Patent ID: 12253094

DETAILED DESCRIPTION

Hereinafter, a pump device1according to an embodiment of the present invention will be described with reference to the drawings. In the following description, an axial direction means a direction in which a rotation axis L of a motor10extends, a radial direction in an inner side in the radial direction and an outer side in the radial direction means a radial direction about the rotation axis L, and a circumferential direction means a rotation direction about the rotation axis L. A direction in which the rotation axis L extends is referred to as an axial direction, one side in the axial direction is referred to as L1, and the other side in the axial direction is referred to as L2.

Entire Configuration

FIG.1is an external perspective view of a pump device1to which the present invention is applied.FIG.2is a cross-sectional view of the pump device1illustrated inFIG.1taken along a plane including the rotation axis L. As illustrated inFIGS.1and2, the pump device1includes a case2provided with a suction pipe21extending to the one side L1in the axial direction and a discharge pipe22, a motor10disposed on the other side L2in the axial direction with respect to the case2, and an impeller25disposed in a pump chamber20inside the case2. The impeller25is rotationally driven around the rotation axis L by the motor10. In the pump device1of the present embodiment, fluid flowing through the pump chamber20is liquid. The pump device1is used, for example, under a condition in which an environmental temperature or a fluid temperature is likely to change.

The motor10includes an annular stator3, a rotor4disposed on an inner side of the stator3, a resin housing6that covers the stator3, and a support shaft5that rotatably supports the rotor4. The support shaft5is made of metal or ceramic. The impeller25rotates integrally with the rotor4. As illustrated inFIG.2, in the pump device1, the impeller25and the pump chamber20are provided on the one side L1in the axial direction with respect to the stator3.

As illustrated inFIG.2, the pump chamber20is provided between the case2and the housing6. The case2constitutes a wall surface23on the one side L1in the axial direction of the pump chamber20and a sidewall29extending in the circumferential direction. As illustrated inFIG.1, the suction pipe21extends in the axial direction at the center in the radial direction of the case2, and the suction pipe21extends from the sidewall29in a direction orthogonal to the rotation axis L of the motor10.

As illustrated inFIG.2, the stator3includes a stator core31, an insulator32overlapping the stator core31from the one side L1in the axial direction, an insulator33overlapping the stator core31from the other side L2in the axial direction, and a plurality of coils35wound around a plurality of salient poles provided on the stator core31via the insulators32and33. The motor10is a three-phase motor. Therefore, the plurality of coils35are constituted by a U-phase coil, a V-phase coil, and a W-phase coil.

The rotor4includes a rotor member40made of resin. The rotor member40includes a cylindrical portion41extending in the axial direction, and a flange portion45formed at an end portion on the one side L1in the axial direction of the cylindrical portion41. The cylindrical portion41extends from the inner side of the stator3in the radial direction toward the pump chamber20and opens in the pump chamber20. A cylindrical drive magnet8is held on an outer peripheral surface of the cylindrical portion41. The drive magnet8is opposed to the stator3on the inner side in the radial direction. The drive magnet8is formed of, for example, a neodymium bond magnet.

The vane wheel24is coupled to the flange portion45of the rotor member40from the one side L1in the axial direction. In the present embodiment, the impeller25connected to the cylindrical portion41of the rotor member40is constituted by the flange portion45and the vane wheel24. The vane wheel24includes a disc portion26that is opposed to the flange portion45in the axial direction, and a plurality of vane portions261that protrude from the disc portion26toward the other side L2in the axial direction. The disc portion26is fixed to the flange portion45via the vane portions261. A center hole260is formed at the center of the disc portion26. The disc portion26is inclined in a direction toward the flange portion45as the disc portion26extends to the outer side in the radial direction. The plurality of vane portions261are disposed at equal angular intervals. Each of the vane portions261extends to the outer side in the radial direction while curving in an arc shape from the periphery of the center hole260. The detailed shape of the vane portion261will be described below.

