Impeller and pump

Abstract

The utility model relates to an impeller and a pump. The impeller comprises a wheel disc and main blades. The wheel disc has a face side and a back side. The surface side and the back side are arranged back to back along the axial direction. A groove is formed in the back side of the wheel disc. The groove is recessed from the surface of the back side. And one end of the inner space of the groove is close to the periphery of the wheel disc relative to the other end. The grooves are distributed in the circumferential direction of the wheel disc at intervals. The main blades are connected to the surface side of the wheel disc. The multiple main blades are distributed in the circumferential direction. And the fluid in the groove is extruded by the inner side wall of the groove. The fluid near the back side surface of the wheel disc flows towards the periphery, so that the fluid on the back side of the wheel disc is also emptied to a certain extent, and the pressure intensity of the fluid on the back side of the wheel disc is reduced. As the pressure on the back side of the wheel disc is synchronously reduced, the axial deflection pressure of fluid borne by the impeller is reduced, the axial pressure at the friction contact position of the supporting assembly is prevented from being too large, the friction force and friction loss in the pump are effectively controlled, and it is guaranteed that the pump has high working efficiency and long service life.

Description

Technical Field

[0001] The present application relates to the technical field of pumps, and in particular to an impeller and a pump. Background Art

[0002] A pump is a machine that transports fluids or pressurizes fluids. It transfers the mechanical energy of the prime mover or other external energy to the fluid, increasing the energy of the fluid. Pumps can be used to transport fluids such as water, oil, acid and alkali liquids, emulsions, suspensions and liquid metals, as well as liquid-gas mixtures and suspended solids. Some pumps use an electric motor to drive the impeller to rotate, so as to generate negative pressure in the pump to continuously suck in and discharge fluids.

[0003] The impeller is rotatably supported by the support. Blades are provided on one side of the impeller. The rotor of the 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 blades is relatively high, and the fluid pressure on one side of the impeller is relatively low compared to the other side. Due to the unbalanced pressure on both sides of the impeller, the impeller is subjected to axial fluid bias pressure. Due to the limiting effect of the support, the axial position of the impeller remains unchanged under the axial fluid bias pressure, but the axial pressure at the friction contact of the support increases, forming a greater friction force, resulting in a decrease in the efficiency of the pump. Utility Model Content

[0004] Based on this, the utility model provides an impeller and a pump which can solve or at least alleviate the above technical problems.

[0005] The utility model provides an impeller, comprising:

[0006] 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 groove is arranged on the back side of the wheel disc; the groove is recessed from the surface of the back side; one end of the inner space of the groove is arranged closer to the outer circumference of the wheel disc than the other end; a plurality of the grooves are spaced apart along the circumference of the wheel disc; and

[0007] The main blades are connected to the surface side of the wheel disc; a plurality of the main blades are distributed along the circumferential direction.

[0008] When the impeller is in use, the wheel disc is connected to the support assembly. The fluid mainly flows on the face side of the wheel disc. When the impeller rotates, the main blades generate thrust on the fluid, and the fluid in the central area of ​​the wheel disc face side is emptied, thereby forming a low-pressure area in this area. Since one end of the internal space of the groove is arranged close to the outer periphery of the wheel disc relative to the other end, when the impeller rotates, the inner side wall of the groove can form a pushing effect on the fluid in the groove. Since the groove is arranged on the back side of the wheel disc, and a plurality of grooves are distributed at intervals along the circumference of the wheel disc, the fluid in the plurality of grooves flows toward the edge. The fluid near the back surface of the wheel disc flows toward the periphery due to the flow trend caused by the grooves, so the fluid on the back side of the wheel disc is also emptied to a certain extent, and the fluid pressure on the back side of the wheel disc decreases. Since the pressure on the back side of the wheel disc decreases synchronously, the axial deflection pressure of the fluid borne by the impeller decreases, avoiding excessive axial pressure at the friction contact of the support assembly, effectively controlling the friction force and friction loss in the pump, and ensuring that the pump has high working efficiency and long service life. At the same time, since the groove is recessed from the surface of the back side, the increase in the overall thickness of the impeller is avoided, which is conducive to maintaining the compactness of the pump structure.

