KR20210142444A - Fan motor - Google Patents

Abstract

The present invention relates to a fan motor comprising: a shroud; a rotation shaft which is rotatably disposed on a straight line crossing the inner center of the shroud; an impeller which is rotatably coupled to one end of the rotation shaft; a rotor which is installed on the rotation shaft to be axially spaced apart from the impeller; an air bearing which is lubricated with air with an air gap between the rotation shaft and the same, to rotatably support one side of the rotation shaft; and a ball bearing which is coupled to the other end of the rotation shaft to be opposite to the air bearing with the rotor interposed therebetween, and rotatably supports the other side of the rotation shaft. The fan motor can rotate at a high speed while realizing reduced size and weight.

Description

fan motor

The present invention relates to a fan motor suitable for high-speed rotation of a fan.

The electric motor may be installed in home appliances such as a vacuum cleaner or a hair dryer.

A vacuum cleaner or a header dryer may use an electric motor as a power source to generate rotational force.

For example, the electric motor may be coupled to the fan FAN. The fan receives power from the electric motor and rotates to generate airflow.

A vacuum cleaner or a hair dryer is operated while being lifted by the user.

In order to increase user's portability and convenience, it is necessary to reduce the size and weight of a vacuum cleaner or a hair dryer.

To this end, while improving the output of the motor, miniaturization and weight reduction of the motor are required. In addition, high-speed rotation of the motor is essential.

US 2010/0215491 A1 (published on August 26, 2010, hereinafter referred to as Patent Document 1) discloses a rotor assembly.

The rotor assembly includes a rotating shaft. An impeller, rotor core and bearing cartridge are mounted on the rotating shaft. A bearing cartridge is disposed between the impeller and the rotor core.

The bearing cartridge contains two ball bearings, a spring and a sleeve.

The bearing cartridge supports the rotating shaft with two ball bearings.

In the bearing cartridge, a spring is disposed between two ball bearings, and the spring applies a preload to each of the two ball bearings, thereby securing the life of the ball bearing.

The bearing cartridge accommodates the two ball bearings in the sleeve, and the outer ring of the ball bearing is aligned by the sleeve, thereby extending the life of the ball bearing.

However, when the two ball bearings of Patent Document 1 are applied to the fan motor, there is a disadvantage in reducing the size and weight of the fan motor.

For example, in order to reduce the size and weight of the fan motor, the size of the ball bearing should be small, but the ball bearing has a structure in which a plurality of balls are in rolling contact between the outer ring and the inner ring. It is disadvantageous, and as the size of the ball bearing increases, it is not suitable for high speed.

In more detail, the smaller the size of the ball bearing, the smaller the diameter of the rotary shaft should be. However, if the diameter of the rotary shaft is too small, a problem of bending of the rotary shaft occurs.

In particular, of the two ball bearings, the support part of the rotating shaft on which the ball bearing adjacent to the impeller is mounted has a greater bending problem due to the unbalanced load of the impeller.

In addition, if the diameter of the rotating shaft is too small, the allowable limit speed of the rotating shaft is lowered, so that the operating speed of the fan motor becomes dangerous as the speed increases.

In addition, in order for the rotating shaft to withstand high-speed rotation, as the diameter of the rotating shaft increases, the diameter of the ball bearing must be increased. In this case, there is a problem in that the life of the ball bearing is shortened.

An electric machine is disclosed in US 2018/0363669 A1 (published on December 20, 2018; hereinafter, Patent Document 2).

The electric machine includes a rotor assembly. The rotor assembly includes a first ball bearing and a second ball bearing mounted on both sides of a rotation shaft with a rotor core permanent magnet interposed therebetween.

The life of the ball bearing can be extended by installing an O-ring on the outer circumferential surface of the ball bearing.

However, when the two ball bearings of Patent Document 2 are applied to the fan motor, there is a disadvantage in reducing the size and weight of the fan motor. A detailed description thereof is the same as or similar to that of Patent Document 1, and thus a redundant description thereof will be omitted.

A first object of the present invention is to provide a fan motor capable of high-speed rotation at 100,000 rpm or more while reducing the size and weight.

A second object of the present invention is to provide a fan motor capable of extending the life of the bearing even when the diameter of the rotating shaft is increased.

A third object of the present invention is to provide a fan motor capable of increasing an allowable limit speed even during high-speed rotation and preventing bending of a rotating shaft.

A fourth object of the present invention is to provide a fan motor capable of aligning a rotating shaft by constantly maintaining an air gap between a bearing and a rotating shaft.

A fifth object of the present invention is to provide a fan motor capable of minimizing the inflow of foreign substances into the bearing.

In order to achieve the first and second objects described above, a fan motor according to the present invention includes a shroud; a rotation shaft rotatably disposed on a straight line crossing the inner center of the shroud; an impeller rotatably coupled to one end of the rotation shaft; a rotor installed on the rotating shaft to be axially spaced apart from the impeller; an air bearing lubricated with air with an air gap between the rotation shaft and the rotation shaft to rotatably support one side of the rotation shaft; It may include a ball bearing coupled to the other end of the rotation shaft opposite to the air bearing with the rotor interposed therebetween and rotatably supporting the other side of the rotation shaft.

According to an example related to the present invention, the air bearing may be disposed between the impeller and the rotor toward a downstream side of the impeller based on a flow direction of air generated by the impeller.

According to an example related to the present invention, the rotation shaft may include a first support part supported by the air bearing; a second support part supported by the ball bearing; and a permanent magnet mounting part disposed between the first support part and the second support part and to which a permanent magnet is mounted.