In the rotor member40, a tubular radial bearing11is held on the inner side of the cylindrical portion41in the radial direction. The rotor4is rotatably supported by the support shaft5via the radial bearing11. An end portion on the other side L2in the axial direction of the support shaft5is held in a shaft hole65formed in a bottom wall63of the housing6. The case2includes three support portions27extending from an inner peripheral surface of the suction pipe21toward the motor10. A tube portion28in which the support shaft5is positioned is formed at an end portion of the support portion27, and an end portion on the one side L1in the axial direction of the support shaft5is held by the tube portion28.

An annular thrust bearing12is mounted on an end portion on the one side L1in the axial direction of the support shaft5, and the thrust bearing12is disposed between the radial bearing11and the tube portion28. Here, at least a part of the end portion of the support shaft5on the other side L2and the shaft hole65has a D-shaped cross section. Further, the end portion of the support shaft5on the one side L1and the hole of the thrust bearing12have a D-shaped cross section. Therefore, rotation of the support shaft5and the thrust bearing12with respect to the housing6is prevented.

The housing6is a resin sealing member60that covers the stator3from both sides in the radial direction and both sides in the axial direction. The resin sealing member60is made of polyphenylene sulfide (PPS). The stator3is integrated with the resin sealing member60by insert molding. The housing6is a partition wall member including a first partition wall portion61that is opposed to a wall surface23on the one side L1in the axial direction of the pump chamber20, a second partition wall portion62interposed between the stator3and the drive magnet8, and the bottom wall63provided at an end of the second partition wall portion62on the other side L2. The housing6includes a cylindrical body portion66that covers the stator3from the outer side in the radial direction.

As illustrated inFIGS.1and2, a cover18is fixed, from the other side L2in the axial direction, to an end portion64on the other side L2in the axial direction of the housing6. As illustrated inFIG.2, a substrate19provided with a circuit for controlling power supply to the coils35is disposed between the cover18and the bottom wall63of the housing6. Metal winding terminals71, which protrude from the stator3through the bottom wall63of the housing6to the other side L2in the axial direction, are connected to the substrate19by soldering. The housing6includes a columnar portion that protrudes from the bottom wall63to the other side L2in the axial direction. The substrate19is fixed to the columnar portion by a screw91.

As illustrated inFIG.1, the housing6includes a tubular connector housing69extending to the outer side in the radial direction from a body portion66surrounding an outer peripheral side of the stator3. A connector terminal whose one end is connected to the substrate19is disposed inside the connector housing69. When a connector is coupled to the connector housing69, a drive current generated by a circuit mounted on the substrate19is supplied to each of the coils35via the winding terminals71. As a result, the rotor4rotates around the rotation axis L of the motor10. Thus, the impeller25rotates in the pump chamber20and pressure in the pump chamber20becomes negative, so that the fluid is sucked into the pump chamber20from the suction pipe21and discharged from the discharge pipe22.

Holding Structure of Drive Magnet and Radial Bearing

FIG.3is an exploded perspective view of the rotor4and the radial bearing11as viewed from the one side L1in the axial direction.FIG.4is an exploded perspective view of the rotor4and the radial bearing11as viewed from the other side L2in the axial direction.FIG.5is a perspective view of the rotor member40as viewed from the one side L1in the axial direction.FIG.6is a cross-sectional view of the rotor4, the vane wheel24, and the radial bearing11taken along a plane including the rotation axis L.FIG.7is a cross-sectional view of the rotor4, the radial bearing11, and the support shaft5taken along a plane perpendicular to the rotation axis L (a cross-sectional view taken along the line A-A inFIG.6).FIG.8is a perspective view of the rotor4, the vane wheel24, and the radial bearing11as viewed from the other side L2in the axial direction.

In the present specification, three directions of XYZ are directions orthogonal to each other. One side in the X direction is referred to as X1, the other side in the X direction as X2, one side in the Y direction as Y1, the other side in the Y direction as Y2, one side in the Z direction as Z1, the other side in the Z direction as Z2. The Z direction coincides with the axial direction, the Z1direction coincides with the one side L1in the axial direction, and the Z2direction coincides with the other side L2in the axial direction.

