Pumping equipment

Abstract

To provide a pump device which can suppress an outer diameter of a cylindrical part becoming large, even in the case where a penetration part is provided extending in the rotation axis direction with respect to the cylindrical part of a rotor.SOLUTION: In a pump device 1, between a rotor 4 and a radial bearing 11, a penetration part 15 extending in a rotation axis direction is provided, so that a large pressure difference hardly occurs on both sides in a rotation central axis direction with respect to the rotor. The penetration part 15 is constituted by: a first groove 48 formed on an inner peripheral surface of a cylindrical part 40 of the rotor 4; and a second groove 111 formed on an outer peripheral surface of the radial bearing 11. Therefore, even in the case where the penetration part 15 having a sufficient opening area is formed, an opening area of the first groove 48 can be narrow. Therefore, since strength of the cylindrical part 40 hardly lowers by the first groove 48, an outer diameter of the cylindrical part 40 does not need to be large.SELECTED DRAWING: Figure 4

Description

[Technical field]

[0001] The present invention relates to a pump device in which an impeller is rotated by a motor. [Background technology]

[0002] In a pump device, an impeller disposed in a pump chamber is rotated by a motor. In the motor, a rotor has a cylindrical portion that holds a cylindrical radial bearing inside, and a cylindrical drive magnet is fixed to the outer periphery of the cylindrical portion. Here, if a large pressure difference occurs on both sides of the rotor in the direction of the central axis of rotation, the rotor may vibrate in the direction of the central axis of rotation. Therefore, a technology has been proposed that provides a through-portion consisting of a through hole that penetrates the cylindrical portion of the rotor in the direction of the central axis of rotation to suppress the pressure difference (see Patent Document 1). [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Patent No. 5180907 Summary of the Invention [Problem to be solved by the invention]

[0004] However, when a through hole is provided in the cylindrical portion of the rotor as in the technology described in Patent Document 1, in order to ensure the strength of the cylindrical portion, it is necessary to make the cylindrical portion thicker in the radial direction, which results in a problem of an increased outer diameter of the cylindrical portion.

[0005] In view of the above problems, an object of the present invention is to provide a pump device that can prevent the outer diameter of the cylindrical portion from becoming large even when a through portion extending in the direction of the rotation axis is provided with respect to the cylindrical portion of the rotor. [Means for solving the problem]

[0006] In order to solve the above problems, the pump device of the present invention comprises a motor, and an impeller arranged in a pump chamber provided on one side of a rotational center axis relative to the motor and connected to a rotor of the motor, wherein the rotor is provided with a cylindrical portion extending along the rotational center axis, holding a drive magnet on the outside and holding a cylindrical radial bearing on the inside, and a through portion is provided between the cylindrical portion and the radial bearing, the through portion penetrating both sides of the rotational center axis by a first groove extending along the rotational center axis on the inner surface of the cylindrical portion and a second groove extending along the rotational center axis on the outer surface of the radial bearing.

[0007] In the present invention, a through-hole extending in the direction of the rotation axis is provided between the rotor and the radial bearing, so that a large pressure difference is unlikely to occur on both sides of the direction of the rotation center axis with respect to the rotor. Therefore, the rotor is unlikely to vibrate in the direction of the rotation center axis. Here, the through-hole is composed of a first groove formed on the inner peripheral surface of the cylindrical portion and a second groove formed on the outer peripheral surface of the radial bearing. Therefore, even when a through-hole having a sufficient opening area is formed, the opening area of ​​the first groove may be small. Therefore, since the strength of the cylindrical portion is unlikely to be reduced by the first groove, there is no need to increase the outer diameter of the cylindrical portion.

[0008] In the present invention, the rotor may be a resin molded product in which the radial bearing is insert molded. When insert molding is performed, if a pin is placed in the second groove of the radial bearing in a mold, the rotor can be manufactured from a resin molded product in which the radial bearing is insert molded.

[0009] In the present invention, a mode may be adopted in which a mark indicating the position of the first groove is provided on one end of the radial bearing in the rotational axis direction.

[0010] In the present invention, a configuration may be adopted in which a plurality of ribs extending along the central axis of rotation are provided on the outer peripheral surface of the cylindrical portion, and the drive magnet is press-fitted into the cylindrical portion so as to contact the plurality of ribs from the radially outer side. According to this configuration, when the drive magnet is press-fitted into the cylindrical portion, eccentricity between the drive magnet and the cylindrical portion can be suppressed. In addition, since the drive magnet and the cylindrical portion are in contact with each other via the ribs, even when a sudden temperature change occurs, a large stress is unlikely to be applied to the drive magnet, and cracking of the drive magnet can be suppressed.