In order to achieve the third object described above, according to an example related to the present invention, the first support portion may be formed to have a larger diameter than the second support portion.

According to an example related to the present invention, the first support portion may be formed to have a larger diameter than the permanent magnet mounting portion.

According to an example related to the present invention, it includes a stator having a stator core formed to surround the rotor with an air gap with the rotor and a stator coil wound around the stator core, and the inner diameter of the air bearing is the stator core It may be formed smaller than the inner diameter of

According to such a structure, the assembly property of a motor can be ensured.

According to an example related to the present invention, the inner diameter of the air bearing may be formed to be larger than the diameter of the rotor.

In order to achieve the fourth object described above, according to an example related to the present invention, a first O-ring holder mounted on the outer circumferential surface of the air bearing to surround the air bearing; and a plurality of first O-rings respectively mounted in a plurality of first O-ring mounting grooves formed in the first O-ring holder.

According to an example related to the present invention, a second O-ring holder mounted on the outer peripheral surface of the ball bearing so as to surround the ball bearing; and a plurality of second O-rings respectively mounted in the plurality of second O-ring mounting grooves formed in the second O-ring holder.

In order to achieve the fifth object described above, according to an example related to the present invention, the first bearing is disposed on the downstream side of the impeller based on the flow direction of the air generated by the impeller, and accommodates the air bearing. a first bearing housing having a receiving portion, wherein the impeller includes a hub and a plurality of blades protruding from an outer circumferential surface of the hub, wherein the hub is disposed to cover an upper portion of the air bearing that is opened toward the impeller can

According to an example related to the present invention, the first bearing housing is disposed on the downstream side of the impeller based on the flow direction of the air generated by the impeller, the first bearing housing having a first bearing accommodating portion for accommodating the air bearing; a first vane hub disposed on a downstream side of the first bearing housing based on the flow direction of the air to cover a part of the first bearing housing and having a plurality of first vanes for guiding the flow of the air; and a second vane hub disposed on a downstream side of the first vane hub with respect to the flow direction of the air and having a plurality of second vanes for guiding the flow of the air.

According to an example related to the present invention, the first vane hub and the second vane hub may be formed in a cylindrical shape having the same diameter, and may be arranged in a straight line in the axial direction.

According to an example related to the present invention, the plurality of first vanes and the plurality of second vanes may be coupled to and supported by fitting to the inner circumferential surface of the shroud.

According to an example related to the present invention, a stator comprising a stator core formed to surround the rotor with an air gap with the rotor and a stator coil wound around the stator core, wherein the stator is of the second vane hub It may be coupled to the inner circumferential surface to be in surface contact, and may be configured to extend to a heat exchange area between the stator and the air by the second vane hub and the plurality of second vanes.

According to an example related to the present invention, the second vane hub and the plurality of second vanes may be formed of a thermally conductive metal material.

According to an example related to the present invention, a first fastening portion formed to protrude downward in the axial direction from the first bearing housing; and a second fastening part formed to protrude upward from the second vane hub in the axial direction, wherein the first fastening part and the second fastening part are disposed to overlap in a radial direction with the first vane hub interposed therebetween, , the first bearing housing, the first vane hub, and the second vane hub may be fastened by a fastening member penetrating the first fastening part, the first vane hub, and the second fastening part.

According to an example related to the present invention, further comprising a second bearing housing disposed on the downstream side of the rotor with respect to the flow direction of the air and having a second bearing accommodating part accommodating the ball bearing, The two-bearing housing may include a plurality of bridges protruding from the second bearing accommodating part toward an inner circumferential surface of the second vane hub and connecting the second bearing accommodating part and the second vane hub.

In order to achieve the first and second objects described above, a fan motor according to the present invention includes a shroud; an impeller rotatably provided inside the shroud to suck air into the shroud; a rotating shaft having one end coupled to the impeller and disposed to cross the center of the shroud in the axial direction; a rotor disposed to be spaced apart from the impeller in the axial direction and having a permanent magnet mounted on the rotating shaft; a stator provided inside the shroud to surround the rotor with a gap with the rotor; a first vane disposed between the impeller and the stator to guide air sucked in by the impeller to flow toward the stator; an air bearing disposed between the impeller and the rotor and lubricated with air with an air gap with one side of the rotation shaft so as to rotatably support one side of the rotation shaft; and a ball bearing disposed on the opposite side of the impeller with respect to the rotor and rotatably supporting the other side of the rotation shaft.

The effect of the fan motor according to the present invention will be described as follows.

First, an air bearing is applied as a first bearing supporting a first support part of a rotation shaft positioned adjacent to the impeller.

Since the air bearing is lubricated with air without a separate working fluid, friction between the air bearing and the rotating shaft does not occur.

For this reason, even when the rotating shaft rotates at a high speed of 100,000 rpm or more, wear due to friction between the air bearing and the rotating shaft does not occur, thereby extending the life of the bearing. In addition, by applying an air bearing, it is possible to extend the life of the fan motor during high-speed rotation.

Second, air bearings have the advantage of extending the lifespan even if the diameter is increased.

Accordingly, it is possible to increase the diameter of the shaft of the first support by increasing the diameter of the air bearing.

In addition, by increasing (thickening) the diameter (thickness) of the first support part of the rotating shaft adjacent to the impeller, it is possible to prevent bending of the rotating shaft due to the load on one side of the impeller during high-speed rotation. In addition, by increasing the thickness of the first support portion, it is possible to increase the allowable speed of the rotation shaft.