As illustrated inFIGS.2and4, the rotor member40includes an annular seat portion42that protrudes to the outer side in the radial direction from the cylindrical portion41at a position spaced apart from the flange portion45toward the other side L2. The cylindrical portion41includes a magnet holding portion410extending from the seat portion42toward the other side L2. The magnet holding portion410is fitted inside the drive magnet8to hold the drive magnet8. At this time, the seat portion42supports an end portion on the one side L1in the axial direction of the drive magnet8. A caulking portion43overlapping with the drive magnet8in the axial direction is formed at an end portion on the other side L2in the axial direction of the magnet holding portion410.

As illustrated inFIGS.5and6, an annular first convex portion441and an annular second convex portion442that protrude to the inner side in the radial direction are formed on an inner peripheral surface of the cylindrical portion41. The first convex portion441is disposed on a step portion116on the one side L1in the axial direction of the radial bearing11. The second convex portion442is disposed on a step portion117on the other side L2in the axial direction of the radial bearing11. When being manufactured, the rotor member40is manufactured as a resin molded product with the radial bearing11insert molded therein. Thus, the radial bearing11can be held between the first convex portion441and the second convex portion442.

As illustrated inFIGS.4and6, the end portion on the other side L2in the axial direction of the magnet holding portion410includes a protruding portion411extending toward the other side L2with respect to the second convex portion442, and the caulking portion43is formed at a tip end of the protruding portion411. As illustrated inFIG.4, the protruding portion411includes cutout portions412that are formed on the one side L1in the axial direction by cutting out two portions on opposite sides in the radial direction. One cutout portion412is provided at an angular position in the X1direction with respect to the rotation axis L, and the other cutout portion412is provided at an angular position in the X2direction with respect to the rotation axis L. In the present embodiment, the caulking portion43extends in an arc shape except for portions where the cutout portions412are formed.

As illustrated inFIG.4, the seat portion42of the rotor member40includes concave portions421that are recessed to the one side L1in the axial direction, and rotation regulating protrusions422that protrude from bottom surfaces of the respective concave portions421toward the other side L2in the axial direction. The concave portions421are provided at a plurality of positions at equal angular intervals (three positions at intervals of 120 degrees in the present embodiment). Portions between the concave portions421adjacent to each other in the circumferential direction are flat portions423perpendicular to the axial direction.

The concave portion421extends from an inner edge to an outer edge of the seat portion42. The rotation regulating protrusion422is disposed at the center in the circumferential direction of the concave portion421and extends from the inner edge of the seat portion42to an intermediate position in the radial direction of the seat portion42. Therefore, both sides in the circumferential direction and an outer side in the radial direction of the rotation regulating protrusion422are surrounded by the concave portion421. The height of the rotation regulating protrusion422in the axial direction is larger than the depth of the concave portion421in the axial direction. Therefore, the rotation regulating protrusion422protrudes to a position on the other side L2in the axial direction with respect to the flat portion423.

When the drive magnet8is fixed to the magnet holding portion410, the end portion on the one side L1in the axial direction of the drive magnet8is brought into contact with the flat portion423of the seat portion42from the other side L2in the axial direction. At this time, the rotation regulating protrusions422are fitted into rotation regulating concave portions81(seeFIG.3) formed in an end surface on the one side L1in the axial direction of the drive magnet8. Thus, an angular position of the drive magnet8in the circumferential direction is defined, and rotation of the drive magnet8with respect to the rotor member40is prevented.

Flow Passage for Cooling Drive Magnet and Radial Bearing

As illustrated inFIGS.3and4, the rotor member40includes first flow passage grooves46formed in an outer peripheral surface of the magnet holding portion410of the cylindrical portion41. The first flow passage grooves46each are a concave portion that is recessed to the inner side in the radial direction to a certain depth. When the magnet holding portion410is fitted inside the drive magnet8, flow passages F1(seeFIG.7) having a shape defined by the first flow passage grooves46are formed between an inner peripheral surface of the drive magnet8and the magnet holding portion410. The flow passages F1communicate with a gap G1(seeFIG.2) between the drive magnet8and the second partition wall portion62of the housing6. Therefore, the fluid in the pump chamber20flows through the flow passages F1via the gap G1, so that the drive magnet8and the magnet holding portion410are cooled. That is, the flow passages F1function as magnet cooling flow passages.

