Impeller and pump

Abstract

Impeller (20) comprising a wheel disc (21) having a front side (211) and a rear side (212), the front side (211) and the rear side (212) being opposite one another along the axial direction, characterized in that the impeller (20) comprises: a plurality of grooves (213) arranged on the rear side (212) of the wheel disc (21), the grooves (213) being recessed relative to the surface of the rear side (212), one end of the interior of the groove (213) being arranged closer to the outer peripheral surface of the wheel disc (21) than the other end, the plurality of grooves (213) being spaced apart from one another along the circumference of the wheel disc (21); and a plurality of vanes (22) formed towards the front side (211) of the wheel disc (21), the vanes (22) being distributed along the circumferential direction.

Description

FIELD OF THE INVENTION

[0001] The present invention relates to the technical field of pumps, in particular the invention relates to an impeller and a pump. BACKGROUND OF THE INVENTION

[0002] A pump is a machine that moves or pressurizes liquids. It transfers the mechanical energy of the prime mover or other external energy sources to the liquid, increasing its energy. The pump can be used to move liquids such as water, oil, acids and alkalis, emulsions, suspensions, and liquid metals. It can also transport liquid-gas mixtures and suspended solids. Some pumps use an electric motor to rotate the impeller, thereby creating a vacuum inside the pump to continuously suck in and expel the liquid.

[0003] An impeller is typically rotatably connected to a support assembly. Vanes are arranged on one side of the impeller. A rotor of an electric motor is connected to the other side of the impeller, and the rotor transmits the rotational driving force to the impeller. When the impeller rotates, the flow velocity of the fluid around the vanes is relatively high and the fluid pressure on one side of the impeller is relatively low compared to the other. Due to the unequal pressure on both sides of the impeller, it is subject to axial fluid pressure. Due to the limiting effect of the support assembly, the axial position of the impeller remains unchanged under the axial fluid pressure, but the axial pressure at the frictional contact point of the support increases, resulting in a larger friction force and reducing the pump efficiency. BRIEF DESCRIPTION OF THE INVENTION

[0004] Accordingly, the present invention proposes an impeller that could solve or mitigate the above-mentioned problem, wherein the impeller comprises a wheel disc having a front side and a back side, the front side and the back side are arranged opposite to each other along the axial direction, a plurality of grooves are arranged on the back side of the wheel disc, the grooves are recessed relative to the surface of the back side, one end of the interior of the grooves is arranged closer to the outer peripheral surface of the wheel disc than the other end, and the grooves are spaced apart along the circumference of the wheel disc, the impeller further comprising a plurality of vanes connected to the front side of the wheel disc, and the vanes are distributed along the circumferential direction.

[0005] When the impeller is in operation, the wheel disc is connected to the support assembly. The fluid flows mainly on the front side of the wheel disc. As the impeller rotates, the vanes create pressure on the fluid, and the fluid in the central area of ​​the front side of the impeller is discharged, creating a negative pressure zone in this area. Since one end of the interior of the grooves is located closer to the outer peripheral surface of the wheel disc than the other end, the inner wall of the groove can exert a pushing effect on the fluid in the groove when the impeller rotates. Since the grooves are located on the back side of the wheel disc and are distributed at intervals along the circumference of the wheel disc, the fluid in the grooves flows toward the edge.

[0006] The fluid near the back of the impeller disc flows toward the periphery due to the flow tendency caused by the grooves. Therefore, the fluid on the back of the impeller disc is also discharged to a certain extent, and the fluid pressure on the back of the impeller disc decreases. As the pressure on the back of the impeller decreases synchronously, the axial pre-pressure of the fluid on the impeller is reduced, thereby avoiding excessive axial pressure at the friction contact point of the support assembly, effectively controlling the friction force and friction loss in the pump, and ensuring high working efficiency and a long service life of the pump. At the same time, since the grooves are recessed compared to the back surface, an increase in the overall thickness of the impeller is avoided, which benefits the compactness of the pump structure.

[0007] In one of the embodiments, the radial distance between one end of the interior of the groove and the other end is greater than a cross-sectional width of the grooves perpendicular to the radial direction.