[0011] In the present invention, the first groove may be provided at an angular position where it overlaps with the rib when viewed from the radial direction. According to this aspect, since the rib overlaps with the through-hole, the rib can prevent the wall thickness of the cylindrical portion from becoming too thin. Effect of the Invention

[0012] In the present invention, a through-hole extending in the direction of the rotation axis is provided between the rotor and the radial bearing, so that a large pressure difference is unlikely to occur on both sides of the direction of the rotation center axis with respect to the rotor. Therefore, the rotor is unlikely to vibrate in the direction of the rotation center axis. Here, the through-hole is composed of a first groove formed on the inner peripheral surface of the cylindrical portion and a second groove formed on the outer peripheral surface of the radial bearing. Therefore, even when a through-hole having a sufficient opening area is formed, the opening area of ​​the first groove may be small. Therefore, since the strength of the cylindrical portion is unlikely to be reduced by the first groove, there is no need to increase the outer diameter of the cylindrical portion. [Brief description of the drawings]

[0013] [Figure 1] 1 is a perspective view showing an embodiment of a pump device and a motor to which the present invention is applied; [Diagram 2] FIG. 2 is a vertical cross-sectional view of the pump device and the motor shown in FIG. [Diagram 3] FIG. 3 is an explanatory diagram of the impeller and the like shown in FIG. 2. [Figure 4] FIG. 3 is a perspective view of the rotor and the like shown in FIG. 2. [Diagram 5] 3 is a longitudinal sectional view showing a state in which a drive magnet is fixed to the rotor shown in FIG. 2. [Figure 6] 3 is a cross-sectional view showing a state in which a drive magnet is fixed to the rotor shown in FIG. 2. [Figure 7] FIG. 3 is a cross-sectional view of the rotor shown in FIG. 2. [Figure 8] 3 is a perspective view of the rotor and the like shown in FIG. 2 as viewed from the other side in the direction of the central axis of rotation. [Figure 9] 3 is a bottom view of the rotor and the like shown in FIG. 2 as viewed from the other side in the direction of the central axis of rotation. [Figure 10] 3 is a plan view of the rotor and the like shown in FIG. 2 as viewed from one side in the direction of the central axis of rotation. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0014] Hereinafter, a motor 10 and a pump device 1 according to an embodiment of the present invention will be described with reference to the drawings. In the following description, the direction of the rotational axis L means the direction in which the rotational axis L extends, the radial direction on the radially inner side and the radially outer side means the radial direction centered on the rotational axis L, and the circumferential direction means the rotational direction centered on the rotational axis L.

[0015] (Overall composition) FIG. 1 is a perspective view showing one embodiment of a pump device 1 and a motor 10 to which the present invention is applied. FIG. 2 is a vertical cross-sectional view of the pump device 1 and the motor 10 shown in FIG. 1. FIG. 3 is an explanatory diagram of an impeller 25 and the like shown in FIG. 2. In FIGS. 1 and 2, the pump device 1 includes a case 2 having an intake port 21a and a discharge port 22a, a motor 10 disposed on the other side L2 of the case 2 in the direction of the central axis L of rotation, and an impeller disposed in a pump chamber 20 inside the case 2. The pump device 1 has an impeller 25, which is driven to rotate about a central axis L of rotation by the motor 10. The motor 10 includes a cylindrical stator 3, a rotor 4 arranged inside the stator 3, a resin housing 6 that covers the stator 3, and a round bar-shaped support shaft 5 that rotatably supports the rotor 4. The support shaft 5 is made of metal or ceramic. In the pump device 1 of this embodiment, the fluid is liquid, and the pump device 1 is used under conditions where the environmental temperature and fluid temperature are likely to change.

[0016] The case 2 constitutes a wall surface 23 on one side L1 of the pump chamber 20 in the direction of the rotation center axis L, and a side wall 29 extending in the circumferential direction. The case 2 includes a suction pipe 21 extending along the rotation center axis L and a discharge pipe 22 extending in a direction perpendicular to the rotation center axis L, and the suction pipe 21 and the discharge pipe 22 each include a suction port 21a and a discharge port 22a at their ends. The suction pipe 21 is provided concentrically with the rotation center axis L.