As illustrated inFIG.5, the rotor member40includes second flow passage grooves47formed in the inner peripheral surface of the cylindrical portion41. The second flow passage grooves47each are a groove portion having a rectangular cross section extending in the axial direction. The second flow passage grooves47each extend to the end portion on the one side L1in the axial direction of the cylindrical portion41, open at an inner peripheral edge of the flange portion45, and communicate with the pump chamber20. On the inner side of the cylindrical portion41, rectangular opening portions471and472which penetrate the first convex portion441and the second convex portion442respectively are formed at the same angular position as the second flow passage groove47.

As illustrated inFIGS.4and5, the second flow passage grooves47are formed at two positions on opposite sides in the radial direction on the inner peripheral surface of the cylindrical portion41. In the present embodiment, the second flow passage grooves47are disposed at two positions opposed to each other in the X direction. The angular positions of the two second flow passage grooves47coincide with the angular positions of the two cutout portions412formed by cutting out the end portion on the other side L2of the cylindrical portion41. Therefore, as illustrated inFIGS.4and8, at an end portion on the other side L2in the axial direction of the cylindrical portion41, the opening portion472through which the second convex portion442passes is disposed on the inner side in the radial direction of each of the two cutout portions412, and an outer side in the radial direction of the opening portion472is not closed by the caulking portion43.

As illustrated inFIGS.3,4, and7, planar portions111extending in the axial direction are provided at a plurality of positions in the circumferential direction on an outer peripheral surface of the radial bearing11. The planar shape of the radial bearing11when viewed from the axial direction is a shape in which arc surfaces110and the planar portions111extending in the circumferential direction are alternately disposed in the circumferential direction. The planar portions111are formed at four positions at angular intervals of 90 degrees, and extend to both ends in the axial direction of the radial bearing11. The four planar portions111include first planar portions111A extending in the Y direction at two positions opposed to each other in the X direction and second planar portions111B extending in the X direction at two positions opposed to each other in the Y direction. A width in the circumferential direction of the first planar portion111A is equal to that of the second planar portion111B.

The two first planar portions111A are disposed at the same angular positions as the second flow passage grooves47. When the radial bearing11are held inside the cylindrical portion41, as illustrated inFIG.7, flow passages F2(seeFIG.7) extending in the axial direction are formed between the inner peripheral surface of the cylindrical portion41and the outer peripheral surface of the radial bearing11by the second flow passage grooves47and the planar portions111. An end portion on the one side L1in the axial direction of the flow passage F2extends to the flange portion45and communicates with the pump chamber20. An end portion on the other side L2in the axial direction of the flow passage F2is opened at the end portion on the other side L2of the cylindrical portion41by the opening portion472provided in the second convex portion442and the cutout portion412provided in the protruding portion411(seeFIG.8). Therefore, the flow passages F2communicate with the gap G2(seeFIG.2) between the drive magnet8and the bottom wall63of the housing6via the opening portion472and the cutout portion412. Thus, the fluid in the pump chamber20flows through the flow passages F2, so that the radial bearing11and the cylindrical portion41are cooled. That is, the flow passages F2function as bearing cooling flow passages.

As illustrated inFIG.7, rotation regulating planar portions413extending in the axial direction are provided at two positions opposed to each other in the Y direction on the inner peripheral surface of the cylindrical portion41. When the radial bearing11is held inside the cylindrical portion41, the rotation regulating planar portions413abut on the second planar portions111B. Therefore, rotation of the radial bearing11with respect to the rotor4is prevented. As described above, in the present embodiment, when being manufactured, the rotor member40is manufactured as a resin molded product with the radial bearing11insert molded therein. At this time, resin is filled around the radial bearing11in a state where mold pins that correspond to the cross-sectional shapes of the second flow passage grooves47are set so as to abut on the first planar portions111A of the radial bearing11, and in a state where the second planar portions111B are exposed in the mold. Thus, the second flow passage grooves47, the opening portions471and472, and the rotation regulating planar portions413are formed in the cylindrical portion41of the rotor member40.