[0008] In one embodiment, the grooves are arranged such that they extend radially along the wheel disc, and / or the grooves are formed curved in the circumferential direction along the direction from the center of the wheel disc to the edge of the wheel disc, and / or the grooves are formed inclined in the circumferential direction along the direction from the center of the wheel disc to the edge of the wheel disc, and / or the grooves have a wavy transition shape along the direction from the center of the wheel disc to the edge of the wheel disc.

[0009] In one embodiment, an end of the interior space of at least one of the plurality of grooves extends to the edge of the wheel disc.

[0010] In one embodiment, the cross section of the interior of the grooves perpendicular to the radial direction is rectangular and / or the cross section of the interior of the grooves perpendicular to the radial direction is semicircular and / or the cross section of the interior of the grooves perpendicular to the radial direction is trapezoidal.

[0011] In one of the embodiments, a plurality of projections are further provided, wherein the projections are connected to the rear side of the wheel disc and extend in a direction away from the front side.

[0012] In one embodiment, the projections extend from the bottom of the grooves in a direction away from the front side and / or the projections project outwardly from the surface of the back side in a direction away from the front side.

[0013] The present invention provides a pump having the impeller of any of the above embodiments.

[0014] In one embodiment, a baffle plate connected to the vanes is also provided. The baffle plate is arranged on the side of the vanes facing away from the wheel disc. A flow opening is provided in the center of the baffle plate. The position of the flow opening corresponds to the central area of ​​the front side.

[0015] In one embodiment, an inner gap and an outer gap are formed between the baffle plate and the housing. The inner gap and the outer gap are each arranged around the axis of the impeller. The outer gap is connected to the inner gap from the outer peripheral side. In the axial section of the pump, the interior of the inner gap and the interior of the outer gap form a broken line. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a schematic three-dimensional representation of a pump according to an embodiment of the present invention; Fig. 2 is a perspective sectional view of the Fig. 1 pump shown; Fig. 3 is a sectional plan view of the Fig. 1 pump shown; Fig. 4 is an enlarged view of point A of the Fig. 3 pump shown; Fig. 5 is a three-dimensional schematic representation of the Fig. 2 after the impeller and the baffle plate have been separated; Fig. 6 is a three-dimensional schematic representation of the Fig. 5 shown impeller from a different angle; Fig. 6a is a plan view of the Fig. 6 impeller shown; Fig. 6b is a three-dimensional cross-sectional view of the Fig. 6a along the direction AA; Fig. 7 is a perspective schematic view of an impeller according to a second embodiment of the present invention; Fig. 8 is a schematic three-dimensional representation of an impeller according to a third embodiment of the present invention; Fig. 9 is a schematic three-dimensional view of an impeller according to a fourth embodiment of the present invention; Fig. 10 is a schematic three-dimensional view of an impeller according to a fifth embodiment of the present invention; Fig. 10a is a plan view of the Fig. 10 impeller shown; Fig. 10b is a three-dimensional cross-sectional view of the Fig. 10a shown impeller along the direction BB; Fig. 11 is a schematic three-dimensional view of an impeller according to a sixth embodiment of the present invention; Fig. 12 is a perspective schematic diagram of an impeller according to a seventh embodiment of the present invention. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT

[0016] The technical solution provided by the embodiments of the present invention will be described below with reference to the accompanying drawings.

[0017] As in Fig. 1 to Fig. As shown in Figure 3, the present invention provides a pump 100 used for pumping fluids such as air and liquids such as water and oil to transfer the fluid from one container to another or to an external environment, such as when emptying a pool. In one embodiment, the pump 100 is a centrifugal drain pump that can be used in washing machines, dishwashers, etc. It should be understood that the pump 100 can also be used to suck in and discharge fluids such as gases.

[0018] How Fig. As shown in Figure 2, the pump 100 has a housing 30 and an impeller 20 disposed within the housing 30. The impeller 20 is rotatably disposed within the housing 30. In some embodiments, the housing 30 is provided with an intake channel 31 and an outlet channel 32. The inner end of the intake channel 31 faces the center of the impeller 20. The inner end of the outlet channel 32 faces an edge of the impeller 20.

