure, few parts and easy assembly.

[0049] The electronic water pump 100 according to an embodiment of the present invention is described below with reference to the accompanying drawings.

[0050] Reference Figures 1-5 As shown, the electronic water pump 100 according to an embodiment of the present invention may include: a pump housing 10, an impeller assembly 20, and a floating port ring 30.

[0051] Specifically, the pump casing 10 is provided with an inlet 101 and an outlet, and the impeller assembly 20 is rotatably disposed inside the pump casing 10. Rotating the impeller assembly 20 inside the pump casing 10 can drive the flow of fluid (which can be, but is not limited to, water) inside the pump casing 10. The fluid can flow into the pump casing 10 through the inlet 101 and flow out of the pump casing 10 through the outlet, thereby realizing fluid pumping.

[0052] For example Figures 1-5As shown, the pump casing 10 has a pump chamber 102, with the inlet 101 located at one axial end of the impeller assembly 20 and the outlet located radially outward of the impeller assembly 20. When the impeller assembly 20 is rotating, the fluid pressure at the outlet is greater than the fluid pressure at the inlet 101, causing the fluid to flow from the outlet to the inlet 101 along the gap between the wall of the pump chamber 102 and the axial end wall of the impeller assembly 20.

[0053] In addition, continue to refer to Figures 1-7 As shown, the inner wall surface of the pump casing 10 includes an annular sealing surface 11 and a mating circumferential surface 12. The annular sealing surface 11 is connected to one axial end of the mating circumferential surface 12, and the annular sealing surface 11 and the mating circumferential surface 12 extend circumferentially along the inlet 101. An inlet cylinder section 21 is provided at one axial end of the impeller assembly 20, and the inlet cylinder section 21 is at least partially located within the area enclosed by the mating circumferential surface 12. A floating port ring 30 is disposed between the mating circumferential surface 12 and the outer circumferential surface of the inlet cylinder section 21. The floating port ring 30 is axially floating to abut against the annular sealing surface 11 for sealing while the impeller assembly 20 is rotating. The inner diameter of the mating circumferential surface 12 is M, the outer diameter of the inlet cylinder section 21 is N, the outer diameter of the floating port ring 30 is P, and the inner diameter is L, where MP is greater than LN.

[0054] Here, the mating circumferential surface 12 can extend along the axial direction of the impeller assembly 20, or it can form a certain angle with the axial direction of the impeller assembly 20; the annular sealing surface 11 can be perpendicular to the axial direction of the impeller assembly 20, or it can form a certain angle with the axial direction of the impeller assembly 20. It is only necessary that the mating circumferential surface 12 has two ends arranged along the axial direction and the annular sealing surface 11 has two sides arranged along the radial direction, so that the mating circumferential surface 12 can define the space for accommodating the liquid inlet cylinder section 21, and the annular sealing surface 11 can axially abut and seal with the floating port ring 30.

[0055] The inlet section 21 defines a channel for fluid to flow into the impeller assembly 20, and the inlet section 21 is at least partially located within the area enclosed by the mating circumferential surface 12, so that fluid flowing into the pump housing 10 from the inlet port 101 can flow into the impeller assembly 20 through the inlet section 21, so that the impeller assembly 20 can apply a pumping force to the fluid.

[0056] The floating inlet ring 30 is an annular structure that fits around the inlet cylinder section 21. The floating inlet ring 30 is movable along the axial direction of the impeller assembly 20, meaning that the connection between the floating inlet ring 30 and the pump housing 10, and between the floating inlet ring 30 and the inlet cylinder section 21, is not fixed. Therefore, the flow path connectivity can be altered depending on the axial position of the floating inlet ring 30. Specifically, when the floating inlet ring 30 is axially moved to a state of sealing against the annular sealing surface 11, the gap between the inner circumferential surface of the floating inlet ring 30 and the outer circumferential surface of the inlet cylinder section 21 connects the inlet port 101 and the outlet port; when the floating inlet ring 30 is axially moved to a state of separation from the annular sealing surface 11, the gap between the outer circumferential surface of the floating inlet ring 30 and the mating circumferential surface 12 connects the inlet port 101 and the outlet port.

[0057] Since the inner diameter of the mating circumferential surface 12 is M, the outer diameter of the liquid inlet section 21 is N, the outer diameter of the floating port ring 30 is P and the inner diameter is L, and MP is greater than LN, a small clearance fit can be formed between the inner circumferential surface of the floating port ring 30 and the outer circumferential surface of the liquid inlet section 21, and a large clearance fit can be formed between the outer circumferential surface of the floating port ring 30 and the mating circumferential surface 12.

