Electric pump

Abstract

The invention provides an electric pump which comprises an impeller assembly, the impeller assembly comprises a plurality of first twisted blades, an upper plate and a lower plate, at least part of the first twisted blades are located between the upper plate and the lower plate, the first twisted blades are distributed in the circumferential direction of the lower plate in an array mode, and each first twisted blade comprises a first head and a first tail. The first head part is close to the central part of the impeller assembly relative to the first tail part, a curve connecting the first twisted blade and the upper plate is defined as a long upper edge curve, a curve connecting the first twisted blade and the lower plate is defined as a long lower edge curve, an intersection point of the long upper edge curve and the first head part is defined as a first point, and an intersection point of the long lower edge curve and the first head part is defined as a second point; the first point is located on the first circumference, the second point is located on the second circumference, the ratio of the diameter of the first circumference to the diameter of the second circumference 103 is 1.3-1.7, and the ratio of the placement angle of the first point to the placement angle of the second point is 1.2-1.6. In this way, the impeller inlet area can be increased, the impeller inlet flow speed can be reduced, and local cavitation of the impeller inlet can be reduced.

Description

Technical Field

[0001] This application relates to the field of thermal management technology, and more particularly to an electric pump for automotive, energy storage, or commercial use. Background Technology

[0002] As a crucial power component within the automotive thermal management system, the electric pump faces increasingly stringent cooling requirements due to the advancement of electric vehicle technology. This places higher demands on the hydraulic efficiency of electric pumps. Electric pumps include impeller assemblies, and to improve hydraulic efficiency, the impeller blades are typically designed with three-dimensional curved surfaces, also known as twisted blades. Currently, localized cavitation exists at the impeller inlet. Summary of the Invention

[0003] The purpose of this invention is to provide an electric pump that helps reduce local cavitation at the impeller inlet.

[0004] To achieve the above objectives, one technical solution of this application is as follows: an electric pump, the electric pump including an impeller assembly, the impeller assembly including a plurality of first twisted blades, an upper plate and a lower plate, at least some of the first twisted blades being located between the upper plate and the lower plate, the plurality of first twisted blades being distributed in a circumferential array along the lower plate, the first twisted blades including a first head and a first tail, the first head being closer to the center of the impeller assembly than the first tail, the curve connecting the first twisted blade to the upper plate being defined as a long upper edge curve, the curve connecting the first twisted blade to the lower plate being defined as a long lower edge curve, the intersection of the long upper edge curve and the first head being a first point, the intersection of the long lower edge curve and the first head being a second point, the first point being located on a first circumference, the second point being located on a second circumference, the ratio of the diameter of the first circumference to the diameter of the second circumference being 1.3 to 1.7, and the ratio of the placement angle of the first point to the placement angle of the second point being 1.2 to 1.6.

[0005] In one technical solution of this application, the ratio of the diameter of the first circumference to the diameter of the second circumference is 1.3 to 1.7, and the ratio of the placement angle of the first point to the placement angle of the second point is 1.2 to 1.6. Regarding the degree of twisting of the multiple first twisted blades, it can be understood that optimizing the design of the first circumference where the first point is located, the second circumference where the second point is located, the placement angle of the second point, and the placement angle of the second point is beneficial to increasing the area at the beginning of the impeller fluid channel, which can be understood as the impeller inlet area. This is beneficial to reducing the flow velocity of the working medium at the beginning of the impeller fluid channel, thereby reducing local cavitation at the impeller inlet. Attached Figure Description

[0006] Figure 1 This is a three-dimensional schematic diagram of the electric pump of this application.

[0007] Figure 2 yes Figure 1 A schematic diagram of the structure along section XX.

[0008] Figure 3 yes Figure 2 A cross-sectional view of the rotating component.

[0009] Figure 4 yes Figure 2 Schematic diagram of the exploded structure of the rotating component.

[0010] Figure 5 yes Figure 2 The first part is a three-dimensional diagram in one direction.

[0011] Figure 6 yes Figure 2 A three-dimensional diagram of the first part from another direction.

[0012] Figure 7 yes Figure 6 The first part of the structure is shown in frontal view along direction A.

[0013] Figure 8 yes Figure 5 Schematic diagram of the first part of the structure along the BB section.

[0014] Figure 9 yes Figure 2 The second part is a three-dimensional diagram in one direction.

[0015] Figure 10 yes Figure 9 A schematic diagram of the second part of the structure viewed from the front along the Y direction.

[0016] Figure 11 yes Figure 2 A schematic diagram of the projection structure of the first and second torsion blades onto the downward plate;

[0017] Figure 12 yes Figure 2 A three-dimensional structural diagram of the pump cover in one direction;

[0018] Figure 13 yes Figure 2 A schematic diagram of the structure of the volute flow channel and impeller assembly projected along the direction perpendicular to the axial direction of the electric pump;

[0019] Figure 14 yes Figure 13 Schematic diagram of the cross-sectional structure at point VIII.