[0019] In some embodiments, the pump 100 comprises, as in Fig. 2 and Fig. 3, further includes a support assembly 40, wherein the support assembly 40 serves to limit the position of the impeller 20 in the housing 30 so that the impeller 20 rotates at a predetermined position. In some embodiments, the support assembly 40 includes a support rod 41 connected to the housing 30. The impeller 20 is attached to the outer periphery of the support rod 41 and can rotate relative to the support rod 41. Specifically, the support rod 41 is fixedly disposed within the housing 30 and maintains a fixed angle relative to the housing 30. In one embodiment, the support assembly 40 further includes a limiting member 42 and a fastening element 43. The limiting member 42 is disposed on one side of the impeller 20 near the intake duct 31. The fastening element 43 is threadedly attached to one end of the support rod 41 and fixes the limiting element 42 to one end of the support rod 41.Since the limiting element 42 is attached to the side of the impeller 20 near the intake channel 31, the impeller 20 can be prevented from moving near the intake channel 31. In particular, the limiting plate 42 is a friction pair.

[0020] In some embodiments, the pump 100 further includes a drive element for rotationally driving the impeller 20. In one embodiment, the drive element is a motor, with the rotor of the drive element being connected to the impeller 20.

[0021] As in the Fig. As shown in Figures 5 to 12, the present invention provides an impeller 20 comprising a wheel disc 21 and a plurality of vanes 22. The wheel disc 21 has a front surface 211 and a rear surface 212. The front surface 211 and the rear surface 212 are arranged opposite each other along the axial direction. The rear surface 212 of the wheel disc 21 is provided with a plurality of grooves 213. The grooves 213 are recessed relative to the surface of the rear surface 212. One end of the interior of the grooves 213 is arranged closer to the outer peripheral surface of the wheel disc 21 than the other end.

[0022] A plurality of grooves 213 are distributed at intervals along the circumference of the wheel disc 21. A plurality of vanes 22 are formed on the front side 211 of the wheel disc 21. The vanes 22 are distributed along the circumferential direction.

[0023] Specifically, when the impeller 20 is in operation, the wheel disc 21 is connected to the support assembly 40. The fluid flows primarily on the front side 211 of the wheel disc 21. As the impeller 20 rotates, the vanes 22 create pressure on the fluid, and the fluid is expelled from the central region 215 of the front side 211 of the wheel disc 21, creating a negative pressure zone in this region. Since one end of the interior of the grooves 213 is located closer to the outer periphery of the wheel disc 21 than the other end, the inner side wall 214 of the groove 213 can push the fluid in the groove 213 upward when the impeller 20 rotates. Since the grooves 213 are located on the rear side 212 of the wheel disc 21 and a plurality of grooves 213 are spaced apart along the periphery of the wheel disc 21, the fluid in the grooves 213 flows toward the outer edge.The fluid near the surface of the back surface 212 of the wheel disc 21 flows toward the periphery due to the flow tendency caused by the grooves 213, so that the fluid on the back surface 212 of the wheel disc 21 also flows out to a certain extent and the fluid pressure on the back surface 212 of the wheel disc 21 decreases.

[0024] Since the pressure on the back surface 212 of the impeller 21 decreases synchronously, the axial pre-pressure of the fluid on the impeller 20 decreases, thereby preventing excessive axial pressure at the frictional contact point of the support assembly 40, effectively controlling the frictional force and friction loss in the pump 100, and ensuring that the pump 100 has high efficiency and a long service life. At the same time, since the grooves 213 are recessed relative to the surface of the back surface 212, an extrusion effect can be created on the fluid, eliminating the need to provide raised vanes on the back surface 212 of the impeller 21, thus also preventing an increase in the overall thickness of the impeller 20. The reserved space in the thickness direction of the impeller 20 within the casing 30 does not need to be increased, thus saving the internal space of the casing 30.This in turn is advantageous for maintaining the compact design of the Pump 100.

