Pumping device

Abstract

To ensure welding strength between a flange part and an impeller that constitute an impeller of a pump device.SOLUTION: An impeller 25 of a pump device 1 comprises an impeller 24 fixed to a flange part 45 of a rotor member 40. The impeller 24 comprises a plurality of blade parts 261 that protrudes from a disc part 26 facing the flange part 45 in an axial direction. Each tip of the plurality of blade parts 261 is provided with a rib 263 inserted into a fixing groove 44 provided in the flange part 45. The rib 263 is provided with an axial gap between a tip of an inner peripheral portion 266 including a radially inner end part and a bottom surface of the fixing groove 44. A tip of the other side L2 in the axial direction of an outer peripheral portion 267 including a radially outer end part is provided with a welding part W welded to the fixing groove 44.SELECTED DRAWING: Figure 6

Description

Technical Field

[0001] The present invention relates to a pump device that rotates an impeller by a motor.

Background Art

[0002] Patent Document 1 describes a pump device that rotates an impeller disposed in a pump chamber by a motor. The motor includes a rotor that rotates integrally with the impeller. The rotor includes a resin holding member that holds a bearing (radial bearing) through which a fixed shaft passes. The holding member has a cylindrical shape with a flange, and the bearing is press-fitted inside the holding member.

[0003] In the pump device of Patent Document 1, an impeller that rotates integrally with the rotor is configured by fixing an impeller to a flange portion (flange portion) provided at the upper end of the holding member. The impeller includes a disk portion that faces the flange portion in the axial direction and a blade portion that protrudes from the disk portion toward the flange portion, and the tip of the blade portion is fixed to the flange portion.

Prior Art Documents

Patent Documents

[0004]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0005] In a structure in which an impeller is formed by fixing an impeller to a flange portion provided on a holding member that holds a radial bearing, a fixing structure has been proposed in which a groove is formed in the flange portion and the tip of the blade portion is inserted into the groove and fixed by welding.

[0006] However, when molding the rotor retaining member from resin, the flange portion warps into an umbrella shape after molding. If the tip of the blade portion is inserted into the groove of the deformed flange portion and fixed, the flange portion and the blade portion interfere excessively with each other on the inner circumference of the impeller, while on the outer circumference of the impeller, a gap is created between the flange portion and the blade portion, or the amount of welding is insufficient. Since the outer circumference of the impeller is subjected to high fluid pressure, insufficient welding results in insufficient strength, and there is a risk that the welded portion will peel off during operation.

[0007] In view of the above, the object of the present invention is to ensure the welding strength between the flange portion and the impeller at the outer circumference of the impeller in a pump device equipped with an impeller in which the impeller is fixed to a resin flange portion. [Means for solving the problem]

[0008] To solve the above problems, the pump device of the present invention comprises a motor having a rotor and a stator, and an impeller disposed in a pump chamber provided on one side of the stator in the axial direction when the direction along the rotation axis of the rotor is defined as the axial direction, and which rotates integrally with the rotor, wherein the rotor comprises a rotor member having a cylindrical magnet holder and a drive magnet fixed to the outer circumferential surface of the magnet holder, and the impeller comprises a flange portion provided at one end of the rotor member in the axial direction and a vane fixed to the flange portion from one side in the axial direction, wherein the vane comprises a disc portion facing the flange portion in the axial direction and a plurality of blade portions protruding from the disc portion to the other side in the axial direction, the plurality of blade portions extending radially outward at multiple positions in the circumferential direction centered on the rotation axis, and a rib is provided at the tip of each of the plurality of blade portions on the other side in the axial direction, which is inserted into a fixing groove provided in the flange portion. The rib comprises an inner circumferential portion including the inner end in the radial direction and an outer circumferential portion including the outer end in the radial direction, with an axial gap provided between the other end of the inner circumferential portion in the axial direction and the bottom surface of the fixing groove, and a welded portion welded to the fixing groove is provided at the other end of the outer circumferential portion in the axial direction.

[0009] According to the present invention, the impeller, which is fixed to a flange portion provided at the end of the rotor member to form the impeller, has a blade portion that protrudes from a disc portion, and the tip of the blade portion is provided with a rib that is inserted into a fixing groove provided in the flange portion. By inserting the rib into the fixing groove in this way, deformation of the blade portion due to water pressure can be suppressed. In addition, the reduction in efficiency caused by fluid passing between the tip of the blade portion and the flange portion can be suppressed. Furthermore, the rib inserted into the fixing groove has a shape in which the outer circumference portion is welded to the fixing groove, while the inner circumference portion has a gap between it and the bottom surface of the fixing groove. In this way, even if the flange portion does not take the shape as designed and warps into an umbrella shape, there is little risk of the inner circumference portion of the rib excessively interfering with the bottom surface of the fixing groove, so there is little risk of a lot of welding burrs being generated in the area of ​​excessive interference and protruding from the fixing groove. In addition, as a result of excessive interference by the inner circumference portion of the rib, there is little risk of insufficient insertion of the outer circumference portion of the rib into the fixing groove, resulting in unwelded or insufficient welding strength. Because the outer circumference of the impeller is subjected to high fluid pressure, if the welding strength is insufficient, the blades may peel off from the flange. However, in this configuration, the welding strength of the outer circumference of the blades can be ensured, so there is less risk of the welded joints peeling off even when subjected to high water pressure.

[0010] In the present invention, it is preferable that the welded portion is a flattened portion in which the welding projection protruding from the tip surface of the outer circumference is flattened. By providing a welding projection on the outer circumference in this way, it is possible to avoid insufficient welding on the outer circumference. Furthermore, by not providing a welding projection on the inner circumference, it is possible to avoid excessive interference on the inner circumference.