[0020] illustrate:

[0021] 100. Electric pump; 11. Pump cover; 111. Inlet; 112. Outlet; 113. Tongue separator;

[0022] 12. Stator assembly; 121. Stator housing; 122. Stator winding;

[0023] 13. Inner cavity; 131. Rotor cavity; 132. Impeller cavity; 1321. Volute flow channel; 1321a. Inlet of volute flow channel; L1. Inlet width of volute flow channel; 1321b. Throat of volute flow channel; 14. Rotating assembly; 141. Rotor assembly; 1411. Rotor; 1412. First bearing; 1413. Second bearing; 1413a. End surface; 1413b. Outer peripheral surface; 1414. Outer peripheral surface;

[0024] 142. Impeller assembly; 142b. First protrusion; 142c. First groove; 142d. Second protrusion; 142e. Second groove; 1421. Upper plate; 1421a. Second hole; 1422. Lower plate; 1422a. Inner surface; 1422b. Outer surface; 1422e. Peripheral side; 1423. First twisted blade; 1423a. First head; 1423b. First tail; 1423c. Pressure surface; 1423d. Suction surface; 1423e. Top; 1423f. Root; 1423g. Long upper edge curve; 1423h. 1424. Long lower edge curve; 1425. Second twisted blade; 1426. Impeller inlet; 1427. Impeller fluid flow channel; 1424b. Second tail section; 1424a. Second head section; 1424c. Short upper edge curve; 1424d. Short lower edge curve; 1424e. Top of the second twisted blade; 1425. Impeller inlet; 1426. Impeller outlet; L2. Impeller outlet width; 142b1. Beginning of the first protrusion; 142b2. End of the first protrusion; 142d1. Beginning of the second protrusion; 142d2. End of the second protrusion;

[0025] 143. First component; 144. First part; 1441. First hole; 145. Second part; 19. Control panel assembly;

[0026] 102. First circumference; 103. Second circumference; A. First point; B. Second point; β1. Angle at which the first point is placed; β2. Angle at which the second point is placed; C. Third point; D. Fourth point; 104. Third circumference; 105. Fourth circumference; 106. Fifth circumference; 107. Sixth circumference. Detailed Implementation

[0027] The present invention will be further described below with reference to the accompanying drawings and specific technical solutions:

[0028] The electric pump in the following embodiments can provide flow power for the working medium of the automotive thermal management system. The working medium can be water or an aqueous solution, such as an aqueous solution containing 50% ethylene glycol, or other substances.

[0029] See Figures 1 to 14As shown, this application provides an electric pump 100, which includes a pump cover 11, a stator assembly 12, a rotating assembly 14, and a shaft. The stator assembly 12 includes a stator winding 122 and a stator housing 121. The stator winding 122 includes a stator core, an insulating frame, and windings. The pump cover 11 is sealed and fixedly connected to the stator assembly 12. It should be noted that the sealing and fixing here means that when the electric pump 100 is working, the working medium inside the electric pump 100 will not leak to the outside of the electric pump 100 through the joint surface between the pump cover 11 and the stator assembly 12. The shaft is fixedly connected to the stator assembly 12. Specifically, the shaft is injection molded and fixed to the stator housing 121. It can be understood that part of the shaft is embedded in the stator housing 121. The electric pump 100 has an inner cavity 13, and the rotating assembly 14 is located in the inner cavity 13. The inner cavity 13 includes a rotor cavity 131 and an impeller cavity 132. In a specific embodiment, the rotor cavity 131 and the impeller cavity 132 are connected. The inner cavity 13 allows the flow of a working medium. The rotating assembly 14 includes a rotor assembly 141 and an impeller assembly 142. The rotor assembly 141 includes a rotor 1411. At least a portion of the rotor assembly 141 is located in the rotor cavity 131, and the impeller assembly 142 is located in the impeller cavity 132. In one specific embodiment, the other end of the shaft is at least partially located in the rotor cavity 131, at least a portion of the rotating assembly 14 is sleeved on the outer periphery of the shaft, and a portion of the shaft is fixed to the stator housing 121. The rotating assembly 14 can rotate around the shaft. Of course, as another embodiment, the rotating assembly 14 and the shaft are fixedly connected, and the shaft rotates together with the rotating assembly 14. The electric pump 100 may also include a control board assembly 19, which is electrically connected to the stator assembly 12. As another embodiment, the electric pump 100 may not include the control board assembly 19, which is integrated into an external structure, thus facilitating the miniaturization design of the electric pump 100. In this embodiment, the electric pump 100 includes the control board assembly 19. The pump cover 11 has an inlet 111 and an outlet 112. The inlet 111 is for the working medium to flow into the electric pump 100, and the outlet 112 is for the working medium to flow out of the electric pump 100. When the electric pump 100 is working, it is connected to an external power source. By controlling the current in the stator winding 122, the excitation magnetic field generated by the stator winding 122 is controlled. Under the action of the excitation magnetic field, the rotating assembly 14 rotates around its axis, causing the working medium that enters the inner cavity 13 through the inlet 111 to rotate with the rotating assembly 14. The direction of movement of the working medium changes from the axial direction of the electric pump to the radial direction. Under the action of centrifugal force, the working medium leaves the electric pump 100 through the outlet 112. It should be noted that the axial direction of the electric pump 100 mentioned above and below refers to the direction in which the shaft of the electric pump extends, and the radial direction of the electric pump is the direction perpendicular to the axial direction of the electric pump.