[0009] In one of the embodiments, a radial distance between one end of the inner space of the groove and the other end is greater than a cross-sectional width of the groove perpendicular to the radial direction.

[0010] In one embodiment, the groove is arranged to extend radially along the wheel disc, and / or, along the direction from the center of the wheel disc to the edge of the wheel disc, the groove is in a circumferentially curved shape; and / or, along the direction from the center of the wheel disc to the edge of the wheel disc, the groove is in a circumferentially inclined shape; and / or, along the direction from the center of the wheel disc to the edge of the wheel disc, the groove is in a wavy transition shape.

[0011] In one embodiment, among the plurality of grooves, one end of the inner space of at least one groove extends to the edge of the wheel disc.

[0012] In one embodiment, the cross-section of the inner space of the groove perpendicular to the radial direction is rectangular, and / or the cross-section of the inner space of the groove perpendicular to the radial direction is semicircular, and / or the cross-section of the inner space of the groove perpendicular to the radial direction is trapezoidal.

[0013] In one of the embodiments, a plurality of protrusions are further included, wherein the protrusions are connected to the back side of the wheel disc and extend in a direction away from the front side.

[0014] In one embodiment, the protrusion extends from the bottom surface of the groove in a direction away from the front side; and / or the protrusion protrudes outward from the surface of the back side in a direction away from the front side.

[0015] The utility model also provides a pump, comprising the impeller of any one of the above embodiments.

[0016] In one of the embodiments, it also includes a baffle plate connected to the main blade; the baffle plate is arranged on the side of the main blade facing away from the wheel disc; a flow hole is provided in the middle of the baffle plate; the position of the flow hole corresponds to the central area of ​​the wheel disc surface side.

[0017] In one of the embodiments, an inner gap and an outer gap are respectively formed between the baffle plate and the shell; the inner gap and the outer gap are respectively arranged around the axis of the impeller; the outer gap is connected with the inner gap from the outer peripheral side; on the axial section of the pump, the internal space of the inner gap and the internal space of the outer gap form a broken line shape. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] Figure 1 It is a three-dimensional schematic diagram of a pump according to an embodiment of the present application.

[0019] Figure 2 for Figure 1 A perspective cutaway view of the pump is shown.

[0020] Figure 3 for Figure 1 A plan cross-sectional view of the pump is shown.

[0021] Figure 4 for Figure 3 An enlarged view of point A of the pump is shown.

[0022] Figure 5 for Figure 2 A three-dimensional schematic diagram of the impeller and baffle of the pump shown is shown separated.

[0023] Figure 6 for Figure 5 The impeller shown is a three-dimensional schematic diagram at another angle.

[0024] Figure 6a for Figure 6 A top view of the impeller is shown.

[0025] Figure 6b for Figure 6a The impeller shown is a three-dimensional cross-sectional view formed along the AA direction.

[0026] Figure 7 It is a three-dimensional schematic diagram of the impeller of the second embodiment of the present application.

[0027] Figure 8 It is a three-dimensional schematic diagram of an impeller according to the third embodiment of the present application.

[0028] Fig. 9 It is a three-dimensional schematic diagram of the impeller of the fourth embodiment of the present application.

[0029] Fig.10 It is a three-dimensional schematic diagram of the impeller of the fifth embodiment of the present application.

[0030] Fig.10a for Fig.10 A top view of the impeller is shown.

[0031] Fig.10b for Fig.10a The impeller shown is a three-dimensional cross-sectional view formed along the BB direction.

[0032] Fig.11 It is a three-dimensional schematic diagram of the impeller of the sixth embodiment of the present application.

[0033] Fig.12 It is a three-dimensional schematic diagram of the impeller of the seventh embodiment of the present application.

[0034] Figure numerals: 100, pump; 20, impeller; 21, wheel disc; 211, face side; 212, back side; 213, groove; 214, inner wall; 215, central area; 22, first blade; 23, bump; 24, second blade; 30, shell; 31, suction channel; 32, discharge channel; 33, first circumferential transition surface; 331, first gap; 34, third circumferential transition surface; 341, second gap; 36, fifth circumferential transition surface; 361, third gap; 40, support assembly; 41, support rod; 42, limit plate; 43, fastener; 50, baffle; 501, flow hole; 51, inner peripheral edge; 52, outer peripheral edge; 53, second circumferential transition surface; 54, fourth circumferential transition surface; 56, sixth circumferential transition surface. DETAILED DESCRIPTION

[0035] The technical solution of the present application will be described clearly and completely below in conjunction with the accompanying drawings. Obviously, the described embodiments are part of the embodiments of the present application, rather than all of the embodiments. Based on the embodiments in the present application, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present application.