[0058] Therefore, when the electric water pump 100 is not working, the impeller assembly 20 stops rotating, and the floating ring 30 can separate from the annular sealing surface 11 under the action of gravity and other forces. At this time, there is a large gap between the floating ring 30 and the pump casing 10, and a seal cannot be formed. When the electric water pump 100 is working, the impeller assembly 20 rotates, and the fluid inside the pump casing 10 flows from the inlet 101 to the outlet under the drive of the impeller assembly 20. This causes the pressure on the end face of the floating ring 30 axially close to the inlet 101 to be less than the pressure on the other end face axially, creating a pressure difference between the two end faces. This generates buoyancy towards the inlet 101, and the floating ring 30 moves closer to the inlet 101 under the action of the pressure difference, eventually abutting against the annular sealing surface 11 to seal. At this time, the gap between the floating ring 30 and the pump casing 10 is zero, and the small gap between the inner circumferential surface of the floating ring 30 and the outer circumferential surface of the inlet cylinder section 21 effectively prevents the fluid at the outlet from flowing towards the inlet 101, thereby greatly reducing hydraulic loss and achieving a sealing effect. Furthermore, given a certain hydraulic efficiency requirement, it is beneficial to reduce the efficiency of the motor (including rotor assembly 60 and stator assembly) of the required electronic water pump 100, thereby reducing the overall size, weight and cost of the electronic water pump 100.

[0059] Furthermore, the floating ring 30 has a simple structure, is smaller in size, and has higher machining precision compared to the pump casing 10. Therefore, by creating a larger gap between the mating circumferential surface 12 and the floating ring 30, the influence of machining and assembly errors of the pump casing 10 on the coaxiality of the impeller assembly 20 can be reduced. Rotational friction is less likely to occur between the pump casing 10 and the floating ring 30, and among the floating rings themselves, thus reducing resistance to the rotation of the impeller assembly 20. Moreover, the sealing structure formed by the floating ring 30 is simple in structure, has fewer parts, lower cost, and a simpler assembly process, reducing cost by 70% compared to sealing structures in related technologies.

[0060] According to the embodiment of the present invention, the electronic water pump 100 is axially movable between the mating circumferential surface 12 of the pump housing 10 and the liquid inlet section 21 of the impeller assembly 20, so that the floating ring 30 can abut against the annular sealing surface 11 and seal during the working state of the impeller assembly 20. A small gap fit is formed between the floating ring 30 and the liquid inlet section 21 to achieve effective sealing, which greatly improves the volumetric efficiency of the electronic water pump 100, significantly improves the hydraulic efficiency of the entire pump, and requires a lower motor efficiency to reduce the size and weight of the motor, achieve weight reduction, and reduce motor cost. In addition, the floating ring 30 has the advantages of simple structure, few parts, and easy assembly.

[0061] In some embodiments, such as Figure 2 and Figure 7 As shown, LN is greater than or equal to 0.2 mm and less than or equal to 0.4 mm. In other words, in a coaxial state, the gap between the inner circumferential surface of the floating port ring 30 and the outer circumferential surface of the inlet cylinder section 21 is 0.1 mm to 0.2 mm. Within the above range, this gap is small enough to effectively prevent fluid at the outlet from flowing through this gap to the inlet 101, essentially achieving a complete seal; furthermore, it can reduce the influence of machining errors on the floating port ring 30 and the inlet cylinder section 21, making it less prone to contact and friction between the floating port ring 30 and the inlet cylinder section 21, effectively reducing the resistance to rotation of the impeller assembly 20. For example, in some specific embodiments, LN can be 0.2 mm, 0.25 mm, 0.3 mm, 0.35 mm, and 0.4 mm, etc.

[0062] In some embodiments, such as Figure 2 and Figure 7As shown, MP is greater than or equal to 0.6 mm and less than or equal to 1 mm. In other words, in a coaxial state, the gap between the outer circumferential surface of the floating ring 30 and the mating circumferential surface 12 is 0.3 mm to 0.5 mm. Within this range, the gap is sufficiently large to effectively reduce the impact of machining errors in the floating ring 30 and pump housing 10, making it less prone to contact friction between the floating ring 30 and the inlet cylinder section 21, effectively reducing the resistance to the rotation of the impeller assembly 20. Furthermore, the gap is not too large, resulting in less fluid diversion to this gap, thereby increasing the fluid flow to the end face of the floating ring 30 facing away from the inlet 101, increasing the buoyancy of the floating ring 30, allowing it to move to contact the annular sealing surface 11 more promptly, and improving the sealing effect. For example, in some specific embodiments, MP can be 0.6 mm, 0.7 mm, 0.8 mm, 0.9 mm, and 1 mm, etc.

