WO2016194697A1 - Blower apparatus and vacuum cleaner - Google Patents

Abstract

A blower apparatus according to an exemplary embodiment of the present invention has: a motor having a shaft arranged along a central axis extending in the vertical direction; an impeller connected to the shaft, and arranged to rotate together with the shaft; an impeller housing arranged on the upper side of or radially outside of the impeller; a motor housing arranged radially outside of the motor; a flow channel member arranged radially outward of the motor housing with a gap therebetween; and a plurality of stationary vanes arranged in the circumferential direction in the gap between the motor housing and the flow channel member. At least one of the stationary vanes has a first stationary vane portion formed in one of the motor housing and the flow channel member, and a second stationary vane portion formed in the other one of the motor housing and the flow channel member, and the first stationary vane portion and the second stationary vane portion are connected to each other in the radial or axial direction.

Description

Blower and vacuum cleaner

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

Conventionally, a blower mounted on a vacuum cleaner is known to have a plurality of stationary blades. An example of such a blower is disclosed in Japanese Laid-Open Patent Publication No. 2002-138996. In the electric blower disclosed in Japanese Laid-Open Patent Publication No. 2002-138996, the height of the diffuser vane is located in the vicinity of the air flow path outlet formed between the diffuser vanes provided on the outer peripheral portion of the centrifugal impeller. It is disclosed that an intermediate vane having a height dimension smaller than the direction dimension can be provided. With this configuration, the air flow from the centrifugal impeller can be efficiently recovered as a static pressure by the diffuser, the loss of the bent portion from the diffuser side to the return side can be reduced, and the blowing efficiency can be improved.

Japanese publication: JP-A-2002-138996

However, in the electric blower disclosed in Japanese Laid-Open Patent Publication No. 2002-138996, the upper end of the intermediate blade in the height direction and the fan casing are arranged with a gap in the height direction. Therefore, there is a problem that the intermediate blade and the fan casing cannot be fixed. Moreover, a turbulent flow may occur in the gap between the upper end of the intermediate blade in the height direction and the fan casing, and the air blowing efficiency of the electric blower may be reduced.

An object of the present invention is to firmly fix a stationary blade configured on one side of a motor housing or a flow path member and the other side of the motor housing or the flow path member in a blower.

An air blower according to an exemplary embodiment of the present invention includes a motor having a shaft disposed along a central axis extending vertically, an impeller connected to the shaft and rotating integrally with the shaft, An impeller housing disposed on an upper side or a radially outer side of the impeller, a motor housing disposed on a radially outer side of the motor, and a flow path member disposed on a radially outer side of the motor housing via a gap. A plurality of stationary blades arranged in a circumferential direction in the gap between the motor housing and the flow channel member, and at least one of the stationary blades is one of the motor housing or the flow channel member A first stationary blade portion formed on a side of the motor housing or a second stationary blade portion formed on the other side of the flow path member, and the first stationary blade portion and the first stationary blade portion. The stationary blade unit is connected to the radial direction or the axial direction.

According to the present invention, it is possible to provide a blower capable of firmly fixing the stationary blade configured on one side of the motor housing or the flow path member and the other side of the motor housing or the flow path member. Moreover, in the vacuum cleaner which has the said air blower, the stationary blade comprised on the one side of a motor housing or a flow-path member, and the other side of a motor housing or a flow-path member can be fixed firmly.

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. 3 is a perspective view showing the rotor assembly of the first embodiment. FIG. 4 is a front view showing the bearing holding member 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 device 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 cross-sectional view illustrating the blower device of the third embodiment. FIG. 10 is a perspective view showing a motor housing of the third embodiment. FIG. 11 is a bottom view showing the flow path member of the third embodiment. FIG. 12 is a side view showing a stationary blade of the fourth embodiment. FIG. 13 is a side view showing a stationary blade of the fifth embodiment. FIG. 14 is a side view showing a stationary blade of the sixth embodiment. FIG. 15 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. The scope of the present invention is not limited to the following embodiments, and can be arbitrarily changed within the scope of the technical idea of the present invention. Moreover, in the following drawings, in order to make each structure easy to understand, the actual structure may be different from the scale or number of each structure.

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 up-down direction. The positive side (+ Z side) in the Z-axis direction is referred to as “upper side (upper axial direction)”, and the negative side (−Z side) in the Z-axis direction is referred to as “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.

