CN115479032A - Pump device - Google Patents

Abstract

The invention provides a pump device, which can restrain the outer diameter of a cylindrical part from increasing even if a through part extending along the rotation axis direction is arranged on the cylindrical part of a rotor. In the pump device (1), a through part (15) extending along the rotation axis direction is provided between the rotor (4) and the radial bearing (11), so that a large pressure difference is not easily generated on both sides of the rotor in the rotation central axis direction. The penetrating section (15) is formed of a first groove (48) formed in the inner peripheral surface of the cylindrical section (40) of the rotor (4) and a second groove (111) formed in the outer peripheral surface of the radial bearing (11). Therefore, even when the through portion (15) having a sufficient opening area is formed, the opening area of the first groove (48) can be made narrow. Therefore, the strength of the cylindrical portion (40) is not easily reduced by the first groove (48), and it is not necessary to increase the outer diameter of the cylindrical portion (40).

Description

Pump device

Technical Field

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

Background

In the pump device, an impeller disposed in a pump chamber is rotated by a motor. In a motor, a rotor includes a cylindrical portion that holds a cylindrical radial bearing inside, and a cylindrical drive magnet is fixed to the outer circumferential side of the cylindrical portion. Here, if a large pressure difference is generated between the rotor and both sides in the rotation center axis direction, the rotor may vibrate in the rotation center axis direction. Therefore, a technique has been proposed in which a penetrating portion formed of a penetrating hole penetrating a cylindrical portion of the rotor in the rotation central axis direction is provided to suppress the pressure difference (see patent document 1).

Documents of the prior art

Patent literature

Patent document 1: japanese patent No. 5180907

Disclosure of Invention

However, when a through-hole is provided in the cylindrical portion of the rotor as in the technique described in patent document 1, the cylindrical portion needs to be radially thick in order to ensure the strength of the cylindrical portion, and as a result, the outer diameter of the cylindrical portion becomes large. In view of the above problems, an object of the present invention is to provide a pump device capable of suppressing an increase in the outer diameter of a cylindrical portion of a rotor even when the cylindrical portion is provided with a through portion extending in the rotation axis direction.

In order to solve the above problem, a pump device according to the present invention includes: a motor; and an impeller that is disposed in a pump chamber provided on one side of a rotation center axis with respect to the motor and is connected to a rotor of the motor, wherein the rotor is provided with a cylindrical portion that extends along the rotation center axis, holds a drive magnet on an outer side, and holds a cylindrical radial bearing on an inner side, and a through portion that penetrates both sides of the rotation center axis is provided between the cylindrical portion and the radial bearing, the through portion being formed 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.

In the present invention, since the penetrating portion extending in the rotation axis direction is provided between the rotor and the radial bearing, a large pressure difference is less likely to occur on both sides of the rotor in the rotation center axis direction. Therefore, the rotor is less likely to vibrate in the rotational center axis direction. Here, the penetrating portion is formed of a first groove formed in the inner peripheral surface of the cylindrical portion and a second groove formed in the outer peripheral surface of the radial bearing. Therefore, even when the through portion having a sufficient opening area is formed, the opening area of the first groove can be made narrow. Therefore, the strength of the cylindrical portion is less likely to be reduced by the first groove, and it is not necessary to increase the outer diameter of the cylindrical portion.

In the present invention, the following manner may be adopted: the rotor is a resin molded product obtained by insert molding the radial bearing. In the case of insert molding, if the pin is disposed in the second groove of the radial bearing in the mold, the rotor can be manufactured from a resin molded product in which the radial bearing is insert molded.

In the present invention, the following manner may be adopted: on an end portion on one side in a rotational axis direction of the radial bearing, a mark showing a position of the first groove is provided.

In the present invention, the following manner may be adopted: a plurality of ribs extending along the rotation center axis are provided on an 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 a radially outer side. According to this aspect, when the drive magnet is press-fitted into the cylindrical portion, eccentricity between the drive magnet and the cylindrical portion can be suppressed. Further, since the driving magnet and the cylindrical portion are in contact with each other via the rib, a large stress is not easily applied to the driving magnet even when a rapid temperature change occurs, and thus, breakage of the driving magnet can be suppressed.