[0017] In the motor 10, the stator 3 has a stator core 31, insulators 32, 33 held by the stator core 31, and a coil 35 wound around the stator core 31 with the insulators 32, 33 interposed therebetween.

[0018] The rotor 4 has a cylindrical portion 40 that extends from a position facing the stator 3 on the radial inside toward the pump chamber 20 along the central axis of rotation L, and the cylindrical portion 40 opens at the pump chamber 20. A cylindrical drive magnet 8 is held on the outer circumferential surface of the cylindrical portion 40 so as to face the stator 3 on the radial inside. The drive magnet 8 is, for example, a neodymium bonded magnet.

[0019] As shown in FIG. 2 and FIG. 3, in the rotor 4, a disk-shaped flange portion 45 is formed at the end of one side L1 in the direction of the rotation central axis L of the cylindrical portion 40, and the disk 26 is connected to the flange portion 45 from the one side L1 in the direction of the rotation central axis L. A central hole 260 is formed in the center of the disk 26. A plurality of blade portions 261 are formed at equal angular intervals on the surface of the disk 26 facing the flange portion 45, and extend radially outward while curving in an arc from the periphery of the central hole 260, and the disk 26 is fixed to the flange portion 45 via the blade portions 261. Therefore, the flange portion 45 and the disk 26 form the impeller 25 connected to the cylindrical portion 40 of the rotor 4. In this embodiment, the disk 26 is inclined so that the radially outer side is located closer to the flange portion 45 than the radially inner side. In this embodiment, a groove 454 is formed in the flange portion 45, with which the ends of the blade portions 261 overlap. Furthermore, a hole 455 is formed in the flange portion 45 at a position overlapping with the groove 454, and a protrusion 265 that fits into the hole 455 is formed in the blade portion 261 of the disk 26. The hole 455 is a through hole, as will be understood from Fig. 8 which will be referred to in the description below.

[0020] 2 again, in the rotor 4, a cylindrical radial bearing 11 is held on the radial inside of the cylindrical portion 40, and the rotor 4 is rotatably supported by the support shaft 5 via the radial bearing 11. An end portion 51 on the other side L2 of the support shaft 5 in the direction of the central axis L of rotation is held in an axial hole 65 formed in a bottom wall 63 of the housing 6. In the case 2, a receiving portion 280 is formed on the side of the pump chamber 20 opposite to the end portion 52 of the support shaft 5 on the pump chamber 20 side, which limits the movable range of the support shaft 5 toward the pump chamber 20 side. The case 2 is provided with three support portions 27 extending from the inner peripheral surface of the suction pipe 21 to the motor 10 side. At the end of the support portion 27, a tubular portion 28 is formed in which an end portion 52 on one side L1 of the central axis L of the support shaft 5 is located inside, and the receiving portion 280 is formed by the bottom of the tubular portion 28 on one side L1 in the direction of the central axis L of rotation. An annular thrust bearing 12 is attached to the end 52 of the support shaft 5, and the thrust bearing 12 is located between the radial bearing 11 and the cylindrical portion 28. At least a portion of the end 51 of the support shaft 5 and the shaft hole 65 are formed to have a D-shaped cross section, and the end 52 of the support shaft 5 and the hole of the thrust bearing 12 are also formed to have a D-shaped cross section. Therefore, the rotation of the support shaft 5 and the thrust bearing 12 is prevented. is.

[0021] The housing 6 is a partition member having a first partition portion 61 facing the wall surface 23 of the pump chamber 20 and a second partition portion 62 interposed between the stator 3 and the drive magnet 8. The housing 6 also has a cylindrical body portion 66 that covers the stator 3 from the outside in the radial direction. Therefore, the housing 6 is a resin sealing member 60 that covers the stator 3 from both sides in the radial direction and both sides in the direction of the central axis L of rotation, and is a resin portion formed when the stator 3 is insert-molded using polyphenylene sulfide (PPS) or the like.