[0025] In some embodiments, the bottom surface of the grooves 213, as in Fig. 6, the inner sidewall 214 transitions into the surface of the rear side 212. The inner sidewall 214 and the bottom surface together form the boundary of the interior of the grooves 213. In some embodiments, the inner sidewall 214 transitions from one end of the interior of the groove 213 to the other end of the interior of the groove 213. In some embodiments, an inner sidewall 214 of the groove 213 is arranged circumferentially opposite another inner sidewall 214 of the groove 213.

[0026] In some embodiments, the radial distance between one end of the interior of the grooves 213 and the other end is greater than the cross-sectional width of the grooves 213 perpendicular to the radial direction, so that the length of the inner wall 214 of the groove 213 is longer, which is useful for increasing the area of ​​the inner wall 214 of the groove 213. At the same time, the curvature of an individual groove 213 can be reduced, which is advantageous for increasing the distribution density of the grooves 213 and improving the compacting effect of the wheel disc 21 on the liquid on the back side 212. It can be seen that the cross-sectional width of the grooves 213 perpendicular to the radial direction is close to the circumferential width of the grooves 213.

[0027] In some embodiments, one end of the interior of the grooves 213 intersects with a circle, and the center of the circle intersects with the axis of the wheel disc 21. The other end of the interior of the grooves 213 intersects with another circle, and the center of the another circle intersects with the axis of the wheel disc 21. The distance between one end of the interior of the groove 213 and the other end in the radial direction is the radius difference between the two circles.

[0028] In some embodiments, the limiting member 42 is as shown in Fig. 2 and Fig. 3, is arranged on the front side 211 of the wheel disc 21. When the pressure on the rear side 212 of the wheel disc 21 decreases synchronously, the axial pre-pressure of the fluid on the impeller 20 decreases, reducing the pressure and friction between the wheel disc 21 and the restrictor plate 42, thereby reducing the wear of the wheel disc 21 and the restrictor plate 42.

[0029] In some embodiments, the inner end of the intake duct 31, as in Fig. 2 and Fig. 3, facing the central region 215 of the front side 211. The inner end of the outlet channel 32 is directed at an angle to the outer periphery of the vanes 22. After the liquid flows into the intake channel 31, it flows from the inner end of the intake channel 31 into the central region 215 of the front side 211. The rotation of the vanes 22 causes the liquid in the central region 215 to flow toward the circumferential positions of all vanes 22. In some embodiments, the outlet channel 32 communicates with the outer peripheral regions of all vanes 22. The liquid in the outer peripheral region of all vanes 22 flows into the inner end of the outlet channel 32.

[0030] In some embodiments, the grooves 213, as in Fig. 6, are arranged so as to extend radially along the wheel disc 21. In particular, the interior of the grooves 213 has the shape of an elongated strip, and the longitudinal direction of the interior coincides with the radial direction of the wheel disc 21. More specifically, each radial direction of the wheel disc 21 points to the rotation axis of the impeller 20.

[0031] In some embodiments, the grooves 213, as in Fig. 7, the vanes 213 are curved in the circumferential direction from the center of the wheel disc 21 to the edge of the wheel disc 21. Specifically, the edges of the grooves 213 are arcuate. Furthermore, the bending direction of the grooves 213 is the same as the bending direction of the vanes 22.

[0032] In some embodiments, the grooves 213 are circumferentially inclined along the direction from the center of the wheel disc 21 to the edge of the wheel disc 21. Specifically, the edge of the grooves 213 is formed in the shape of an oblique line, and the angle between the edge of the groove 213 and any radius line of the wheel disc 21 is greater than zero.

[0033] In some embodiments, the grooves 213, as shown in Fig. 8, the wheel disc 21 has a corrugated transition shape along the direction from the center of the wheel disc 21 to the edge of the wheel disc 21. In particular, the edges of the grooves 213 are corrugated.

[0034] In some embodiments, one end of the interior of the grooves 213 is radially spaced from the edge of the wheel disc 21, and the other end is relatively far from the edge of the wheel disc 21. In some embodiments, the plurality of grooves 213 on the wheel disc 21 may have different shapes.