[0036] In the description of the present application, it should be noted that the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc., indicating the orientation or positional relationship, are based on the orientation or positional relationship shown in the drawings, and are only for the convenience of describing the present application and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as limiting the present application. In addition, the terms "first", "second", and "third" are used for descriptive purposes only, and cannot be understood as indicating or implying relative importance.

[0037] In the description of this application, it should be noted that, unless otherwise clearly specified and limited, the terms "installed", "connected", and "connected" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, an integral connection, a mechanical connection, an electrical connection, a direct connection, an indirect connection through an intermediate medium, or the internal connection of two components. For ordinary technicians in this field, the specific meanings of the above terms in this application can be understood according to specific circumstances.

[0038] The technical solution provided by the embodiments of the present application is described below in conjunction with the accompanying drawings.

[0039] Combination Figures 1 to 3 As shown, the present application provides a pump 100, which is used to suck air, water, oil and other fluids to transport the fluid from one container to another container or the external environment. For example, water is discharged from a pool to the outside of the pool. In one embodiment, the pump 100 is a centrifugal drainage pump, which can be used for washing machines and dishwashers. It can be understood that the pump 100 can also be used to suck and discharge fluids such as gases with fluidity.

[0040] Combination Figure 2 As shown, the pump 100 includes a housing 30 and an impeller 20 accommodated in the housing 30. The impeller 20 is rotatably arranged in the housing 30. In some embodiments, the housing 30 is provided with a suction channel 31 and a discharge channel 32. The inner port of the suction channel 31 faces the center position of the impeller 20. The inner port of the discharge channel 32 faces the edge position of the impeller 20.

[0041] In some embodiments, in combination Figure 2 and Figure 3 As shown, the pump 100 also includes a support assembly 40, which is used 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 mounted on the outer periphery of the support rod 41 and is rotatably arranged relative to the support rod 41. More specifically, the support rod 41 is fixedly arranged in the housing 30, and the support rod 41 maintains a fixed angle relative to the housing 30. In one embodiment, the support assembly 40 also includes a limit plate 42 and a fastener 43. The limit plate 42 is arranged on the side of the impeller 20 close to the suction channel 31. The fastener 43 is threadedly fixed to one end of the support rod 41, and the fastener 43 fixes the limit plate 42 to one end of the support rod 41. Since the limit plate 42 is fixed to the side of the impeller 20 close to the suction channel 31, the impeller 20 can be prevented from moving close to the suction channel 31. More specifically, the limit plate 42 is a friction pair.

[0042] In some embodiments, the pump 100 further comprises a driving member for driving the impeller 20 to rotate. In one embodiment, the driving member is a motor, and a rotor of the driving member is connected to the impeller 20.

[0043] Combination Figures 5 to 12 As shown, the present application also provides an impeller 20, which includes a wheel disc 21 and main blades 22. The wheel disc 21 has a face side 211 and a back side 212. The face side 211 and the back side 212 are arranged opposite to each other in the axial direction. A groove 213 is provided on the back side 212 of the wheel disc 21. The groove 213 is recessed from the surface of the back side 212. One end of the internal space of the groove 213 is arranged close to the outer periphery of the wheel disc 21 relative to the other end. A plurality of grooves 213 are distributed at intervals along the circumference of the wheel disc 21. The main blades 22 are connected to the face side 211 of the wheel disc 21. A plurality of main blades 22 are distributed along the circumference.