[0022] A cover 18 is fixed to an end portion 64 on the other side L2 of the housing 6 in the direction of the central axis L of rotation from the other side L2 in the direction of the central axis L of rotation, and a board 19 on which a circuit for controlling power supply to the coil 35 and the like are provided is disposed between the cover 18 and the bottom wall 63 of the housing 6. The board 19 is fixed to the housing 6 by a screw 92. A metallic winding terminal 71 protruding from the stator 3 to the other side L2 in the direction of the central axis L of rotation through the bottom wall 63 of the housing 6 and a metallic connector terminal 75 held by the housing 6 are connected to the board 19 by solder. Electronic components constituting a drive circuit are mounted on the board 19. Wiring and the like are also formed on the board 19.

[0023] A cylindrical connector housing 69 is formed in the housing 6, and an end 750 of a connector terminal 75 is located inside the connector housing 69. Therefore, when a connector is connected to the connector housing 69 and a signal or the like is supplied, the signal is supplied to each coil 35 via the connector terminal 75, the board 19, and the winding terminal 71. As a result, the rotor 4 rotates about the central axis of rotation L. This causes the impeller 25 to rotate within the pump chamber 20, creating a negative pressure inside the pump chamber 20, so that the fluid is sucked into the pump chamber 20 from the suction pipe 21 and discharged from the discharge pipe 22.

[0024] (Fixing structure of the drive magnet 8 to the cylindrical portion 40 of the rotor 4, etc.) FIG. 4 is a perspective view of the rotor 4 etc. shown in FIG. 2. FIG. 5 is a longitudinal sectional view showing the state where the drive magnet 8 is fixed to the rotor 4 shown in FIG. 2. FIG. 6 is a transverse sectional view showing the state where the drive magnet 8 is fixed to the rotor 4 shown in FIG. 2. FIG. 7 is a longitudinal sectional view of the rotor 4 shown in FIG. 2. FIG. 8 is a perspective view of the rotor 4 etc. shown in FIG. 2 as viewed from the other side L2 in the direction of the central axis L of rotation. FIG. 9 is a bottom view of the rotor 4 etc. shown in FIG. 2 as viewed from the other side L2 in the direction of the central axis L of rotation.

[0025] 2, 4, 5, 6, 7, 8, and 9, in the motor 10, an annular seat 42 is formed on the outer circumferential side of the cylindrical portion 40 of the rotor 4, protruding radially outward at a position spaced from the flange portion 45 to the other side L2, and the cylindrical portion 40, from the seat 42 to the other side L2, serves as a magnet holding portion 43. The magnet holding portion 43 fits inside the cylindrical drive magnet 8 to hold the drive magnet 8. In this case, the seat 42 supports an end 81 of the drive magnet 8 on one side L1.

[0026] On the inner peripheral side of the cylindrical portion 40 of the rotor 4, a first convex portion 441 having a circular ring shape is formed at a position overlapping with the seat portion 42 when viewed from the radial direction, and on the other side L2 of the first convex portion 441, a second convex portion 442 having a circular ring shape is formed protruding radially inward.

[0027] 8 is provided between the seat portion 42 and the flange portion 45. The through holes 44 penetrate the cylindrical portion 40 in the radial direction. In this embodiment, the through holes 44 are provided at two positions in the cylindrical portion 40 that are angularly shifted by 180 degrees from each other. Therefore, when the impeller 25 rotates, a part of the fluid flows from the pump chamber 20 to the inside of the cylindrical portion 40 of the rotor 4. After being sucked into the pump chamber 20, the fluid passes through the through hole 44 of the cylindrical portion 40 and flows along the bottom wall 24 back into the pump chamber 20. As a result, air or the like that has become mixed in the fluid is discharged from the pump chamber 20.

[0028] In the rotor 4 configured in this manner, ribs 46 extending along the central axis of rotation L are provided at multiple locations in the circumferential direction on the outer circumferential surface of the magnet holding portion 43, and the drive magnet 8 is press-fitted into the magnet holding portion 43 so as to contact the multiple ribs 46 from the radial outside. Therefore, between the magnet holding portion 43 and the drive magnet 8, a gap G (see FIG. 6) is formed between two ribs 46 adjacent to each other in the circumferential direction.

[0029] The seat 42 is also formed with a protrusion 421 that fits into a recess 811 formed in an end 81 of one side L1 of the drive magnet 8. The protrusion 421 fits into the recess 811 to determine the circumferential angular position of the drive magnet 8 and prevent the drive magnet 8 from rotating. The seat 42 is also formed with a recess 422 at a position spaced apart from the protrusion 421 in the circumferential direction, and the recess 422 extends from the inner edge to the outer edge of the seat 42. When the drive magnet 8 is fixed to the magnet holding portion 43, the recess 422 is connected to a gap G sandwiched between two ribs 46 adjacent to each other in the circumferential direction.