The second flow passage grooves47each are a groove having a rectangular cross section in which the groove width in the Y direction is larger than the groove depth in the X direction. A width in the circumferential direction of the first planar portion111A is equal to a groove width of the second flow passage groove47. The mold pin used for forming the second flow passage groove47is a mold pin having a rectangular cross section in which the circumferential direction of the rotor member40is a long side direction.

Detailed Configuration of Flow Passage Groove in Rotor Member

AR1direction illustrated inFIGS.3,4, and7is a front side in the rotation direction of the rotor4, and a R2direction is a rear side in the rotation direction of the rotor4. As illustrated inFIG.4, the first flow passage groove46includes a first groove portion461extending in the axial direction, a second groove portion462extending in the axial direction on the rear side R2in the rotation direction of the rotor4with respect to the first groove portion461, and a third groove portion463extending in the circumferential direction and connecting end portions on the other side L2in the axial direction of the first groove portion461and the second groove portion462. That is, the first flow passage groove46is a groove having a shape folded back once in the axial direction, and is a substantially U-shaped groove.

As illustrated inFIG.4, the concave portion421is formed in the seat portion42of the rotor member40. As illustrated inFIG.8, when the drive magnet8is fixed to the magnet holding portion410of the rotor member40, an inflow port48that opens to the outer side in the radial direction is formed between the end surface on the one side L1in the axial direction of the drive magnet8and the bottom surface of the concave portion421. As illustrated inFIG.4, since a position in the circumferential direction of the concave portion421coincides with that of the first groove portion461, the first groove portion461and the gap G1(seeFIG.2) on an outer peripheral side of the drive magnet8communicate with each other via the inflow port48.

As illustrated inFIG.7, the rotation regulating concave portion81formed in the drive magnet8is longer in radial dimension than the rotation regulating protrusion422. Therefore, a gap G3serving as a flow passage is formed between a side surface on the outer side in the radial direction of the rotation regulating protrusion422and an inner side surface of the rotation regulating concave portion81. As illustrated inFIG.6, a depth in the axial direction of the rotation regulating concave portion81is dimensioned such that a gap G4in the axial direction is formed between the rotation regulating concave portion81and the rotation regulating protrusion422. Therefore, the fluid that has flowed in from the inflow port48not only flows on both sides in the circumferential direction of the rotation regulating protrusion422, but also flows into the first groove portion461via the gaps G3and G4.

As illustrated inFIG.4, in the first flow passage groove46, the third groove portion463and the second groove portion462are provided on the rear side R2in the rotation direction with respect to the first groove portion461communicating with the inflow port48. Therefore, when the rotor4rotates in the R1direction, the fluid in the first groove portion461moves in the R2direction due to inertia force and flows through the third groove portion463and the second groove portion462, and a flow in the D direction illustrated inFIG.4is generated. Thus, pressure in the first groove portion461becomes negative, and the fluid further flows in. That is, while the rotor4rotates, the fluid continues to flow through the first flow passage groove46in the direction D illustrated inFIG.4.

As illustrated inFIGS.3,4, and7, on the outer peripheral surface of the magnet holding portion410, portions between the first groove portions461and the second groove portions462adjacent to each other in the circumferential direction are first ribs51extending in the axial direction from the seat portion42to the third groove portion463. Since a portion of the seat portion42on the outer side in the radial direction of the second groove portion462is the flat portion423that supports the drive magnet8, a wide opening portion such as the inflow port48is not formed on the outer side in the radial direction of the second groove portion462(seeFIG.8). Therefore, a differential pressure is generated between the inflow side and the outflow side of the first flow passage groove46, so that the fluid easily flows into the first flow passage groove46.