[0030] As a crucial power component within the automotive thermal management system, the electric pump faces increasingly stringent heat dissipation requirements with the development of electric vehicle technology, placing higher demands on the pump's hydraulic efficiency. Electric pumps include impeller assemblies. To improve hydraulic efficiency, the impeller assembly is typically designed as a three-dimensional curved surface, or twisted blades. Multiple twisted blades, along with upper and lower plates, define the impeller fluid passage, which includes an impeller inlet and an outlet. The impeller inlet is located at one end of the fluid passage, and the outlet at the other, with the inlet closer to the center of the impeller than the outlet. Currently, localized cavitation exists at the impeller inlet. It should be noted that the long or short upper edge curves mentioned here and below refer to the curves formed by the connection between the suction or pressure surface of the twisted blade and the upper plate, and the long or short lower edge curves refer to the curves formed by the connection between the suction or pressure surface of the twisted blade and the lower plate. The blade angle is the angle between the tangent direction at a point on the twisted blade and the tangent direction of the circumference; it can be understood as the placement angle. It should be noted that in this application, since the suction surface and pressure surface are symmetrically distributed relative to the intermediate curved surface, the "intermediate curved surface" here refers to the curved surface between the suction surface and pressure surface relative to the thickness direction of the twisted blade. The "intermediate curved surface" is merely a virtual surface shown for descriptive purposes. The degree of twisting of the suction surface and pressure surface blades is approximately the same. Here, "approximately" means that within a certain range of manufacturing tolerances, variations in the degree of twisting of the suction surface and pressure surface blades are permissible. For ease of description, the long upper edge curve below represents the curve connecting the suction surface to the upper plate, and the long lower edge curve represents the curve connecting the suction surface to the lower plate.

[0031] As one implementation method, please refer to Figures 1 to 14 As shown, an electric pump 100 includes a rotating assembly 14, which includes an impeller assembly 142 and a rotor assembly 141. The rotor assembly 141 includes a rotor 1411. The impeller assembly 142 is formed by insert injection molding at least on the rotor 1411. The impeller assembly 142 includes a plurality of first twisted blades 1423, a plurality of second twisted blades 1424, an upper plate 1421, and a lower plate 1422. The first twisted blades 1423 and the lower plate 1422 are integral structural components, and the second twisted blades 1424 and the upper plate 1421 are integral structural components. The structure formed by the first twisted blades 1423 and the lower plate 1422 is defined as a first part 144, and the structure formed by the second twisted blades 1424 and the upper plate 1421 is defined as a second part 145. The first part 144 and the second part 145 are welded and fixed. In this way, the impeller assembly 142 can be assembled with only one welding, which improves the efficiency of the electric pump 100 and simplifies the manufacturing process of the electric pump 100.

[0032] For a specific implementation method, please refer to Figures 1 to 10As shown, the rotating assembly 14 includes a first bearing 1412 and a second bearing 1413. A first assembly 143 is formed by injection molding using the first bearing 1412 and the rotor 1411 as inserts. A first part 144 is formed by injection molding the first assembly 143 and the second bearing 1413. The first part 144 includes a first twisted blade 1423 and a lower plate 1422. The first twisted blade 1423 and the lower plate 1422 are injection molded and fixed, meaning they are essentially an integral structural component. The first part 144 also includes a rotor assembly 141. The rotor assembly 141, the first twisted blade 1423 of the impeller assembly 142, and the lower plate 1422 of the impeller assembly 142 are all integral structural components. This method of designing the rotor assembly 141, the first twisted blade 1423 of the impeller assembly 142, and the lower plate 1422 of the impeller assembly 142 as an integral structural component improves the structural strength of the rotating assembly 14. Specifically, the outer peripheral surface 1414 of the rotor assembly 141 extends along the axial direction of the electric pump 100 to the lower plate 1422. This simplifies the injection mold for forming the rotor assembly 141.

[0033] As a specific implementation method, please refer to Figures 1 to 8 As shown, the first part 144 includes a first hole 1441 extending from the inner surface 1422a to the outer surface 1422b in a direction parallel to the axial direction of the electric pump 100, and extending to the end surface 1413a of the second bearing 1413. It can be understood that the wall portion corresponding to the first hole 1441 includes the end surface 1413a of the second bearing 1413. The radial dimension of the first hole 1441 in the electric pump 100 is larger than the radial dimension of the outer peripheral surface 1413b of the second bearing 1413 in the electric pump. It can be understood that the diameter of the first hole 1441 is larger than the diameter of the outer peripheral surface 1413b of the second bearing 1413. The first twisted blade 1423 includes a first head 1423a, a first tail 1423b, a pressure surface 1423c, a suction surface 1423d, a top 1423e, and a root 1423f. The first head 1423a is near the impeller inlet 1425, the first tail 1423b is near the impeller outlet 1426, the root 1423f is injection molded to the lower plate 1422, and the top 1423e is welded to the upper plate 1421. Specifically, the suction surface is a concave curve, and the pressure surface is a convex curved surface.