[0011] In the present invention, each of the plurality of blade portions is provided with a blade portion body that protrudes from the disc portion to the other side in the axial direction, and it is preferable that the plate thickness of the blade portion body is greater than the width of the fixing groove, and the width of the rib protruding from the tip surface of the blade portion body is smaller than the width of the fixing groove. This increases the rigidity of the portion that receives water pressure (blade portion body). In addition, a gap can be secured between the fixing groove and the rib to accommodate welding burrs.

[0012] In the present invention, it is preferable that the rib includes an intermediate portion connecting the inner circumferential portion and the outer circumferential portion, and that the intermediate portion includes a reference surface that abuts against the bottom surface of the fixing groove. By providing a reference surface for axial positioning in the radial intermediate portion in this way, even if the flange portion does not take the shape as designed and warps into an umbrella shape, the inner circumferential portion is less likely to interfere excessively, and the amount of welding in the outer circumferential portion is less likely to be insufficient.

[0013] In the present invention, it is preferable that the tip surface of the inner circumferential portion is a stepped surface recessed on one side in the axial direction relative to the reference surface. This prevents excessive interference of the inner circumferential portion when the reference surface contacts the bottom surface of the fixed groove.

[0014] In the present invention, it is preferable that in at least a portion of the plurality of blade portions, the rib has an intermediate portion connecting the inner circumferential portion and the outer circumferential portion, the intermediate portion has a positioning projection that protrudes to the other side in the axial direction, and the positioning projection fits into a positioning recess provided on the bottom surface of the fixing groove. In this way, even if a gap is provided between the fixing groove and the rib to accommodate welding burrs, the impeller can be positioned in a direction intersecting the axial direction by fitting the positioning projection and the positioning recess. For example, the impeller can be positioned in the circumferential direction. [Effects of the Invention]

[0015] According to the present invention, the impeller, which is fixed to a flange portion provided at the end of the rotor member to form the impeller, has blades protruding from a disc portion, and the tip of the blade is provided with a rib that is inserted into a fixing groove provided in the flange portion. By inserting the rib into the fixing groove in this way, deformation of the blade due to water pressure can be suppressed. In addition, the reduction in efficiency caused by fluid passing between the tip of the blade and the flange portion can be suppressed. Furthermore, the rib inserted into the fixing groove has a shape in which the outer circumference is welded to the fixing groove, while the inner circumference has a gap between it and the bottom surface of the fixing groove. In this way, even if the flange portion does not take the shape as designed and warps into an umbrella shape, there is little risk of the inner circumference of the rib excessively interfering with the bottom surface of the fixing groove, so there is little risk of a lot of welding burrs being generated at the point of excessive interference and protruding from the fixing groove. In addition, as a result of excessive interference by the inner circumference of the rib, there is little risk of insufficient insertion of the outer circumference of the rib into the fixing groove, resulting in unwelded or insufficient welding strength. Because the outer circumference of the impeller is subjected to high fluid pressure, if the welding strength is insufficient, the blades may peel off from the flange. However, in this configuration, the welding strength of the outer circumference of the blades can be ensured, so there is less risk of the welded joints peeling off even when subjected to high water pressure. [Brief explanation of the drawing]

[0016] [Figure 1] This is an external perspective view of a pump device to which the present invention is applied. [Figure 2] Figure 1 is a cross-sectional view of the pump device shown, cut along a plane containing the axis of rotation. [Figure 3] This is an exploded perspective view of the rotor and radial bearings, seen from one side in the axial direction. [Figure 4] This is an exploded perspective view of the rotor and radial bearings, seen from the other side in the axial direction. [Figure 5] This is a perspective view of the rotor component from one side in the axial direction. [Figure 6] This is a cross-sectional view of the rotor, impeller, and radial bearing, cut along a plane containing the axis of rotation (BB position in Figure 7). [Figure 7]It is a cross-sectional view obtained by cutting a rotor, a radial bearing, and a support shaft in a plane perpendicular to the rotation axis (a cross-sectional view taken at the A-A position in FIG. 6). [Figure 8] It is a perspective view of a rotor, an impeller, and a radial bearing as viewed from the other side in the axial direction. [Figure 9] It is a plan view of the impeller as viewed from one side in the axial direction. [Figure 10] It is a perspective view of the impeller as viewed from one side in the axial direction.

Embodiments for Carrying Out the Invention

[0017] Hereinafter, the pump device 1 according to an embodiment of the present invention will be described with reference to the drawings. In the following description, the axial direction means the direction in which the rotation axis L of the motor 10 extends, the radial direction on the inner side and the outer side in the radial direction means the radial direction centered on the rotation axis L, and the circumferential direction means the rotation direction centered on the rotation axis L. Further, the direction in which the rotation axis L extends is defined as the axial direction, one side in the axial direction is defined as L1, and the other side in the axial direction is defined as L2.

[0018] (Overall Configuration) FIG. 1 is an external perspective view of a pump device 1 to which the present invention is applied. FIG. 2 is a cross-sectional view of the pump device 1 shown in FIG. 1 cut in a plane including the rotation axis L. As shown in FIGS. 1 and 2, the pump device 1 includes a case 2 having a suction pipe 21 and a discharge pipe 22 extending to one side L1 in the axial direction, a motor 10 disposed on the other side L2 in the axial direction with respect to the case 2, and an impeller 25 disposed in a pump chamber 20 inside the case 2. The impeller 25 is rotationally driven around the rotation axis L by the motor 10. In the pump device 1 of the present embodiment, the fluid flowing through the pump chamber 20 is a liquid. The pump device 1 is used, for example, under conditions where the environmental temperature and the fluid temperature are likely to change.

[0019] The motor 10 includes an annular stator 3, a rotor 4 disposed inside the stator 3, a resin housing 6 covering the stator 3, and a support shaft 5 that rotatably supports the rotor 4. The support shaft 5 is made of metal or ceramic. The impeller 25 rotates integrally with the rotor 4. As shown in Figure 2, in the pump device 1, the impeller 25 and the pump chamber 20 are located on one side L1 in the axial direction relative to the stator 3.