In the present invention, the following manner may be adopted: the first groove is provided at an angular position overlapping with the rib when viewed from the radial direction. According to this aspect, since the rib overlaps with the penetrating portion, the wall thickness of the cylindrical portion can be suppressed from becoming too thin by the rib.

Effects of the invention

In the present invention, since the through portion extending in the rotation axis direction is provided between the rotor and the radial bearing, a large pressure difference is less likely to occur between the rotor and the radial bearing on both sides in the rotation center axis direction. Therefore, the rotor is less likely to vibrate in the rotational center axis direction. Here, the penetrating portion is formed of a first groove formed in the inner peripheral surface of the cylindrical portion and a second groove formed in the outer peripheral surface of the radial bearing. Therefore, even when the penetrating portion having a sufficient opening area is formed, the opening area of the first groove can be made narrow. Therefore, the strength of the cylindrical portion is less likely to be reduced by the first groove, and therefore, it is not necessary to increase the outer diameter of the cylindrical portion.

Drawings

Fig. 1 is a perspective view showing one embodiment of a pump device and a motor to which the present invention is applied.

Fig. 2 is a longitudinal sectional view of the pump device and the motor shown in fig. 1.

Fig. 3 is an explanatory view of the impeller and the like shown in fig. 2.

Fig. 4 is a perspective view of the rotor and the like shown in fig. 2.

Fig. 5 is a longitudinal sectional view showing a state in which the driving magnet is fixed to the rotor shown in fig. 2.

Fig. 6 is a cross-sectional view showing a state in which a driving magnet is fixed to the rotor shown in fig. 2.

Fig. 7 is a cross-sectional view of the rotor shown in fig. 2.

Fig. 8 is a perspective view of the rotor and the like shown in fig. 2 viewed from the other side in the rotation center axis direction.

Fig. 9 is a bottom view of the rotor and the like shown in fig. 2 as viewed from the other side in the rotational center axis direction.

Fig. 10 is a plan view of the rotor and the like shown in fig. 2, as viewed from one side in the direction of the rotation center axis.

Detailed Description

Hereinafter, the motor 10 and the pump device 1 according to the embodiment of the present invention will be described with reference to the drawings. In the following description, the direction of the rotation center axis L refers to a direction in which the rotation center axis L extends, the radial directions of the radially inner and radially outer sides refer to radial directions centered on the rotation center axis L, and the circumferential direction refers to a rotation direction centered on the rotation center axis L.

(Overall Structure)

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 longitudinal sectional view of the pump device 1 and the motor 10 shown in fig. 1. Fig. 3 is an explanatory view of the impeller 25 and the like shown in fig. 2. In fig. 1 and 2, a pump apparatus 1 includes: a casing 2 having a suction port 21a and a discharge port 22a; a motor 10 disposed on the other side L2 in the direction of the rotation center axis L with respect to the housing 2; and an impeller 25 disposed in the pump chamber 20 inside the housing 2, the impeller 25 being driven by the motor 10 to rotate about the rotation center axis L. The motor 10 includes a cylindrical stator 3, a rotor 4 disposed inside the stator 3, a resin case 6 covering the stator 3, and a support shaft 5 rotatably supporting the rotor 4 in a circular bar shape. The fulcrum 5 is made of metal or ceramic. In the pump device 1 of the present embodiment, the fluid is a liquid, and the pump device 1 is used under conditions where the ambient temperature or the fluid temperature is likely to change.

The housing 2 constitutes a wall surface 23 of one side L1 in the direction of the rotational center axis L of the pump chamber 20 and a side wall 29 extending in the circumferential direction. The casing 2 has a suction pipe 21 extending along the rotation center axis L and a discharge pipe 22 extending in a direction orthogonal to the rotation center axis L, and the suction pipe 21 and the discharge pipe 22 have a suction port 21a and a discharge port 22a at end portions, respectively. The suction pipe 21 is disposed concentrically with respect to the rotation center axis L.