[0063] According to some embodiments of this utility model, such as Figure 4 , Figure 5 and Figure 7 As shown, when the floating ring 30 is in contact with the annular sealing surface 11, the axial distance between the end face of the floating ring 30 furthest from the liquid inlet 101 and the end face of the liquid inlet cylinder section 21 closest to the liquid inlet 101 is J, where J is greater than or equal to 0.1L and less than or equal to 0.2L. In other words, the sealing length of the floating ring 30 is J and 0.1L≤J≤0.2L.

[0064] The fluid flowing into the inlet 101 passes through the floating ring 30 and the inlet cylinder section 21 before entering the impeller assembly 20. Therefore, the larger the inner diameter L of the floating ring 30, the greater the inlet flow rate, and the greater the effective sealing length required between the floating ring 30 and the inlet cylinder section 21. If the sealing length of the floating ring 30 is too small, the sealing effect will be reduced. On the other hand, if the sealing length of the floating ring 30 is too large, the axial dimension of the floating ring 30 will be too long, making it difficult to control the cylindricity of the inner and outer circumferential surfaces of the floating ring 30, increasing the difficulty of processing, and easily causing friction between the floating ring 30 and the impeller assembly 20 due to processing errors.

[0065] Within the above range of values, the effective sealing length of the floating ring 30 is large enough, which improves the sealing effect. Furthermore, the manufacturing error of the floating ring 30 is smaller, making it less likely to rub against the impeller assembly 20 and affect the rotation of the impeller assembly 20.

[0066] In some embodiments of this utility model, such as Figure 7 As shown, the distance between the inner and outer circumferential surfaces of the floating ring 30 is G, which is greater than or equal to 1.5 mm and less than or equal to 4 mm. When the inner and outer circumferential surfaces of the floating ring 30 are arranged coaxially, 2G = PL, that is, the radial wall thickness of the floating ring 30 is G.

[0067] The greater the radial wall thickness of the floating ring 30, the larger the end face area of ​​the floating ring 30 away from the inlet 101 in the axial direction, the greater the buoyancy that can be generated when the fluid impacts the end face, and the greater the weight of the floating ring 30; however, the greater the weight of the floating ring 30, the greater the buoyancy required to drive the floating ring 30 to abut and seal with the annular sealing surface 11.

[0068] Within the aforementioned value range, the weight of the floating ring 30 itself and the buoyancy it experiences are balanced, allowing the floating ring 30 to smoothly abut against the annular sealing surface 11 under the buoyancy of the fluid, achieving a good sealing effect. In some specific embodiments, the distance G between the inner and outer circumferential surfaces of the floating ring 30 can be 1.5mm, 2mm, 2.5mm, 3mm, 3.5mm, and 4mm, etc.

[0069] According to some embodiments of this utility model, such as Figure 3 , Figure 5 and Figure 7 As shown, the floating ring 30 has a boss 31 on its axial end face facing away from the annular sealing surface 11. The boss 31 extends along the circumference of the floating ring 30, and the distance between the boss 31 and the outer circumferential surface of the floating ring 30 is less than the distance between the boss 31 and the inner circumferential surface of the floating ring 30.

[0070] The buoyancy of the floating ring 30 increases with the flow rate of the electric water pump 100, therefore, the buoyancy at low flow rates is crucial. The fluid flowing from the outlet to the inlet 101 impacts the end face of the floating ring 30 facing away from the annular sealing surface 11, generally impacting the middle of this end face in the inward and outward directions. Because the distance between the boss 31 and the outer circumferential surface of the floating ring 30 is smaller than the distance between the boss 31 and the inner circumferential surface of the floating ring 30, the boss 31 is generally located outside the point of fluid impact. After impacting the end face, the fluid flows radially and is blocked by the boss 31, thus forming a vortex at the corner between the boss 31 and the end face. The vortex increases the residence time of the fluid at the end face, thereby increasing the buoyancy effect on the floating ring 30.