[0035] In one embodiment, a part of the grooves 213 of the wheel disc 21 extends radially, another part of the grooves 213 is curved in the circumferential direction, and another part of the grooves 213 has edges in the form of oblique edges.

[0036] In some embodiments, an end of the interior of at least one of the plurality of grooves 213 extends to the edge of the wheel disc 21, as shown in Fig. 6. In particular, the other end of the inner space of the groove 213 is located relatively far from the outer periphery of the wheel disc 21. Since one end of the inner space of the groove 213 is directly connected to the space of the outer peripheral edge 52 of the wheel disc 21, the fluid in the groove 213 is not blocked by the wall of the groove 213 when flowing radially toward the periphery, thereby reducing the resistance encountered by the fluid and improving the uniformity of the fluid flow toward the periphery. The fluid discharge effect on the back surface 212 of the wheel disc 21 is also ensured.

[0037] In some embodiments, one end of the interior of all grooves 213 extends to the edge of the wheel disc 21.

[0038] In some embodiments, the cross-section of the interior of the grooves 213 perpendicular to the radial direction is rectangular, as shown in the Fig. 6, Fig. 6a and Fig. 6b. In particular, the cross-sectional edge of the groove 213 is open perpendicular to the radial direction, and the opening direction leads away from the front side 211 of the wheel disc 21. When the interior of the grooves 213 has a rectangular cross-section perpendicular to the radial direction, the inner wall 214 of the groove 213 is arranged perpendicular to the surface of the rear side 212 of the wheel disc 21, thereby facilitating an improvement in the pressure of the inner wall 214 of the groove 213 on the fluid.

[0039] In some other embodiments described in Fig. 10, Fig. 10a and Fig. 10b, the cross-section of the interior of the groove 213 perpendicular to the radial direction is semicircular. In some other embodiments, the cross-section of the interior of the grooves 213 perpendicular to the radial direction is trapezoidal, as shown in Fig. 12. In particular, the cross-section of the interior of the groove 213 perpendicular to the radial direction may also have other shapes that promote the flow of fluid into the groove 213.

[0040] In some embodiments, the interior of the grooves 213 is perpendicular to the radial cross section, the cross section is parallel to the axis of the wheel disc 21 and is spaced from the axis of the wheel disc 21, as in Fig. 6b and Fig. 10b shown,

[0041] In some embodiments, the cross-sectional shape of the interior of the grooves 213 perpendicular to the radial direction is selected from one or more of the following shapes: rectangle, semicircle, and trapezoid. It is understood that, for the plurality of grooves 213, the interior of a portion of the grooves 213 perpendicular to the radial direction may have a rectangular cross-section, and the interior of another portion of the grooves 213 perpendicular to the radial direction may have a semicircular cross-section. Alternatively, the interior of a portion of the grooves 213 perpendicular to the radial direction may have a rectangular cross-section, the interior of a portion of the grooves 213 perpendicular to the radial direction may have a semicircular cross-section, and the interior of another portion of the grooves 213 perpendicular to the radial direction may have a trapezoidal cross-section.

[0042] In some embodiments described in Fig. 11, the impeller 20 further includes a plurality of projections 23 connected to the rear side 212 of the wheel disc 21 and extending in a direction away from the front side 211. Specifically, the inner wall 214 of the grooves 213 and the side surface of the projections 23 simultaneously exert a pressure action on the liquid, thereby increasing the effective area between the impeller 20 and the liquid, which is advantageous for further increasing the pressure of the impeller 20 on the liquid on the rear side 212 of the wheel disc 21.In particular, the shape change of the projection 23 in the direction from the center of the wheel disc 21 along the shortest path to the edge of the wheel disc 21 corresponds to the shape change of the groove 213, so that the projection 23 and the inner wall 214 of the grooves 213 are evenly spaced on both sides along the circumferential direction, so that the side surface of the projection 23 and the inner wall 214 of the grooves 213 can simultaneously generate pressure on the liquid.

[0043] In some embodiments, the projection 23 extends from the bottom of the grooves 213 in a direction away from the front surface 211, thereby reducing the projection height of the projection 23 relative to the surface of the back surface 212 of the wheel disc 21, which is advantageous for controlling the overall thickness of the impeller 20.