For example, the diameter of the first support part may be formed to be larger than the diameter of the impeller coupling part of the rotation shaft to which the impeller is coupled.

In addition, the diameter of the first support part may be formed to be larger than the diameter of the permanent magnet mounting part of the rotation shaft on which the permanent magnet is mounted.

In addition, the diameter of the first support portion may be formed to be larger than the diameter of the second support portion supported by the second bearing.

Third, after the stator is pre-assembled inside the shroud, it passes through the rotor receiving hole formed inside the stator core and is assembled so as to be disposed on the same center line of the first receiving part and the second receiving part of the shroud.

In order for the first support part to pass through the rotor receiving hole and be coupled to the inner circumferential surface of the first bearing, it is preferable that the diameter of the first support part is smaller than the inner diameter of the stator core.

In addition, the inner diameter of the first bearing is formed to be smaller than the inner diameter of the stator core, so that assembly of the rotating shaft and the like can be secured.

Fourth, the air bearing is not disposed in the suction passage, the expansion passage, and the cooling passage, which are the main passages of the fan motor, but is disposed so that the impeller covers the first bearing receiving part in which the air bearing is accommodated, thereby preventing the inflow of foreign substances such as dust into the air bearing. can be blocked

Fifth, a first O-ring mounting groove is formed on the outer wall of the first O-ring holder surrounding the air bearing, and a plurality of first O-rings are mounted in the plurality of first O-ring mounting grooves, so that the axis of rotation is axially positioned on the center line of the shroud. can be sorted accordingly.

Sixth, the first O-ring may be formed of an elastic material to attenuate an impact transmitted from the outside to the first bearing.

Seventh, a ball bearing may be applied as a second bearing for supporting a second support portion of a rotation shaft positioned opposite to the impeller with respect to the permanent magnet mounting portion.

Since the second support portion of the rotary shaft opposite to the impeller is less affected by the load on one side of the impeller, the shaft diameter of the second support portion may be smaller than the shaft diameter of the first support portion.

Due to this, a ball bearing may be applied to the second support part. Ball bearings are cheaper than air bearings. Therefore, it is more advantageous in terms of cost to apply one air bearing and one ball bearing than to apply two air bearings as bearings supporting both sides of the rotating shaft.

Eighth, when using two bearings only with air bearings, a thrust bearing, which is an essential element, must be used. However, if one air bearing and one ball bearing are applied, it is not necessary to use a thrust bearing, which will greatly contribute to the miniaturization and weight reduction of the fan motor. can

Ninth, the first vane hub and the second vane hub are arranged in a straight line with each other on the downstream side of the impeller based on the flow direction of the air generated by the impeller, and are formed between the shroud and the first and second vane hubs Since the cooling passages have the same diameter and are formed in a straight line without bending, flow resistance of air can be minimized and the cooling efficiency of the motor can be increased with air.

Tenth, a plurality of second vanes are formed to protrude into the cooling passage on the outer circumferential surface of the second vane hub, and the plurality of second vanes not only guide the flow of air but also expand the heat exchange area between the air and the stator. The cooling performance can be maximized.

Eleventh, the plurality of first fastening portions protrude downward in the axial direction from the first bearing housing. A plurality of second fastening portions protrude upward in the axial direction from the second vane hub. The first fastening portion and the second fastening portion are disposed to overlap in a radial direction with the first vane hub interposed therebetween. The first bearing housing and the first vane hub are arranged along the axial direction by fastening a fastening member such as a screw through the first fastening part of the first bearing housing, the first vane hub, and the second fastening part of the second bearing housing. and the second vane hub can be securely fastened to each other, and the fastening structure is simple, and the compact fastening structure can greatly contribute to miniaturization and weight reduction of the motor.

1 is a perspective view showing the exterior of a fan motor according to the present invention.
FIG. 2 is an exploded view of the fan motor in FIG. 1 .
3 is a cross-sectional view taken along III-III in FIG. 1 .
FIG. 4 is a conceptual diagram illustrating a state in which the first bearing housing, the first vane hub, and the second vane hub are fastened to each other in FIG. 3 .
5 is a perspective view illustrating a state in which the first O-ring holder is mounted to surround the outer surface of the air bearing in FIG. 3 .
FIG. 6 is an enlarged cross-sectional view illustrating a state in which the air bearing is mounted inside the O-ring holder by enlarging VI in FIG. 3 .

Hereinafter, the embodiments disclosed in the present specification will be described in detail with reference to the accompanying drawings, but the same or similar components are assigned the same reference numerals regardless of reference numerals, and overlapping descriptions thereof will be omitted. The suffixes "module" and "part" for the components used in the following description are given or mixed in consideration of only the ease of writing the specification, and do not have a meaning or role distinct from each other by themselves. In addition, in describing the embodiments disclosed in the present specification, if it is determined that detailed descriptions of related known technologies may obscure the gist of the embodiments disclosed in the present specification, the detailed description thereof will be omitted. In addition, the accompanying drawings are only for easy understanding of the embodiments disclosed in the present specification, and the technical spirit disclosed herein is not limited by the accompanying drawings, and all changes included in the spirit and scope of the present invention , should be understood to include equivalents or substitutes.

Terms including an ordinal number, such as first, second, etc., may be used to describe various elements, but the elements are not limited by the terms. The above terms are used only for the purpose of distinguishing one component from another.