[0034] The upper plate 1421 includes a second hole 1421a. The radial value of the second hole 1421a in the electric pump is greater than that of the first hole 1441 in the electric pump. The top 1423e of the first head 1423a extends to the wall corresponding to the second hole 1421a and fits against the wall corresponding to the second hole 1421a. This helps to prevent a reduction in the working medium entering the impeller flow channel 1427, thereby improving the hydraulic efficiency of the electric pump 100. A portion of the first head 1423a is located within the second hole 1421a, allowing the fluid entering the impeller assembly 142 to enter the impeller flow channel 1427 more smoothly, increasing the inlet area, reducing the fluid inlet velocity, preventing cavitation, and reducing vibration. Specifically, the first head 1423a is located in the second hole 1421a, and the top 1423e of the first head 1423a is in contact with the wall corresponding to the second hole 1421a, and the root 1423f of the first head 1423a extends to the wall corresponding to the second hole 1421a.

[0035] For a specific implementation method, please refer to Figures 1 to 14 As shown in the figure, in a specific embodiment, there are 4 first twisted blades and 4 second twisted blades. The 4 second twisted blades and 4 first twisted blades are staggered along the circumferential direction of the electric pump. The second twisted blades divide the impeller flow channel into two parts, which facilitates the processing and manufacturing of the first twisted blades and the second twisted blades. Figure 11 This is a schematic diagram showing the projection of the second twisted blade 1424 and the first twisted blade 1421 onto the plane containing the lower plate 1422.

[0036] As one implementation method, please refer to Figures 1 to 14As shown, an electric pump 100 includes an impeller assembly 142. The impeller assembly 142 includes a plurality of first twisted blades 1423, an upper plate 1421, and a lower plate 1422. At least a portion of the first twisted blades 1423 are located between the upper plate 1421 and the lower plate 1422. The plurality of first twisted blades 1423 are arranged in a circumferential array along the lower plate 1422. Each first twisted blade 1423 includes a first head 1423a and a first tail 1423b. The first head 1423a is closer to the center of the impeller assembly 1422 than the first tail 1423b, defining the first twisted blade. The curve connecting blade 1423 and upper plate 1421 is the long upper edge curve 1423g, and the curve connecting the first twisted blade 1423 and lower plate 1422 is the long lower edge curve 1423h. The intersection of the long upper edge curve 1423g and the first head 1423a is defined as the first point A, and the intersection of the long lower edge curve 1423h and the first head 1423a is defined as the second point B. The first point A is located on the first circumference 102, and specifically, the second point B is located on the second circumference 103. Both the first circumference 102 and the second circumference 103 are concentric with the circumference of the circumferential side surface 1422e of the lower plate 1422. The ratio of the diameters of the first circumference 102 to the second circumference 103 is 1.3 to 1.7, and the ratio of the placement angle β1 of the first point A to the placement angle β1 of the second point B is 1.2 to 1.6. In this way, firstly, the working medium enters the electric pump along the axial direction and then flows out along the radial direction. As the working medium transitions from the axial to the radial direction, the first head facilitates flow guidance. Optimizing the torsion of at least the first head—that is, optimizing the first circumference where the first point is located, the second circumference where the second point is located, the placement angle of the second point, and the placement angle of the second point—increases the area at the beginning of the impeller fluid passage, which is equivalent to the impeller inlet area. This helps reduce the flow velocity of the working medium at the beginning of the impeller fluid passage, thereby reducing localized cavitation at the impeller inlet. Secondly, this method, while reducing cavitation, also helps reduce vibration and pump noise. In this embodiment, only the blade angle at the intersection of the long upper edge curve 1423g and the first tail 1423b is the same as the blade angle at the intersection of the long lower edge curve 1423g and the first tail 1423b. Except for these two points, the blade angles of the other long upper and lower edge curves are different. This is beneficial for the manufacturing and processing of the impeller assembly. In this embodiment, the placement angle β1 of the first point A is 35° to 45°, and the diameter of the first circumference 102 ranges from 16mm to 20mm. This further reduces cavitation at the impeller inlet.