[0044] Specifically, when the impeller 20 is in use, the wheel disc 21 is connected to the support assembly 40. The fluid mainly flows on the face side 211 of the wheel disc 21. When the impeller 20 rotates, the main blades 22 generate thrust on the fluid, and the fluid in the central area 215 of the face side 211 of the wheel disc 21 is drained, thereby forming a low-pressure area in this area. Since one end of the internal space of the groove 213 is arranged closer to the outer periphery of the wheel disc 21 relative to the other end, when the impeller 20 rotates, the inner side wall 214 of the groove 213 can form a pushing effect on the fluid in the groove 213. Since the groove 213 is arranged on the back side 212 of the wheel disc 21, and a plurality of grooves 213 are distributed at intervals along the circumference of the wheel disc 21, the fluid in the plurality of grooves 213 flows toward the outer edge. The fluid near the surface of the back side 212 of the wheel disc 21 flows toward the periphery due to the flow tendency caused by the grooves 213, so the fluid on the back side 212 of the wheel disc 21 is also drained to a certain extent, and the fluid pressure on the back side 212 of the wheel disc 21 decreases.

[0045] Since the pressure on the back side 212 of the wheel disc 21 decreases synchronously, the axial bias pressure of the fluid borne by the impeller 20 decreases, thereby avoiding excessive axial pressure at the friction contact of the support assembly 40, effectively controlling the friction force and friction loss in the pump 100, and ensuring that the pump 100 has high working efficiency and a long service life. At the same time, since the groove 213 is set in a concave position from the surface of the back side 212, compared with the situation where a raised blade is set on the back side 212 of the wheel disc 21 and the raised blade is used to squeeze the fluid, the groove 213 set in a concave position relative to the surface of the back side 212 can produce an extrusion effect on the fluid, thereby avoiding the need to set a raised blade on the back side 212 of the wheel disc 21, and preventing the overall thickness of the impeller 20 from increasing. There is no need to increase the reserved space in the thickness direction of the impeller 20 inside the housing 30, thereby saving the internal space of the housing 30, which is conducive to maintaining the compactness of the structure of the pump 100.

[0046] In some embodiments, in combination Figure 6 As shown, the bottom surface of the groove 213 transitions to the surface of the back side 212 through the inner side wall 214. The inner side wall 214 and the bottom surface together form the boundary of the inner space of the groove 213. In some embodiments, the inner side wall 214 transitions from one end of the inner space of the groove 213 to the other end of the inner space of the groove 213. In some embodiments, one inner side wall 214 of the groove 213 is arranged opposite to the other inner side wall 214 of the groove 213 along the circumferential direction.

[0047] In some embodiments, the distance between one end of the inner space of the groove 213 and the other end along the radial direction is greater than the cross-sectional width of the groove 213 perpendicular to the radial direction, so that the length of the inner side wall 214 of the groove 213 is relatively large, which is conducive to increasing the area of ​​the inner side wall 214 of the groove 213. At the same time, the curvature of a single groove 213 can be reduced, which is conducive to increasing the distribution density of the groove 213 and improving the squeezing effect of the wheel 21 on the fluid on the back side 212. It can be understood that the cross-sectional width of the groove 213 perpendicular to the radial direction is close to the circumferential width of the groove 213.

[0048] In some embodiments, one end of the inner space of the groove 213 intersects with a circle whose center intersects with the axis of the wheel disc 21. The other end of the inner space of the groove 213 intersects with another circle whose center intersects with the axis of the wheel disc 21. The radial distance between one end of the inner space of the groove 213 and the other end is the radius difference between the two circles.

[0049] In some embodiments, in combination Figure 2 and Figure 3 As shown, the limiting plate 42 is arranged on the face side 211 of the wheel disc 21. As the pressure on the back side 212 of the wheel disc 21 decreases synchronously, the axial bias pressure of the fluid borne by the impeller 20 decreases, thereby reducing the pressure and friction between the wheel disc 21 and the limiting plate 42, and reducing the wear of the wheel disc 21 and the limiting plate 42.

[0050] In some embodiments, in combination Figure 2 and Figure 3 As shown, the inner port of the suction channel 31 faces the central area 215 of the face side 211 of the wheel disk 21. The inner port of the discharge channel 32 faces the outer periphery of the main blades 22 from one angle. After the fluid enters the suction channel 31, it flows into the central area 215 of the face side 211 of the wheel disk 21 from the inner port of the suction channel 31. The rotation of the main blades 22 allows the fluid in the central area 215 to flow to the peripheral positions of all the main blades 22. In some embodiments, the discharge channel 32 is connected to the peripheral areas of all the main blades 22. The fluid in the peripheral areas of all the main blades 22 enters the inner port of the discharge channel 32.

