JP2016223428A - Air blower and cleaner - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an air blower capable of adjusting rotation balance of a rotor assembly with high accuracy.SOLUTION: An air blower includes: a rotor that has a shaft arranged along a central axis J running vertically; a stator that is positioned outside the radial direction of the rotor; a housing that is opened upward and formed into a cylindrical shape, and houses the stator; a bearing that supports the shaft in a rotatable manner; a cylindrical bearing holding member 60 that is positioned at the opening on the upper side of the housing, and holds the bearing so as to surround the same in a peripheral direction; and an impeller that is attached to the shaft on the side above the bearing holding member. The bearing holding member comprises a plurality of holding member pieces 60a arranged along the peripheral direction.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a blower and a vacuum cleaner.

  Conventionally, a configuration has been proposed in which a diffuser is divided in the circumferential direction for the purpose of correcting rotational imbalance from the side of a fan connected to a rotor (see, for example, Patent Document 1).

JP 2014-58870 A

  In the above configuration, after assembling the electric motor, the fan is attached to the rotating shaft protruding from the electric motor case. For this reason, in the state of the assembly in which the fan is attached to the rotor, unbalance adjustment cannot be performed on the core of the rotor. Therefore, there is a possibility that the rotation unbalance adjustment cannot be performed with high accuracy.

  In view of the above problems, an exemplary embodiment of the present invention has an object to provide a blower having a structure capable of adjusting the rotational balance of a rotor assembly with high accuracy. Another object is to provide a vacuum cleaner provided with such a blower.

  An air blower according to an exemplary embodiment of the present invention is a rotor having a shaft disposed along a central axis extending vertically, a stator positioned on the radially outer side of the rotor, and a cylindrical shape opening upward. A housing that accommodates the stator therein, a bearing that rotatably supports the shaft, and a cylindrical bearing holding member that is positioned in an upper opening of the housing and that surrounds and holds the bearing in a circumferential direction. And an impeller attached to the shaft above the bearing holding member, and the bearing holding member is constituted by a plurality of holding member pieces arranged along a circumferential direction.

  A vacuum cleaner according to an exemplary embodiment of the present invention includes the air blowing device.

  According to an exemplary embodiment of the present invention, a blower having a structure capable of adjusting the rotational balance of the rotor assembly with high accuracy is provided. Moreover, the vacuum cleaner provided with such an air blower is provided.

FIG. 1 is a cross-sectional view showing the blower of the first embodiment. FIG. 2 is a perspective view showing the blower of the first embodiment. FIG. 4 is a perspective view showing the bearing holding member of the first embodiment. FIG. 3 is a front view showing the rotor assembly of the first embodiment. FIG. 5 is an enlarged cross-sectional view showing a portion of the blower device of the first embodiment. FIG. 6 is a cross-sectional view showing the blower of the second embodiment, and is a cross-sectional view taken along the line VI-VI in FIG. FIG. 7 is a perspective view showing the blower of the second embodiment. FIG. 8 is a plan view showing the blower of the second embodiment. FIG. 9 is a perspective view illustrating the vacuum cleaner according to the embodiment.

  Hereinafter, an air blower according to an embodiment of the present invention will be described with reference to the drawings. In the drawings, an XYZ coordinate system is appropriately shown as a three-dimensional orthogonal coordinate system. In the XYZ coordinate system, the Z-axis direction is a direction parallel to the axial direction of the central axis J shown in FIG. The Y-axis direction is a direction orthogonal to the Z-axis direction and is the left-right direction in FIG. The X-axis direction is a direction orthogonal to both the Y-axis direction and the Z-axis direction.

  In the following description, the direction in which the central axis J extends (Z-axis direction) is the vertical direction. The positive side (+ Z side) in the Z-axis direction is called “upper side (upper axial direction)”, and the negative side (−Z side) in the Z-axis direction is called “lower side (lower axial direction)”. In addition, the up-down direction, the upper side, and the lower side are names used for explanation only, and do not limit the actual positional relationship and direction. Unless otherwise specified, a direction parallel to the central axis J (Z-axis direction) is simply referred to as an “axial direction”, and a radial direction around the central axis J is simply referred to as a “radial direction”. The circumferential direction centered on is simply referred to as the “circumferential direction”.

<First Embodiment>
As shown in FIGS. 1 and 2, the blower device 1 includes a motor 10, a bearing holding member 60, an impeller 70, a flow path member 61, a plurality of stationary blades 67, and an impeller housing 80. A bearing holding member 60 is attached to the upper side (+ Z side) of the motor 10. The flow path member 61 surrounds the radially outer side of the motor 10 in the circumferential direction. The impeller housing 80 is attached to the upper side of the flow path member 61. The impeller 70 is accommodated between the bearing holding member 60 and the impeller housing 80 in the axial direction (Z-axis direction). The impeller 70 is attached to the motor 10 so as to be rotatable around the central axis J. In FIG. 2, the flow path member 61 and the impeller housing 80 are not shown.

  As shown in FIG. 1, the motor 10 includes a housing 20, a rotor 30 having a shaft 31, a stator 40, a lower bearing 52 a, an upper bearing 52 b, and a connector 90. In the present embodiment, the upper bearing 52b corresponds to a bearing. Thus, the blower 1 includes the rotor 30, the stator 40, the housing 20, the bearing, the bearing holding member 60, and the impeller 70. Note that the lower bearing 52a, or both the lower bearing 52a and the upper bearing 52b may correspond to bearings.

  The housing 20 has a cylindrical shape that opens upward. The housing 20 accommodates the stator 40 therein. The housing 20 accommodates the rotor 30 therein. The housing 20 is, for example, a bottomed cylindrical container. The housing 20 includes a cylindrical peripheral wall 21, a lower lid portion 22 positioned at the lower end of the peripheral wall 21, and a lower bearing holding portion 22 b positioned at the center of the lower lid portion 22. A stator 40 is fixed to the inner surface of the peripheral wall 21 in the housing 20. The lower bearing holding portion 22b has a cylindrical shape that protrudes downward (−Z side) from the center portion of the lower lid portion 22. The lower bearing holding portion 22b holds the lower bearing 52a inside.