[0071] Furthermore, simulations and tests revealed that for an electronic water pump 100 operating at 2350 rpm and a flow rate of 5.5 L / min, in the embodiment without the boss 31, the pressure difference (i.e., buoyancy) between the two end faces of the floating ring 30 was 5 g. In the embodiment with the boss 31, a significant vortex was formed inside the boss 31, and the pressure difference between the two end faces of the floating ring 30 was 8.8 g. This indicates that providing the boss 31 on the end face of the floating ring 30 facing away from the annular sealing surface 11, forming a stepped structure, can obtain greater buoyancy, enabling the floating ring 30 to float smoothly under low flow conditions of the electronic water pump 100.

[0072] In some specific embodiments, the boss 31 can extend along the circumference of the floating ring 30 into a closed ring or an arc with a notch. The closed ring-shaped boss 31 is more conducive to the formation of eddies and improves buoyancy. In some specific embodiments, the distance between the boss 31 and the outer circumferential surface of the floating ring 30 is zero, further enhancing the formation of eddies and improving buoyancy.

[0073] In some embodiments, such as Figure 5 As shown, the distance between the inner and outer circumferential surfaces of the floating ring 30 is G, and the radial width of the boss 31 is K, where K is greater than or equal to 0.2G and less than or equal to 0.3G.

[0074] If the radial width of the boss 31 is too small, it will result in low strength and difficulty in processing; if the radial width of the boss 31 is too large, it will not only increase the end face blocking area of ​​the floating ring 30 away from the liquid inlet 101, reducing the buoyancy force area of ​​the floating ring 30, but also make it easy for the fluid to directly impact the boss 31, affecting the formation of eddies.

[0075] Within the aforementioned value range, the vortex formation effect on the inner side of the boss 31 is better, the water-blocking effect is better, the buoyancy of the floating ring 30 is better, and the boss 31 has high strength and is not easy to break. For example, in some specific embodiments, the radial dimension of the boss 31 can be 0.2G, 0.22G, 0.25G, 0.28G, and 0.3G, etc.

[0076] In some embodiments, such as Figure 5 As shown, the axial height of the boss 31 is H, which is greater than or equal to 0.3 mm and less than or equal to 1 mm. If the axial height of the boss 31 is too small, it will affect the formation of eddies; if the axial height of the boss 31 is too large, it will reduce the strength of the boss 31, making it prone to breakage and difficult to process. Within the above-mentioned range, the boss 31 is less likely to break and can effectively form eddies to increase buoyancy. For example, in some specific embodiments, the axial height H of the boss 31 can be 0.3 mm, 0.5 mm, 0.7 mm, 0.9 mm, and 1 mm, etc.

[0077] In some embodiments of this utility model, such as Figures 8-10 As shown, the outer circumferential surface of the liquid inlet section 21 is provided with a support protrusion 22. For example... Figure 2 and Figure 3 As shown, when the impeller assembly 20 stops rotating, the floating port ring 30 is supported on the support protrusion 22 and spaced apart from the annular sealing surface 11. The support area of ​​the support protrusion 22 is smaller than the end face area of ​​the floating port ring 30 at the end away from the liquid inlet 101.

[0078] When the impeller assembly 20 first starts rotating, the larger the contact area between the end face of the floating ring 30 furthest from the inlet 101 and the fluid, the better it is for improving the buoyancy of the floating ring 30. By supporting the floating ring 30 with the support protrusion 22, the obstruction of the force-bearing surface of the floating ring 30 facing away from the inlet 101 by the impeller assembly 20 can be minimized. This makes the contact areas between the two ends of the floating ring 30 and the fluid more similar, resulting in a better effect on improving the buoyancy of the floating ring 30. Furthermore, the support protrusion 22 can also provide support and positioning for the floating ring 30.

[0079] In some embodiments, continue to refer to Figures 8-10 Multiple support protrusions 22 are provided, and these protrusions are spaced apart circumferentially along the inlet cylinder section 21. By providing multiple support protrusions 22, the floating ring 30 can be evenly supported circumferentially, improving its stability and coaxiality with the impeller assembly 20. This allows the floating ring 30 to float more smoothly relative to the impeller assembly 20, reducing the likelihood of jamming. Furthermore, this design allows for a smaller support area for each protrusion 22, increasing the force-bearing area of ​​the floating ring 30 and further enhancing its buoyancy. This enables the floating ring 30 to float smoothly even under low-flow conditions of the electronic water pump 100.