[0051] In some embodiments, in combination Figure 6 As shown, the groove 213 is arranged to extend along the radial direction of the wheel disc 21. Specifically, the inner space of the groove 213 is in the shape of an elongated strip, and the length direction of the inner space is arranged to coincide with the radial direction of the wheel disc 21. More specifically, any radial direction of the wheel disc 21 points to the rotation axis of the impeller 20.

[0052] In some embodiments, in combination Figure 7 As shown, the groove 213 is circumferentially curved along the direction from the center of the wheel disc 21 to the edge of the wheel disc 21. Specifically, the edge of the groove 213 is arc-shaped. Further, the curvature direction of the groove 213 is the same as the curvature direction of the main blade 22.

[0053] In some embodiments, the groove 213 is 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 groove 213 is in an oblique line shape, and the angle between the edge of the groove 213 and any radius line of the wheel disc 21 is greater than zero.

[0054] In some embodiments, in combination Figure 8 As shown, the groove 213 is in a wave transition shape from the center of the wheel disc 21 to the edge of the wheel disc 21. Specifically, the edge of the groove 213 is in a wave shape.

[0055] In some embodiments, one end of the inner space of the groove 213 is radially spaced from the edge of the wheel disc 21 , and the other end is relatively far away from the edge of the wheel disc 21 .

[0056] In some embodiments, the plurality of grooves 213 on the wheel disc 21 may be in different shapes. In one embodiment, a portion of the grooves 213 of the wheel disc 21 extend radially, another portion of the grooves 213 are circumferentially curved, and another portion of the grooves 213 have oblique edges.

[0057] In some embodiments, in combination Figure 6 As shown, among the plurality of grooves 213, one end of the internal space of at least one groove 213 extends to the edge of the wheel disc 21. Specifically, the other end of the internal space of the groove 213 is located relatively far away from the outer periphery of the wheel disc 21. Since one end of the internal 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 will not be blocked by the wall of the groove 213 when flowing radially toward the periphery, thereby reducing the resistance of the fluid, improving the smoothness of the fluid when flowing toward the periphery, and ensuring the fluid emptying effect on the back side 212 of the wheel disc 21.

[0058] In some embodiments, one end of the inner space of all the grooves 213 extends to the edge of the wheel disc 21 .

[0059] In some embodiments, in combination Figure 6 , Figure 6a and Figure 6b As shown, the cross section of the inner space of the groove 213 perpendicular to the radial direction is rectangular. More specifically, the edge of the cross section of the groove 213 perpendicular to the radial direction is open, and the direction of the opening is opposite to the face side 211 of the wheel disc 21. In the case where the cross section of the inner space of the groove 213 perpendicular to the radial direction is rectangular, the inner side wall 214 of the groove 213 is vertically arranged relative to the surface of the back side 212 of the wheel disc 21, which is conducive to improving the thrust of the inner side wall 214 of the groove 213 on the fluid.

[0060] In other embodiments, in combination Fig.10 , Fig.10a and Fig.10b As shown, the cross section of the inner space of the groove 213 perpendicular to the radial direction is semicircular. Fig.12 As shown, the cross section of the inner space of the groove 213 perpendicular to the radial direction is trapezoidal. More specifically, the cross section of the inner space of the groove 213 perpendicular to the radial direction can also be in other shapes that are conducive to the fluid flowing into the groove 213.

[0061] In some embodiments, in combination Figure 6b and Fig.10b As shown, for the cross section of the inner space of the groove 213 perpendicular to the radial direction, the cross section is parallel to the axis of the wheel disc 21 , and the cross section is spaced apart from the axis of the wheel disc 21 .

[0062] In some embodiments, the cross-sectional shape of the inner space of several grooves 213 perpendicular to the radial direction is selected from one or more of a rectangle, a semicircle and a trapezoid. Understandably, for multiple grooves 213, the cross-sectional shape of the inner space of some grooves 213 perpendicular to the radial direction may be a rectangle, and the cross-sectional shape of the inner space of another part of the grooves 213 perpendicular to the radial direction may be a semicircle. Alternatively, the cross-sectional shape of the inner space of some grooves 213 perpendicular to the radial direction may be a rectangle, the cross-sectional shape of the inner space of some grooves 213 perpendicular to the radial direction may be a semicircle, and the cross-sectional shape of the inner space of another part of the grooves 213 perpendicular to the radial direction may be a trapezoid.