[0044] In some embodiments, the protrusion 23 projects outwardly from the surface of the back side 212 in a direction away from the front side 211, thereby facilitating the increase in the area of ​​the side surface of the protrusion 23 and the increase in the force acting on the liquid.

[0045] In some other embodiments, the projection 23 extends from the surface of the rear side 212 of the wheel disc 21 in a direction away from the front side 211.

[0046] In some embodiments, the vanes 22 are curved circumferentially along the direction from the center of the wheel disc 21 to the edge of the wheel disc 21, as shown in Fig. 5. In some embodiments, the vanes 22 extend from the edge of the central region 215 to the edge of the wheel disc 21.

[0047] In some embodiments, each of the wings 22 includes a first wing 22 and a second wing 24, as shown in Fig. 5. The first vane 22 and the second vane 24 are each connected to the front surface 211 of the impeller 21, and the first vanes 22 are distributed along the circumference of the impeller 21, with the second vanes 24 being arranged between adjacent first vanes 22. The radial length of the second vanes 24 is smaller than the radial length of the vanes 22. The center point of the second vanes 24 is closer to the outer periphery of the impeller 22 than the center point of the vanes 22, thereby increasing the contact area of ​​the liquid at the front surface 211 of the impeller 20, which contributes to improving the efficiency of the liquid flowing from the intake passage 31 to the exhaust passage 32.

[0048] As in connection with the Fig. 3 to 5, in some embodiments, the pump 100 further includes a baffle plate 50 connected to the vanes 22. The baffle plate 50 is arranged on a side of the vanes 22 facing away from the wheel disc 21. A through opening 501 is provided in the center of the baffle plate 50. The position of the through-hole 501 corresponds to the central region 215 of the front side 211 of the wheel disc 21. In particular, the baffle plate 50 rotates with the vanes 22. Since the baffle plate 50 is arranged on the side of the vanes 22 facing away from the impeller 21, the baffle plate 50 prevents the liquid from flowing between the vanes 22 along the front side 211 of the impeller 21, whereby the liquid on the front side 211 of the impeller 21 can flow more concentrated to the edge region of all vanes 22, thereby ensuring efficient operation of the pump 100.Specifically, the through-hole 501 is disposed between the inner end of the intake passage 31 and the central portion 215 of the front side 211 of the wheel disc 21. The fluid flows sequentially through the intake passage 31 and the through-hole 501 and then reaches the central portion 215 of the front side 211 of the wheel disc 21.

[0049] As in Fig. 3 and Fig. 5, the inner surface of the baffle plate 50 is inclined along the direction from the center of the wheel disc 21 to the edge of the wheel disc 21 in the direction close to the wheel disc 21. Therefore, the distance between the inner surface of the baffle plate 50 and the wheel disc 21 gradually decreases in the direction from the center of the wheel disc 21 to the edge of the wheel disc 21. When the liquid flows from the central region 215 to the outer peripheral edge 52 of the wheel disc 21, the liquid can be closer to the front side 211 of the wheel disc 21, whereby the liquid can flow more precisely to the outlet channel 32 guided by the wheel disc 21 and the baffle plate 50. In one embodiment, the baffle plate 50 is trumpet-shaped or funnel-shaped.

[0050] In some embodiments, an inner gap and an outer gap are formed between the baffle plate 50 and the housing 30, as shown in Fig. 3 and Fig. 4, wherein the inner gap and the outer gap are each arranged around the axis of the impeller 20, and the outer gap is arranged to communicate with the inner gap from the outer peripheral side.

[0051] In the axial section of the pump 100, the interior of the inner gap and the interior of the outer gap form a broken line shape.