[0080] In some embodiments, such as Figure 5 As shown, the axial height of the supporting protrusion 22 is F, and the axial height of the boss 31 is H, where FH is greater than or equal to 0.6 mm and less than or equal to 1 mm.

[0081] Thus, the supporting protrusion 22 and the boss 31 form a height difference in the axial direction, with the supporting protrusion 22 being higher than the boss 31. When the impeller assembly 20 is not rotating and the floating port ring 30 is supported by the supporting protrusion 22, a sufficiently large gap can be formed between the boss 31 and the impeller assembly 20, allowing fluid to flow through this gap to the inside of the boss 31 and impact the end face of the floating port ring 30 facing away from the inlet 101, which is beneficial for the formation of vortices. Furthermore, an excessively large height difference would result in an excessively large overall axial dimension of the inlet cylinder section 21, occupying space and increasing weight and cost.

[0082] Within the above-mentioned value range, the eddy current generation effect is good, and the space occupied by each component is small, resulting in lower cost. In some specific embodiments, FH can be 0.6mm, 0.7mm, 0.8mm, 0.9mm, and 1mm, etc.

[0083] In some embodiments, such as Figure 10 As shown, the dimension of the support protrusion 22 along the circumference of the liquid inlet cylinder section 21 is Q, where Q is greater than or equal to 1 mm and less than or equal to 1.5 mm.

[0084] If the circumferential dimension of the support protrusion 22 along the liquid inlet section 21 is too large, it will be difficult to increase the contact area between the end face of the floating port ring 30 facing away from the liquid inlet 101 and the fluid; if the circumferential dimension of the support protrusion 22 along the liquid inlet section 21 is too small, it will reduce the support stability and support strength of the floating port ring 30.

[0085] Within the aforementioned value range, the supporting protrusion 22 balances the stability of supporting the floating inlet ring 30 with maximizing the buoyancy of the floating inlet ring 30. In some specific embodiments, the circumferential dimension Q of the supporting protrusion 22 along the liquid inlet cylinder section 21 can be 1mm, 1.1mm, 1.2mm, 1.3mm, 1.4mm, and 1.5mm, etc.

[0086] In some embodiments, such as Figures 2-3 and Figure 7 As shown, the radial dimension of the support protrusion 22 is R, where R-(LN) is greater than or equal to 0.1 mm and less than or equal to 0.3 mm.

[0087] Because a small gap exists between the inner circumferential surface of the floating port ring 30 and the outer circumferential surface of the liquid inlet section 21, the floating port ring 30 can be radially offset relative to the liquid inlet section 21. If R-(LN) is too small, the radial support dimension of the support protrusion 22 will be too small. Due to factors such as machining errors, when the radial offset of the floating port ring 30 relative to the liquid inlet section 21 is large, the support protrusion 22 is prone to getting stuck in the floating port ring 30, affecting the support and the floating of the floating port ring 30. If the radial support dimension of the support protrusion 22 is too large, it will affect the contact area between the end face of the floating port ring 30 facing away from the liquid inlet 101 and the fluid.

[0088] Within the aforementioned value range, the supporting protrusion 22 provides good support for the floating ring 30, preventing the floating ring 30 from easily getting stuck. Furthermore, it maximizes the buoyancy of the floating ring 30, allowing it to float smoothly even under low-flow conditions of the electronic water pump 100. In some specific embodiments, R-(LN) can be 0.1mm, 0.15mm, 0.2mm, 0.25mm, and 0.3mm, etc.

[0089] According to some embodiments of this utility model, such as Figure 2 and Figure 4As shown, the impeller assembly 20 includes a thrust fitting 23, and the electronic water pump 100 also includes a thrust part 40, which stops the thrust fitting 23 on the side near the inlet 101. During the rotation of the impeller assembly 20, the axial positioning effect of the thrust part 40 on the thrust fitting 23 prevents the impeller assembly 20 from moving towards the inlet 101. As a result, a certain gap can be formed between the impeller assembly 20 and the end face of the floating ring 30 away from the inlet 101. This reduces the resistance to the rotation of the impeller assembly 20 and increases the area of ​​the floating ring 30 that bears the buoyancy from the fluid, resulting in a better sealing effect between the floating ring 30 and the annular sealing surface 11.

[0090] Here, the specific structure of the thrust portion 40 and the thrust mating portion 23 can be flexibly set according to the actual situation. For example, in some embodiments, the thrust portion 40 is provided on the pump housing 10, so that the thrust portion 40 and the housing can be integrally machined to reduce assembly steps.