[0063] In some embodiments, in combination Fig.11As shown, the impeller 20 further includes a plurality of protrusions 23, which are connected to the back side 212 of the wheel disc 21 and extend in a direction away from the front side 211. Specifically, the inner side wall 214 of the groove 213 and the side of the protrusion 23 simultaneously exert a pushing effect on the fluid, thereby increasing the action area between the impeller 20 and the fluid, which is beneficial to further increase the thrust of the impeller 20 on the fluid on the back side 212 of the wheel disc 21. Specifically, in the direction from the center of the wheel disc 21 along the shortest path to the edge of the wheel disc 21, the shape change of the protrusion 23 corresponds to the shape change of the groove 213, so that the two sides of the protrusion 23 along the circumferential direction are evenly spaced from the inner side wall 214 of the groove 213, so that the side of the protrusion 23 and the inner side wall 214 of the groove 213 simultaneously exert thrust on the fluid.

[0064] In some embodiments, the protrusion 23 extends from the bottom surface of the groove 213 in a direction away from the face side 211, thereby reducing the protrusion height of the protrusion 23 relative to the surface of the back side 212 of the wheel disc 21, which is beneficial to controlling the overall thickness of the impeller 20. In some embodiments, the protrusion 23 protrudes outward from the surface of the back side 212 in a direction away from the face side 211, which is beneficial to increase the area of ​​the side surface of the protrusion 23 and increase the force on the fluid.

[0065] In some other embodiments, the protrusion 23 extends from the surface of the back side 212 of the wheel disc 21 in a direction away from the front side 211 .

[0066] In some embodiments, in combination Figure 5 As shown, the main blades 22 are circumferentially curved along the direction from the center of the wheel disc 21 to the edge of the wheel disc 21. In some embodiments, the main blades 22 extend from the edge of the central area 215 to the edge of the wheel disc 21.

[0067] In some embodiments, in combination Figure 5 As shown, the main blades include a first blade 22 and a second blade 24; the first blade 22 and the second blade 24 are respectively connected to the face side 211 of the wheel disc 21; a plurality of first blades 22 are distributed along the circumference of the wheel disc 21. A second blade 24 is arranged between adjacent first blades 22. The radial length of the second blade 24 is smaller than the radial length of the main blade 22, and the center of the second blade 24 is arranged close to the outer periphery of the wheel disc 21 relative to the center of the main blade 22, so that the contact area of ​​the impeller 20 with the fluid on the opposite side 211 can be increased, which is conducive to improving the efficiency of the fluid flowing from the suction channel 31 to the discharge channel 32.

[0068] In some embodiments, in combination Figures 3 to 5As shown, the pump 100 also includes a baffle 50 connected to the main blade 22. The baffle 50 is arranged on the side of the main blade 22 facing away from the wheel disc 21. A through hole 501 is arranged in the middle of the baffle 50. The position of the through hole 501 corresponds to the central area 215 of the face side 211 of the wheel disc 21. Specifically, the baffle 50 rotates with the main blade 22. Since the baffle 50 is arranged on the side of the main blade 22 facing away from the wheel disc 21, the baffle 50 prevents the fluid between the main blades 22 from flowing along the direction of the face side 211 of the wheel disc 21, allowing the fluid on the face side 211 of the wheel disc 21 to flow more concentratedly to the peripheral area of ​​all the main blades 22, thereby ensuring the working efficiency of the pump 100. More specifically, the through hole 501 is arranged between the inner port of the suction channel 31 and the central area 215 of the face side 211 of the wheel disc 21. The fluid passes through the suction channel 31 and the through-hole 501 in sequence, and then reaches the central area 215 of the face side 211 of the wheel disc 21 .