As illustrated inFIG.7, on the outer peripheral surface of the magnet holding portion410, the first flow passage grooves46are formed at two positions side by side in the circumferential direction. Further, two third flow passage grooves49extending in the axial direction and having the same widths as those of the first groove portion461and the second groove portion462are formed side by side in a region (region in the X2direction) of the outer peripheral surface of the magnet holding portion410where the first flow passage grooves46are not formed. The third flow passage grooves49extend to the end portion on the other side L2in the axial direction of the cylindrical portion41.

As illustrated inFIG.7, two of the three concave portions421formed in the seat portion42are provided at angular positions corresponding to the first groove portion461of the first flow passage groove46. On the other hand, the remaining one concave portion421is provided at an angular position corresponding to one of the two third flow passage grooves49. Therefore, the fluid flows into one of the two third flow passage grooves49via the inflow port48formed between the concave portion421and the drive magnet8.

As illustrated inFIGS.3and4, second ribs52extending in the axial direction in a range from the seat portion42to the caulking portion43are provided on the outer peripheral surface of the magnet holding portion410. The second ribs52are provided between the first groove portions461adjacent to each other in the circumferential direction, between the third flow passage grooves49adjacent to each other in the circumferential direction, and between the first groove portion461and the third flow passage groove49adjacent to each other in the circumferential direction. Therefore, four second ribs52are formed on the outer peripheral surface of the magnet holding portion410.

Two of the four second ribs52are provided at angular positions opposite to each other in the X direction with respect to the rotation axis L, and circumferential positions of the two second ribs52coincide with those of the second flow passage grooves47provided on the inner peripheral surface of the cylindrical portion41. The first ribs51and the second ribs52are protruding portions that protrude to the outer side in the radial direction from bottom surfaces of the first flow passage grooves46and the third flow passage grooves49. Therefore, since the angular positions of the second flow passage grooves47coincide with the angular positions of the second ribs52respectively, wall thicknesses of the magnet holding portion410at portions where the second flow passage grooves47are formed can be secured.

Fixing Structure of Vane Wheel

FIG.9is a plan view of the vane wheel24as viewed f from the one side L1in the axial direction.FIG.10is a perspective view of the vane wheel24as viewed from the one side L1in the axial direction. As illustrated inFIGS.2and6, in the present embodiment, the impeller25that rotates integrally with the rotor4is configured by coupling the vane wheel24to the flange portion45of the rotor member40. As illustrated inFIGS.5and6, the flange portion45is provided with a plurality of fixing grooves44recessed into the other side L2in the axial direction. The plurality of fixing grooves44are provided at positions at equal angular intervals in the circumferential direction around the rotation axis L. In the present embodiment, ten fixing grooves44having identical shapes are provided on the flange portion45. Each fixing groove44extends to the outer side in the radial direction while being curved in an arc shape. Each fixing groove44extends from a vicinity of the inner peripheral edge of the flange portion45to a vicinity of the outer peripheral edge.

As illustrated inFIG.6, tip ends of the vane portions261protruding from the disc portion26toward the other side L2in the axial direction are inserted into the fixing grooves44. The vane wheel24is fixed to the flange portion45by welding the tip ends of the vane portions261to the fixing grooves44. In the present embodiment, welded portions W welded to the fixing grooves44are formed in portions on the outer side in the radial direction (outer peripheral portions267to be described below) of the vane portions261.

The vane wheel24is provided with ten vane portions261at positions opposed to the fixing grooves44in the axial direction. As illustrated inFIGS.9and10, each of the vane portions261includes a vane portion main body262protruding from the disc portion26, a rib263protruding from a tip end surface of the vane portion main body262, and a welding convex portion264protruding from a tip end surface of the rib263. The welding convex portion264has a substantially triangular cross-sectional shape, and has a shape in which the thickness decreases toward a tip end thereof. The welded portion W illustrated inFIG.6is a crushed portion where the welding convex portion264is crushed by a bottom surface of the fixing groove44. A thickness of the vane portion main body262is larger than a width of the fixing groove44, but a thickness of the rib263is smaller than the width of the fixing groove44. Further, a thickness of the welding convex portion264is smaller than the thickness of the rib263. Therefore, a gap capable of accommodating welding burrs is secured around the rib263and the welding convex portion264that are inserted into the fixing groove44.