When a component is referred to as being “connected” or “connected” to another component, it is understood that the other component may be directly connected or connected to the other component, but other components may exist in between. it should be On the other hand, when it is mentioned that a certain element is "directly connected" or "directly connected" to another element, it should be understood that the other element does not exist in the middle.

The singular expression includes the plural expression unless the context clearly dictates otherwise.

In the present application, terms such as "comprises" or "have" are intended to designate that a feature, number, step, operation, component, part, or combination thereof described in the specification exists, but one or more other features It should be understood that this does not preclude the existence or addition of numbers, steps, operations, components, parts, or combinations thereof.

1 is a perspective view showing the exterior of a fan motor according to the present invention.

FIG. 2 is an exploded view of the fan motor in FIG. 1 .

3 is a cross-sectional view taken along III-III in FIG. 1 .

4 is a conceptual diagram illustrating a state in which the first bearing housing 150, the first vane hub 160, and the second vane hub 163 are fastened to each other in FIG. 3 .

5 is a perspective view illustrating a state in which the first O-ring holder 181 is mounted to surround the outer surface of the air bearing 180 in FIG. 3 .

FIG. 6 is an enlarged cross-sectional view illustrating a state in which the air bearing 180 is mounted inside the O-ring holder by enlarging VI in FIG. 3 .

The fan motor according to the present invention includes a shroud 100, a rotating shaft 110, an impeller 120, a first bearing housing 150, a first vane hub 160, a second vane hub 163, and a second bearing. It is configured to include a housing 170 , a stator 130 , a rotor 140 , an air bearing 180 , and a ball bearing 190 .

The shroud 100 forms the exterior of the fan motor. The shroud 100 has a circular cross-sectional shape.

The shroud 100 has an accommodation space therein.

The shroud 100 may be divided into an inlet 101 , a first accommodating part 102 , a second accommodating part 104 , and an outlet 106 along the longitudinal direction (up and down or axial direction).

The suction port 101 and the first accommodating part 102 may be formed in a cone shape. The second accommodating part 104 may be formed in a cylindrical shape.

A suction port 101 is formed at the upper end of the shroud 100 . External air may be sucked into the shroud 100 through the inlet 101 .

A bottle neck portion having a narrow cross-sectional area may be formed on the downstream side of the inlet 101 based on the flow direction of the air. The flow rate of air at the bottleneck can be increased to increase the suction speed.

Based on the flow direction of the air, the first accommodating part 102 is disposed on the downstream side of the suction port 101 .

Based on the air flow direction, the second accommodating part 104 is disposed on the downstream side of the first accommodating part 102 .

The impeller 120 and the first bearing housing 150 may be accommodated in the first accommodating part 102 .

The cross-sectional area of the first accommodating part 102 may be formed to gradually increase from the bottleneck to the second accommodating part 104 . An outer circumferential surface of the first accommodating part 102 may be inclined toward the second accommodating part 104 from the bottleneck.

The second accommodating part 104 may be disposed downstream of the first accommodating part 102 .

The second accommodating part 104 may be formed in a cylindrical shape having a diameter larger than that of the suction port 101 .

The first vane hub 160 and the second vane hub 121 may be accommodated in the second accommodating part 104 .

The stator 130 may be accommodated inside the second vane hub 163 .

The second bearing housing 170 may be accommodated inside the second vane hub 163 .

A discharge port 106 is formed at the lower end of the second receiving part 104 . The discharge port 106 is configured to discharge the air inside the second accommodating part 104 to the outside.

The rotation shaft 110 is disposed along the center line of the shroud 100 that crosses the center of the shroud 100 in the axial direction.

The impeller 120 is configured to suck in outside air.

The impeller 120 includes a hub 121 and a plurality of blades 122 .

The hub 121 is located at the center of the impeller 120 . The hub 121 may be formed in a cone shape having a larger diameter from the top to the bottom.

The plurality of blades 122 may be formed to protrude spirally from the outer circumferential surface of the hub 121 . The plurality of blades 122 may be disposed to be spaced apart from each other in the circumferential direction of the hub 121 .

The plurality of blades 122 may be formed to be more spaced apart from each other from the top to the bottom of the hub 121 .

The plurality of blades 122 may be spaced apart from the first accommodating part 102 at a distance.

A suction flow path may be formed between the first accommodating part 102 and the hub 121 .

An impeller coupling part 111 may be formed at one end of the rotation shaft 110 . The impeller 120 is coupled to one end of the rotation shaft 110 , and may rotate together with the rotation shaft 110 .

As the impeller 120 rotates, external air may be introduced along the suction path of the shroud 100 through the suction port 101 .

The rotation shaft 110 may include a first support part 112 , a permanent magnet mounting part 113 , and a second support part 114 having different diameters in the axial direction from the top to the bottom.

The diameter of the first support part 112 is the largest. The first support part 112 is positioned adjacent to the impeller coupling part 111 .

A first bearing is coupled to the first support 112 . The first bearing may be implemented as an air bearing 180 .

The first bearing is configured to rotatably support the first support part 112 of the rotation shaft 110 .

The permanent magnet mounting part 113 is positioned between the first support part 112 and the second support part 114 .

The permanent magnet mounting part 113 may have a smaller diameter than the first support part 112 .

The permanent magnet 141 of the rotor 140 is mounted on the permanent magnet mounting part 113 so as to surround the outer peripheral surface of the permanent magnet mounting part 113 .

The diameter of the second support part 114 is smaller than the diameter of the permanent magnet mounting part 113 .