[0091] In other embodiments, such as Figure 2 and Figure 4 As shown, the electric water pump 100 also includes a mounting shaft 50 and a rotor assembly 60. The rotor assembly 60 is rotatably mounted on the mounting shaft 50, the impeller assembly 20 is connected to the rotor assembly 60, and a thrust portion 40 is provided on the mounting shaft 50. For example, the electric water pump 100 may include a housing, the mounting shaft 50 is fixedly connected to the housing, the rotor assembly 60 is located inside the housing and mounted on the mounting shaft 50, and a pump housing 10 is provided on one end of the housing to define the pump chamber 102.

[0092] The thrust portion 40 is located on the mounting shaft 50, which not only enables reliable positioning of the rotor assembly 60 but also does not occupy space within the pump casing 10, thus improving the pumping efficiency of the fluid. For example, the thrust portion 40 can be a fastener mounted on the mounting shaft 50, or it can be integrally formed with the mounting shaft 50.

[0093] like Figure 11As shown, the thermal management system 200 according to an embodiment of the present invention includes an electronic water pump 100 according to an embodiment of the present invention. Since the electronic water pump 100 according to an embodiment of the present invention has the aforementioned beneficial technical effects, the thermal management system 200 according to an embodiment of the present invention, by means of a floating ring 30 axially movable between the mating circumferential surface 12 of the pump housing 10 and the liquid inlet section 21 of the impeller assembly 20, allows the floating ring 30 to abut against and seal with the annular sealing surface 11 during the working state of the impeller assembly 20. A small clearance fit is formed between the floating ring 30 and the liquid inlet section 21, achieving effective sealing, greatly improving the volumetric efficiency of the electronic water pump 100, significantly improving the overall pump hydraulic efficiency, and requiring a lower motor efficiency to reduce the size and weight of the motor, achieving lightweighting and reducing motor costs. Furthermore, the floating ring 30 has advantages such as simple structure, few parts, and easy assembly.

[0094] The thermal management system 200 can be used to regulate the automotive cabin environment (temperature, humidity, etc.) and the working environment of other components. In some embodiments, the thermal management system 200 mainly includes: valves, heat exchangers, compressors, and pumps, such as an electric water pump 100 or other water pumps. The thermal management system 200 has a circulating working medium, which can be carbon dioxide refrigerant, etc.

[0095] like Figure 11 As shown, the vehicle 300 according to an embodiment of the present invention includes a thermal management system 200 according to an embodiment of the present invention. Since the thermal management system 200 according to an embodiment of the present invention has the aforementioned beneficial technical effects, the vehicle 300 according to an embodiment of the present invention, by means of a floating ring 30 axially movable between the mating circumferential surface 12 of the pump housing 10 and the liquid inlet section 21 of the impeller assembly 20, allows the floating ring 30 to abut against and seal the annular sealing surface 11 during the working state of the impeller assembly 20. A small clearance fit is formed between the floating ring 30 and the liquid inlet section 21, achieving effective sealing, greatly improving the volumetric efficiency of the electronic water pump 100, significantly improving the overall pump hydraulic efficiency, and requiring a lower motor efficiency to reduce the motor's size and weight, achieving lightweighting and reducing motor costs. Furthermore, the floating ring 30 has advantages such as simple structure, few parts, and easy assembly.

[0096] In this embodiment, vehicle 300 can be a new energy vehicle. In some embodiments, the new energy vehicle can be a pure electric vehicle with an electric motor as the main driving force. In other embodiments, the new energy vehicle can also be a hybrid vehicle with both an internal combustion engine and an electric motor as the main driving force. Regarding the internal combustion engine and electric motor mentioned in the above embodiments that provide driving power for the new energy vehicle, the internal combustion engine can use gasoline, diesel, hydrogen, etc. as fuel, and the way to provide electrical energy to the electric motor can be a power battery, hydrogen fuel cell, etc., without special limitations. It should be noted that this is merely an exemplary description of the structure of new energy vehicles, etc., and is not intended to limit the scope of protection of this utility model.

[0097] The following describes in detail an electronic water pump 100 according to a specific embodiment of the present invention with reference to the accompanying drawings. It is to be understood that the following description is merely illustrative and should not be construed as limiting the present invention.