[0020] As shown in Figure 2, the pump chamber 20 is located between the case 2 and the housing 6. The case 2 constitutes the wall surface 23 on one axial side L1 of the pump chamber 20, and the side wall 29 extending in the circumferential direction. As shown in Figure 1, the suction pipe 21 extends axially from the radial center of the case 2, and the suction pipe 21 extends from the side wall 29 in a direction perpendicular to the rotation axis L of the motor 10.

[0021] As shown in Figure 2, the stator 3 includes a stator core 31, an insulator 32 overlapping the stator core 31 from one axial side L1, an insulator 33 overlapping the stator core 31 from the other axial side L2, and a plurality of coils 35 wound around a plurality of salient poles provided on the stator core 31 via the insulators 32 and 33. The motor 10 is a three-phase motor. Therefore, the plurality of coils 35 are composed of U-phase coils, V-phase coils, and W-phase coils.

[0022] The rotor 4 comprises a rotor member 40 made of resin. The rotor member 40 comprises a cylindrical portion 41 extending in the axial direction and a flange portion 45 formed at one end L1 in the axial direction of the cylindrical portion 41. The cylindrical portion 41 extends from the radially inner side of the stator 3 toward the pump chamber 20 and opens in the pump chamber 20. A cylindrical drive magnet 8 is held on the outer circumferential surface of the cylindrical portion 41. The drive magnet 8 faces the stator 3 radially inward. The drive magnet 8 is made of, for example, a neodymium bonded magnet.

[0023] An impeller 24 is connected to the flange portion 45 of the rotor member 40 from one side L1 in the axial direction. In this embodiment, the flange portion 45 and the impeller 24 constitute an impeller 25 connected to the cylindrical portion 41 of the rotor member 40. The impeller 24 comprises a disc portion 26 facing the flange portion 45 in the axial direction, and a plurality of blade portions 261 projecting from the disc portion 26 to the other side L2 in the axial direction. The disc portion 26 is fixed to the flange portion 45 via the blade portions 261. A central hole 260 is formed in the center of the disc portion 26. The disc portion 26 is inclined toward the flange portion 45 as it extends radially outward. The plurality of blade portions 261 are arranged at equal angular intervals. Each blade portion 261 extends radially outward from around the central hole 260, curving in an arc shape. The detailed shape of the blade portions 261 will be described later.

[0024] In the rotor member 40, a cylindrical radial bearing 11 is held on the radially inner side of the cylindrical portion 41. The rotor 4 is rotatably supported on the support shaft 5 via the radial bearing 11. The other axial end L2 of the support shaft 5 is held in a shaft hole 65 formed in the bottom wall 63 of the housing 6. The case 2 has three support portions 27 that extend from the inner circumferential surface of the suction pipe 21 toward the motor 10. A cylindrical portion 28 is formed at the end of the support portion 27, on which the support shaft 5 is positioned, and the one axial end L1 of the support shaft 5 is held in the cylindrical portion 28.

[0025] An annular thrust bearing 12 is mounted on one end L1 in the axial direction of the support shaft 5, and the thrust bearing 12 is positioned between the radial bearing 11 and the cylindrical portion 28. Here, at least a portion of the other end L2 of the support shaft 5 and the shaft hole 65 has a D-shaped cross-section. Also, the end L1 of the support shaft 5 and the hole of the thrust bearing 12 have a D-shaped cross-section. Therefore, rotation of the support shaft 5 and the thrust bearing 12 relative to the housing 6 is prevented.

[0026] The housing 6 is a resin sealing member 60 that covers the stator 3 from both radial and axial sides. The resin sealing member 60 is made of polyphenylene sulfide (PPS). The stator 3 is manufactured by insert molding. It is integrated with the resin sealing member 60. The housing 6 is a partition member having a first partition 61 facing the wall surface 23 on one side L1 in the axial direction of the pump chamber 20, a second partition 62 interposed between the stator 3 and the drive magnet 8, and a bottom wall 63 provided at the other end L2 of the second partition 62. The housing 6 also includes a cylindrical body 66 that covers the stator 3 from the radial outside.

[0027] As shown in Figures 1 and 2, a cover 18 is fixed to the other axial end L2 of the housing 6 from the other axial end L2. As shown in Figure 2, a circuit board 19, which controls the power supply to the coil 35, is placed between the cover 18 and the bottom wall 63 of the housing 6. Metal winding terminals 71, which protrude from the stator 3 through the bottom wall 63 of the housing 6 to the other axial end L2, are connected to the circuit board 19 by solder. The housing 6 has a columnar portion that protrudes from the bottom wall 63 to the other axial end L2. The circuit board 19 is fixed to the columnar portion by screws 91.

[0028] As shown in Figure 1, the housing 6 includes a cylindrical connector housing 69 that extends radially outward from a body portion 66 surrounding the outer circumference of the stator 3. Inside the connector housing 69, connector terminals are arranged, one end of which is connected to the circuit board 19. When a connector is connected to the connector housing 69, the drive current generated by the circuit mounted on the circuit board 19 is supplied to each coil 35 via the winding terminals 71. As a result, the rotor 4 rotates around the rotation axis L of the motor 10. This causes the impeller 25 to rotate inside the pump chamber 20, creating negative pressure inside the pump chamber 20, so that fluid is drawn into the pump chamber 20 from the suction pipe 21 and discharged from the discharge pipe 22.

[0029] (Retaining structure for drive magnet and radial bearing) Figure 3 is an exploded perspective view of the rotor 4 and radial bearing 11 viewed from one side L1 in the axial direction. Figure 4 is an exploded perspective view of the rotor 4 and radial bearing 11 viewed from the other side L2 in the axial direction. Figure 5 is a perspective view of the rotor member 40 viewed from one side L1 in the axial direction. Figure 6 is a cross-sectional view of the rotor 4, impeller 24, and radial bearing 11 cut by a plane containing the axis of rotation L. Figure 7 is a cross-sectional view of the rotor 4, radial bearing 11, and support shaft 5 cut by a plane perpendicular to the axis of rotation L (cross-sectional view cut at position AA in Figure 6). Figure 8 is a perspective view of the rotor 4, impeller 24, and radial bearing 11 viewed from the other side L2 in the axial direction.