  As shown in FIGS. 1 and 2, the housing 20 is provided with a through hole 21 a. The through hole 21 a is provided across the lower lid portion 22 from the lower side of the peripheral wall 21. That is, the through hole 21a penetrates the peripheral wall 21 in the radial direction and penetrates the lower lid portion 22 in the axial direction (Z-axis direction). Although illustration is omitted, for example, three through holes 21a are provided along the circumferential direction.

  As shown in FIG. 1, the upper end portion of the through hole 21 a is located above the lower end portion of the stator core 41 described later. Therefore, the lower side of the stator core 41 is exposed to the outside of the housing 20. Thus, the radially outer surface of the stator core 41 faces an exhaust passage 87 (described later) provided between the motor 10 and the passage member 61. Therefore, the stator core 41 can be cooled by the air flowing through the exhaust passage 87.

  For example, as a method of cooling the stator core 41, a method of flowing air into the housing 20 is also conceivable. However, in this method, the stator core 41, the coil 42, and the like in the housing 20 become resistances that hinder the flow of air, and air loss occurs. Therefore, there existed a problem that the ventilation efficiency of the air blower 1 fell.

  On the other hand, according to the present embodiment, since the outer surface of the stator core 41 is exposed facing the exhaust flow path 87, the stator core 41 does not provide resistance to the air flow in the exhaust flow path 87. Thereby, according to this embodiment, it is possible to cool the stator core 41, without reducing ventilation efficiency.

  The upper end portion of the through hole 21a is located substantially at the center of the stator core 41 in the axial direction (Z-axis direction). That is, in the present embodiment, the lower half of the stator core 41 is exposed to the exhaust passage 87. Therefore, the stator core 41 can be further cooled.

  As shown in FIG. 1, the rotor 30 includes a shaft 31, a rotor magnet 33, a lower magnet fixing member 32a, and an upper magnet fixing member 32b. The rotor magnet 33 has a cylindrical shape that surrounds the shaft 31 radially around the axis (θz direction). The lower magnet fixing member 32 a and the upper magnet fixing member 32 b have a cylindrical shape having an outer diameter equivalent to that of the rotor magnet 33. The lower magnet fixing member 32a and the upper magnet fixing member 32b are attached to the shaft 31 with the rotor magnet 33 sandwiched from both sides in the axial direction. The upper magnet fixing member 32b has a small-diameter portion 32c having an outer diameter smaller than that of the lower portion (rotor magnet 33 side) in the upper portion in the axial direction (Z-axis direction).

  The rotor 30 has a shaft 31 that is disposed along a central axis J that extends vertically (in the Z-axis direction). The shaft 31 is supported by the lower bearing 52a and the upper bearing 52b so as to be rotatable around the axis (± θz direction). That is, the bearing supports the shaft 31 in a rotatable manner. An impeller 70 is attached to the shaft 31 above the bearing holding member 60. In FIG. 1, for example, the impeller 70 is attached to the upper end (+ Z side) of the shaft 31.

  The stator 40 is located on the radially outer side of the rotor 30. The stator 40 surrounds the rotor 30 around the axis (θz direction). The stator 40 includes a stator core 41, an insulator 43, and a coil 42.

  The stator core 41 has a core back part 41a and a plurality (three) of teeth parts 41b. The core back portion 41a has a ring shape around the central axis. The teeth portion 41b extends radially inward from the inner peripheral surface of the core back portion 41a. The teeth 41b are arranged at equal intervals in the circumferential direction.

  The insulator 43 is attached to the tooth portion 41b. The coil 42 is attached to the tooth portion 41 b via the insulator 43. The coil 42 is configured by winding a conductive wire.

  The lower bearing 52a is held by the lower bearing holding portion 22b via the elastic member 53a. The upper bearing 52b is held by the holding cylinder portion 62d via the elastic member 53b. By providing the elastic members 53a and 53b, the vibration of the rotor 30 can be suppressed.

  The elastic members 53a and 53b have a cylindrical shape that opens on both sides in the axial direction. The elastic members 53a and 53b are made of an elastic body. In the present embodiment, the material of the elastic members 53a and 53b may be, for example, a thermosetting elastomer (rubber) or a thermoplastic elastomer.

  The elastic member 53a is located on the radially inner side of the lower bearing holding portion 22b. The elastic member 53a is fitted, for example, on the radially inner side of the lower bearing holding portion 22b. The lower bearing 52a is fitted inside the elastic member 53a in the radial direction. The elastic member 53b is located on the radially inner side of the holding cylinder portion 62d. For example, the elastic member 53b is fitted inside the holding cylinder portion 62d in the radial direction. The upper bearing 52b is fitted inside the elastic member 53b in the radial direction.

  The bearing holding member 60 is located in the upper opening of the housing 20. The bearing holding member 60 has a cylindrical shape that surrounds and holds the upper bearing 52b in the circumferential direction. As shown in FIG. 3, the bearing holding member 60 includes a holding member main body portion 62c, and a first convex portion 62a and a second convex portion 62b.

  As shown in FIGS. 1 and 2, the holding member main body 62 c is, for example, a covered cylindrical shape with the central axis J as the center. The upper lid portion of the holding member main body portion 62c has a hole through which the shaft 31 passes. As shown in FIG. 1, the holding member main body 62 c is fitted inside the peripheral wall 21 of the housing 20. Thereby, the bearing holding member 60 is fixed inside the housing 20.

  As shown in FIGS. 1 and 3, the holding member main body 62 c has an outer protrusion 63 that protrudes radially outward. That is, the bearing holding member 60 has an outer protrusion 63. In FIGS. 1 and 3, the outer protrusion 63 has an annular shape surrounding the central axis J. Therefore, by providing the outer protrusion 63, a step is formed on the outer peripheral surface of the holding member main body 62c so that the outer diameter of the holding member main body 62c increases from the lower side to the upper side. The lower surface of the outer protrusion 63 is in contact with the upper end surface of the housing 20. More specifically, the lower surface of the outer protruding portion 63, that is, the step surface orthogonal to the axial direction of the step of the holding member main body portion 62 c is in contact with the upper end surface of the housing 20, that is, the upper end portion of the peripheral wall 21. Thereby, the axial direction position of the holding member main-body part 62c (bearing holding member 60) is positioned.