The motor 10 includes a housing 20, a rotor 30 having a shaft 31, a stator 40, a lower bearing 52a, an upper bearing 52b, and a connector 90, as shown in FIG. 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 21a. 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 21a 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 lower 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 disposed along a central axis J extending vertically (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 outside the rotor 30 in the radial direction. 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 teeth 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 62c has, 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 62c 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 62 c has a holding cylinder 62 d and an inner protrusion 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 projecting portion 64 is opposed to at least a part of the upper surface of the upper bearing 52b 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 located 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 inner 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 protrusion 62b protrudes upward from the upper surface of the holding member main body 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 includes 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 this 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.

Also, since the rotational balance of the rotor assembly 11 can be adjusted with high accuracy, there is no need 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.

Further, since the bearing holding member 60 is composed of a plurality of holding member pieces 60a, it is necessary to hold the state in which the holding member pieces 60a are 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.

Further, for example, when the bearing holding member 60 is constituted 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 from 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 part of the inner cylinder part 71c is smoothly connected to the upper end part of the outer cylinder part 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 on the radially inner side of the inner cylindrical portion 71c. 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 the 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 portion 71c functions as a spacer that defines the position of the disc portion 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 cylinder 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 portion 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 facing the upper surface of the disc 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 has 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 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 that surrounds 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.

The inner diameter of the flow path member 61 is, for example, the 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, an exhaust flow path 87 extending in the 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. Change.

That is, the radial width of the exhaust flow path 87 decreases from the upper end to the lower side, and then increases from the position where the width is minimized to 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 flow path 87 becomes radially inner as the radial width of the exhaust flow path 87 becomes smaller, and becomes radially outer as the radial width of the exhaust flow path 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.

In contrast, according to the present embodiment, the radial position of the exhaust flow path 87 becomes radially inner as the radial width of the exhaust flow path 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, the lower end portion of the impeller housing main body 82 is provided with a step 83 in which the inner diameter of the impeller housing main 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 radially outer opening 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 to 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 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.

隙間 Gap GA2 is smaller than gap GA3 between an opposing surface 82b described later and the outer surface of 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 above 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.

In contrast, 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 intake port 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 can also be adopted.

In this 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 52a and an upper bearing 52b, 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 121b is a part that is notched from the upper end of the peripheral wall 121 to the lower side. 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 protrusion 141 c faces the exhaust passage 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 upper 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 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 167a and the stationary blade upper portion 167b may be configured as a single member with the holding member piece constituting the bearing holding member 160.

<Third Embodiment>
FIG. 9 is a cross-sectional view showing the blower 3 of the third embodiment. The blower 3 includes a motor 210, an impeller 270, an impeller housing 280, a motor housing 260, a flow path member 261, and a plurality of stationary blades 267. The motor housing 260 is a member corresponding to the bearing holding member 60 in the first embodiment. However, the upper bearing 252b may be held by a member other than the motor housing 260.

The motor 210 has a shaft 231 disposed along a central axis J that extends vertically. The motor 210 includes a rotor 230, a stator 240, a lower bearing 252a, and an upper bearing 252b. The rotor 230 is disposed radially inward of the stator 240 and connected to the shaft 231. The shaft 231 is rotatably supported around the central axis J with respect to the stator 240 via the lower bearing 252a and the upper bearing 252b.

The impeller 270 is connected to the shaft 231 and rotates together with the shaft 231. The impeller housing 280 is disposed on the upper side or the radially outer side of the impeller 270. In the air blower 3, the impeller housing 280 has an intake port 280a that surrounds the upper side and the radially outer side of the impeller 270 and penetrates in the axial direction at the center.

The motor housing 260 is disposed outside the motor 210 in the radial direction. The motor housing 260 is a substantially covered cylindrical member that opens downward. The flow path member 261 is disposed on the radially outer side of the motor housing 260 via a gap. That is, the outer surface in the radial direction of the motor housing 260 and the inner surface in the radial direction of the flow path member 261 are disposed with a gap in the radial direction. Thereby, the gap formed between the motor housing 260 and the flow path member 261 becomes a flow path.