[0030] In this specification, the three directions X, Y, and Z are mutually orthogonal. One side of the X direction is denoted as X1, the other side as X2, one side of the Y direction as Y1, the other side as Y2, one side of the Z direction as Z1, and the other side as Z2. The Z direction coincides with the axial direction, the Z1 direction coincides with one side L1 of the axial direction, and the Z2 direction coincides with the other side L2 of the axial direction.

[0031] As shown in Figures 2 and 4, the rotor member 40 has an annular seat portion 42 that protrudes radially outward from the cylindrical portion 41 at a position spaced apart from the flange portion 45 on the other side L2. The cylindrical portion 41 has a magnet holding portion 410 that extends from the seat portion 42 to the other side L2. The magnet holding portion 410 fits inside the drive magnet 8 and holds the drive magnet 8. At this time, the seat portion 42 supports one end L1 in the axial direction of the drive magnet 8. A crimped portion 43 is formed at the other end L2 in the axial direction of the magnet holding portion 410, which overlaps the drive magnet 8 in the axial direction.

[0032] As shown in Figures 5 and 6, the inner circumferential surface of the cylindrical portion 41 has annular first protrusion 441 and a second protrusion 442 that project radially inward. The first protrusion 441 is located on the stepped portion 116 on one side L1 in the axial direction of the radial bearing 11. The second protrusion 442 is located on the radial shaft It is positioned on the stepped portion 117 on the other side L2 in the axial direction of the receiver 11. When manufacturing the rotor member 40, the radial bearing 11 is made into a resin molded product by insert molding. This allows the radial bearing 11 to be held between the first protrusion 441 and the second protrusion 442.

[0033] As shown in Figures 4 and 6, the other end L2 in the axial direction of the magnet holder 410 is provided with a projection 411 extending toward the other side L2 relative to the second protrusion 442, and a crimping portion 43 is formed at the tip of the projection 411. As shown in Figure 4, the projection 411 is provided with two notches 412 cut out on opposite radial sides toward one side L1 in the axial direction. One notch 412 is located at an angular position in the X1 direction with respect to the rotation axis L, and the other notch 412 is located at an angular position in the X2 direction with respect to the rotation axis L. In this embodiment, the crimping portion 43 extends in an arc shape except for the portion where the notch 412 is formed.

[0034] As shown in Figure 4, the seat portion 42 of the rotor member 40 is provided with a recess 421 that is recessed on one side L1 in the axial direction, and an anti-rotation projection 422 that protrudes from the bottom surface of each recess 421 on the other side L2 in the axial direction. Multiple recesses 421 are provided at equal angular intervals (in this embodiment, three locations at 120-degree intervals). The portion between adjacent recesses 421 in the circumferential direction is a flat portion 423 perpendicular to the axial direction.

[0035] The recess 421 extends from the inner edge to the outer edge of the seat portion 42. The anti-rotation projection 422 is located in the circumferential center of the recess 421 and extends from the inner edge of the seat portion 42 to a point midway along the radial direction of the seat portion 42. Therefore, the anti-rotation projection 422 is surrounded by the recess 421 on both sides in the circumferential direction and radially outward. The axial height of the anti-rotation projection 422 is greater than the axial depth of the recess 421. Therefore, the anti-rotation projection 422 protrudes from the flat portion 423 to a position L2 on the other side in the axial direction.

[0036] When fixing the drive magnet 8 to the magnet holder 410, one end L1 in the axial direction of the drive magnet 8 is brought into contact with the flat portion 423 of the seat portion 42 from the other end L2 in the axial direction. At this time, the anti-rotation projection 422 fits into the anti-rotation recess 81 (see Figure 3) formed on the end face of the one end L1 in the axial direction of the drive magnet 8. This defines the angular position of the drive magnet 8 in the circumferential direction and prevents the drive magnet 8 from rotating relative to the rotor member 40.

[0037] (A flow path for cooling the drive magnet and radial bearing) As shown in Figures 3 and 4, the rotor member 40 is provided with a first flow channel groove 46 formed on the outer circumferential surface of the magnet holder portion 410 in the cylindrical portion 41. The first flow channel groove 46 is a recess that is recessed radially inward to a certain depth. When the magnet holder portion 410 is fitted inside the drive magnet 8, a flow channel F1 (see Figure 7) with a shape defined by the first flow channel groove 46 is formed between the inner circumferential surface of the drive magnet 8 and the magnet holder portion 410. This flow channel F1 communicates with the gap G1 (see Figure 2) between the drive magnet 8 and the second partition wall portion 62 of the housing 6. Therefore, the fluid from the pump chamber 20 flows through the flow channel F1 via the gap G1, cooling the drive magnet 8 and the magnet holder portion 410. In other words, the flow channel F1 functions as a magnet cooling flow channel.

[0038] As shown in Figure 5, the rotor member 40 is provided with a second flow channel groove 47 formed on the inner circumferential surface of the cylindrical portion 41. The second flow channel groove 47 is a groove with a rectangular cross-section that extends in the axial direction. The second flow channel groove 47 extends to one end L1 in the axial direction of the cylindrical portion 41 and opens to the inner circumferential edge of the flange portion 45, communicating with the pump chamber 20. Inside the cylindrical portion 41, rectangular openings 471 and 472 are formed that penetrate the first protrusion 441 and the second protrusion 442 at the same angular position as the second flow channel groove 47.