[0037] As one implementation method, please refer to Figures 1 to 14As shown, the impeller assembly 142 includes a plurality of second twisted blades 1424, at least some of which are located between the upper plate 1421 and the lower plate 1422. The plurality of second twisted blades 1424 are distributed in a circumferential array along the upper plate 1421. The number of first twisted blades 1423 and second twisted blades 1424 is equal. Specifically, the degree of twist of the first twisted blades 1423 and the second twisted blades 1424 is the same. It can be understood that, for the same circumferential diameter, the first twisted blades 1423 and the second twisted blades 1424 have the same placement angle. This is beneficial for increasing the area of ​​the impeller fluid passage, reducing cavitation within the impeller fluid passage, and thus improving the hydraulic efficiency of the electric pump. The second twisted blade 1424 is located between two adjacent first twisted blades 1423. The length of the second twisted blade 1424 is less than the length of the first twisted blade 1423. The second twisted blade 1424 includes a second head 1424a and a second tail 1424b. The second head 1424a is closer to the center of the impeller assembly 142 than the second tail 1424b. The first head 1423a is closer to the center of the impeller assembly 142 than the second head 1424a. The curve connecting the second twisted blade 1424 to the upper plate 1421 is defined as the short upper edge curve 1424c, and the curve connecting the second twisted blade 1424 to the lower plate 1422 is defined as the short lower edge curve 1424d. At least part of the short upper edge curve 1424c is different from the short lower edge curve 1424d. In this manner, the first head 1423a is positioned closer to the center of the impeller assembly 142 than the second head 1424a. The first head 1423a and the second head 1424a are staggered, which, compared to both heads being positioned close to the center of the impeller assembly simultaneously, increases the impeller inlet area, reduces the risk of cavitation at the impeller inlet, and improves pump efficiency. In this embodiment, the short upper edge curve is the curve formed by the connection between the suction surface of the second twisted blade and the upper plate, and the short lower edge curve is the curve formed by the connection between the suction surface of the second twisted blade and the lower plate. The suction surface of the second twisted blade is a concave curved surface, and the pressure surface is a convex curved surface. Only the blade angle at the intersection of the short upper edge curve 1424c and the second tail 1424b differs from the blade angle at the intersection of the short lower edge curve 1424d and the second tail 1424b. Apart from these two points, the blade angles of the other short upper and lower edge curves are different, which facilitates the manufacturing and processing of the impeller assembly.

[0038] As one implementation method, please refer to Figures 1 to 14As shown, the intersection of the short upper edge curve 1424c and the second head 1424a is defined as the third point C, and the intersection of the short lower edge curve 1424d and the second head 1424a is defined as the fourth point D. The third point C is located on the third circumference 104, and the fourth point D is located on the fourth circumference 105. Both the third circumference 104 and the fourth circumference 105 are concentric with the circumference of the circumferential side surface of the upper plate 1421. The ratio of the diameter of the first circumference 102 to the diameter of the third circumference 102 is 0.4 to 0.8, and the ratio of the diameter of the second circumference 102 to the diameter of the fourth circumference 105 is 0.3 to 0.6. This method facilitates the guidance of the working medium in the impeller fluid channel, and by setting the working medium in the impeller fluid channel at this location for diversion, it helps to reduce eddies.

[0039] As one implementation method, please refer to Figures 1 to 14 As shown, the first twisted blade 1423, the upper plate 1421, and the lower plate 1422 form an impeller fluid channel 1427. The impeller fluid channel 1427 near the first head 1423a of the first twisted blade 1423 is defined as the impeller inlet 1425 of the impeller fluid channel 1427, and the impeller fluid channel 1427 near the first tail 1423b of the first twisted blade 1423 is defined as the impeller outlet 1426 of the impeller fluid channel 1427. The area ratio of the impeller outlet 1426 to the impeller inlet 1425 is 1.5 to 2. In this way, while ensuring performance, it is beneficial to control the working medium flow velocity within the impeller fluid channel 1427 within a reasonable range, which helps to reduce cavitation. On the other hand, it also helps to reduce the noise of the electric pump.

[0040] As one implementation method, please refer to Figures 1 to 14 As shown, the electric pump 100 includes a pump cover 11 and an impeller cavity 132. A wall portion corresponding to the impeller cavity 132 is formed in the pump cover 11. An impeller assembly 142 is located in the impeller cavity 132. The impeller cavity 132 includes a volute flow channel 1321. Along the radial outer side of the electric pump 100, the volute flow channel 1321 is located radially outer side of the impeller assembly 142. The ratio of the inlet width L1 of the volute flow channel 1321a to the impeller outlet width L2 is 2.4 to 3.2. This design helps reduce the noise of the electric pump. It should be noted that the inlet position of the volute flow channel 1321a is the position where the maximum radial radius of the volute flow channel is located. For a more convenient description of the volute flow channel 1321, please refer to [reference needed]. Figure 12 and Figure 13 As shown, Figure 13 The diagram shows the projection of the impeller assembly and the volute flow channel onto a plane perpendicular to the axial direction of the electric pump. In this embodiment, the width L1 of the volute inlet is 6mm to 8mm. This further helps to reduce the noise of the electric pump.