The plurality of stationary blades 267 are arranged in the circumferential direction in the gap between the motor housing 260 and the flow path member 261. The plurality of stationary blades 267 are located radially outside the radially outer end of the impeller 270. Further, the upper ends in the axial direction of the plurality of stationary blades 267 are located on the lower side in the axial direction than the lower ends in the axial direction of the impeller 270. At least one of the plurality of stationary blades 267 includes a plurality of divided portions. That is, at least one of the stationary blades 267 includes a first stationary blade portion 268 formed on one side of the motor housing 260 or the flow channel member 261 and a first stationary blade portion 268 formed on the other side of the motor housing 260 or the flow channel member 261. Two stationary blade portions 269. In the present embodiment, the outer surface of the motor housing 260 has a first stationary blade portion 268, and the inner surface of the flow path member 261 has a second stationary blade portion 269.

The first stationary blade portion 268 and the second stationary blade portion 269 are connected in the radial direction or the axial direction. Thereby, the 1st stator blade part 268 and the 2nd stator blade part 269 can be fixed firmly. Further, by fixing the first stationary blade portion 268 formed on the motor housing 260 and the second stationary blade portion 269 formed on the flow path member 261, the radial outer surface of the motor housing 260 and the flow path member 261 are fixed. The coaxiality with the inner surface in the radial direction can be improved. Therefore, since the radial width of the flow path can be made more uniform in the circumferential direction, the blowing efficiency of the blower 3 is improved.

FIG. 10 is a perspective view of the motor housing 260 of the third embodiment, and FIG. 11 is a bottom view of the flow path member 261 of the third embodiment. Referring to FIGS. 9 to 11, first stator blade portion 268 and second stator blade portion 269 each have a first connecting portion 268 </ b> A and a second connecting portion 269 </ b> A. The first connecting portion 268 </ b> A is a portion that is formed on the first stationary blade portion 268 and contacts a part of the second stationary blade portion 269. The second connecting portion 269A is a part formed on the second stationary blade portion 269 and in contact with a part of the first stationary blade portion. At least a part of the first connecting part 268A and at least a part of the second connecting part 269A abut in the axial direction. Thereby, when the 1st stator blade part 268 and the 2nd stator blade part 269 are connected, the axial positioning of the 1st stator blade part 268 and the 2nd stator blade part 269 can be performed.

Also, at least a part of the first connecting part 268A and at least a part of the second connecting part 269A are in contact with each other in the circumferential direction. Thereby, when the 1st stator blade part 268 and the 2nd stator blade part 269 are connected, the circumferential positioning of the 1st stator blade part 268 and the 2nd stator blade part 269 can be performed. That is, the first connecting portion 268A and the second connecting portion 269A are in contact with each other in the axial direction and the circumferential direction, and are positioned in the axial direction and the circumferential direction. By positioning in the axial direction and the circumferential direction, the first stationary blade portion 268 and the second stationary blade portion 269 can be fixed without being displaced from each other.

The first connecting portion 268A has a convex portion 268B extending in the axial direction or the radial direction, and the second connecting portion 269A has a concave portion 269B recessed in the axial direction or the radial direction. In the present embodiment, the convex portion 268B extends downward in the axial direction from the surface facing downward in the axial direction at the lower portion of the first stationary blade portion 268. A first connecting portion 268A is configured by the axially lower surface of the lower portion of the first stationary blade portion 268 and the convex portion 268B. In addition, the recess 269 </ b> B is recessed from the radially inner side to the outer side in the second stationary blade part 269. A second connecting portion 269A is configured by the upper surface of the second stationary blade portion 269 and the concave portion 269B.

The circumferential width W1 of at least a part of the convex portion 268B is narrower than the circumferential width W2 of the stationary blade 267. When the blower 3 is assembled, the motor housing 260 having the first stationary blade portion 268 is moved downward in the axial direction. And the convex part 268B is inserted in the recessed part 269B. As a result, the positions of the first stator blade part 268 and the second stator blade part 269 are simultaneously restricted in the axial direction and the circumferential direction, and the first stator blade part 268 and the second stator blade part are easily configured and assembled. 269 can be firmly fixed, and mass productivity is improved.