[0030] At the end 47 of the cylindrical portion 40 opposite the seat portion 42, crimped portions 471 (see Figure 9) that overlap the driving magnet 8 are provided at multiple locations in the circumferential direction, and at least a portion of the gap G is open between two of the crimped portions 471 that are adjacent to each other in the circumferential direction.

[0031] In this embodiment, the ribs 46 and the recesses 422 are formed at six positions in the circumferential direction at equal angular intervals, and the recesses 811, the protrusions 421, and the crimped portions 471 are formed at three positions in the circumferential direction at equal angular intervals. Note that, at positions in the end portion 81 of the drive magnet 8 that are spaced apart in the circumferential direction from the recesses 811, gate marks 812 formed when the drive magnet 8 was molded are formed at three positions in the circumferential direction at equal angular intervals.

[0032] In the pump device 1 equipped with the motor 10 thus configured, when the drive magnet 8 is press-fitted into the cylindrical portion 40 of the motor 10 that drives the impeller 25, the drive magnet 8 comes into contact with the rib 46 formed on the cylindrical portion 40 of the rotor 4 from the radially outer side. This makes it possible to suppress eccentricity between the drive magnet 8 and the cylindrical portion 40. In addition, since the drive magnet 8 and the cylindrical portion 40 are in contact with each other via the rib 46, even when a sudden temperature change occurs, a large stress is unlikely to be applied to the drive magnet 8, so that cracking of the drive magnet 8 can be suppressed.

[0033] Furthermore, the seat portion 42 supporting the end portion 81 of the drive magnet 8 in the rotor 4 is provided with recesses 422 at multiple locations in the circumferential direction, and a gap G sandwiched between two ribs 46 adjacent to each other in the circumferential direction between the cylindrical portion 40 and the drive magnet 8 is connected to the recesses 422. Therefore, the fluid flowing through the pump device 1 can flow through the recesses 422 of the seat portion 42 and the gap G between the cylindrical portion 40 and the drive magnet 8. This allows the rotor 4 and the drive magnet 8 to be cooled, thereby suppressing heat generation from the drive magnet 8, etc.

[0034] Furthermore, crimped portions 471 overlapping the drive magnet 8 are provided at multiple locations in the circumferential direction on the end portion 47 of the cylindrical portion 40 opposite the seat portion 42, and at least a portion of the gap G is open between two crimped portions 471 adjacent to each other in the circumferential direction among the multiple crimped portions 471. Therefore, the fluid flowing through the recess 422 of the seat portion 42 and the gap G between the cylindrical portion 40 and the drive magnet 8 can pass between the crimped portions 471, so that heat generation of the drive magnet 8, etc. can be efficiently suppressed.

[0035] (Structure of the penetrating portion 15 of the rotor 45) FIG. 10 is a plan view of the rotor 4 and the like shown in FIG. 2, seen from one side L1 in the direction of the rotation central axis L. As shown in FIGS. 4, 5, 6, and 7, in the motor 10 and the pump device 1, between the cylindrical portion 40 of the rotor 4 and the radial bearing 11, a through-portion 15 is provided that penetrates both sides of the rotation central axis L by a first groove 48 extending along the rotation central axis L on the inner peripheral surface of the cylindrical portion 40 and a second groove 111 extending along the rotation central axis L on the outer peripheral surface of the radial bearing 11. More specifically, the second groove 111 overlaps the first groove 48 from the radially inner side, and constitutes the through-portion 15 together with the first groove 48. The first groove 48 and the second groove 111 are each a groove having a semicircular cross section. Therefore, the through-portion 15 extends linearly as a hole having a circular cross section. Here, the second grooves 111 are formed at four positions in the circumferential direction at equal angular intervals, and the first grooves 48 are formed at two positions in the circumferential direction at equal angular intervals. Therefore, the two first grooves 48 overlap two of the four second grooves 111 from the radial outside to form the through-portion 15.

[0036] In the cylindrical portion 40, the first grooves 48 are provided at angular positions that overlap with the ribs 46 when viewed from the radial direction. Therefore, the formation of the first grooves 48 can prevent the wall thickness of the cylindrical portion 40 from becoming too thin, by the ribs 46.