[0039] As shown in Figures 4 and 5, the second flow channel grooves 47 are formed at two locations on the inner circumferential surface of the cylindrical portion 41, on opposite sides in the radial direction. In this embodiment, the second flow channel grooves 47 are arranged at two locations facing each other in the X direction. The angular positions of the two second flow channel grooves 47 coincide with the angular positions of the two notches 412 formed by cutting out the other end L2 of the cylindrical portion 41. Therefore, as shown in Figures 4 and 8, at the other end L2 in the axial direction of the cylindrical portion 41, openings 472 that penetrate the second protrusion 442 are located radially inside each of the two notches 412, and the radially outside of the openings 472 is not closed by the crimped portion 43.

[0040] As shown in Figures 3, 4, and 7, the outer circumferential surface of the radial bearing 11 has multiple planar portions 111 extending in the axial direction at various positions along its circumference. The planar shape of the radial bearing 11 when viewed from the axial direction is such that arcuate surfaces 110 extending in the circumferential direction and planar portions 111 are alternately arranged along its circumference. The planar portions 111 are formed at four locations at 90-degree angular intervals and extend to both ends of the radial bearing 11 in the axial direction. The four planar portions 111 include two first planar portions 111A that extend in the Y direction at locations facing each other in the X direction, and two second planar portions 111B that extend in the X direction at locations facing each other in the Y direction. The circumferential widths of the first planar portions 111A and the second planar portions 111B are the same.

[0041] The two first flat sections 111A are positioned at the same angular position as the second flow channel groove 47. When the radial bearing 11 is held inside the cylindrical section 41, as shown in Figure 7, a flow channel F2 (see Figure 7) extending in the axial direction is formed between the inner circumferential surface of the cylindrical section 41 and the outer circumferential surface of the radial bearing 11 by the second flow channel groove 47 and the flat sections 111. One end L1 of the flow channel F2 in the axial direction extends to the flange section 45 and communicates with the pump chamber 20. The other end L2 of the flow channel F2 in the axial direction opens to the other end L2 of the cylindrical section 41 by an opening 472 provided in the second protrusion 442 and a notch 412 provided in the projection 411 (see Figure 8). Therefore, the flow channel F2 communicates with the gap G2 (see Figure 2) between the drive magnet 8 and the bottom wall 63 of the housing 6 via the opening 472 and the notch 412. Therefore, the fluid in the pump chamber 20 flows through the flow path F2, cooling the radial bearing 11 and the cylindrical portion 41. In other words, the flow path F2 functions as a bearing cooling flow path.

[0042] As shown in Figure 7, anti-rotation flat portions 413 extending in the axial direction are provided at two opposing locations in the Y direction on the inner circumferential surface of the cylindrical portion 41. When the radial bearing 11 is held inside the cylindrical portion 41, each anti-rotation flat portion 413 comes into contact with the second flat portion 111B. Therefore, rotation of the radial bearing 11 relative to the rotor 4 is prevented. As described above, in this embodiment, when manufacturing the rotor member 40, the radial bearing 11 is made into a resin molded product by insert molding. At this time, a mold pin matching the cross-sectional shape of the second flow channel groove 47 is set so as to contact the first flat portion 111A of the radial bearing 11, and resin is filled around the radial bearing 11 with the second flat portion 111B exposed inside the mold. As a result, the second flow channel groove 47, openings 471 and 472, and anti-rotation flat portions 413 are formed in the cylindrical portion 41 of the rotor member 40.

[0043] The second flow channel groove 47 is a rectangular cross-section groove in which the groove width in the Y direction is greater than the groove depth in the X direction. The circumferential width of the first flat portion 111A is the same as the groove width of the second flow channel groove 47. The mold pin used to form the second flow channel groove 47 is a rectangular cross-section mold pin with the circumferential direction of the rotor member 40 as the direction of the longer side.

[0044] (Detailed configuration of flow channel grooves in the rotor component) In Figures 3, 4, and 7, the R1 direction is the front side in the direction of rotation of the rotor 4, and the R2 direction is the rear side in the direction of rotation of the rotor 4. As shown in Figure 4, the first flow channel groove 46 has a first groove portion 461 extending in the axial direction, a second groove portion 462 extending in the axial direction on the rear side R2 in the direction of rotation of the rotor 4 relative to the first groove portion 461, and a circumferential groove portion extending between the first groove portion 461 and the second groove portion 46 It is provided with a third groove 463 that connects to the other end L2 in the axial direction of 2. That is, the first flow channel groove 46 is a groove that has been folded once in the axial direction, and is a substantially U-shaped groove.

[0045] As shown in Figure 4, a recess 421 is formed in the seat portion 42 of the rotor member 40. As shown in Figure 8, when the drive magnet 8 is fixed to the magnet holding portion 410 of the rotor member 40, an inlet 48 opening radially outward is formed between the end face L1 on one axial side of the drive magnet 8 and the bottom surface of the recess 421. As shown in Figure 4, since the recess 421 coincides with the circumferential position of the first groove portion 461, the first groove portion 461 and the gap G1 on the outer circumference side of the drive magnet 8 (see Figure 2) are in communication via the inlet 48.

[0046] As shown in Figure 7, the anti-rotation recess 81 formed in the drive magnet 8 has a radial dimension longer than the anti-rotation projection 422. Therefore, a gap G3, which serves as a flow path, is formed between the radially outer side surface of the anti-rotation projection 422 and the inner surface facing the anti-rotation recess 81. As shown in Figure 6, the axial depth of the anti-rotation recess 81 is such that an axial gap G4 is formed between it and the anti-rotation projection 422. Consequently, the fluid flowing in from the inlet 48 flows not only along both sides of the anti-rotation projection 422 in the circumferential direction, but also flows into the first groove 461 via gaps G3 and G4.

[0047] As shown in Figure 4, in the first flow channel groove 46, the third groove 463 and the second groove 462 are located on the rear side R2 in the rotational direction relative to the first groove 461 which communicates with the inlet 48. Therefore, when the rotor 4 rotates in the R1 direction, the fluid in the first groove 461 moves in the R2 direction due to inertial force and flows through the third groove 463 and the second groove 462, generating a flow in the D direction shown in Figure 4. This creates negative pressure inside the first groove 461, causing further fluid to flow in. In other words, while the rotor 4 is rotating, fluid continues to flow in the first flow channel groove 46 in the D direction shown in Figure 4.