  As shown in FIG. 1, the holding member main body portion 62 c includes a holding cylinder portion 62 d and an inner protruding portion 64. That is, the bearing holding member 60 has a holding cylinder portion 62d and an inner protrusion 64. The holding cylinder portion 62d is located at the center of the holding member main body portion 62c. The holding cylinder portion 62d has a cylindrical shape that opens at both ends in the axial direction with the central axis J as the center. The holding cylinder portion 62d has a cylindrical shape that holds the upper bearing 52b.

  The inner projecting portion 64 projects radially inward from the inner surface of the holding cylinder portion 62d. In FIG. 1, the inner protruding portion 64 protrudes from the upper end portion of the holding cylinder portion 62d. As shown in FIGS. 1 and 3, the upper surface of the inner projecting portion 64 is located on the same plane as the upper surface of the holding cylinder portion 62d.

  As shown in FIG. 1, the inner protruding portion 64 faces at least a part of the upper surface of the upper bearing 52 b in the axial direction. Therefore, the upper bearing 52b can be positioned in the axial direction by bringing the upper surface of the upper bearing 52b into direct or indirect contact with the inner protrusion 64. In FIG. 1, the upper surface of the upper bearing 52b indirectly contacts the inner protrusion 64 via the elastic member 53b.

  The radially inner end of the inner projecting portion 64 is positioned more radially inward than the radially outer end of the rotor 30. In other words, the radial distance from the central axis J to the radially outer end of the rotor 30 is larger than the radial distance from the central axis J to the radially inner end of the inner protrusion 64. Thereby, the outer diameter of the rotor 30 can be relatively easily increased, and the output of the motor 10 can be increased. The radially outer end of the rotor 30 is, for example, the radially outer end of the rotor magnet 33.

  The first protrusion 62a protrudes upward from the upper surface of the holding member main body 62c. The first convex portion 62a is an annular shape surrounding the circumferential direction of the central axis J. For example, the central axis J passes through the center of the first convex portion 62a.

  The second convex portion 62b protrudes upward from the upper surface of the holding member main body portion 62c. That is, the 1st convex part 62a and the 2nd convex part 62b protrude upwards from the upper surface of the holding member main-body part 62c. The 2nd convex part 62b is located in the radial direction outer side of the 1st convex part 62a. The second convex portion 62b is an annular shape surrounding the central axis J and the first convex portion 62a in the circumferential direction. For example, the central axis J passes through the center of the second convex portion 62b. That is, the first convex portion 62a and the second convex portion 62b are annular shapes surrounding the central axis J.

  In the present embodiment, the bearing holding member 60 is constituted by a plurality of holding member pieces 60a arranged along the circumferential direction. Therefore, the rotation balance of the rotor assembly 11 shown in FIG. 4 can be adjusted with high accuracy. As shown in FIG. 4, the rotor assembly 11 is configured by fixing an impeller 70 to a rotor 30 to which an upper bearing 52b is attached. Details will be described below.

  Conventionally, the adjustment of the rotational balance of the rotor assembly 11 is performed by separately adjusting the balance of the rotor 30 alone and the balance of the impeller 70 separately. Thereafter, the motor 10 including the rotor 30 is assembled, and the impeller 70 is fixed to the shaft 31 of the rotor 30. Here, since an assembly error occurs when the impeller 70 is fixed to the shaft 31, the balance adjustment of the rotor assembly 11 is performed again in a state where the impeller 70 is fixed to the shaft 31, that is, in the state of the rotor assembly 11. Thus, conventionally, in order to adjust the rotational balance of the rotor assembly 11, it has been necessary to perform balance adjustment a plurality of times, which is troublesome.

  Further, the balance adjustment of the rotor assembly 11 is performed, for example, by notching a part of the parts constituting the rotor assembly 11. Here, in the conventional method described above, since the impeller 70 is attached to the shaft 31 after the motor 10 is assembled, the rotor 30 is surrounded by the stator 40 and the housing 20 in a state where the rotor assembly 11 is assembled. Therefore, when the balance adjustment of the rotor assembly 11 is performed, a part of the rotor 30 cannot be cut out, and the balance adjustment must be performed only by cutting out the impeller 70. That is, in the conventional method, the balance adjustment of the rotor assembly 11 can be performed only on one surface. Therefore, depending on how the rotor assembly 11 is out of balance, the rotational balance of the rotor assembly 11 may not be adjusted with high accuracy.

  On the other hand, according to the present embodiment, the bearing holding member 60 is constituted by a plurality of holding member pieces 60a. Therefore, after assembling the rotor assembly 11 shown in FIG. 4, the rotor assembly 11 is inserted into the stator 40, and then the holding member piece 60a is assembled from the radially outer side of the upper bearing 52b to assemble the motor 10. Can do. Thereby, the balance adjustment of the rotor assembly 11 can be performed before the motor 10 is assembled. Therefore, it is possible to adjust the balance by cutting out both the rotor 30 and the impeller 70. That is, balance adjustment of the rotor assembly 11 can be performed on two or more surfaces. As a result, according to the present embodiment, the rotational balance of the rotor assembly 11 can be adjusted with high accuracy.

  Further, since the rotation balance of the rotor assembly 11 can be adjusted with high accuracy, it is not necessary to separately adjust the balance between the rotor 30 alone and the impeller 70 alone. Thereby, the frequency | count of performing balance adjustment of the rotor assembly 11 can be made into 1 time. Therefore, according to the present embodiment, it is possible to reduce time and effort required for adjusting the rotation balance of the rotor assembly 11.

  Moreover, since the bearing holding member 60 is comprised by several holding member piece 60a, it is necessary to hold | maintain the state with which each holding member piece 60a was combined. Here, in the present embodiment, the bearing holding member 60 is fixed inside the housing 20. Therefore, for example, the holding member pieces 60 a can be combined by fitting the bearing holding member 60 to the housing 20. In this case, the state in which the holding member pieces 60a are combined can be held without fixing the holding member pieces 60a with an adhesive or the like. Therefore, the trouble of combining the holding member pieces 60a can be reduced.