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

The rotor 4 has a cylindrical portion 40, the cylindrical portion 40 extending from a position radially inward opposite to the stator 3 toward the pump chamber 20 along the rotation center axis L, the cylindrical portion 40 opening at the pump chamber 20. A cylindrical drive magnet 8 is held on the outer peripheral surface of the cylindrical portion 40 so as to face the stator 3 on the radially inner side. The drive magnet 8 is, for example, a neodymium bonded magnet.

As shown in fig. 2 and 3, in the rotor 4, a disk-shaped flange 45 is formed at an end portion of one side L1 in the direction of the rotation center axis L of the cylindrical portion 40, and the disk 26 is connected to the flange 45 from the one side L1 in the direction of the rotation center axis L. A central hole 260 is formed in the center of the circular plate 26. A plurality of blade portions 261 curved in an arc shape from the periphery of the center hole 260 and extending radially outward are formed at equal angular intervals on the surface of the disk 26 facing the flange portion 45, and the disk 26 is fixed to the flange portion 45 via the blade portions 261. Therefore, the flange 45 and the circular plate 26 constitute the impeller 25 connected to the cylindrical portion 40 of the rotor 4. In the present embodiment, the disk 26 is inclined so that the radially outer side is located closer to the flange 45 than the radially inner side.

In fig. 2 again, a cylindrical radial bearing 11 is held in the rotor 4 radially inward of the cylindrical portion 40, and the rotor 4 is rotatably supported on the support shaft 5 via the radial bearing 11. The end 51 of the other side L2 of the pivot shaft 5 in the direction of the rotation center axis L is held in a shaft hole 65 formed in the bottom wall 63 of the housing 6. The housing 2 is formed with a receiving portion 280 which faces the end 52 of the support shaft 5 on the pump chamber 20 side and limits the movable range of the support shaft 5 toward the pump chamber 20 side. The housing 2 includes 3 support portions 27 extending from the inner peripheral surface of the suction pipe 21 toward the motor 10. A tube portion 28 is formed at the end of the support portion 27 such that the end 52 of one side L1 in the direction of the rotation center axis L of the support shaft 5 is located inside, and a receiving portion 280 is formed by the bottom of one side L1 in the direction of the rotation center axis L of the tube portion 28. An annular thrust bearing 12 is attached to an end 52 of the support shaft 5, and the thrust bearing 12 is disposed between the radial bearing 11 and the cylindrical portion 28. At least a part of the end 51 of the support shaft 5 and the shaft hole 65 is formed in a D-shaped cross section, and the end 52 of the support shaft 5 and the hole of the thrust bearing 12 are formed in a D-shaped cross section. Therefore, the rotation of the support shaft 5 and the thrust bearing 12 is prevented.

The housing 6 is a partition wall member having a first partition wall portion 61 facing the wall surface 23 of the pump chamber 20 and a second partition wall portion 62 interposed between the stator 3 and the drive magnet 8. The housing 6 has a cylindrical body portion 66 covering the stator 3 from the radially outer side. Therefore, the housing 6 is a resin seal member 60 that covers the stator 3 from both sides in the radial direction and both sides in the direction of the rotation center axis L, and is a resin portion when the stator 3 is insert-molded with Polyphenylene Sulfide (PPS) or the like.

A cover 18 is fixed to an end portion 64 of the other side L2 of the housing 6 in the direction of the rotation center axis L from the other side L2 in the direction of the rotation center axis L, a substrate 19 is disposed between the cover 18 and the bottom wall 63 of the housing 6, and the substrate 19 is provided with a circuit and the like for controlling the power supply to the coil 35. The base plate 19 is fixed to the housing 6 by screws 92. A metallic winding terminal 71 that protrudes from the stator 3 to the other side L2 in the direction of the rotation center axis L through the bottom wall 63 of the housing 6 and a metallic connector terminal 75 that is held by the housing 6 are connected to the substrate 19 by solder. Electronic components constituting a drive circuit are mounted on the substrate 19. Further, wiring and the like are formed on the substrate 19.