[0048] As shown in Figures 3, 4, and 7, on the outer circumferential surface of the magnet holder 410, the portion between the circumferentially adjacent first groove 461 and second groove 462 forms a first rib 51 that extends axially from the seat portion 42 to the third groove 463. The radially outer portion of the second groove 462 in the seat portion 422 is a flat portion 423 that supports the drive magnet 8, so a wide opening such as an inlet 48 is not formed on the radially outer side of the second groove 462 (see Figure 8). For this reason, a differential pressure is generated between the inflow and outflow sides of the first flow channel groove 46, making it easy for fluid to flow into the first flow channel groove 46.

[0049] As shown in Figure 7, two first flow channel grooves 46 are formed on the outer circumferential surface of the magnet holder 410, aligned in the circumferential direction. Furthermore, in the region on the outer circumferential surface of the magnet holder 410 where the first flow channel grooves 46 are not formed (the region in the X2 direction), two third flow channel grooves 49 are formed side by side, extending axially with the same width as the first groove 461 and the second groove 462. The third flow channel grooves 49 extend to the other end L2 in the axial direction of the cylindrical portion 41.

[0050] As shown in Figure 7, two of the three recesses 421 formed in the seat portion 42 are located at angular positions corresponding to the first groove portion 461 of the first flow channel groove 46. On the other hand, the remaining recess 421 is located at an angular position corresponding to one of the two third flow channel grooves 49. Therefore, fluid flows into one of the two third flow channel grooves 49 via an inlet 48 formed between the recess 421 and the drive magnet 8.

[0051] As shown in Figures 3 and 4, the outer circumferential surface of the magnet holder 410 is provided with second ribs 52 that extend axially from the seat portion 42 to the crimping portion 43. The second ribs 52 are provided between adjacent first grooves 461 in the circumferential direction, between adjacent third flow channel grooves 49 in the circumferential direction, and between adjacent first grooves 461 and third flow channel grooves 49 in the circumferential direction. Therefore, four second ribs 52 are formed on the outer circumferential surface of the magnet holder 410.

[0052] Two of the four second ribs 52 are positioned at opposite angular positions in the X direction with respect to the rotation axis L, and their circumferential positions coincide with the second flow channel grooves 47 provided on the inner circumferential surface of the cylindrical portion 41. The first rib 51 and the second rib 52 are protrusions that project radially outward from the bottom surfaces of the first flow channel groove 46 and the third flow channel groove 49. Therefore, by having the angular positions of the second flow channel groove 47 and the second rib 52 coincide, the wall thickness of the magnet holding portion 410 in the portion where the second flow channel groove 47 is formed can be ensured.

[0053] (Impeller fixing structure) Figure 9 is a plan view of the impeller 24 as seen from one side L1 in the axial direction. Figure 10 is a perspective view of the impeller 24 as seen from one side L1 in the axial direction. As shown in Figures 2 and 6, in this embodiment, the impeller 25 that rotates integrally with the rotor 4 is constructed by connecting the impeller 24 to the flange portion 45 of the rotor member 40. As shown in Figures 5 and 6, the flange portion 45 is provided with a plurality of fixing grooves 44 recessed into the other side L2 in the axial direction. The plurality of fixing grooves 44 are provided at positions at equal angular intervals in the circumferential direction with respect to the rotation axis L. In this embodiment, 10 fixing grooves 44 of the same shape are provided in the flange portion 45. Each fixing groove 44 extends radially outward while curving in an arc shape. Each fixing groove 44 extends from near the inner circumferential edge to near the outer circumferential edge of the flange portion 45.

[0054] As shown in Figure 6, the tip of the blade portion 261, which protrudes from the disc portion 26 to the other side L2 in the axial direction, is inserted into the fixing groove 44. The impeller 24 is fixed to the flange portion 45 by welding the tip of the blade portion 261 to the fixing groove 44. In this embodiment, a welded portion W is formed on the radially outer portion of the blade portion 261 (the outer peripheral portion 267, which will be described later) that is welded to the fixing groove 44.

[0055] The impeller 24 has 10 blades 261 positioned opposite the fixing groove 44 in the axial direction. As shown in Figures 9 and 10, each blade 261 comprises a blade body 262 protruding from the disc portion 26, a rib 263 protruding from the tip surface of the blade body 262, and a welding projection 264 protruding from the tip surface of the rib 263. The welding projection 264 has a roughly triangular cross-sectional shape, and its thickness decreases towards the tip. The welded portion W shown in Figure 6 is a crushed portion where the welding projection 264 is crushed by the bottom surface of the fixing groove 44. The thickness of the blade body 262 is greater than the width of the fixing groove 44, but the thickness of the rib 263 is less than the width of the fixing groove 44. Furthermore, the thickness of the welding projection 264 is even less than the thickness of the rib 263. Therefore, a gap is ensured around the rib 263 inserted into the fixing groove 44 and the welding projection 264 that can accommodate welding burrs.

[0056] As shown in Figures 9 and 10, each blade portion 261 comprises an intermediate portion 265 including the radial center position P of each blade portion 261, an inner circumferential portion 266 extending radially inward from the intermediate portion 265, and an outer circumferential portion 267 extending radially outward from the intermediate portion 265. The inner circumferential portion 266 extends from the intermediate portion 265 to the radially inward end of the blade portion 261. The outer circumferential portion 267 extends from the intermediate portion 265 to the radially outward end of the blade portion 261. The welding projection 264 is formed on the outer circumferential portion 267, but not on the intermediate portion 265 or the inner circumferential portion 266.