  For example, when the bearing holding member 60 is configured by a plurality of holding member pieces 60a as in the present embodiment, a dimensional error of each holding member piece 60a and an assembling error between the holding member pieces 60a are likely to occur. Therefore, there is a possibility that the dimensional error of the holding cylinder portion 62d of the bearing holding member 60 becomes larger than when the bearing holding member 60 is a single member. Thereby, there is a possibility that the upper bearing 52b cannot be stably held on the holding cylinder portion 62d.

  On the other hand, according to the present embodiment, the upper bearing 52b is held by the holding cylinder portion 62d via the elastic member 53b. Therefore, even when a dimensional error occurs in the holding cylinder portion 62d, the dimensional error can be absorbed by the elastic member 53b. Therefore, according to the present embodiment, the upper bearing 52b can be stably held even when the bearing holding member 60 is constituted by a plurality of holding member pieces 60a.

  In the example of FIG. 3, the bearing holding member 60 is configured by combining, for example, three holding member pieces 60a. In the present embodiment, the plurality of holding member pieces 60a have the same shape. Therefore, it is easy to manufacture the holding member piece 60a. As an example, when the holding member piece 60a is made of resin and manufactured by injection molding, the mold for manufacturing the holding member piece 60a can be the same. Thereby, the effort and cost which manufacture the holding member piece 60a can be reduced. In the example of FIG. 3, the planar view shape of the holding member piece 60 a is, for example, a sector shape with a central angle of 120 °.

  As shown in FIG. 1, the connector 90 extends downward from the stator 40. The connector 90 protrudes to the lower side of the housing 20 through the through hole 21a. The connector 90 has connection wiring (not shown). The connection wiring is electrically connected to the coil 42. When an external power source (not shown) is connected to the connector 90, power is supplied to the coil 42 through the connection wiring.

  The impeller 70 is fixed to the shaft 31. The impeller 70 can rotate around the central axis J together with the shaft 31. The impeller 70 includes a base member 71, a moving blade 73, and a shroud 72. In this embodiment, the base member 71 is a single member, for example. That is, the base member 71 is a separate member from the moving blade 73. The base member 71 is made of metal, for example.

  The base member 71 has a flat plate shape that expands in the radial direction. That is, the impeller 70 has a flat base member 71 that expands in the radial direction. The base member 71 is opposed to the bearing holding member 60 in the axial direction through a gap. Therefore, the labyrinth structure in the axial direction can be configured by the first convex portion 62a, the second convex portion 62b, and the base member 71. More specifically, a labyrinth structure is formed between the impeller 70 and the bearing holding member 60 in the axial direction (Z-axis direction) by the first convex portion 62a, the second convex portion 62b, and a disc portion 71a described later. Can do. Thereby, it can suppress that air flows into the clearance gap between the impeller 70 and the bearing holding member 60. FIG. Therefore, according to this embodiment, the ventilation efficiency of the air blower 1 can be improved.

  The base member 71 has a disc part 71a, an outer cylinder part 71b, and an inner cylinder part 71c. Although not shown, the disk portion 71a has a disk shape extending in the radial direction, and the central axis J passes through the center thereof. The outer cylinder part 71b has a cylindrical shape extending upward from the inner edge of the disk part 71a. The outer cylinder part 71b is centered on the central axis J, for example. The upper end portion of the outer cylindrical portion 71b is curved radially inward.

  Therefore, the air that has flowed into the impeller 70 through the air inlet 80a described later tends to flow radially outward along the upper surface of the outer cylindrical portion 71b. Thereby, according to this embodiment, the ventilation efficiency of the air blower 1 can be improved.

  The inner cylinder part 71c is located radially inward of the outer cylinder part 71b. The inner cylinder part 71c is a cylindrical cylinder part extending in the axial direction (Z-axis direction). The inner cylinder part 71c is centered on the central axis J, for example. The upper end portion of the inner cylindrical portion 71c is curved outward in the radial direction.

  The upper end portion of the inner cylinder portion 71c is smoothly connected to the upper end portion of the outer cylinder portion 71b. The shape in which the part above the disc part 71a and the outer cylinder part 71b in the inner cylinder part 71c are connected to each other is a U-shape that opens downward in a sectional view.

  The shaft 31 is press-fitted inside the inner cylindrical portion 71c in the radial direction. Thereby, the impeller 70 is fixed to the shaft 31. Thus, according to the impeller 70 of the present embodiment, the impeller 70 can be fixed to the shaft 31 without separately providing a fixing member by press-fitting the shaft 31 inside the inner cylindrical portion 71c in the radial direction. . Therefore, the number of parts of the blower 1 can be reduced. Moreover, since the disc part 71a, the outer cylinder part 71b, and the inner cylinder part 71c are comprised with a single member, the number of parts of the air blower 1 can be reduced more. Thereby, the assembly man-hour of the air blower 1 can be reduced. The fixing member that fixes the impeller 70 to the shaft 31 is, for example, a nut.

  In addition, for example, when the shaft 31 is press-fitted into a cylindrical portion extending in the axial direction from the inner edge of the disc portion 71a, stress is likely to concentrate at a connection portion between the disc portion 71a and the cylindrical portion. Therefore, for example, when stress is applied to the impeller 70 due to a gyro effect or the like generated when the impeller 70 rotates, the impeller 70 may swing around.

  On the other hand, according to the present embodiment, the shaft 31 is press-fitted into the inner cylindrical portion 71c positioned radially inward from the outer cylindrical portion 71b extending upward from the inner edge of the disc portion 71a. Thereby, it can suppress that stress concentrates on the connection location of the disc part 71a and the outer side cylinder part 71b, and the rigidity of the part to which the disc part 71a, the outer side cylinder part 71b, and the inner side cylinder part 71c are connected is enlarged. it can. Therefore, when stress is applied to the impeller 70, the impeller 70 can be prevented from swinging.

  The lower end part of the inner cylinder part 71c is located below the disk part 71a. The lower end portion of the inner cylindrical portion 71c overlaps the bearing holding member 60 in the radial direction. The portion where the shaft 31 is press-fitted in the inner cylinder portion 71c is located below the disc portion 71a. The lower end portion of the inner cylindrical portion 71c is in contact with the upper end portion of the inner ring of the upper bearing 52b.