[0098] like Figures 1-10 As shown, the electronic water pump 100 includes a housing, a pump housing 10, a rotor assembly 60, an impeller assembly 20, a floating port ring 30, a thrust portion 40, and a mounting shaft 50.

[0099] The housing defines a mounting cavity for accommodating the rotor assembly 60. The pump housing 10 covers one end opening of the mounting cavity and defines a pump chamber 102. The mounting shaft 50 is fixed to the housing, and the rotor assembly 60 is located within the mounting cavity and rotatably mounted on the mounting shaft 50. The impeller assembly 20 is located within the pump chamber 102 and is fixedly connected to the rotor assembly 60.

[0100] The pump casing 10 has an inlet 101 located at one axial end of the impeller assembly 20 and an outlet located radially outward of the impeller assembly 20. The inlet 101 is directly opposite to and communicates with the inlet cylinder section 21 of the impeller assembly 20. The thrust portion 40 is mounted on the mounting shaft 50 and stops the thrust fitting portion 23 of the impeller assembly 20 on the side near the inlet 101 to limit the axial movement of the impeller assembly 20.

[0101] The inner wall of the pump casing 10 has a mating circumferential surface 12 extending around the inlet cylinder section 21 and an annular sealing surface 11 extending axially perpendicular to the rotor assembly 60. The annular sealing surface 11 is located on the side of the mating circumferential surface 12 near the inlet port 101 and is connected to one axial end of the mating circumferential surface 12. A floating port ring 30 is axially movable between the mating circumferential surface 12 and the inlet cylinder section 21. The inner circumferential surface of the floating port ring 30 and the outer circumferential surface of the inlet cylinder section 21 are fitted with a small clearance.

[0102] When the electric water pump 100 is not working, such as Figure 2 and Figure 3As shown, the floating ring 30, under the influence of gravity, is located at the bottom, i.e., in contact with the support protrusion 22 on the impeller assembly 20. At this time, the axial gap between the floating ring 30 and the pump casing 10 still exists, and a seal cannot be formed. After the electric water pump 100 starts running, the fluid entering the pump chamber 102 will exert a force on the upper end face (the end face near the inlet 101) and the lower end face (the end face away from the inlet 101) of the floating ring 30. Since the pressure on the lower end face of the floating ring 30 is greater than the pressure on the upper end face, a pressure difference is formed between the upper and lower end faces, thereby generating an upward force. The floating ring 30 moves upward under the action of pressure, and finally the upper end face of the floating ring 30 abuts against the annular sealing surface 11, as shown. Figure 4 and Figure 5 As shown, the axial clearance between the floating inlet ring 30 and the pump casing 10 is now zero, and the clearance between the floating inlet ring 30 and the inlet cylinder section 21 is small, greatly reducing hydraulic loss and achieving a sealing effect. Furthermore, the impeller assembly 20 will not move upwards due to the axial positioning of the thrust portion 40.

[0103] Furthermore, the lower end face of the floating ring 30 adopts a stepped structure, i.e., a boss 31 is provided, which can obtain greater buoyancy. Four spaced-apart support protrusions 22 are provided on the impeller assembly 20 to support the floating ring 30, ensuring both axial positioning of the floating ring 30 and a large exposed area of ​​the lower end face of the floating ring 30. Making the exposed areas of the upper and lower end faces of the floating ring 30 as close as possible also contributes to obtaining greater buoyancy. Thus, the floating ring 30 can still float under the low flow conditions of the electric water pump 100.

[0104] Simulations and tests were conducted on the embodiment using the floating ring 30 and the comparative embodiment without the floating ring 30. The hydraulic performance test results are shown in Table 1.

[0105] Table 1

[0106]

[0107] As shown in Table 1, this embodiment can improve the hydraulic efficiency of the electronic water pump 100 by 3% to 5% by setting the floating ring 30. Furthermore, due to the significant increase in hydraulic efficiency, the motor of the electronic water pump 100 does not need to achieve a very high efficiency. Therefore, the size and weight of the motor can be reduced, achieving weight reduction and lower motor costs. For example, for a 150W electronic water pump 100, the overall pump weight can be reduced by 30g to 50g. Moreover, the floating ring 30 has advantages such as simple structure, fewer parts required for the sealing structure, and low cost.

[0108] Other configurations and operations of the electronic water pump 100, thermal management system 200, and vehicle 300 according to embodiments of the present invention are known to those skilled in the art and will not be described in detail here.

[0109] In the description of this utility model, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "joining" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this utility model based on the specific circumstances.