[0037] Here, the cylindrical portion 40 is formed with annular first and second protrusions 441 and 442 that protrude radially inward and overlap with the step 116 on one side L1 in the direction of the rotation center axis L of the radial bearing 11 and the step 117 on the other side L2 in the direction of the rotation center axis L. On the other hand, the first groove 48 is formed along the inner peripheral surface of the cylindrical portion 40. Therefore, the first groove 48 penetrates the first and second protrusions 441 and 442 as a circular hole, and does not reach the inner edge of the first and second protrusions 441 and 442. Therefore, the inner edge of the first and second protrusions 441 and 442 each have a continuous arc shape.

[0038] In this embodiment, since the through-hole 15 is provided to penetrate both sides of the rotation axis L of the rotor 4, a large pressure difference is unlikely to occur on both sides of the rotation axis L direction with respect to the rotor 4. Therefore, the rotor 4 is unlikely to vibrate in the rotation axis L direction. Here, the through-hole 15 is configured by the first groove 48 formed on the inner peripheral surface of the cylindrical portion 40 and the second groove 111 formed on the outer peripheral surface of the radial bearing 11 overlapping in the radial direction. Therefore, even when the through-hole 15 having a sufficient opening area is formed, the opening area of ​​the first groove 48 may be narrow. Therefore, since the strength of the cylindrical portion 40 is unlikely to be reduced by the first groove 48, there is no need to increase the outer diameter of the cylindrical portion 40.

[0039] Moreover, the first groove 48 and the second groove 111 extend linearly. Therefore, the rotor 4 can be configured as a resin molded product in which the radial bearing 11 is insert molded. More specifically, when performing insert molding, a pin with a circular cross section is placed in the second groove 111 of the radial bearing 11 in a mold and insert molded, and then the pin is removed, whereby the rotor 4 can be manufactured by insert molding while forming the through portion 15.

[0040] Furthermore, a groove-shaped mark 119 indicating the position of the second groove 111 is provided at an end 118 on one side L1 in the direction of the rotation center axis L of the radial bearing 11. Therefore, during insert molding, the pins can be positioned, etc., based on the mark 119 provided at the end 118 of the radial bearing 11.

[0041] [Other embodiments] In the above embodiment, the housing 6 is a resin sealing member 60 that covers the stator 3 from both radial sides and both sides in the direction of the central axis of rotation L. However, the present invention can be applied to a case where the housing 6 is a member that covers only the inner side of the stator 3 in the radial direction and the other side L2 in the direction of the central axis of rotation L. You may do so. [Explanation of symbols]

[0042] Reference Signs List 1...pump device, 2...case, 3...stator, 4...rotor, 5...support shaft, 6...housing, 8...drive magnet, 10...motor, 11...radial bearing, 15...penetration portion, 18...cover, 19...substrate, 20...pump chamber, 25...impeller, 35...coil, 40...cylindrical portion, 42...seat portion, 43...magnet holding portion, 45...flange portion, 46...rib, 48...first groove, 60...resin sealing member, 65...shaft hole, 111...second groove, 119...mark, 261...blade portion, 471...crimped portion, G...gap, L...rotational center axis

Claims

1. The pump includes a motor, and an impeller disposed in a pump chamber provided on one side of a rotational central axis of the motor and connected to a rotor of the motor, The rotor is provided with a cylindrical portion that extends along the central axis of rotation, holds a drive magnet on an outer side, and holds a cylindrical radial bearing on an inner side. Between the cylindrical portion and the radial bearing, a through-portion is provided that penetrates both sides of the rotation center axis by a first groove that extends along the rotation center axis on an inner peripheral surface of the cylindrical portion, and a second groove that extends along the rotation center axis on an outer peripheral surface of the radial bearing and overlaps with the first groove from the radial inside, A plurality of ribs extending along the central axis of rotation are provided on an outer circumferential surface of the cylindrical portion, the drive magnet is press-fitted into the cylindrical portion so as to be in contact with the plurality of ribs from the radially outer side, The pump device according to claim 1, wherein the first groove is provided at an angular position where it overlaps with the rib when viewed from a radial direction.

2. 2. The pump device according to claim 1, The pump device according to claim 1, wherein the rotor is a resin molded product into which the radial bearing is insert-molded.

3. 3. The pump device according to claim 2, A pump device characterized in that a mark indicating the position of the first groove is provided on one end of the radial bearing in the rotational axis direction.

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