[0041] As one implementation method, please refer to Figures 1 to 14 As shown, the volute flow channel 1321 includes a throat 1321b. Along the flow direction of the working medium within the volute flow channel 1321, the throat 1321b is located downstream of the inlet 1321a. The ratio of the area of ​​the throat 1321b to the area of ​​the impeller outlet 1426 is 0.18 to 0.3. This design, firstly, improves efficiency in high-flow-rate areas; and secondly, reduces the noise of the electric pump. Specifically, the pump cover 11 includes a tongue 113. The throat 1321b of the volute flow channel 1321 refers to the portion perpendicular to the volute flow channel at the end of the tongue. See reference [reference needed]. Figure 13 As shown. In this embodiment, the area of ​​the throat 1321b of the volute flow channel is 95 mm². 2 Up to 102mm 2 This further improves efficiency in high-flow-rate areas and also helps reduce the noise of the electric pump.

[0042] As one implementation method, please refer to Figures 1 to 14 As shown, the twisted blade 1423 and the lower plate 1422 are integral structural components, and the second twisted blade 1424 and the upper plate 1421 are integral structural components. The structure formed by the first twisted blade 1423 and the lower plate 1422 is defined as the first part 144, and the structure formed by the second twisted blade 1424 and the upper plate 1421 is defined as the second part 145. The first part 144 and the second part 145 are welded and fixed together. This method simplifies the manufacturing process of the electric pump.

[0043] Specifically, as one implementation method, please refer to Figures 1 to 14 As shown, the impeller assembly 142 includes a first protrusion 142b and a first groove 142c. One of the first protrusion 142b and the first groove 142c is disposed on the first twist blade 1423, and the other of the first protrusion 142b and the second groove 142c is disposed on the upper plate 1421. At least the molten portion of the first protrusion 142b is located in the first groove 142c. In this way, the connection between the first and second parts is strengthened while reducing the generation of weld flash.

[0044] Specifically, as one implementation method, please refer to Figures 1 to 14As shown, the first protrusion 142b and the first twisted blade 1423 are integral structural components. The first protrusion 142b is disposed near the tail 1423b of the first twisted blade 1423. The first protrusion is disposed along the top 1423e of the first twisted blade 1423. The first protrusion 142b extends in the radial direction of the first twisted blade 1423. The first groove 142c is recessed in the upper plate 1421. The top 1423e of the first twisted blade 1423 contacts the upper plate 1421. In this way, the first protrusion 142b is positioned close to the first tail 1423b of the first twisted blade 1423. The tail 1423b of the first twisted blade 1423 is subjected to greater external force than the first head of the first twisted blade 1423. The first protrusion 142b only occupies part of the top area of ​​the first twisted blade 1423. The first protrusion 142b does not need to extend the entire first twisted blade 1423. This helps to reduce the amount of material used in the first protrusion 142b, laying a foundation for the lightweighting of the electric pump, and also helps to reduce the operating cost of the electric pump.

[0045] Specifically, as one implementation method, please refer to Figures 1 to 14 As shown, the impeller assembly 142 includes a second protrusion 142d and a second groove 142e. One of the second protrusion 142d and the second groove 142e is located on the second twist blade 1424, and the other of the second protrusion 142d and the second groove 142e is located on the lower plate 1422. At least the molten portion of the second protrusion 142d is located in the second groove 142e. This helps to reduce the amount of overflow entering the working medium during the welding of the first and second parts, and helps to improve the cleanliness of the working medium.

[0046] Specifically, as one implementation method, please refer to Figures 1 to 14 As shown, the second protrusion 142d and the second twisted blade 1424 are an integral structural component. The second protrusion 142d is disposed near the second head 1424a of the second twisted blade 1424, and protrudes along the top 1424e of the second twisted blade 1424. The second protrusion 142d extends in the radial direction of the second twisted blade 1424, and the second groove 142e is recessed into the lower plate 1422, with the top 1424e of the second twisted blade 1424 in contact with the lower plate 1422. This arrangement helps to reduce overflow material entering the working medium during welding of the first and second parts, thus improving the cleanliness of the working medium. Specifically, the second protrusion 142d is disposed near the head of the second twisted blade 1424, the second groove 142e is recessed into the lower plate, and the second protrusion 142d extends in the radial direction of the second twisted blade 1424. This approach is beneficial for the processing and manufacturing of electric pumps.

[0047] Specifically, as one implementation method, please refer to Figures 1 to 14 As shown, the first protrusion 142b includes a starting portion 142b1 and a ending portion 142b2. The starting portion 142b1 is closer to the center of the impeller than the ending portion 142b2. The second protrusion 142d includes a starting portion 142d1 and a ending portion 142d2. The starting portion 142d1 is closer to the center of the impeller than the ending portion 142d2. The circumference where the starting portion 142b1 of the first protrusion is located is defined as the fifth circumference 106, and the circumference where the starting portion 142d1 of the second protrusion is located is defined as the sixth circumference 107. The diameter of the fifth circumference 106 is larger than the diameter of the sixth circumference 107. This arrangement helps to ensure the welding strength between the first and second parts.