A second bearing is coupled to the second support 114 . The second bearing may be implemented as a ball bearing 190 .

The second bearing is configured to rotatably support the second support part 114 of the rotation shaft 110 .

The first support part 112 and the second support part 114 may be respectively disposed above and below the rotation shaft 110 with the permanent magnet mounting part 113 interposed therebetween. The second support part 114 may be located opposite to the impeller coupling part 111 in the axial direction.

The first bearing housing 150 is disposed to be spaced apart from each other at a predetermined distance on the downstream side of the impeller 120 .

The first bearing housing 150 may be formed in a form in which a conical shape and a cylindrical shape are combined.

An upstream side of the first bearing housing 150 may be formed in a conical shape, and a downstream side of the first bearing housing 150 may be formed in a cylindrical shape.

The first bearing accommodating part 151 is formed to be recessed in the center of the first bearing housing 150 .

The first bearing receiving part 151 may be formed to open toward the impeller 120 .

The first bearing receiving portion 151 may be formed to penetrate in the axial direction.

The first bearing accommodating part 151 may have a larger diameter than the diameters of the first support part 112 and the first bearing.

The first bearing receiving part 151 may be formed in a cylindrical shape. The first bearing may be accommodated in the first bearing accommodating part 151 .

The first axial movement limiting portion 152 may extend radially inward from the lower end of the first bearing receiving portion 151 .

A through hole may be formed inside the first axial movement limiter 152 . A diameter of the through hole may be larger than a diameter of the first support part 112 and smaller than a diameter of the first bearing.

According to this configuration, the first axial movement limiting unit 152 may restrict movement in the axial direction toward the rotor 140 while the first bearing is accommodated in the first bearing receiving unit 151 .

A first snap ring receiving groove 153 may be formed radially outward from the upper end of the first bearing receiving portion 151 .

The first snap ring receiving groove 153 is mounted so that a snap ring (not shown) is accommodated therein. The snap ring may be formed in a “C” shape. The snap ring is formed in a ring shape with one side open, and is elastically deformable so that the open area inside the snap ring is expanded or reduced in the radial direction.

The snap ring may prevent the first bearing from being separated from the first bearing receiving portion 151 toward the impeller 120 in the axial direction in a state accommodated in the first snap ring receiving groove 153 .

The impeller 120 is disposed to overlap the first bearing housing 150 in the axial direction so as to cover the first bearing receiving part 151 .

The first bearing housing 150 may be formed in a conical shape such that the diameter gradually increases from the upstream side to the downstream side based on the air flow direction.

The ratio of the diameter increasing from the top of the first bearing housing 150 to the bottom in the axial direction is greater than the ratio of the diameter increasing from the top to the bottom of the hub 121 .

The inclination of the outer surface of the hub 121 is steeper than the inclination of the outer surface of the first bearing housing 150 .

The upper end of the first bearing housing 150 has a slightly larger diameter than the lower end of the hub 121 , but is formed at a rate similar to the diameter increase rate of the first bearing housing 150 .

According to this configuration, it is possible to minimize the flow resistance of the air.

An expansion passage 103 may be formed between the first accommodating part 102 and the first bearing housing 150 . The expansion passage 103 is a passage for transferring air sucked from the suction passage to a first vane 161 to be described later. The expansion passage 103 may be formed so that the diameter of the passage extends from the impeller 120 to the first vane 161 .

The first vane hub 160 is configured to surround a portion of the outer surface of the first bearing housing 150 .

An upper portion of the first vane hub 160 may surround the first bearing housing 150 , and a lower portion of the first vane hub 160 may be formed in a cylindrical shape having a constant diameter in the axial direction.

A connection ring 135 may be mounted on a lower inner circumferential surface of the first vane hub 160 . The lower portion of the first vane hub 160 is formed to surround the circular connection ring 135 . The connection ring 135 is configured to connect the ends (neutral wire) of the three-phase stator coil 134 .

A wrapping groove may be concavely formed on the outer surface of the first bearing housing 150 to have the same depth as the thickness of the first vane hub 160 . According to this, the first vane hub 160 is inserted and coupled to the wrapping groove, so that a step difference between the first bearing housing 150 and the first vane hub 160 does not occur.

The first vane hub 160 and the first bearing housing 150 may be coupled to each other by a wrapping groove.

A plurality of first vanes 161 may be formed to protrude along the spiral direction on the outer circumferential surface of the first vane hub 160 .

The plurality of first vanes 161 are disposed to be spaced apart from each other in the circumferential direction of the first vane hub 160 .

The first vane hub 160 and the first vane 161 may be integrally formed of an insulating plastic material. The first vane 161 is configured to guide the air introduced through the expansion passage 103 to the second vane 164 .

The plurality of first vanes 161 may be coupled to the inside of the second accommodating part 104 of the shroud 100 by an interference fit.

The second vane hub 163 is disposed downstream of the first vane hub 160 .

The second vane hub 163 may be formed in a cylindrical shape.

The second vane hub 163 is configured to surround the stator 130 .

The stator 130 may be mounted to be accommodated inside the second vane hub 163 .

The stator 130 may be adhered to the upper inner peripheral surface of the second vane hub 163 by an adhesive means such as an adhesive.

The stator 130 includes a stator core 131 and a stator coil 134 .

The stator core 131 may include a back yoke 132 and a plurality of teeth 133 .

The back yoke 132 may be formed in a ring shape. Each of the plurality of teeth 133 is formed to protrude from the inner surface of the back yoke 132 toward the center of the back yoke 132 .