  Therefore, the inner cylinder part 71c functions as a spacer that defines the position of the disk part 71a in the axial direction (Z-axis direction). Thereby, according to this embodiment, it is not necessary to provide a separate spacer, the number of parts of the blower 1 can be reduced, and the number of assembling steps of the blower 1 can be reduced.

  Further, for example, a configuration in which the inner cylinder portion 71c is extended above the outer cylinder portion 71b and the portion of the inner cylinder portion 71c into which the shaft 31 is press-fitted is positioned above the disk portion 71a is conceivable. However, in this case, it is necessary to increase the dimension for projecting the shaft 31 upward. Therefore, there is a problem that the dimension of the shaft 31 in the axial direction (Z-axis direction) becomes large.

  On the other hand, according to the present embodiment, the inner cylindrical portion 71c extends below the disc portion 71a. Thereby, the part in which the shaft 31 in the inner cylinder part 71c is press-fit can be made lower than the disk part 71a, and the dimension of the axial direction (Z-axis direction) of the shaft 31 can be reduced.

  The manufacturing method of the base member 71 is not particularly limited. In the present embodiment, the base member 71 is a single member made of metal having a disc part 71a, a cylindrical outer cylinder part 71b, and an inner cylinder part 71c. Therefore, for example, the base member 71 can be manufactured by burring a metal plate-like member. Thereby, manufacture of the impeller 70 can be made easy. Moreover, when manufacturing the base member 71 from a plate-shaped member, compared with the case where the base member 71 is manufactured, for example by die-casting, it is easy to reduce the weight of the base member 71.

  The moving blade 73 is located on the upper surface of the disc part 71a. The moving blade 73 is inserted into a groove provided on the upper surface of the disc portion 71a, for example, and is fixed to the upper surface of the disc portion 71a. A plurality of moving blades 73 are provided along the circumferential direction.

  The shroud 72 is an annular portion that faces the upper surface of the disk portion 71a. The inner edge of the shroud 72 has, for example, a circular shape concentric with the disk portion 71a. The shroud 72 is fixed to the disc portion 71 a via the moving blade 73.

  As shown in FIG. 2, the shroud 72 includes a shroud ring portion 72a and a shroud cylindrical portion 72b. The shroud annular portion 72a has an annular plate shape. The shroud cylindrical portion 72b has a cylindrical shape extending upward from the inner edge of the shroud annular portion 72a. The shroud cylinder 72b has an impeller opening 72c that opens upward. The shroud cylindrical portion 72 b is located on the radially outer side than the outer cylindrical portion 71 b of the base member 71.

  As shown in FIG. 5, the inner side surface of the shroud cylindrical portion 72b has a curved surface portion 72d. The curved surface portion 72d is located at the upper end portion of the inner surface of the shroud cylindrical portion 72b. The curved surface portion 72d is curved outward in the radial direction from the lower side toward the upper side.

  An impeller channel 86 is provided between the shroud ring portion 72a and the disc portion 71a in the axial direction (Z-axis direction). The impeller channel 86 is partitioned by a plurality of moving blades 73. The impeller channel 86 communicates with the impeller opening 72c. The impeller channel 86 opens to the outside in the radial direction of the impeller 70.

  The axial position of the impeller 70 is determined by the inner cylindrical portion 71c that functions as a spacer. The lower surface of the impeller 70, that is, the lower surface of the disk portion 71a is provided at a position close to the upper end of the first convex portion 62a and the upper end of the second convex portion 62b in the bearing holding member 60. Thereby, the labyrinth structure mentioned above is comprised. Therefore, it is possible to suppress the air discharged radially outward from the impeller flow path 86 of the impeller 70 from flowing from the radially outer side to the radially inner side via the gap between the impeller 70 and the bearing holding member 60. As a result, according to this embodiment, the ventilation efficiency of the air blower 1 can be improved more.

  As shown in FIG. 1, the flow path member 61 has a cylindrical shape surrounding the radially outer side of the motor 10. The inner diameter of the flow path member 61 decreases from the upper end portion toward the lower side, and then increases from the portion where the inner diameter becomes the minimum toward the lower side. In other words, the flow path member inner side surface 61c, which is the radially inner surface of the flow path member 61, is positioned radially inward from the upper end portion toward the lower side, and then from the location where the radial position is the innermost side. It is located radially outward as it goes down.

  For example, the inner diameter of the flow path member 61 is maximum at the upper end. In other words, the radial direction position of the flow path member inner side surface 61c is, for example, located on the outermost side in the upper end portion.

  Between the radial direction of the flow path member 61 and the motor 10, the exhaust flow path 87 extended in an axial direction (Z-axis direction) is provided. That is, the exhaust passage 87 is formed by the passage member 61 and the motor 10. The exhaust passage 87 is provided over one circumference in the circumferential direction. In the present embodiment, the outer surface of the motor 10, that is, the outer peripheral surface of the housing 20, has a cylindrical shape that extends linearly in the axial direction, and therefore the radial width of the exhaust passage 87 depends on the inner diameter of the passage member 61. Change.

  That is, the radial width of the exhaust passage 87 decreases from the upper end portion toward the lower side, and then increases from the portion where the width becomes the minimum toward the lower side. For example, the radial width of the exhaust passage 87 is maximized at the upper end. Thus, by changing the width of the exhaust passage 87, the static pressure of the air passing through the exhaust passage 87 can be increased. Thereby, it can suppress that the air which passes the inside of the exhaust flow path 87 flows backward, ie, the air flows from the lower side toward the upper side.

  The radial position of the exhaust passage 87 becomes radially inner as the radial width of the exhaust passage 87 becomes smaller, and becomes radially outer as the radial width of the exhaust passage 87 becomes larger. Here, as the radial position of the exhaust flow path 87 becomes radially inward, the circumferential length of the exhaust flow path 87 becomes smaller, so the flow area of the exhaust flow path 87 becomes smaller. On the other hand, as the radial position of the exhaust flow path 87 is radially outward, the circumferential length of the exhaust flow path 87 increases, and thus the flow area of the exhaust flow path 87 increases.