[0048] As one implementation method, please refer to Figures 1 to 14 As shown, the rotating assembly 14 includes a bearing portion 141a. A portion of the impeller assembly 142 is injection molded with the rotor 1411 and the bearing portion 141a as inserts. The rotating assembly 14 includes a first hole 1441. Along the axial direction of the electric pump 100, the first hole 1441 extends along the inner surface 1422a of the lower plate 1422 to the outer surface 1422b of the lower plate 1422. The wall portion corresponding to the first hole 1441 includes the end surface 1413a of the bearing portion 141a. In one specific implementation, the bearing portion 141a includes a first bearing 1412 and a second bearing 1413. Along the axial direction of the electric pump 100, the first bearing 1412 is away from the impeller assembly 142 relative to the second bearing 1413. The wall portion corresponding to the first hole 1441 includes the end surface 1413a of the second bearing 1413. This helps to reduce the amount of bearing portion 141a used, laying a certain foundation for reducing the cost of the electric pump 100. Along the radial direction of the electric pump 100, the radial diameter of the first hole 1441 is smaller than the radial diameter of the impeller inlet 1425. The first twisted blade 1423 includes a top 1423e and a root 1423f. A first reference plane is defined, which is perpendicular to the axis of the impeller assembly. Projecting the first twisted blade 1423 and the impeller inlet 1425 onto the first reference plane, the intersection line of the top 1423e and the first head 1423a coincides with the projected outline of the impeller inlet 1425, and the intersection line of the root 1423f and the first head 1423a coincides with the projected outline of the inlet hole. The placement angle of the top 1423e is larger than the placement angle of the root 1423f. Thus, the twist of the first twisted blade 1423 is more conducive to guiding the working medium, resulting in less fluid loss of the working medium, thereby improving the hydraulic efficiency of the electric pump.

[0049] It should be noted that some of the circles mentioned above are virtual circles added for the purpose of clarification.

[0050] The above descriptions merely illustrate several technical solutions of the present invention, and while the details are relatively specific, they should not be construed as limiting the scope of the invention patent. It should be noted that those skilled in the art can make various modifications and controls without departing from the concept of the present invention, and these all fall within the protection scope of the present invention. Therefore, the protection scope of this invention patent should be determined by the technical solutions described in this application.

Claims

1. An electric pump (100) characterized by: The electric pump (100) comprises an impeller assembly (142), the impeller assembly (142) comprises a plurality of first twisted blades (1423), an upper plate (1421) and a lower plate (1422), at least part of the first twisted blades (1423) are located between the upper plate (1421) and the lower plate (1422), a plurality of the first twisted blades (1423) are arranged along the circumference of the lower plate (1422), the first twisted blade (1423) comprises a first head (1423a) and a first tail (1423b), the first head (1423a) is close to the central part of the impeller assembly (142) relative to the first tail (1423b), the curve defining the connection between the first twisted blade (1423) and the upper plate (1421) is a long upper edge curve (1423g), the curve defining the connection between the first twisted blade (1423) and the lower plate (1422) is a long lower edge curve (1423h), the intersection of the long upper edge curve (1423g) and the first head (1423a) is a first point (A), the intersection of the long lower edge curve (1423h) and the first head (1423a) is a second point (B), the first point (A) is located on a first circle (102), the second point (B) is located on a second circle (103), the first circle (102) and the second circle (103) are concentric with the circle in which the circumferential side surface (1422e) of the lower plate (1422) is located, the ratio of the diameters of the first circle (102) and the second circle (103) is 1.3 to 1.7, the ratio of the installation angle (β1) of the first point (A) and the installation angle (β1) of the second point (B) is 1.2 to 1.

6.

2. The electric pump (100) according to claim 1, characterized in that: The impeller assembly (142) comprises a plurality of second twisted blades (1424), at least part of the second twisted blades (1424) are located between the upper plate (1421) and the lower plate (1422), a plurality of the second twisted blades (1424) are arranged along the circumference of the upper plate (1421), the second twisted blades (1424) are located between two adjacent first twisted blades (1423), the length of the second twisted blades (1424) is less than the length of the first twisted blades (1423), the second twisted blades (1424) comprise a second head (1424a) and a second tail (1424b), the second head (1424a) is closer to the central part of the impeller assembly (142) than the second tail (1424b), the first head (1423a) is closer to the central part of the impeller assembly (142) than the second head (1424a), the curve connecting the second twisted blades (1424) and the upper plate (1421) is defined as a short upper edge curve (1424c), the curve connecting the second twisted blades (1424) and the lower plate (1422) is defined as a short lower edge curve (1424d), the blade angle of at least part of the short upper edge curve (1424c) is different from the blade angle of at least part of the short lower edge curve (1424d).

3. The electric pump (100) according to claim 2, characterized in that: The intersection of the short upper edge curve (1424c) and the second head (1424a) is defined as a third point (C), the intersection of the short lower edge curve (1424d) and the second head (1424a) is defined as a fourth point (D), the third point (C) is located on a third circle (104), the fourth point (D) is located on a fourth circle (105), the ratio of the diameter of the third circle (104) to the diameter of the first circle (102) is 0.4 to 0.