As illustrated inFIGS.9and10, each vane portion261includes an intermediate portion265including a central position P in the radial direction of each vane portion261, an inner peripheral portion266extending to the inner side in the radial direction from the intermediate portion265, and an outer peripheral portion267extending to the outer side in the radial direction from the intermediate portion265. The inner peripheral portion266extends from the intermediate portion265to an end portion on the inner side in the radial direction of the vane portion261. The outer peripheral portion267extends from the intermediate portion265to an end portion on the outer side in the radial direction of the vane portion261. The welding convex portion264is formed at the outer peripheral portion267, and is not formed at the intermediate portion265and the inner peripheral portion266.

Each vane portion261has a shape in which a height of the inner peripheral portion266in the axial direction is lower than heights of the intermediate portion265and the outer peripheral portion267in the axial direction. In each vane portion261, the tip end surface of the rib263is on the same surface having a fixed height in the axial direction in a range from the intermediate portion265to the outer peripheral portion267, but the tip end surface of the rib263at the inner peripheral portion266is a step surface268recessed from the tip end surface of the rib263in the range from the intermediate portion265to the outer peripheral portion267.

In each vane portion261, the tip end surface of the rib263at the intermediate portion265is not formed with the welding convex portion264, and is a flat surface. The tip end surface of the rib263at the intermediate portion265is a reference surface269that abuts on the flange portion45in the axial direction. In the present embodiment, when the vane wheel24is assembled to the flange portion45, the tip end surface (the reference surface269) of the rib263at the intermediate portion265is made to abut on the bottom surface of the fixing groove44. Thus, the vane wheel24is positioned in the axial direction.

Some of the ten vane portions261provided in the vane wheel24are provided with positioning convex portions270protruding from the reference surface269to the other side L2in the axial direction. In the present embodiment, three of the ten vane portions261include the positioning convex portions270. Three positioning convex portions270are dispersedly arranged in the circumferential direction. As illustrated inFIG.5, in the flange portion45, positioning concave portions271are provided in all of the ten fixing grooves44. When the vane wheel24is coupled to the flange portion45, the three positioning convex portions270are fitted into the positioning concave portions271of the opposing fixing grooves44.

Main Effects of the Present Embodiment

As described above, the pump device1of the present embodiment includes the motor10including the rotor4and the stator3, and the impeller25that is disposed, when the direction along the rotation axis L of the rotor4is defined as the axial direction, in the pump chamber20provided on the one side L1in the axial direction with respect to the stator3and rotates integrally with the rotor4. The rotor4includes a rotor member40having the magnet holding portion410in a tubular shape, and the drive magnet8fixed to the outer peripheral surface of the magnet holding portion410. The impeller25includes the flange portion45provided at the end portion on the one side L1in the axial direction of the rotor member40, and a vane wheel24fixed to the flange portion45from the one side L1in the axial direction. The vane wheel24includes the disc portion26that is opposed to the flange portion45in the axial direction, and the plurality of vane portions261that protrude from the disc portion26toward the other side L2in the axial direction. The plurality of vane portions261extend to the outer side in the radial direction at a plurality of positions in the circumferential direction around the rotation axis L, and at the tip end on the other side L2in the axial direction of each of the plurality of vane portions261, the rib263that is inserted into the fixing groove44provided in the flange portion45is provided. The rib263includes the inner peripheral portion266including the end portion on the inner side in the radial direction of the rib263, and the outer peripheral portion267including the end portion on the outer side in the radial direction portion of the rib263. A gap in the axial direction is provided between a tip end on the other side L2in the axial direction of the inner peripheral portion266and the bottom surface of the fixing groove44, and the welded portion W welded to the fixing groove44is provided at a tip end on the other side L2in the axial direction of the outer peripheral portion267.