  Therefore, for example, even if the radial width of the exhaust passage 87 is reduced, if the radial position of the exhaust passage 87 is radially outward, the flow passage area of the exhaust passage 87 is sufficiently reduced. It is difficult to increase the static pressure of air passing through the exhaust passage 87.

  On the other hand, according to this embodiment, the radial position of the exhaust passage 87 becomes radially inner as the radial width of the exhaust passage 87 becomes smaller. Therefore, it is easy to sufficiently reduce the channel area by reducing the radial width of the exhaust channel 87. On the other hand, by increasing the radial width of the exhaust passage 87, the passage area can be easily increased sufficiently. Thereby, since the change of the flow path area of the exhaust flow path 87 can be increased, the static pressure of the air passing through the exhaust flow path 87 can be easily increased. Therefore, according to this embodiment, it can suppress more that the air which passes the exhaust flow path 87 flows backward.

  In the present specification, the radial position of the exhaust passage includes the radial position of the radially outer end of the exhaust passage.

  An exhaust port 88 is provided at the lower end of the exhaust channel 87. The exhaust port 88 is a portion from which air that has flowed into the blower 1 from an air intake port 80a described later is discharged. In the present embodiment, the axial position of the exhaust port 88 is substantially the same as the axial position of the lower end portion of the motor 10.

  In the present embodiment, the flow path member 61 includes an upper flow path member 61b and a lower flow path member 61a. The upper flow path member 61b is connected to the upper side of the lower flow path member 61a. The inner diameter of the upper flow path member 61b decreases from the upper end to the lower side. The inner diameter of the lower flow path member 61a increases from the upper end toward the lower side. That is, the position where the inner diameter is minimum in the flow path member 61 is the same in the axial direction (Z-axis direction) as the connection position P1 where the upper flow path member 61b and the lower flow path member 61a are connected. Similarly, the position at which the radial width of the exhaust flow path 87 is minimized is the same as the connection position P1 in the axial direction.

  The blower device 1 includes a plurality of stationary blades 67. The plurality of stationary blades 67 are fixed to the outer surface of the bearing holding member 60. The holding member piece 60a and the stationary blade 67 may be a single member. The plurality of stationary blades 67 are provided between the flow path member 61 and the motor 10 in the radial direction. That is, the stationary blade 67 is provided in the exhaust passage 87. The stationary blade 67 rectifies the air flowing in the exhaust passage 87. As shown in FIG. 2, the plurality of stationary blades 67 are arranged at equal intervals along the circumferential direction. The stationary blade 67 has a stationary blade lower portion 67a and a stationary blade upper portion 67b. The stationary blade lower portion 67a extends in the axial direction (Z-axis direction).

The stationary blade upper portion 67b is connected to the upper end portion of the stationary blade lower portion 67a. Stationary blade top 67b is toward the lower side to the upper, curved clockwise direction in a plan view (- [theta] _Z direction).

  As shown in FIG. 1, the stationary blade lower portion 67a overlaps, for example, the lower flow path member 61a in the radial direction. The stationary blade upper portion 67b overlaps, for example, the upper flow path member 61b in the radial direction. In the present embodiment, the stationary blade lower portion 67a and the stationary blade upper portion 67b are, for example, a part of a single member. In the present embodiment, the stationary blade 67 is manufactured, for example, as a single member with the upper flow path member 61b.

  The impeller housing 80 is a cylindrical member. The impeller housing 80 is attached to the upper end portion of the flow path member 61. The impeller housing 80 has an intake port 80a that opens upward.

  The impeller housing 80 includes an impeller housing main body portion 82 and an intake guide portion 81. The impeller housing main body 82 has a cylindrical shape that surrounds the radially outer side of the impeller 70 and opens on both axial sides. The upper end portion of the flow path member 61 is fitted inside the impeller housing main body portion 82 in the radial direction. In the present embodiment, the upper end portion of the flow path member 61 is press-fitted, for example, on the radially inner side of the impeller housing body portion 82.

  As shown in FIG. 5, a step 83 is provided at the lower end of the impeller housing body 82 so that the inner diameter of the impeller housing body 82 increases from the upper side to the lower side. The upper end surface of the flow path member 61 is in contact with a step surface 83 a that is orthogonal to the axial direction of the step 83. Thereby, the impeller housing body 82 is positioned in the axial direction (Z-axis direction) with respect to the flow path member 61.

  The inner surface of the impeller housing main body 82 has a curved surface 82a and a facing surface 82b. The curved surface 82a is a curved surface having a circular arc shape in cross section, located radially outward from the upper side to the lower side. The curved surface 82a is continuously connected to the inner surface 61c of the flow path member without a step. Therefore, when the air flowing along the curved surface 82a flows into the exhaust passage 87, a loss is hardly generated. Therefore, according to this embodiment, the ventilation efficiency of the air blower 1 can be improved.

  The curved surface 82a faces the opening portion on the radially outer side of the impeller 70 in the radial direction. A connecting flow path 84 that connects the impeller flow path 86 and the exhaust flow path 87 is provided between the curved surface 82a and the impeller 70 in the radial direction.

  The radial width of the connection channel 84 increases from the upper side toward the lower side. That is, the radial width of the connection channel 84 is maximized at the lower end. The lower end portion of the connection channel 84 is a portion connected to the upper end portion of the exhaust channel 87. The radial width of the lower end portion of the connection flow path 84 and the radial width of the upper end portion of the exhaust flow path 87 are the same.

  As described above, on the upper side of the exhaust passage 87, the width of the exhaust passage 87 becomes smaller from the upper side to the lower side. Therefore, in the flow path from the connection flow path 84 to the upper side of the exhaust flow path 87, the width of the flow path is the largest at the location where the connection flow path 84 and the exhaust flow path 87 are connected. In other words, the step 83 which is a connection portion between the impeller housing 80 and the flow path member 61 is provided at a position where the width is the largest in the flow path from the connection flow path 84 to the upper side of the exhaust flow path 87.

  The upper end portion P2 of the curved surface 82a is positioned above the radially outer end portion of the lower surface of the shroud ring portion 72a. Therefore, the air discharged from the impeller flow path 86 to the radially outer side of the impeller 70 does not collide with the upper end portion P2. Thereby, air can be prevented from entering the gap GA2 between the radial outer end of the shroud ring portion 72a and the impeller housing main body portion 82 in the radial direction. Therefore, according to this embodiment, the ventilation efficiency of the air blower 1 can be improved.