[0052] Specifically, after the fluid flows from the central portion 215 of the front surface 211 of the impeller 21 to the outer periphery of the impeller 21, a portion of the fluid flows back along the gap between the baffle plate 50 and the housing 30 to the inner end of the intake passage 31. Since the inner gap and the outer gap are located between the baffle plate 50 and the housing 30, and the inner gap and the outer gap are each arranged around the axis of the impeller 20, the fluid must flow through the outer gap and the inner gap at the periphery of the impeller 21 to reach the inner end of the intake passage 31.Since the interior of the inner gap and the interior of the outer gap form a broken line shape, the flow direction of the liquid is greatly adjusted when the liquid flows from the outer to the inner gap, whereby the flow velocity of the liquid decreases significantly and the backflow of the liquid along the outer surface of the baffle plate 50 to the inner end of the suction channel 31 is reduced.

[0053] As in Fig. 3 and Fig. 4, in some embodiments, the housing 30 is provided with a first circumferential transition surface 33. A second circumferential transition surface 53 is provided on a side of the impact plate 50 facing away from the vanes 22. The second circumferential transition surface 53 is axially opposite the first circumferential transition surface 33. In particular, the gap between the first circumferential transition surface 33 and the second circumferential transition surface 53 is a first gap 331. The first circumferential transition surface 33 and the second circumferential transition surface 53 could be annular surfaces. In particular, on a side of the impact plate 50 facing away from the vanes 22, the second circumferential transition surface 53 is located between the inner circumferential edge 51 and the outer circumferential edge 52 of the impact plate 50. In one embodiment, the second circumferential transition surface 53 is arranged near the inner circumferential edge 51.

[0054] As can be seen from the Fig. 3 and Fig. 4, in some embodiments, the housing 30 is provided with a third circumferential transition surface 34 adjacent to the first circumferential transition surface 33 from the outer circumferential side, and the impact plate 50 is provided on the side facing away from the blade 22 with a fourth circumferential transition surface 54 adjacent to the second circumferential transition surface 53 from the outer circumferential side, the fourth circumferential overlay surface 54 being radially opposite the third circumferential transition surface 34.The included angle α1 between the tangential surface of the third circumferential transition surface 34 and the first circumferential transition surface 33 is 90° to 130°, and the included angle α2 between the tangential surface of the fourth circumferential transition surface 54 and the second circumferential transition surface 53 is 230° to 270°, and the included angle α1 is complementary to the included angle α2. In particular, the gap between the third circumferential transition surface 34 and the fourth circumferential transition surface 54 is the second gap 341. The sum of the angle α1 and the angle α2 is 360°. In some embodiments, the third circumferential transition surface 34 is similar to the inner wall surface of a circular through-hole. The fourth circumferential transition surface is comparable to the outer wall of a cylinder.

[0055] In some embodiments, the second gap 341 serves as the outer gap, and the first gap 331 serves as the inner gap. Specifically, the angle formed by the first gap 331 and the second gap 341 is a right angle or slightly larger than 90° in cross-section, allowing for easier assembly between the impeller 20 and the housing 30 while simultaneously significantly rotating the fluid flow direction between the first gap 331 and the second gap 341. This provides greater resistance to the fluid flowing from the first gap 331 to the second gap 341, thereby preventing the fluid from flowing back along the outer surface of the baffle plate 50 toward the inner end of the intake channel 31, which is beneficial for ensuring efficient operation of the pump 100.

[0056] As can be seen from the Fig. 3 and Fig.4, the housing 30 is provided in some embodiments with a fifth circumferential transition surface 36, which is adjacent to the first circumferential transition surface 33 from the inner circumferential side, and the baffle plate 50 is provided on the side facing away from the vanes 22 with a sixth circumferential transition surface 56, which is adjacent to the second circumferential transition surface 53 from the inner circumferential side, wherein the sixth circumferential transition surface 56 is radially opposite the fifth circumferential transition surface 36 and the angle β1 between the tangential surface of the fifth circumferential transition surface 36 and the first circumferential transition surface 33 is between 230° and 270° and the angle β2 between the tangential surface of the sixth circumferential transition surface 56 and the second circumferential transition surface 53 90° to 130° and the angle β1 is complementary to the angle β2.In particular, the gap between the fifth circumferential transition surface 36 and the sixth circumferential transition surface 56 is the second gap 341. The sum of the angle β1 and the angle β2 is 360°. In some embodiments, the fifth circumferential transition surface 36 is similar to the inner wall surface of a circular through-hole. The sixth circumferential transition surface resembles the outer wall of a cylinder.