A cylindrical connector housing 69 is formed in the housing 6, and an end 750 of the connector terminal 75 is positioned inside the connector housing 69. Therefore, when a signal or the like is supplied by connecting the connector to the connector housing 69, the signal is supplied to each coil 35 via the connector terminal 75, the substrate 19, the winding terminal 71, and the metal connector terminal 75 held by the housing 6. As a result, the rotor 4 rotates around the rotation center axis L. As a result, the impeller 25 rotates in the pump chamber 20, and the inside of the pump chamber 20 becomes a negative pressure, so that the fluid is sucked into the pump chamber 20 from the suction pipe 21 and discharged from the discharge pipe 22.

(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 and the like shown in fig. 2. Fig. 5 is a longitudinal sectional view showing how the drive magnet 8 is fixed to the rotor 4 shown in fig. 2. Fig. 6 is a cross-sectional view showing how 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 and the like shown in fig. 2 as viewed from the other side L2 in the direction of the rotation center axis L. Fig. 9 is a bottom view of the rotor 4 and the like shown in fig. 2, as viewed from the other side L2 in the direction of the rotation center axis L.

As shown in fig. 2, 4, 5, 6, 7, 8, and 9, in the motor 10, an annular seat portion 42 protruding outward in the radial direction is formed on the outer peripheral side of the cylindrical portion 40 of the rotor 4 at a position spaced apart from the flange portion 45 toward the other side L2, and a magnet holding portion 43 is formed in the cylindrical portion 40 from the seat portion 42 toward the other side L2. The seat 42 is fitted into the inside of the cylindrical drive magnet 8 to hold the drive magnet 8. At this time, the seat 42 supports the end 81 of the one side L1 of the driving magnet 8.

An annular first convex portion 441 protruding radially inward is formed on the inner circumferential side of the cylindrical portion 40 of the rotor 4 at a position overlapping the seat portion 42 when viewed in the radial direction, and an annular second convex portion 442 protruding radially inward is formed on the other side L2 of the first convex portion 441.

Further, a through hole 44 shown in fig. 8 is provided between the seat portion 42 and the flange portion 45. The through hole 44 penetrates the cylindrical portion 40 in the radial direction. In the present embodiment, the through-hole 44 is provided at two positions shifted from each other by 180 degrees in angular position at the cylindrical portion 40. Therefore, when the impeller 25 rotates, a part of the fluid flows from the pump chamber 20 into the inside of the cylindrical portion 40 of the rotor 4, and then flows into the pump chamber 20 again along the bottom wall 24 through the through hole 44 of the cylindrical portion 40. Therefore, air or the like mixed in the fluid is discharged from the pump chamber 20.

In the rotor 4 configured as described above, the magnet holding portion 43 is provided with the ribs 46 extending along the rotation center axis L at a plurality of positions in the circumferential direction on the outer circumferential surface thereof, and the drive magnet 8 is press-fitted into the magnet holding portion 43 so as to contact the plurality of ribs 46 from the radially outer side. Therefore, a gap G (see fig. 6) is formed between two circumferentially adjacent ribs 46 between the magnet holding portion 43 and the drive magnet 8.

In addition, a convex portion 421 that fits into a concave portion 811 formed at the end portion 81 of the one side L1 of the drive magnet 8 is formed at the seat portion 42. The convex portion 421 defines the circumferential angular position of the drive magnet 8 by fitting into the concave portion 811, and prevents the rotation of the drive magnet 8. In addition, at the seat portion 42, a concave portion 422 is formed at a position separated from the convex portion 421 in the circumferential direction, and the concave portion 422 extends from the inner edge to the outer edge of the seat portion 42. When the driving magnet 8 is fixed to the magnet holding portion 43, the recess 422 is continuous with the gap G sandwiched by the two ribs 46 adjacent in the circumferential direction.

In an end portion 47 of the cylindrical portion 40 on the opposite side of the seat portion 42, caulking portions 471 (see fig. 9) overlapping the drive magnet 8 are provided at a plurality of circumferential locations, and at least a part of the gap G is opened between the caulking portions 471 at two circumferentially adjacent locations among the plurality of locations of the caulking portions 471.