In the present embodiment, the first stationary blade portion 268 is located on the upper side in the axial direction than the second stationary blade portion 269. The first stationary blade portion 268 has a first side surface 268C that faces the rear side in the rotation direction R of the impeller. The second stationary blade portion 269 has a second side surface 269C that faces the rear side in the rotation direction R of the impeller. The first side surface 268C and the second side surface 269C are smoothly connected. That is, when the first stationary blade portion 268 and the second stationary blade portion 269 are connected, the first side surface 268C and the second side surface 269C cause the side surface of the stationary blade 267 facing the rear side in the rotation direction R of the impeller. Composed. Thereby, since the air which flows through a flow path is smoothly guided toward the axial direction lower side along the 1st side 268C and the 2nd side 269C, the ventilation efficiency of the air blower 3 improves. The surface of the stationary blade 267 facing the front side in the rotational direction R of the impeller is also the surface facing the front side of the impeller in the rotational direction R of the first stationary blade portion 268 and the forward side of the rotational direction R of the impeller in the second stationary blade portion 269. And a surface that faces. Thereby, the ventilation efficiency of the air blower 3 further improves.

As shown in FIG. 10, the upper portion of the first side surface 268C is curved forward in the rotational direction R from the upper side in the axial direction toward the lower side. More specifically, the upper portion of the first side surface 268C is a smooth curved surface that protrudes forward in the rotational direction R of the impeller and upward in the axial direction. As a result, the air discharged radially outward from the impeller 270 smoothly rotates along the curved surface above the first side surface 268C while having a component swirling in the circumferential direction toward the front side in the rotation direction R of the impeller. It is guided downward in the direction and flows downward in the axial direction. Therefore, the blowing efficiency of the blower 3 is improved.

Referring to FIG. 9, in the gap in the axial region A where the stationary blade 267 is disposed, the radial gap d1 at the upper end of the axial region A is wider than the radial gap d2 at the lower end of the axial region A. That is, in the axial region A where the stationary blade 267 is disposed, the radial gap of the flow path at the upper end is wider than the radial gap of the flow path at the lower end. Thereby, since the cross-sectional area of the flow path becomes narrow in the region where the stationary blades 267 are arranged, the static pressure of the air flowing in the flow channel becomes high, and generation of turbulent flow in the axial region A can be reduced. Therefore, the flow of air flowing in the flow path becomes smooth, and the blowing efficiency of the blower 3 is improved.

The radial gap d2 at the lower end of the axial region A is narrower than the radial gap d3 between the outer surface of the motor housing 260 and the inner surface of the flow path member 261 below the axial region A. That is, the radial gap d3 of the flow path below the axial direction area A is wider than the radial gap of the flow path below the axial direction area A. As a result, the air whose static pressure has been increased in the axial region A has a gradually lower resistance in the flow channel as the cross-sectional area of the flow channel expands below the axial region A in the axial direction. Smoothly flows downward in the axial direction. Therefore, the blowing efficiency of the blower 3 is improved.

Referring to FIG. 11, a plurality of stator blades 267 having first stator blade portions 268 and second stator blade portions 269 are arranged unevenly in the circumferential direction. That is, in FIG. 11, the circumferential gaps in the plurality of second stationary blade portions 269 are different from the other circumferential gaps at least at one location. Similarly, the circumferential gaps of the plurality of first stator blade portions 268 are the same as those of the plurality of second stator blade portions 269. Thereby, the motor housing 260 and the flow path member 261 are positioned in the circumferential direction.

In the third embodiment, the first stationary blade portion 268 is disposed above the second stationary blade portion 269. However, the first stationary blade portion 268 may be disposed below the second stationary blade portion 269. Further, the first stationary blade portion 268 may be formed in the flow path member 261 instead of the motor housing 260. Further, the convex portion 268B may be formed in the second stationary blade portion 269, and the concave portion 269B may be formed in the first stationary blade portion 268.

In the third embodiment, each of the first connecting portion 268A and the second connecting portion 269A includes a plane that is substantially orthogonal to the axial direction and a convex portion 268B that protrudes axially from the plane, or a recess that extends in the axial direction. However, the first connecting portion 268A and the second connecting portion 269A may have other shapes. For example, the lower surface of the first connecting portion 268A may be an inclined surface that is inclined with respect to the axial direction.