The plurality of teeth 133 may be formed detachably from the back yoke 132 . In this embodiment, the plurality of teeth 133 may be formed of three.

A coupling protrusion may be formed to protrude from one end of each of the plurality of teeth 133 .

The coupling protrusion may be slidably coupled in the axial direction along the coupling groove formed inside the back yoke 132 .

A pole shoe may be formed to protrude in the circumferential direction at the other end of each of the plurality of teeth 133 . The plurality of teeth 133 are disposed to be spaced apart from each other in the circumferential direction of the back yoke 132 .

The stator coil 134 may be configured as a three-phase coil. The plurality of stator coils 134 may be wound on the teeth 133 for each phase in the form of a central winding, respectively.

According to this configuration, it is possible to not only improve the output of the motor, but also contribute to the miniaturization and weight reduction of the motor.

An insulator 137 that insulates between the stator core 131 and the stator coil 134 may be interposed between the stator core 131 and the stator coil 134 . The insulator 137 may include a tooth insulator 137 formed to surround a portion of the teeth 133 and a back yoke insulator 137 formed to surround a portion of the back yoke 132 . The insulator 137 is formed of an insulating material such as plastic.

The rotor 140 includes a permanent magnet 141 .

The permanent magnet 141 may be mounted on the outer peripheral surface of the permanent magnet mounting part 113 .

The permanent magnet mounting part 113 extends in the axial direction from the first support part 112 . The permanent magnet mounting part 113 may have a smaller diameter than the first support part 112 .

The permanent magnet 141 may have a diameter smaller than the inner diameter of the stator core 131 .

The inner diameter of the stator core 131 means the diameter of the circumference passing through the inner ends of the plurality of pole shoes in the circumferential direction.

The permanent magnet 141 and the first support part 112 may have the same diameter as each other.

The permanent magnet 141 may be rotatably mounted to the permanent magnet mounting part 113 of the rotating shaft 110 with an air gap inwardly radially from the pole shoe of the stator core 131 .

In order to limit the axial movement of the permanent magnet 141 , an end cap 142 may be installed on the downstream side of the permanent magnet mounting part 113 . The end cap 142 may be formed in a cylindrical shape having the same diameter as the permanent magnet 141 .

One side of the permanent magnet 141 is in contact with the first support portion 112 having a larger diameter than the permanent magnet mounting portion 113 , so that the upstream movement in the axial direction may be restricted.

On the other side of the permanent magnet 141 , the downstream movement in the axial direction may be restricted by the end cap 142 .

When the three-phase alternating current is applied to each of the plurality of stator coils 134 , the permanent magnet 141 may generate a rotational force by electromagnetic interaction with a magnetic field generated around the stator coil 134 .

According to this configuration, the rotating shaft 110 may rotate by electromagnetic interaction between the rotor 140 and the stator 130 .

A plurality of second vanes 164 may be formed to protrude along the spiral direction on the outer circumferential surface of the second vane hub 163 .

The plurality of second vanes 164 are disposed to be spaced apart from each other in the circumferential direction of the second vane hub 163 .

The plurality of second vanes 164 are configured to guide the air passing through the first vanes 161 to the outlet 106 .

The plurality of first vanes 161 and the plurality of second vanes 164 are disposed to be spaced apart on a straight line in the axial direction.

A cooling passage 105 may be formed between the second accommodating part 104 and the first vane hub 160 .

A cooling passage 105 may be formed between the second accommodating part 104 and the second vane hub 163 .

The cooling flow path 105 is formed in a straight line along the axial direction, so that flow path resistance can be minimized.

The cooling passage 105 is configured to cool the motor using air moving from the expansion passage.

The plurality of second vanes 164 are arranged to be accommodated in the cooling passage 105 .

The plurality of second vanes 164 may be integrally formed with the second vane hub 163 . The plurality of second vanes 164 may be formed of a metal material of the same material as that of the second vane hub 163 . The second vane hub 163 and the second vane 164 may be formed of aluminum or an aluminum alloy material having excellent thermal conductivity.

The plurality of second vanes 164 serve not only to guide air, but also to radiate heat from the motor transmitted through the second vane hub 163 to the cooling passage 105 .

The second vane hub 163 may discharge heat transferred from the stator 130 to the cooling passage 105 through heat conduction.

For example, when a current is applied to the stator coil 134 , heat is generated in the stator coil 134 . The heat generated in the stator coil 134 is thermally conducted through the teeth 133 and the back yoke 132 of the stator core 131 to be transferred to the second vane hub 163 .

The plurality of second vanes 164 are configured to expand a heat exchange area with air.

Looking at the movement path of the air, the air is sucked into the shroud 100 through the suction port 101, and the discharge port 106 while moving along the cooling flow path 105 through the suction flow path and the expansion flow path 103. discharged to the outside through

Air flowing along the cooling passage 105 may exchange heat with the plurality of second vanes 164 and the second vane hub 163 to cool the heat of the stator 130 .

The plurality of second vanes 164 are coupled to the inner surface of the second accommodating part 104 of the shroud 100 by interference fit.

The second bearing housing 170 is disposed under the second vane hub 163 .

The second bearing housing 170 includes a second bearing accommodating portion 171 in the inner central portion.

The second bearing receiving part 171 may be formed in a ring shape.

The second bearing is accommodated in the second bearing accommodating part 171 .

The second bearing may be implemented as a ball bearing 190 .