[0057] Each wing portion 261 has a shape in which the axial height of the inner circumference portion 266 is lower than the axial height of the intermediate portion 265 and the outer circumference portion 267. In each wing portion 261, the tip surface of the rib 263 is a uniform surface with a constant axial height from the intermediate portion 265 to the outer circumference portion 267, but the tip surface of the rib 263 in the inner circumference portion 266 is a stepped surface 268 that is recessed compared to the tip surface of the rib 263 from the intermediate portion 265 to the outer circumference portion 267.

[0058] In each wing portion 261, the tip surface of the rib 263 in the intermediate portion 265 does not have a welding projection 264 formed on it and is a flat surface. The tip surface is a reference surface 269 that abuts the flange portion 45 in the axial direction. In this embodiment, when assembling the impeller 24 to the flange portion 45, the tip surface (reference surface 269) of the rib 263 in the intermediate portion 265 is brought into contact with the bottom surface of the fixing groove 44. This positions the impeller 24 in the axial direction.

[0059] Some of the 10 blades 261 on the impeller 24 are provided with positioning protrusions 270 that project from the reference surface 269 to the other side L2 in the axial direction. In this embodiment, three of the 10 blades 261 are equipped with positioning protrusions 270. The three positioning protrusions 270 are distributed in the circumferential direction. As shown in Figure 5, in the flange portion 45, positioning recesses 271 are provided in all 10 fixing grooves 44. When connecting the impeller 24 to the flange portion 45, the three positioning protrusions 270 are fitted into the positioning recesses 271 of the opposing fixing grooves 44.

[0060] (Main effects and benefits of this form) As described above, the pump device 1 of this embodiment includes a motor 10 equipped with a rotor 4 and a stator 3, and an impeller 25 arranged in a pump chamber 20 provided on one side L1 in the axial direction relative to the stator 3, when the direction along the rotation axis L of the rotor 4 is defined as the axial direction, and which rotates integrally with the rotor 4. The rotor 4 includes a rotor member 40 equipped with a cylindrical magnet holder 410 and a drive magnet 8 fixed to the outer circumferential surface of the magnet holder 410. The impeller 25 includes a flange portion 45 provided at the end of one side L1 in the axial direction of the rotor member 40, and a vane 24 fixed to the flange portion 45 from one side L1 in the axial direction. The vane 24 includes a disc portion 26 facing the flange portion 45 in the axial direction, and a plurality of blade portions 261 protruding from the disc portion 26 to the other side L2 in the axial direction. Multiple blade portions 261 extend radially outward at multiple positions in the circumferential direction centered on the rotation axis L, and a rib 263 is provided at the tip of the other axial side L2 of each of the multiple blade portions 261, which is inserted into a fixing groove 44 provided in the flange portion 45. The rib 263 has an inner circumferential portion 266 including the radially inner end and an outer circumferential portion 267 including the radially outer end, and an axial gap is provided between the tip of the other axial side L2 of the inner circumferential portion 266 and the bottom surface of the fixing groove 44, and a welded portion W is provided at the tip of the other axial side L2 of the outer circumferential portion 267 which is welded to the fixing groove 44.

[0061] In this embodiment, by inserting the rib 263 provided at the tip of the blade portion 261 into the fixing groove 44 provided in the flange portion 45, deformation of the blade portion 261 due to water pressure can be suppressed. In addition, it is possible to suppress the loss of efficiency caused by fluid passing between the tip of the blade portion 261 and the flange portion 45. Furthermore, the rib 263 inserted into the fixing groove 44 has an outer circumference portion 267 that is welded to the fixing groove 44, while the inner circumference portion 266 has a shape that creates a gap between it and the bottom surface of the fixing groove 44. Therefore, even if the flange portion 45 does not take the shape as designed and warps into an umbrella shape, there is little risk of the inner circumference portion 266 of the rib 263 excessively interfering with the bottom surface of the fixing groove 44, so there is little risk of a lot of welding burrs being generated at the point of excessive interference and protruding from the fixing groove 44. Furthermore, there is less risk of insufficient insertion of the outer circumference portion 267 of the rib 263 into the fixing groove 44 due to excessive interference of the inner circumference portion 266 of the rib 263, resulting in non-welding or insufficient welding strength. The outer circumference portion 267 of the impeller 25 is subjected to high fluid pressure, and if the welding strength is insufficient, there is a risk that the blade portion 261 will peel off from the flange portion 45. However, in this embodiment, the welding strength of the outer circumference portion 267 of the blade portion 261 can be ensured, so there is less risk of the welded area peeling off even when subjected to high water pressure.

[0062] In this embodiment, the welded portion W welded to the fixing groove 44 of the flange 45 is a flattened portion where the welding projection 264 protruding from the tip surface of the outer peripheral portion 267 of the rib 263 is crushed. By providing the welding projection 264 on the outer peripheral portion 267 in this way, it is possible to avoid insufficient welding on the outer peripheral portion 267. Furthermore, by not providing the welding projection 264 on the inner peripheral portion 266, This prevents excessive interference in the inner circumference portion 266.

[0063] In this embodiment, each of the 10 blade sections 261 is equipped with a blade section body 262 that protrudes from the disc section 26 to the other side L2 in the axial direction. The plate thickness of the blade section body 262 is greater than the width of the fixing groove 44, and the width of the rib 263 protruding from the tip surface of the blade section body 262 is smaller than the width of the fixing groove 44. Therefore, the rigidity of the part that receives water pressure (blade section body 262) is high. In addition, a gap can be secured between the fixing groove 44 and the rib 263 to accommodate welding burrs.

[0064] In this embodiment, the rib 263 inserted into the fixing groove 44 has an intermediate portion 265 that connects the inner circumferential portion 266 and the outer circumferential portion 267, and the intermediate portion 265 has a reference surface 269 that abuts against the bottom surface of the fixing groove 44. By providing a reference surface 269 for axial positioning on the radial intermediate portion 265, even if the flange portion 45 does not take the shape as designed and warps into an umbrella shape, the inner circumferential portion 266 is less likely to interfere excessively, and the amount of welding on the outer circumferential portion 267 is less likely to be insufficient. In this embodiment, the reference surface 269 is provided on all ribs 263, but a configuration in which the reference surface 269 is provided on only some of the multiple wing portions 261 may also be adopted.