In the present embodiment, the ribs 46 are formed at six circumferential locations at equal angular intervals, and the recesses 811, the projections 421, the recesses 422, and the caulking portions 471 are formed at three circumferential locations at equal angular intervals. Gate marks 812 at the time of molding the drive magnet 8 are formed at three positions in the circumferential direction at equal angular intervals at positions spaced apart from the concave portion 811 in the circumferential direction at the end portion 81 of the drive magnet 8.

In the pump device 1 including the motor 10 configured as described above, when the drive magnet 8 is press-fitted into the cylindrical portion 40 in the motor 10 that drives the impeller 25, the drive magnet 8 comes into contact with the rib 46 formed in the cylindrical portion 40 of the rotor 4 from the radially outer side. Therefore, eccentricity between the driving magnet 8 and the cylindrical portion 40 can be suppressed. Further, since the driving magnet 8 and the cylindrical portion 40 are in contact with each other via the rib 46, a large stress is not easily applied to the driving magnet 8 even when a rapid temperature change occurs, and thus, breakage of the driving magnet 8 can be suppressed.

Further, the seat portion 42 of the rotor 4 that supports the end portion 81 of the drive magnet 8 is provided with recesses 422 at a plurality of locations in the circumferential direction, and a gap G between two ribs 46 adjacent in the circumferential direction is continuous with the recesses 422 between the cylindrical portion 40 and the drive magnet 8. Therefore, the fluid flowing through the pump device 1 can flow through the concave portion 422 of the seat portion 42 and the gap G between the cylindrical portion 40 and the drive magnet 8. Therefore, the rotor 4 and the driving magnet 8 can be cooled, and heat generation of the driving magnet 8 and the like can be suppressed.

Further, the cylindrical portion 40 is provided at an end portion 47 on the opposite side from the seat portion 42 with caulking portions 471 overlapping the drive magnet 8 at a plurality of locations in the circumferential direction, and at least a part of the gap G is opened between the caulking portions 471 at two locations adjacent in the circumferential direction among the caulking portions 471 at the plurality of locations. Therefore, the fluid flowing through the recess 422 of the seat portion 42 and the gap G between the cylindrical portion 40 and the driving magnet 8 can pass through the caulking portions 471, and thus heat generation of the driving magnet 8 and the like can be effectively suppressed.

(construction of penetrating part 15 of rotor 45)

Fig. 10 is a plan view of the rotor 4 and the like shown in fig. 2, as viewed from one side L1 in the direction of the rotation center axis L. As shown in fig. 4, 5, 6, and 7, in the motor 10 and the pump device 1, a through portion 15 that penetrates both sides of the rotation center axis L is provided between the cylindrical portion 40 of the rotor 4 and the radial bearing 11 by a first groove 48 that extends along the rotation center axis L in the inner circumferential surface of the cylindrical portion 40 and a second groove 111 that extends along the rotation center axis L in the outer circumferential 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 grooves each having a semicircular cross section. Therefore, the through portion 15 extends linearly as a hole having a circular cross section.

In the cylindrical portion 40, the first groove 48 is provided at an angular position overlapping the rib 46 as viewed from the radial direction. Therefore, the rib 46 can suppress the wall thickness of the cylindrical portion 40 from becoming too thin due to the formation of the first groove 48.

Here, the cylindrical portion 40 is formed with annular first and second convex portions 441 and 442 that protrude radially inward and overlap the stepped portion 116 on one side L1 in the rotational center axis L direction and the stepped portion 117 on the other side L2 in the rotational center axis L direction of the radial bearing 11. On the other hand, the first groove 48 is formed along the inner circumferential surface of the cylindrical portion 40. Therefore, the first groove 48 penetrates the first convex portion 441 and the second convex portion 442 as a circular hole, and does not reach the inner edges of the first convex portion 441 and the second convex portion 442. Therefore, the inner edge of the first convex portion 441 and the inner edge of the second convex portion 442 are each a continuous circular arc shape.