[0069] In some embodiments, in combination Figure 3 and Figure 5 As shown, along the direction from the center of the wheel disc 21 to the edge of the wheel disc 21, the inner surface of the baffle plate 50 is inclined toward the direction close to the wheel disc 21. Therefore, in the direction from the center of the wheel disc 21 to the edge of the wheel disc 21, the distance between the inner surface of the baffle plate 50 and the wheel disc 21 is gradually reduced. When the fluid flows from the central area 215 of the wheel disc 21 to the outer peripheral edge 52, the fluid can be closer to the surface side 211 of the wheel disc 21, so that the fluid can flow more accurately to the discharge channel 32 under the guidance of the wheel disc 21 and the baffle plate 50. In one embodiment, the baffle plate 50 is trumpet-shaped or funnel-shaped.

[0070] In some embodiments, in combination Figure 3 and Figure 4 As shown, an inner gap and an outer gap are formed between the baffle plate 50 and the housing 30 respectively; the inner gap and the outer gap are respectively 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. On the axial section of the pump 100, the inner space of the inner gap and the inner space of the outer gap form a broken line shape.

[0071] Specifically, after the fluid flows from the central area 215 of the face side 211 of the impeller 21 to the periphery of the impeller 21, part of the fluid flows back to the inner port of the suction channel 31 along the space between the baffle plate 50 and the shell 30. Since the inner gap and the outer gap are located between the baffle plate 50 and the shell 30, and the inner gap and the outer gap are respectively arranged around the axis of the impeller 20, the fluid on the periphery of the impeller 21 needs to pass through the outer gap and the inner gap to flow to the inner port of the suction channel 31. Since the internal space of the inner gap and the internal space of the outer gap form a broken line shape, when the fluid flows from the outer gap to the inner gap, the flow direction of the fluid is greatly adjusted, causing the flow velocity of the fluid to drop significantly, reducing the fluid from flowing back to the inner port of the suction channel 31 along the outer surface of the baffle plate 50.

[0072] In some embodiments, in combination Figure 3 and Figure 4 As shown, the housing 30 is provided with a first circumferential transition surface 33. A second circumferential transition surface 53 is provided on the side of the baffle plate 50 facing away from the main blade 22, and the second circumferential transition surface 53 is arranged opposite to the first circumferential transition surface 33 in the axial direction. Specifically, 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 can be annular surfaces. Specifically, on the side of the baffle plate 50 facing away from the main blade 22, the second circumferential transition surface 53 is between the inner peripheral edge 51 and the outer peripheral edge 52 of the baffle plate 50. In one embodiment, the second circumferential transition surface 53 is arranged close to the inner peripheral edge 51.

[0073] In some embodiments, in combination Figure 3 and Figure 4 As shown, the shell 30 is provided with a third circumferential transition surface 34, and the third circumferential transition surface 34 is arranged adjacent to the first circumferential transition surface 33 from the outer peripheral side. The baffle plate 50 is provided with a fourth circumferential transition surface 54 on the side facing away from the main blade 22, and the fourth circumferential transition surface 54 is arranged adjacent to the second circumferential transition surface 53 from the outer peripheral side. The fourth circumferential transition surface 54 is arranged opposite to the third circumferential transition surface 34 in the radial direction. The angle α1 between the tangent surface of the third circumferential transition surface 34 and the first circumferential transition surface 33 ranges from 90° to 130°, and the angle α2 between the tangent surface of the fourth circumferential transition surface 54 and the second circumferential transition surface 53 ranges from 230° to 270°, and the angle α1 and the angle α2 complement each other. Specifically, 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 round through hole, and the fourth circumferential transition surface is similar to the outer wall surface of a cylinder.

[0074] In some embodiments, the second gap 341 is used as an outer gap, and the first gap 331 is used as an inner gap. Specifically, the angle formed by the first gap 331 and the second gap 341 in the cross section is a right angle or slightly greater than 90°, so that the assembly between the impeller 20 and the housing 30 is facilitated, and the flow direction of the fluid between the first gap 331 and the second gap 341 can be greatly turned, and a greater resistance is generated for the fluid flowing from the first gap 331 to the second gap 341, so as to prevent the fluid from flowing back along the outer surface of the baffle 50 to the inner port of the suction channel 31, which is conducive to ensuring the working efficiency of the pump 100.