[0065] In this embodiment, the tip surface of the inner circumferential portion 266 of the rib 263 is a stepped surface 268 that is recessed on one side L1 in the axial direction relative to the reference surface 269. By providing a step on the tip surface of the rib 263, it is possible to avoid excessive interference of the inner circumferential portion 266 when the reference surface 269 comes into contact with the bottom surface of the fixing groove 44.

[0066] In this embodiment, the rib 263 inserted into the fixing groove 44 has an intermediate portion 265 connecting the inner circumferential portion 266 and the outer circumferential portion 267. At three locations of the multiple blade portions 261, the intermediate portion 265 has a positioning projection 270 that protrudes to the other side L2 in the axial direction, and the positioning projection 270 fits into a positioning projection 270 provided on the bottom surface of the fixing groove 44. In this way, even if a gap is provided between the fixing groove 44 and the rib 263 to accommodate welding burrs, the impeller 24 can be positioned in a direction intersecting the axial direction by fitting the positioning projections 270 together. For example, the impeller 24 can be positioned in the circumferential direction. The number of blade portions 261 provided with positioning projections 270 may be four or more, or it may be two. [Explanation of Symbols]

[0067] 1...Pump device, 2...Case, 3...Stator, 4...Rotor, 5...Support shaft, 6...Housing, 8...Drive magnet, 10...Motor, 11...Radial bearing, 12...Thrust bearing, 18...Cover, 19...Base plate, 20...Pump chamber, 21...Suction pipe, 22...Discharge pipe, 23...Wall surface, 24...Impeller, 25...Impeller, 26...Disc section, 27...Support section, 28...Cylinder section, 29...Side wall, 31...Stator core, 32, 33...Insulation 35...Coil, 40...Rotor member, 41...Cylindrical part, 42...Seat part, 43...Crimping part, 44...Fixing groove, 45...Flange part, 46...First flow channel groove, 47...Second flow channel groove, 48...Inlet, 49...Third flow channel groove, 51...First rib, 52...Second rib, 60...Resin sealing member, 61...First partition wall part, 62...Second partition wall part, 63...Bottom wall, 64...Other end of the housing in the axial direction, 65...Shaft hole, 66...Body part, 69...Connector Housing, 71...winding terminal, 81...anti-rotation recess, 110...arc surface, 111...flat surface, 111A...first flat surface, 111B...second flat surface, 116, 117...stepped section, 260...central hole, 261...wing section, 262...wing section body, 263...rib, 264...welding projection, 265...intermediate section, 266...inner circumference section, 267...outer circumference section, 268...stepped surface, 269...reference surface, 270...positioning projection, 271...positioning recess ,410...Magnet holding part, 411...Protruding part, 412...Notch part, 413...Flat part for preventing rotation, 421...Recess, 422...Protrusion, 423...Flat part, 441...First convex part, 442...Second convex part, 461...First groove part, 462...Second groove part, 463...Third groove part, 471, 472...Opening, F1...Flow path (magnet cooling flow path), F2...Flow path (bearing cooling flow path), G1, G2, G3, G4...Gap, L...Rotation axis, L1... L2...One side in the axial direction, P...The other side in the axial direction, R1...The center position, R2...The front side in the rotation direction, R2...The rear side in the rotation direction, W...The welded area

Claims

1. A motor comprising a rotor and a stator, When the direction along the rotation axis of the rotor is defined as the axial direction, the system includes an impeller disposed in a pump chamber located on one side of the stator in the axial direction and rotating integrally with the rotor, The rotor comprises a rotor member having a cylindrical magnet holder and a drive magnet fixed to the outer circumferential surface of the magnet holder, The impeller comprises a flange portion provided at one end of the rotor member in the axial direction, and a vane fixed to the flange portion from one side in the axial direction. The impeller comprises a disc portion facing the flange portion in the axial direction, and a plurality of blade portions protruding from the disc portion to the other side in the axial direction. The aforementioned multiple blade portions extend radially outward at multiple positions in the circumferential direction centered on the axis of rotation, Each of the plurality of blade portions is provided with a rib at the other end in the axial direction, which is inserted into a fixing groove provided in the flange portion. The rib comprises an inner circumferential portion including the radially inner end and an outer circumferential portion including the radially outer end, A gap in the axial direction is provided between the other end of the inner circumference portion in the axial direction and the bottom surface of the fixing groove. A pump device characterized in that a welded portion is provided at the other end of the outer peripheral portion in the axial direction, which is welded to the fixing groove.

2. The pump device according to claim 1, characterized in that the welded portion is a flattened portion in which a welding projection protruding from the tip surface of the outer peripheral portion is flattened.

3. Each of the plurality of blade portions comprises a blade portion body that protrudes from the disc portion toward the other side in the axial direction, and the plate thickness of the blade portion body is greater than the width of the fixing groove. The pump device according to claim 1, characterized in that the width of the rib protruding from the tip surface of the blade body is smaller than the width of the fixing groove.

4. The rib has an intermediate portion that connects the inner circumferential portion and the outer circumferential portion, The pump device according to claim 1, characterized in that the intermediate portion includes a reference surface that contacts the bottom surface of the fixed groove.

5. The pump device according to claim 4, characterized in that the tip surface of the inner circumferential portion is a stepped surface recessed on one side in the axial direction with respect to the reference surface.

6. The rib has an intermediate portion that connects the inner circumferential portion and the outer circumferential portion, In at least a portion of the plurality of wing portions, The aforementioned intermediate portion is provided with a positioning projection that protrudes to the other side in the axial direction, The pump device according to claim 1, characterized in that the positioning projection fits into a positioning recess provided on the bottom surface of the fixing groove.

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