In this way, in the present embodiment, since the penetrating portion 15 that penetrates both sides of the rotation center axis L of the rotor 4 is provided, a large pressure difference is less likely to occur between both sides of the rotor 4 in the rotation center axis L direction. Therefore, the rotor 4 is less likely to vibrate in the direction of the rotation central axis L. Here, the through portion 15 is formed by overlapping a first groove 48 formed in the inner circumferential surface of the cylindrical portion 40 and a second groove 111 formed in the outer circumferential surface of the radial bearing 11 in the radial direction. Therefore, even when the through portion 15 having a sufficient opening area is formed, the opening area of the first groove 48 can be made narrow. Therefore, the strength of the cylindrical portion 40 is less likely to be reduced by the first groove 48, and therefore, it is not necessary to increase the outer diameter of the cylindrical portion 40.

In addition, 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 insert molding is performed, a pin having a circular cross section is disposed in the second groove 111 of the radial bearing 11 in the mold and insert molded, and then the pin is removed, the rotor 4 can be manufactured by insert molding while forming the through portion 15.

Further, a groove-like mark 119 indicating the position of the second groove 111 is provided on an end portion 118 on one side L1 in the direction of the rotation center axis L of the radial bearing 11. Therefore, at the time of insert molding, the arrangement of the pin and the like can be performed with reference to the mark 119 provided at the end portion 118 of the radial bearing 11.

[ other embodiments ]

In the above embodiment, the housing 6 is the resin seal member 60 covering the stator 3 from both sides in the radial direction and both sides in the direction of the rotation center axis L, but the present invention may be applied to a case where the housing 6 is a member covering only the inner side in the radial direction of the stator 3 and the other side L2 in the direction of the rotation center axis L.

Description of the symbols

1 method 8230, a pump device, 2 method 8230, a shell, 3 method 8230, a stator, 4 method 8230, a rotor, 5 method 8230, a fulcrum, 6 method 8230, a shell, 8 method 8230, a driving magnet, 10 method 8230, a motor, 11 method 8230, a radial bearing, 15 method 8230, a through portion, 18 method 8230, a cover, 19 method 8230, a substrate, 20 method 8230, a pump chamber, 25 method 8230, an impeller, 35 method 8230, a coil, 40 method 8230, a cylinder portion, 42 method 8230, a seat portion, 43 method 8230, a magnet holding portion, 45 method 8230, a flange portion, 46 method 30, a rib, 48 method 8230, a first groove, 60 method 30, a resin sealing component, 65 method 8230, a coil, 111 method 8230, a second groove, 119 8230, a flange portion, a blade portion, a central axis line, a central line, and a central line L method 30.

Claims (5)

1. A pump device, characterized in that,

having a motor and an impeller disposed in a pump chamber provided on one side of a rotation center axis with respect to the motor and connected to a rotor of the motor,

a cylindrical portion extending along the rotation center axis, holding a drive magnet on an outer side and holding a cylindrical radial bearing on an inner side,

a through portion is provided between the cylindrical portion and the radial bearing, and the through portion penetrates both sides of the rotation center axis by a first groove extending along the rotation center axis on an inner circumferential surface of the cylindrical portion and a second groove extending along the rotation center axis on an outer circumferential surface of the radial bearing and overlapping with the first groove from a radially inner side.

2. Pump apparatus according to claim 1,

the rotor is a resin molded product in which the radial bearing is insert-molded.

3. Pump apparatus according to claim 2,

a mark showing a position of the first groove is provided on an end portion on one side in a rotation axis direction of the radial bearing.

4. Pump arrangement according to any one of claims 1 to 3,

a plurality of ribs extending along the rotation center axis are provided on the outer peripheral surface of the cylindrical portion,

the drive magnet is press-fitted into the cylindrical portion so as to contact the plurality of ribs from a radially outer side.

5. The pump arrangement according to claim 4,

the first groove is provided at an angular position overlapping with the rib when viewed from the radial direction.

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