  The gap GA2 is smaller than the gap GA3 between a facing surface 82b described later and the outer surface of the shroud 72. Thereby, it can suppress that the air which flows through the connection flow path 84 flows in into the clearance gap GA3 via the clearance gap GA2.

  The upper end portion P2 of the curved surface 82a is located below the radially outer end of the upper surface of the shroud ring portion 72a. Therefore, the air discharged from the impeller flow path 86 to the radially outer side of the impeller 70 tends to flow along the curved surface 82a. Thereby, the loss at the time of air flowing from the impeller channel 86 to the exhaust channel 87 via the connection channel 84 can be reduced. Therefore, according to this embodiment, the ventilation efficiency of the air blower 1 can be improved.

  The facing surface 82 b is a surface facing the shroud 72 of the impeller 70. The facing surface 82 b has a shape that follows the outer surface of the shroud 72. Therefore, it is easy to reduce the width of the gap GA3 between the facing surface 82b and the outer surface of the shroud 72.

  For example, if the width of the gap GA3 is too large, the pressure in the gap GA3 becomes low, so that air easily flows in the gap GA3 and loss tends to increase. On the other hand, according to this embodiment, since the width of the gap GA3 can be easily reduced, it is possible to suppress the flow of air into the gap GA3 and to reduce air loss. The width of the gap GA3 is, for example, substantially uniform.

  The intake guide portion 81 protrudes radially inward from the inner edge of the upper end portion of the impeller housing body portion 82. The intake guide portion 81 is, for example, an annular shape. The upper opening of the intake guide part 81 is an intake port 80a. The radially inner side surface of the intake guide portion 81 is a curved surface located radially outward as it goes from the lower side to the upper side.

  The intake guide portion 81 is located on the upper side of the shroud cylindrical portion 72b. A gap GA1 in the axial direction between the intake guide portion 81 and the shroud cylindrical portion 72b is smaller than the gap GA3. Thereby, it can suppress that the air which flows in into the impeller 70 from the inlet port 80a flows in into the gap GA3 via the gap GA1.

  The radial position of the radially inner end of the intake guide portion 81 is substantially the same as the radial position of the radially inner end of the shroud cylindrical portion 72b. Therefore, the air that has entered the impeller 70 along the intake guide portion 81 tends to flow along the shroud cylindrical portion 72b. Thereby, the loss of the air suck | inhaled in the impeller 70 can be reduced.

  For example, when the radial position of the impeller 70 is shifted inward due to vibration during rotation, the air flowing along the intake guide portion 81 from the intake port 80a hits the upper end portion of the shroud cylindrical portion 72b, and separation may occur. There is. Therefore, there is a risk that air loss will increase.

  On the other hand, according to the present embodiment, as described above, the inner surface of the shroud cylindrical portion 72b has the curved surface portion 72d positioned at the upper end portion. For this reason, even when the radial position of the impeller 70 is shifted, air tends to flow downward along the curved surface portion 72d. Therefore, air loss can be reduced.

  As shown in FIG. 1, when the impeller 70 is rotated by the motor 10, air flows into the impeller 70 from the air inlet 80a. The air that has flowed into the impeller 70 is discharged radially outward from the impeller flow path 86. The air discharged from the impeller flow path 86 proceeds from the upper side to the lower side through the connection flow path 84 and the exhaust flow path 87, and is discharged downward from the exhaust port 88. In this way, the blower 1 sends air.

  In the present embodiment, the following configuration may be employed.

  In the present embodiment, the impeller 70 may be a single member. In the present embodiment, the bearing holding member 60 may be constituted by two holding member pieces 60a, or may be constituted by four or more holding member pieces 60a.

  Further, the shape of each holding member piece 60a may be different from each other. Moreover, the structure provided with two or more outer side protrusion parts 63 along the circumferential direction may be sufficient.

Second Embodiment
7 and 8, the flow path member 161, the bearing holding member 160, the impeller 70, and the impeller housing 80 are not shown. In addition, about the structure similar to 1st Embodiment, description may be abbreviate | omitted by attaching | subjecting the same code | symbol suitably.

  As shown in FIG. 6, the blower 2 includes a motor 110, a bearing holding member 160, an impeller 70, a flow path member 161, a plurality of stationary blades 167, and an impeller housing 80.

  The motor 110 includes a housing 120, a rotor 30 having a shaft 31, a stator 140, a lower bearing 52 a and an upper bearing 52 b, and a connector 90. The housing 120 includes a peripheral wall 121, a lower lid portion 22, and a lower bearing holding portion 22b.

  As shown in FIG. 7, the peripheral wall 121 is provided with a plurality of through holes 121a and a plurality of notches 121b. As shown in FIG. 6, the upper end portion of the through hole 121 a is located below the stator core 141 described later. The other configuration of the through hole 121a is the same as the configuration of the through hole 21a of the first embodiment.

  As shown in FIG. 7, the notch 121 b is a part that is notched downward from the upper end portion of the peripheral wall 121. That is, the notch 121b penetrates the peripheral wall 121 in the radial direction and opens upward. For example, six notches 121b are provided at equal intervals along the circumferential direction. The shape of the notch 121b when viewed in the radial direction is, for example, a rectangular shape extending in the axial direction.

  As shown in FIG. 8, the stator 140 has a stator core 141. The stator core 141 includes a core back portion 41a, a teeth portion 41b, and a core protruding portion 141c. The core protruding portion 141c protrudes radially outward from the outer peripheral surface of the core back portion 41a. For example, six core protrusions 141c are provided along the circumferential direction.

  Each core protrusion 141c is fitted in the notch 121b. The radially outer surface of the core protrusion 141 c is located on the same plane as the outer peripheral surface of the housing 120. The radially outer surface of the core protrusion 141 c is exposed to the outside of the housing 120. In the present embodiment, since the plurality of notches 121b are arranged at equal intervals along the circumferential direction, on the outer peripheral surface of the motor 110, the outer peripheral surface of the core protruding portion 141c and the outer peripheral surface of the housing 120 are Line up alternately along the circumferential direction.