8.

4. The electric pump (100) according to any one of claims 1 to 3, characterized in that: The first twisted blades (1423), the upper plate (1421) and the lower plate (1422) form the impeller fluid channel (1427), the impeller fluid channel (1427) close to the first head (1423a) of the first twisted blade (1423) is defined as the impeller inlet (1425) of the impeller fluid channel (1427), the impeller fluid channel (1427) close to the first tail (1423b) of the first twisted blade (1423) is defined as the impeller outlet (1426) of the impeller fluid channel (1427), the area ratio of the impeller outlet (1426) to the impeller inlet (1425) is 1.5 to 2.

5. The electric pump (100) according to any one of claims 1 to 3, characterized in that: The electric pump (100) comprises a pump cover (11), the electric pump (100) comprises an impeller cavity (132), a wall part corresponding to the impeller cavity (132) is formed in the pump cover (11), the impeller assembly (142) is located in the impeller cavity (132), the impeller cavity (132) comprises a volute flow channel (1321), the volute flow channel (1321) is located radially outward of the impeller assembly (142) along the radial direction of the electric pump (100), and a ratio of an inlet width (L1) of the volute flow channel (1321) to a width (L2) of the impeller outlet (1426) is 2.4-3.

2.

6. The electric pump (100) according to claim 5, characterized in that: The volute flow channel (1321) comprises a volute throat (1321b), which is located downstream of the inlet (1321a) of the volute flow channel (1321) along the flow direction of the working medium in the volute flow channel (1321), and a ratio of an area of the volute throat (1321b) to an area of the impeller outlet (1426) is 0.18-0.

3.

7. The electric pump (100) according to any one of claims 1 to 6, characterized in that The first twisted blade (1423) and the lower plate (1422) are an integral structure, the second twisted blade (1424) and the upper plate (1421) are an integral structure, the first twisted blade (1423) and the lower plate (1422) form a first part (144), the second twisted blade (1424) and the upper plate (1421) form a second part (145), and the first part (144) and the second part (145) are welded and fixed.

8. The electric pump (100) according to claim 7, characterized in that: The impeller assembly (142) comprises a first protruding part (142b) and a first recessed part (142c), one of the first protruding part (142b) and the first recessed part (142c) is arranged on the first twisted blade (1423), and the other of the first protruding part (142b) and the first recessed part (142c) is arranged on the upper plate (1421), and at least a molten part of the first protruding part (142b) is located in the first recessed part (142c).

9. The electric pump (100) according to claim 8, characterized in that The first protruding part (142b) and the first twisted blade (1423) are an integral structure, the first protruding part (142b) is arranged close to a first tail part (1423b) of the first twisted blade (1423), the first protruding part is arranged protruding along a top part (1423e) of the first twisted blade (1423), the first protruding part (142b) extends along a direction in which the first twisted blade (1423) extends radially, and the first recessed part (142c) is recessed in the upper plate (1421), and the top part (1423e) of the first twisted blade (1423) is in contact with the upper plate (1421).

10. The electric pump (100) according to claim 8 or 9, characterized in that The impeller assembly (142) comprises a second protruding part (142d) and a second recessed part (142e), one of the second protruding part (142d) and the second recessed part (142e) is located at the second twisted blade (1424), the other of the second protruding part (142d) and the second recessed part (142e) is located at the lower plate (1422), and at least a molten part of the second protruding part (142d) is located in the second recessed part (142e).

11. The electric pump (100) according to claim 10, characterized in that The second protruding part (142d) is an integral structure with the second twisted blade (1424), the second protruding part (142d) is arranged close to the second head part (1424a) of the second twisted blade (1424), the second protruding part (142d) is arranged protruding along the top part (1424e) of the second twisted blade (1424), the second protruding part (142d) extends along the radial direction of the second twisted blade (1424), the second protruding part (142d) extends along the direction of the radial extension of the second twisted blade (1424), the second recessed part (142e) is recessed in the lower plate (1422), and the top part (1424e) of the second twisted blade (1424) is in contact with the lower plate (1422).

12. The electric pump (100) according to claim 11, characterized in that The first protruding part (142b) comprises a first protruding part start part (142b1) and a first protruding part end part (142b2), the first protruding part start part (142b1) is close to the center of the impeller relative to the first protruding part end part (142b2), the second protruding part (142d) comprises a second protruding part start part (142d1) and a second protruding part end part (142d2), the second protruding part start part (142d1) is close to the center of the impeller relative to the second protruding part end part (142d2), a circumference where the first protruding part start part (142b1) is located is defined as a fifth circumference (106), a circumference where the second protruding part start part (142d1) is located is defined as a sixth circumference (107), and the diameter of the fifth circumference (106) is greater than the diameter of the sixth circumference (107).

Images