Furthermore, as another structure, when the stationary blade 267 is viewed from the upper side in the axial direction, the upper end portion of the second connecting portion 269A may be exposed on the upper side in the axial direction. That is, in the third embodiment, since the upper end portion of the second connecting portion 269A is in contact with the first connecting portion 268A in the axial direction, the second connecting portion is viewed when the stationary blade 267 is viewed from the upper side in the axial direction. 269A is not exposed on the upper side in the axial direction, but may be exposed on the upper side in the axial direction. Further, when viewed from the lower side in the axial direction, the lower end portion of the first connecting portion 268A may be exposed on the lower side in the axial direction.

<Fourth embodiment>
FIG. 12 is a side view showing a stationary blade 367 of the fourth embodiment. For convenience, the flow path member disposed on the radially outer side is omitted. A plurality of stationary blades 367 are arranged in the circumferential direction. At least one of the plurality of stationary blades 367 includes a plurality of divided parts. That is, at least one of the stationary blades 367 includes a first stationary blade portion 368 formed on one side of the motor housing 360 or the flow path member and a second stationary blade formed on the other side of the motor housing 360 or the flow path member. And a wing portion 369.

The first stator blade portion 368 and the second stator blade portion 369 have a first connecting portion 368A and a second connecting portion 369A, respectively. The first connecting portion 368A and the second connecting portion 369A each have a first step portion 368E and a second step portion 369E that extend in the axial direction. Either the surface facing the axial direction or the surface facing the circumferential direction of the first step portion 368E and the second step portion 369E abuts. In the fourth embodiment, the surface facing the axial direction of the first stepped portion 368E, that is, the lower surface is in contact with the surface facing the axial direction of the second stepped portion 369E, that is, the upper surface. Furthermore, the circumferential surface, that is, the side surface of the first step portion 368E is in contact with the circumferential surface of the second step portion 369E, that is, the side surface. Thereby, the 1st stator blade part 368 and the 2nd stator blade part 369 can be positioned in both an axial direction and the circumferential direction. Moreover, since the structure of the 1st connection part 368A and the 2nd connection part 369A can be simplified compared with the structure of 3rd Embodiment, an air blower can be assembled by a cheap and simple operation | work. The first step portion 368A and the second step portion 369A only need to be in contact with either one of the surfaces facing the axial direction or the surface facing the circumferential direction, and both surfaces are in contact. It does not have to be.

The first stationary blade portion 368 has a first side surface 368C facing the impeller rotation direction R rear side, and the second stationary blade portion 369 has a second side surface 369C facing the impeller rotation direction R rear side. The lower end portion 368D of the first side surface is located on the rear side in the rotational direction R of the impeller with respect to the upper end portion 369D of the second side surface in the circumferential direction. As a result, the resistance received by the air flowing near the first side surface is lower than in the case where the lower end portion 368D of the first side surface is positioned more forward in the rotational direction R of the impeller than the upper end portion 369D of the second side surface in the circumferential direction. Is reduced. Further, in the assembly process, even when the position of the upper end portion 369D of the second side surface is slightly shifted to the rear side in the rotation direction R of the impeller, the upper end portion 369D of the second side surface rotates the impeller more than the first side surface 368C. Exiting in the direction R rear side is suppressed. In the rotation direction R of the impeller, the lower end portion 368D on the first side surface and the upper end portion 369D on the second side surface are arranged in the same position, so that the air blowing efficiency is further improved.

<Fifth Embodiment>
FIG. 13 is a side view showing a stationary blade 467 of the fifth embodiment. For the sake of convenience, in FIG. 13, the flow path member disposed on the radially outer side of the stationary blade 467 is omitted. The air blower of 5th Embodiment is the same as that of 3rd Embodiment except for the stationary blade 467.

The stationary blade 467 is formed on one side of the motor housing or the flow path member, and has a recess 468F that is recessed in the axial direction at the lower end in the axial direction. Further, a connecting portion 469F is formed on the other side of the motor housing or the flow path member. In the present embodiment, the stationary blade 467 is formed integrally with the flow path member, and the connecting portion 469F is formed integrally with the motor housing. The connecting portion 469F is engaged with at least a part of the recess 468F. Thereby, the stationary blade 467 and the connecting portion 469F can be firmly fixed by an inexpensive and high-productivity configuration.