[0110] In the description of this specification, the references to terms such as "embodiment," "specific embodiment," and "example" indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0111] Although embodiments of the present invention have been shown and described, those skilled in the art will understand that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of the present invention, the scope of which is defined by the claims and their equivalents.

Claims

1. An electronic water pump, characterized in that, include: The pump housing has an inlet and an outlet. The inner wall of the pump housing includes an annular sealing surface and a mating circumferential surface. The annular sealing surface is connected to one axial end of the mating circumferential surface, and the annular sealing surface and the mating circumferential surface extend circumferentially along the inlet. An impeller assembly is rotatably disposed within the pump casing, and one axial end of the impeller assembly is provided with a liquid inlet section, the liquid inlet section being at least partially located within the area enclosed by the mating circumferential surface; A floating inlet ring is disposed between the mating circumferential surface and the outer circumferential surface of the liquid inlet cylinder section, wherein... The floating port ring can float axially to abut against and seal with the annular sealing surface while the impeller assembly is rotating. The inner diameter of the mating circumferential surface is M, the outer diameter of the liquid inlet section is N, the outer diameter of the floating port ring is P and the inner diameter is L, and MP is greater than LN.

2. The electronic water pump according to claim 1, characterized in that, LN is greater than or equal to 0.2 mm and less than or equal to 0.4 mm; and / or, MP is greater than or equal to 0.6 mm and less than or equal to 1 mm.

3. The electronic water pump according to claim 1, characterized in that, When the floating port ring is in contact with the annular sealing surface, the axial distance between the end face of the floating port ring away from the liquid inlet and the end face of the liquid inlet cylinder section near the liquid inlet is J, where J is greater than or equal to 0.1L and less than or equal to 0.2L.

4. The electronic water pump according to claim 1, characterized in that, The distance between the inner and outer circumferential surfaces of the floating ring is G, where G is greater than or equal to 1.5 mm and less than or equal to 4 mm.

5. The electronic water pump according to any one of claims 1-4, characterized in that, The floating ring has a boss on its axial end face facing away from the annular sealing surface. The boss extends circumferentially along the floating ring, and the distance between the boss and the outer circumferential surface of the floating ring is less than the distance between the boss and the inner circumferential surface of the floating ring.

6. The electronic water pump according to claim 5, characterized in that, The axial height of the boss is H, which is greater than or equal to 0.3 mm and less than or equal to 1 mm.

7. The electronic water pump according to claim 5, characterized in that, The distance between the inner and outer circumferential surfaces of the floating ring is G, and the radial width of the boss is K, where K is greater than or equal to 0.2G and less than or equal to 0.3G.

8. The electronic water pump according to claim 5, characterized in that, The outer circumferential surface of the liquid inlet section is provided with a support protrusion. When the impeller assembly stops rotating, the floating port ring is supported on the support protrusion and spaced apart from the annular sealing surface. The support area of ​​the support protrusion is smaller than the end face area of ​​the floating port ring at the end away from the liquid inlet.

9. The electronic water pump according to claim 8, characterized in that, There are multiple supporting protrusions, and the multiple supporting protrusions are spaced apart circumferentially along the liquid inlet cylinder section.

10. The electronic water pump according to claim 8, characterized in that, The axial height of the supporting protrusion is F, and the axial height of the boss is H, where FH is greater than or equal to 0.6 mm and less than or equal to 1 mm.

11. The electronic water pump according to claim 8, characterized in that, The dimension of the support protrusion along the circumferential direction of the liquid inlet cylinder section is Q, where Q is greater than or equal to 1 mm and less than or equal to 1.5 mm.

12. The electronic water pump according to claim 8, characterized in that, The radial dimension of the support protrusion is R, where R-(LN) is greater than or equal to 0.1 mm and less than or equal to 0.3 mm.

13. The electronic water pump according to any one of claims 1-4, characterized in that, The impeller assembly includes a thrust fitting, and the electronic water pump further includes a thrust member, which stops against the side of the thrust fitting near the liquid inlet. The thrust stop is located in the pump housing; or... The electronic water pump also includes a mounting shaft and a rotor assembly, the rotor assembly being rotatably mounted on the mounting shaft, the impeller assembly being connected to the rotor assembly, and the thrust portion being disposed on the mounting shaft.

14. A thermal management system, characterized in that, Including the electronic water pump according to any one of claims 1-13.

15. A vehicle, characterized in that, Includes the thermal management system according to claim 14.

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