[0057] In some embodiments, the first gap 331 serves as the outer gap, and the third gap 361 serves as the inner gap. Specifically, the angle formed by the first gap 331 and the third gap 361 is a right angle or slightly larger than 90° in cross-section, allowing for easier assembly between the impeller 20 and the housing 30 while simultaneously significantly rotating the fluid flow direction between the first gap 331 and the third gap 361. This provides greater resistance to the fluid flowing from the first gap 331 to the second gap 341, thereby preventing the fluid from flowing back along the outer surface of the baffle plate 50 toward the inner end of the intake channel 31, which is beneficial for ensuring efficient operation of the pump 100.

[0058] The embodiments described above serve only to illustrate the present invention and do not represent a limitation on the scope of the invention. Those skilled in the art will recognize that various modifications and further developments of the technical solutions of the present invention are possible without departing from the essence of the invention, all such modifications and further developments falling within the scope of the appended claims.

Claims

[1] Impeller (20) comprising a wheel disc (21) having a front side (211) and a rear side (212), the front side (211) and the rear side (212) being opposite each other along the axial direction, characterized by that the impeller (20) comprises: a plurality of grooves (213) arranged on the rear side (212) of the wheel disc (21), the grooves (213) being recessed relative to the surface of the rear side (212), one end of the interior of the groove (213) being arranged closer to the outer peripheral surface of the wheel disc (21) than the other end, the plurality of grooves (213) being spaced apart from one another along the circumference of the wheel disc (21); and a plurality of vanes (22) formed towards the front side (211) of the wheel disc (21), the vanes (22) being distributed along the circumferential direction. [2] The impeller (20) according to claim 1, wherein a radial distance between one end of the interior of the grooves (213) and the other end is greater than a cross-sectional width of the grooves (213) perpendicular to the radial direction. [3] Impeller (20) according to claim 2, wherein the grooves (213) are arranged so as to extend radially along the wheel disc (21), and / or the grooves (213) have a circumferentially curved shape along the direction from the center of the wheel disc to the edge of the wheel disc (211), and / or the grooves (213) have a circumferentially inclined shape along the direction from the center of the wheel disc (21) to the edge of the wheel disc (21), and / or the grooves have a wavy transition shape along the direction from the center of the wheel disc (21) to the edge of the wheel disc (21). [4] Impeller (20) according to claim 1, wherein one end of the interior space of at least one of the grooves (213) extends to the edge of the wheel disc (21). [5] Impeller (20) according to claim 1, wherein the cross section of the interior of the grooves (213) perpendicular to the radial direction is rectangular and / or the cross section of the interior of the grooves perpendicular to the radial direction is semicircular and / or the cross section of the interior of the grooves (213) perpendicular to the radial direction is trapezoidal. [6] Impeller (20) according to claim 1, wherein it has a plurality of projections (23) connected to the rear side (212) of the wheel disc (21) and extending in a direction away from the front side (211). [7] Impeller (20) according to claim 6, wherein the projection (23) extends from the bottom of the grooves (213) in a direction away from the front side (211) and / or wherein the projections (23) extend from the surface of the back side (212) in a direction away from the front side (211). [8] Pump (100), characterized bythat it comprises an impeller (20) according to one of claims 1 to 7. [9] Pump (100) according to claim 8, comprising a baffle plate (50) connected to the vanes (22), the baffle plate (50) being arranged on the side of the vanes (22) facing away from the wheel disc (21), a flow opening (501) being provided in the center of the baffle plate (50), the position of the flow opening (501) corresponding to the central region of the front side (211). [10] Pump (100) according to claim 9, wherein the pump (100) also comprises a housing (30), the impeller (20) is arranged in the housing (30), and an inner gap and an outer gap are formed between the baffle plate (50) and the housing (30), wherein the inner gap and the outer gap are each arranged around the axis of the impeller, the outer gap is connected to the inner gap from the outer peripheral side, and the interior of the inner gap and the interior of the outer gap form a broken line shape in the axial section of the pump (100).

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