The stator blade 467 of the fifth embodiment differs from the stator blade 267 of the third embodiment and the stator blade 367 of the fourth embodiment in that the connecting portion 469F does not constitute the side surface of the stator blade 467. That is, in the stationary blade 467, the side surface of the stationary blade 467 is constituted only by the stationary blade 467 formed integrally with one side of the motor housing or the flow path member. Further, the connecting portion 469F constitutes a part of the lower surface of the stationary blade 467 and is not exposed to other surfaces. Further, in the present embodiment, the stationary blade 467 is disposed on the upper side of the connecting portion 469F, but the stationary blade is disposed on the lower side of the connecting portion, and is a concave portion that is recessed downward on the upper surface of the stationary blade. You may have.

<Sixth Embodiment>
FIG. 14 is a side view showing a stationary blade 567 of the sixth embodiment. For the sake of convenience, in FIG. 14, the flow path member disposed on the radially outer side of the stationary blade 567 is omitted. The air blower of 6th Embodiment is the same as that of 3rd Embodiment except for the stationary blade 567.

The stationary blade 567 is formed on one side of the motor housing or the flow path member, and has a recess 568F that is recessed toward the rear side in the rotational direction R of the impeller on the front side in the rotational direction R of the impeller. A connecting portion 569F is formed on the other side of the motor housing or the flow path member. The connecting portion 569F is engaged with at least a part of the recess 568F. In the present embodiment, the stationary blade 567 is formed integrally with the motor housing, and the connecting portion 569F is formed integrally with the flow path member. As a result, the stationary blade 567 and the connecting portion 569F can be firmly fixed by an inexpensive and highly productive configuration.

In the stationary blade 567, unlike the stationary blade 267 of the third embodiment and the stationary blade 367 of the fourth embodiment, the connecting portion 569F does not constitute a side surface of the stationary blade 567. Further, the connecting portion 569F constitutes a part of the surface of the stationary blade 567 on the front side in the rotation direction R of the impeller, and is not exposed to other surfaces. The concave portion 568F may be configured on the surface on the rear side in the rotation direction R of the impeller and may be engaged with the connecting portion 569F.

15 includes a blower according to the present invention. Thereby, the 1st stator blade part and the 2nd stator blade part can be firmly fixed in the air blower mounted in a cleaner.

In addition, the air blower of said 1st Embodiment to 6th Embodiment may be used for any apparatuses. The blower of the first to sixth embodiments can be used for, for example, a vacuum cleaner and a dryer.

Further, the configurations described in the first to sixth embodiments can be appropriately combined within a range that does not contradict each other.

1, 2, 3 ... Blower, 10, 110, 210 ... Motor, 20, 120 ... Housing, 30, 230 ... Rotor, 31, 231, Shaft, 40, 140, 240 ... Stator, 52a, 252a ... Lower bearing (Bearings), 52b, 252b ... Upper bearing (bearing), 53b ... Elastic member, 60, 160, 260, 360 ... Bearing holding member (motor housing), 60a ... Holding member piece, 61, 161, 261 ... Channel member 62a, first convex portion, 62b, second convex portion, 62c, holding member main body portion, 62d, holding cylinder portion, 63, outer protruding portion, 64, inner protruding portion, 67, 167, 267, 367, 467,. 567 ... Stator blade, 268, 368 ... First stator blade portion, 268A, 368A ... First connecting portion, 268B ... Convex portion, 268C, 368C ... First side surface, 68D: lower end portion of first side surface, 368E: first step portion, 468F, 568F ... concave portion, 269, 369 ... second stationary blade portion, 269A, 369A ... second connecting portion, 269B ... concave portion, 269C, 369C ... first 2 side surfaces, 369D ... upper end portion of second side surface, 369E ... second stepped portion, 469F, 569F ... connecting portion, 70, 270 ... impeller, 71 ... base member, 80, 280 ... impeller housing, 80a, 280a ... intake port , 100 ... Vacuum cleaner, 167a ... Lower blade (static blade), 167b ... Upper blade (static blade), A ... Axial region, d1, d2, d3 ... Radial gap, J ... Central shaft, R ... Impeller Rotation direction, W1, W2 ... circumferential width

Claims (14)