A second axial movement limiting portion 173 may extend radially inwardly to the upper end of the second bearing receiving portion 171 .

A through hole may be formed inside the second axial movement limiter 173 . The diameter of the through hole may be formed to be larger than the diameters of the second support part 114 and the permanent magnet mounting part 113 .

The second axial movement limiter 173 may have an inner diameter smaller than the outer diameter of the second bearing and protrude inward in the radial direction. According to this, the second bearing may limit movement in the axial direction toward the permanent magnet mounting part 113 in a state accommodated in the second bearing receiving part 171 .

The second bearing receiving part 171 may be formed to open downward.

A second snap ring receiving groove 174 may be concave radially outwardly at the lower end of the second bearing receiving portion 171 .

The snap ring may be mounted to be accommodated in the second snap ring receiving groove 174 .

The snap ring may prevent the second bearing from being separated outwardly from the second bearing receiving part 171 while being accommodated in the second snap ring receiving groove 174 .

The second bearing housing 170 may include a plurality of bridges 172 .

The plurality of bridges 172 may be formed to protrude upward from the upper side of the second bearing receiving part 171 toward the inner circumferential surface of the second vane hub 163 .

The upper end of each of the plurality of bridges 172 is in contact with the lower inner peripheral surface of the second vane hub 163 and may be bonded by bonding means such as an adhesive.

A plurality of bus bars 136 may be installed at a lower end of each of the plurality of bridges 172 .

The plurality of bus bars 136 are respectively connected to the three-phase stator coil 134 to apply a three-phase alternating current.

A fastening structure of the first vane hub 160 , the first bearing housing 150 , and the second vane hub 163 will be described with reference to FIG. 4 .

The first vane hub 160 , the first bearing housing 150 , and the second vane hub 163 may be coupled to each other.

A plurality of first fastening holes 162 may be formed in the first vane hub 160 .

A plurality of first fastening portions 154 may be formed to protrude downwardly at the lower end of the first bearing housing 150 . The plurality of first fastening parts 154 may be disposed to be spaced apart from each other in the circumferential direction of the first bearing housing 150 .

A plurality of second fastening holes 155 may be formed to penetrate through the plurality of first fastening parts 154 in the thickness direction.

A plurality of second fastening portions 165 may be formed to protrude upwardly on the upper end of the second vane hub 163 . The plurality of second fastening parts 165 may be disposed to be spaced apart from each other in the circumferential direction of the second vane hub 163 .

A plurality of third fastening holes 166 may be formed in the plurality of second fastening parts 165 to penetrate in the thickness direction, respectively.

The plurality of first fastening parts 154 and the plurality of second fastening parts 165 are formed in the thickness direction of the first fastening part 154 (direction perpendicular to the radial direction or the axial direction of the first vane hub 160 ). may be overlapped.

The second fastening part 165 may be disposed to overlap the inner circumferential surface of the first vane hub 160 in the thickness direction.

The first fastening part 154 may be disposed to overlap the inner side of the second fastening part 165 .

The plurality of first fastening holes 162 , the plurality of second fastening holes 155 , and the plurality of third fastening holes 166 may be disposed to overlap in a thickness direction or a radial direction of the first vane hub 160 . .

A fastening member such as a screw is coupled through the first fastening hole 162, the second fastening hole 155, and the third fastening hole 166, so that the first vane hub 160 and the second vane hub 163 are coupled. and the first bearing housing 150 may be fastened to each other.

A connection ring mounting groove may be concavely formed in the thickness direction on the upper side of the outer peripheral surface of the first fastening part 154 . The connection ring 135 may be inserted and coupled to the connection ring mounting groove. The connection ring 135 may be disposed between the first vane hub 160 and the first fastening part 154 of the first bearing housing 150 .

A fastening groove may be concavely formed in the thickness direction on the lower side of the outer circumferential surface of the first fastening part 154 . The second fastening part 165 may be inserted into the fastening groove.

The thickness of the upper side of the first fastening part 154 may be the same as the sum of the thicknesses of the second fastening part 165 and the lower thickness of the first fastening part 154 , respectively.

The second fastening portion 165 may be formed to be thinner than the thickness of the second vane hub 163 .

The first vane hub 160 may be formed to surround the second fastening part 165 .

When mounted to surround the second fastening portion 165 of the first vane hub 160 , the first vane hub 160 and the second vane hub 163 may be disposed to overlap in the axial direction without a step difference.

According to this configuration, the first fastening part 154 of the first bearing housing 150 , the first vane hub 160 , and the second fastening part 165 of the second vane hub 163 are radially from the inside to the outside. The first bearing housing ( 150), the first vane hub 160 and the second vane hub 163 are firmly fastened to each other and have a simple fastening structure, and are compactly arranged to contribute to miniaturization and weight reduction.

A plurality of confirmation windows 107 may be formed on one side of the shroud 100 in the thickness direction.

The confirmation window 107 may be disposed in the radial direction of the first fastening hole 162 , the second fastening hole 155 , the third fastening hole 166 and the shroud 100 .

The first fastening hole 162 to the third fastening hole 166 may be exposed through the confirmation window 107 .

The fastening members fastened to the first fastening hole 162 to the third fastening hole 166 may be exposed through the confirmation window 107 .

When the rotation shaft 110 is not aligned with the center of the shroud 100 in the axial direction, the rotation shaft 110 may be aligned through the confirmation window 107 .

For example, when one side of the rotating shaft 110 is misaligned, a tool such as a screwdriver passes through the confirmation window 107 to press or rotate one side of the first vane hub 160 to align in the axial direction.