  As shown in FIG. 6, the radially outer surface of the core protruding portion 141 c faces the exhaust flow path 87. Therefore, according to the present embodiment, the stator core 141 can be cooled by the air flowing through the exhaust passage 87.

  The lower end of the core protrusion 141c is in contact with the lower edge of the notch 121b. As a result, the stator core 141 is positioned in the axial direction.

  The stationary blade 167 has a stationary blade lower portion 167a and a stationary blade upper portion 167b. The stationary blade lower portion 167a and the stationary blade upper portion 167b are separate members, for example. Other configurations of the stationary blade lower portion 167a are the same as the configurations of the stationary blade lower portion 67a of the first embodiment. Other configurations of the stationary blade upper portion 167b are the same as the configurations of the stationary blade upper portion 67b of the first embodiment.

  The bearing holding member 160 is the same as the bearing holding member 60 of the first embodiment except that the stationary blade upper part 167b is fixed to the outer peripheral surface. The stationary blade upper portion 167 b is fixed to the outer surface of the bearing holding member 160. The holding member piece and the stationary blade upper portion 167b are, for example, a single member. In the present embodiment, the bearing holding member 160 functions as a diffuser having a stationary blade upper portion 167b as a stationary blade.

  The number of the holding member pieces constituting the bearing holding member 160 is a divisor of the number of the stationary blade upper portions 167b. That is, the number of holding member pieces is a divisor of the number of stationary blades 167. Therefore, the number of the stationary blade upper portions 167b included in each holding member piece can be made the same for each holding member piece. Thereby, when the stationary blade upper part 167b is provided in the bearing holding member 160, the shape of each holding member piece can be made the same. Therefore, each holding member piece can be easily manufactured.

  As an example, when the number of the stationary blade upper portions 167b is 15 and the number of the holding member pieces constituting the bearing holding member 160 is 3, the number of the stationary blade upper portions 167b provided in one holding member piece is 5 It is.

  In the present embodiment, the flow path member 161 is a single member. A stationary blade lower portion 167 a is fixed to the inner peripheral surface of the flow path member 161. The flow path member 161 and the stationary blade lower portion 167a are, for example, a single member. The other configuration of the flow path member 161 is the same as the configuration of the flow path member 61 of the first embodiment. The other structure of the air blower 2 is the same as that of the air blower 1 of 1st Embodiment.

  In the present embodiment, the number of the notches 121b is not particularly limited, and may be 5 or less, or 7 or more. Moreover, in this embodiment, the through-hole which penetrates the surrounding wall 121 to radial direction may be provided instead of the notch 121b.

  Further, for example, the entire stationary blade 167 composed of the stationary blade lower portion 167 a and the stationary blade upper portion 167 b may be configured as a single member with the holding member piece constituting the bearing holding member 160.

  The vacuum cleaner 100 shown in FIG. 9 includes a blower according to the present invention. Thereby, in the air blower mounted in a cleaner, the rotation balance of a rotor assembly can be adjusted with high precision.

  In addition, the air blower of said 1st Embodiment and 2nd Embodiment may be used for any apparatuses. For example, the blower of the first embodiment and the second embodiment described above can be used for, for example, a vacuum cleaner and a dryer.

  In addition, the configurations described in the first embodiment and the second embodiment can be appropriately combined within a range that does not contradict each other.

  DESCRIPTION OF SYMBOLS 1, 2 ... Blower, 20, 120 ... Housing, 30 ... Rotor, 31 ... Shaft, 40, 140 ... Stator, 52b ... Upper bearing (bearing), 53b ... Elastic member, 60, 160 ... Bearing holding member, 60a ... Holding member piece, 62a ... 1st convex part, 62b ... 2nd convex part, 62c ... Holding member main-body part, 62d ... Holding cylinder part, 63 ... Outer protrusion part, 64 ... Inner protrusion part, 67,167 ... Stator blade, DESCRIPTION OF SYMBOLS 100 ... Vacuum cleaner, 167a ... Lower blade (static blade), 167b ... Upper blade (static blade), 70 ... Impeller, 71 ... Base member, J ... Central axis

Claims (10)

A rotor having a shaft disposed along a central axis extending vertically;
A stator located radially outside the rotor;
A housing that is open on the upper side and that houses the stator therein;
A bearing rotatably supporting the shaft;
A cylindrical bearing holding member located in the upper opening of the housing and surrounding and holding the bearing in a circumferential direction;
An impeller attached to the shaft above the bearing holding member;
With
The said bearing holding member is an air blower comprised by the several holding member piece arrange | positioned along the circumferential direction.   The blower device according to claim 1, wherein the bearing holding member is fixed inside the housing. The bearing holding member has a cylindrical holding cylinder part that holds the bearing, and an inner protrusion part that protrudes radially inward from an inner surface of the holding cylinder part,
The air blower according to claim 1 or 2, wherein the inner protruding portion opposes at least a part of an upper surface of the bearing in the axial direction.   The blower according to claim 3, wherein a radial distance from the central axis to a radially outer end of the rotor is larger than a radial distance from the central axis to a radially inner end of the inner protrusion. . The bearing holding member has an outer protrusion that protrudes radially outward,
The blower according to claim 1, wherein a lower surface of the outer projecting portion is in contact with an upper end surface of the housing.   The blower device according to claim 1, wherein the plurality of holding member pieces have the same shape. An elastic member is located on the radially inner side of the holding cylinder portion,
The blower according to claim 3, wherein the bearing is held by the holding cylinder portion via the elastic member. A plurality of stationary blades fixed to the outer surface of the bearing holding member;
The holding member piece and the stationary blade are a single member,
The blower device according to claim 6, wherein the number of the holding member pieces is a divisor of the number of the stationary blades. The impeller has a flat base member extending in the radial direction,
The base member is opposed to the bearing holding member in the axial direction through a gap,
The bearing holding member has a holding member main body part, and a first convex part and a second convex part protruding upward from the upper surface of the holding member main body part,
The first convex portion and the second convex portion are annular shapes surrounding the central axis,
The blower according to claim 1, wherein the second convex portion is located on a radially outer side of the first convex portion.   A vacuum cleaner provided with the air blower as described in any one of Claims 1-9.

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