1. A motor having a shaft disposed along a central axis extending vertically;
   An impeller connected to the shaft and rotating integrally with the shaft;
   An impeller housing disposed on an upper side or a radially outer side of the impeller;
   A motor housing disposed radially outside the motor;
   A flow path member disposed via a gap radially outside the motor housing;
   A plurality of stationary blades arranged in a circumferential direction in the gap between the motor housing and the flow path member;
   Have
   At least one of the stationary blades is
   A first stator blade portion formed on one side of the motor housing or the flow path member;
   A second stationary blade portion formed on the other side of the motor housing or the flow path member;
   Have
   The first stationary blade portion and the second stationary blade portion are air blowers connected in a radial direction or an axial direction.
2. The first stator blade part and the second stator blade part have a first connecting part and a second connecting part, respectively.
   The blower according to claim 1, wherein at least a part of the first connecting part and at least a part of the second connecting part abut in the axial direction.
3. The first stator blade part and the second stator blade part have a first connecting part and a second connecting part, respectively.
   The blower according to claim 1, wherein at least a part of the first connecting part and at least a part of the second connecting part are in contact with each other in a circumferential direction.
4. The first connecting portion has a convex portion extending in the axial direction or the radial direction,
   The second connecting portion has a concave portion that is recessed in the axial direction or the radial direction,
   The circumferential width of at least a part of the convex portion is narrower than the circumferential width of the stationary blade,
   The blower according to claim 2, wherein the convex portion is inserted into the concave portion.
5. Each of the first connecting portion and the second connecting portion includes a first step portion and a second step portion extending in the axial direction,
   The surface of the said 1st level | step-difference part and the said 2nd level | step-difference part, either one surface of the surface which faces an axial direction, or the circumferential direction contact | abuts. Blower device.
6. The first stationary blade portion is located on the upper side in the axial direction than the second stationary blade portion,
   The first stationary blade portion has a first side surface facing toward the rear side in the rotation direction of the impeller,
   The second stationary blade portion has a second side surface facing the rear side in the rotational direction of the impeller,
   The blower according to any one of claims 1 to 5, wherein the first side surface and the second side surface are smoothly connected.
7. The blower according to any one of claims 1 to 5, wherein the lower end portion of the first side surface is located on the rear side in the rotation direction of the impeller with respect to the upper end portion of the second side surface in the circumferential direction.
8. The blower according to any one of claims 1 to 7, wherein a plurality of the stationary blades having the first stationary blade portion and the second stationary blade portion are arranged in an uneven manner in the circumferential direction.
   
9. The blower according to any one of claims 6 and 7, wherein the upper portion of the first side surface is curved forward in the rotational direction from the upper side in the axial direction toward the lower side.
10. In the gap in the axial region where the stationary blade is disposed,
    The blower according to any one of claims 1 to 9, wherein a radial clearance at an upper end of the axial region is wider than a radial clearance at a lower end of the axial region.
11. The radial clearance at the lower end of the axial region is
    The blower according to claim 10, wherein the blower is narrower than a radial gap between an outer surface of the motor housing and an inner surface of the flow path member below the axial region.
12. A motor having a shaft disposed along a central axis extending vertically;
    An impeller connected to the shaft and rotating integrally with the shaft;
    An impeller housing disposed on an upper side or a radially outer side of the impeller;
    A motor housing disposed radially outside the motor;
    A flow path member disposed via a gap radially outside the motor housing;
    A plurality of stationary blades arranged in a circumferential direction in the gap between the motor housing and the flow path member;
    Have
    The stationary blade is formed on one side of the motor housing or the flow path member, and has a concave portion that is recessed in the axial direction at the lower end in the axial direction.
    A connecting portion is formed on the other side of the motor housing or the flow path member,
    The connecting part is an air blower engaged with at least a part of the recess.
13. A motor having a shaft disposed along a central axis extending vertically;
    An impeller connected to the shaft and rotating integrally with the shaft;
    An impeller housing disposed on an upper side or a radially outer side of the impeller;
    A motor housing disposed radially outside the motor;
    A flow path member disposed via a gap radially outside the motor housing;
    A plurality of stationary blades arranged in a circumferential direction in the gap between the motor housing and the flow path member;
    Have
    The stationary blade is formed on one side of the motor housing or the flow path member, and has a concave portion recessed in a circumferential direction on a surface facing the front side in the rotation direction of the impeller,
    A connecting portion is formed on the other side of the motor housing or the flow path member,
    The connecting part is an air blower engaged with at least a part of the recess.
14. A vacuum cleaner comprising the blower device according to any one of claims 1 to 13.

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