[0075] In some embodiments, in combination Figure 3 and Figure 4 As shown, the housing 30 is provided with a fifth circumferential transition surface 36, which is arranged adjacent to the first circumferential transition surface 33 from the inner circumferential side, and the baffle 50 is provided with a sixth circumferential transition surface 56 on the side facing away from the main blade 22, which is arranged adjacent to the second circumferential transition surface 53 from the inner circumferential side, and the sixth circumferential transition surface 56 is arranged radially opposite to the fifth circumferential transition surface 36, and the angle β1 between the tangent surface of the fifth circumferential transition surface 36 and the first circumferential transition surface 33 is in the range of 230° to 270°, and the angle β2 between the tangent surface of the sixth circumferential transition surface 56 and the second circumferential transition surface 53 is in the range of 90° to 130°, and the angle β1 and the angle β2 complement each other. Specifically, 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 round through hole, and the sixth circumferential transition surface is similar to the outer wall surface of a cylinder.

[0076] In some embodiments, the first gap 331 is used as an outer gap, and the third gap 361 is used as an inner gap. Specifically, the angle formed by the first gap 331 and the third gap 361 in the cross section is a right angle or slightly greater than 90°, so that the assembly between the impeller 20 and the housing 30 is facilitated, and the flow direction of the fluid between the first gap 331 and the third gap 361 can be greatly turned, and a greater resistance is generated for the fluid flowing from the first gap 331 to the third gap 361, so as to prevent the fluid from flowing back along the outer surface of the baffle 50 to the inner port of the suction channel 31, which is conducive to ensuring the working efficiency of the pump 100.

[0077] The above implementation modes are merely descriptions of the preferred implementation modes of the present application, and are not intended to limit the scope of the present application. Without departing from the design spirit of the present application, various modifications and improvements made to the technical solutions of the present application by ordinary engineering and technical personnel in the field shall fall within the protection scope determined by the claims of the present application.

Claims

1. An impeller, characterized in that: include: 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 arranged recessed from the surface of the back side; one end of the inner space of the groove is arranged closer to the outer circumference of the wheel disc than the other end; the plurality of grooves are spaced apart along the circumference of the wheel disc; and The main blades are connected to the surface side of the wheel disc; a plurality of the main blades are distributed along the circumferential direction.

2. The impeller according to claim 1, characterized in that: A distance between one end of the inner space of the groove and the other end in a radial direction is greater than a cross-sectional width of the groove perpendicular to the radial direction.

3. The impeller according to claim 1, characterized in that: The groove is arranged to extend radially along the wheel disc, and / or, along the direction from the center of the wheel disc to the edge of the wheel disc, the groove is in a circumferentially curved shape; and / or, along the direction from the center of the wheel disc to the edge of the wheel disc, the groove is in a circumferentially inclined shape; and / or, along the direction from the center of the wheel disc to the edge of the wheel disc, the groove is in a wavy transition shape.

4. The impeller according to claim 1, characterized in that: Among the plurality of grooves, one end of the inner space of at least one groove extends to the edge of the wheel disc.

5. The impeller according to claim 1, characterized in that: The cross section of the inner space of the groove perpendicular to the radial direction is rectangular, and / or the cross section of the inner space of the groove perpendicular to the radial direction is semicircular, and / or the cross section of the inner space of the groove perpendicular to the radial direction is trapezoidal.

6. The impeller according to claim 1, characterized in that: It also includes a plurality of protrusions, which are connected to the back side of the wheel disc and extend in a direction away from the front side.

7. The impeller according to claim 6, characterized in that The protrusion extends from the bottom surface of the groove in a direction away from the front side; and / or the protrusion protrudes outward from the surface of the back side in a direction away from the front side.

8. A pump, characterized in that: Comprising an impeller as claimed in any one of claims 1 to 7.

9. The pump according to claim 8, characterized in that It also includes a baffle plate connected to the main blade; the baffle plate is arranged on the side of the main blade facing away from the wheel disc; a flow hole is arranged in the middle of the baffle plate; the position of the flow hole corresponds to the central area of ​​the wheel disc surface side.

10. The pump according to claim 9, characterized in that The pump also includes a casing, the impeller is accommodated in the casing, an inner gap and an outer gap are respectively formed between the baffle plate and the casing; the inner gap and the outer gap are respectively arranged around the axis of the impeller; the outer gap is connected to the inner gap from the outer peripheral side; on the axial section of the pump, the internal space of the inner gap and the internal space of the outer gap form a broken line shape.

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