According to the present embodiment, by inserting the ribs263provided at the tip ends of the vane portions261into the fixing grooves44provided in the flange portion45, it is possible to suppress deformation of the vane portions261due to water pressure. In addition, it is possible to suppress a decrease in efficiency due to the fluid passing between the tip ends of the vane portions261and the flange portion45. Further, the rib263inserted into the fixing groove44has a shape in which the outer peripheral portion267is welded to the fixing groove44, while the inner peripheral portion266forms a gap with the bottom surface of the fixing groove44. Therefore, even in a case where the flange portion45is not formed into a designed shape and is curved into an umbrella shape, the inner peripheral portion266of the rib263is less likely to excessively interfere with the bottom surface of the fixing groove44. Therefore, a large number of welding burrs are less likely to be generated at the excessively interfering portion and overflow from the fixing groove44. Further, there is little risk that, as a result of excessive interference of the inner peripheral portion266of the rib263, the amount of insertion of the outer peripheral portion267of the rib263into the fixing groove44is insufficient, resulting in non-welding or insufficient welding strength. Since the outer peripheral portion267of the impeller25receives a high fluid pressure, the vane portions261may be peeled off from the flange portion45if welding strength is insufficient. However, in the present embodiment, since the welding strength of the outer peripheral portions267of the vane portions261can be secured, the welded portions are less likely to be peeled off even when a high water pressure is received.

In the present embodiment, the welded portion W welded to the fixing groove44of the flange portion45is a crushed portion where the welding convex portion264protruding from the tip end surface of the outer peripheral portion267of the rib263is crushed. In this way, by providing the welding convex portion264at the outer peripheral portion267, it is possible to avoid that the welding amount at the outer peripheral portion267is insufficient. In addition, since the welding convex portion264is not provided at the inner peripheral portion266, it is possible to prevent the inner peripheral portion266from becoming excessive interference.

In the present embodiment, each of the ten vane portions261includes the vane portion main body262that protrudes from the disc portion26toward the other side L2in the axial direction. The plate thickness of the vane portion main body262is larger than the width of the fixing groove44, and the width of the rib263protruding from the tip end surface of the vane portion main body262is smaller than the width of the fixing groove44. Therefore, the rigidity of the portion (vane portion main body262) that receives water pressure is high. In addition, a gap for accommodating welding burrs can be secured between the fixing groove44and the rib263.

In the present embodiment, the rib263inserted into the fixing groove44includes the intermediate portion265connecting the inner peripheral portion266and the outer peripheral portion267, and the intermediate portion265includes the reference surface269that abuts on the bottom surface of the fixing groove44. When the reference surface269for positioning in the axial direction is provided in the intermediate portion265in the radial direction, even in a case where the flange portion45does not have a designed shape and is curved into an umbrella shape, the inner peripheral portion266is unlikely to become excessive interference, and the welding amount of the outer peripheral portion267is unlikely to be insufficient. In the present embodiment, the reference surface269is provided on all the ribs263, but a configuration in which the reference surface269is provided on only a part of the plurality of vane portions261may be adopted.

In the present embodiment, the tip end surface of the inner peripheral portion266of the rib263is the step surface268recessed to the one side L1in the axial direction with respect to the reference surface269. By providing the step on the tip end surface of the rib263, it is possible to prevent the inner peripheral portion266from becoming excessive interference when the reference surface269abuts on the bottom surface of the fixing groove44.

In the present embodiment, the rib263inserted into the fixing groove44includes the intermediate portion265connecting the inner peripheral portion266and the outer peripheral portion267, and in three of the plurality of vane portions261, the intermediate portions265each include the positioning convex portion270protruding to the other side L2in the axial direction, and the positioning convex portion270is fitted to the positioning concave portions271provided on the bottom surface of the fixing groove44. In this way, even in a case where a gap is provided between the fixing groove44and the rib263so that the welding burrs can be accommodated, the vane wheel24can be positioned in the direction intersecting the axial direction by fitting the positioning convex portion270and the positioning concave portions271. For example, the vane wheel24can be positioned in the circumferential direction. The number of the vane portions261provided with the positioning convex portions270may be four or more, or may be two.