5 and 6 , the first bearing supporting the first support part 112 may be implemented as an air bearing 180 .

The air bearing 180 may be formed in a hollow hollow cylindrical shape. A shaft receiving portion is formed inside the air bearing 180 .

The air bearing 180 is configured to form an air gap between the outer circumferential surface of the first support 112 and the inner circumferential surface of the air bearing 180 .

The air gap may be 0.04 mm or less.

In order to secure assembly of the rotating shaft 110 and the rotor 140 , the inner diameter of the air bearing 180 may be smaller than the inner diameter of the stator core 131 .

In the air bearing 180 , the inner diameter d of the air bearing 180 may be formed to be larger than the length (height) of the air bearing 180 in order to reduce wear of the inner diameter surface of the air bearing 180 .

The inner diameter of the stator core 131 means the diameter of a circle passing through the inner ends of the plurality of teeth 133 in the circumferential direction.

The ratio of the length L of the air bearing 180 to the inner diameter d of the air bearing 180 may be 0.7 or less. When the length/inner diameter ratio of the air bearing 180 exceeds 0.7, the wear amount of the inner diameter surface of the air bearing 180 may be greatly increased.

Since the air bearing 180 rotatably supports the rotation shaft 110 in a non-lubricated state, a material having a low coefficient of friction and excellent wear resistance is used.

For example, the air bearing 180 may be formed of a polyetheretherketone (PEEK) or polyaryletherketone (PAEK) material having excellent non-lubricating friction characteristics and wear resistance.

PEEK or PAEK has a low bearing wear after operation and a small change in clearance with the shaft.

The air bearing 180 may form an air film between the rotation shaft 110 and the inner circumferential surface of the air bearing 180 without a separate working fluid such as lubricating oil to rotatably support the rotation shaft 110 in a non-contact manner.

The first O-ring holder 181 may be mounted on the outer circumferential surface of the first bearing so as to surround the outer circumferential surface of the first bearing.

The first O-ring holder 181 may be formed in a cylindrical shape.

The first O-ring holder 181 may have a diameter equal to or similar to an outer diameter of the first bearing.

The first bearing may be press-fitted to the inner circumferential surface of the first O-ring holder 181 to be coupled thereto.

The first O-ring holder 181 may be accommodated in the first bearing receiving part 151 .

A first O-ring mounting groove 182 may be concave in a radial direction along a circumferential direction on an outer circumferential surface of the first O-ring holder 181 .

The O-ring may be mounted in the first O-ring mounting groove 182 to be accommodated.

The plurality of first O-rings 183 are made of an elastic material such as rubber.

A plurality of first O-ring mounting grooves 182 may be formed on the outer circumferential surface of the first O-ring holder 181 . In this embodiment, it shows a state in which two first O-ring mounting grooves 182 are formed.

The plurality of first O-ring mounting grooves 182 may be disposed to be spaced apart from each other in the axial direction of the first O-ring holder 181 .

The plurality of first O-rings 183 are in close contact with the first bearing receiving part 151 .

According to this configuration, the plurality of first O-rings 183 may align the concentricity of the first bearing. The plurality of first O-rings 183 may prevent the first O-ring holder 181 from rotating in the first bearing receiving part 151 .

The plurality of first O-rings 183 may damp vibration and shock transmitted from the outside to the first bearing.

The second bearing supporting the second support part 114 may be implemented as a ball bearing 190 .

A second O-ring holder 191 may be mounted on an outer circumferential surface of the ball bearing 190 to surround the ball bearing 190 .

A plurality of second O-ring mounting grooves 192 may be formed on an outer circumferential surface of the second O-ring holder 191 . In this embodiment, the second O-ring mounting groove 192 shows a state formed in two.

A plurality of second O-rings 193 may be respectively mounted in the plurality of second O-ring mounting grooves 192 .

The plurality of second O-rings 193 may align concentricity of the second bearing. The plurality of second O-rings 193 may prevent the second O-ring holder 191 from rotating with respect to the second bearing receiving part 171 .

The plurality of second O-rings 193 are made of an elastic material such as rubber.

The plurality of second O-rings 193 may attenuate vibration and shock transmitted from the outside to the second bearing.

The ball bearing 190 may include an outer ring, an inner ring, and a plurality of balls.

The outer ring is fixedly installed on the inner circumferential surface of the second O-ring holder 191 . The inner ring is coupled to the outer circumferential surface of the second support part 114 . A plurality of balls are interposed between the outer ring and the inner ring to support the relative rotational motion of the inner ring with respect to the outer ring.

Therefore, according to the present invention, the air bearing 180 is applied as the first bearing supporting the first support part 112 of the rotation shaft 110 positioned adjacent to the impeller 120 .

Since the air bearing 180 is lubricated with air without a separate working fluid, friction between the air bearing 180 and the rotating shaft 110 does not occur.

For this reason, even when the rotating shaft 110 rotates at a high speed of 100,000 rpm or more, wear due to friction between the air bearing 180 and the rotating shaft 110 does not occur, thereby extending the life of the bearing. In addition, by applying the air bearing 180, it is possible to extend the life of the fan motor during high-speed rotation.

In addition, the air bearing 180 has the advantage of extending the life even if the diameter is increased.

Accordingly, by increasing the diameter of the air bearing 180 , the shaft diameter of the first support part 112 may be increased.

In addition, by increasing (thickening) the diameter (thickness) of the first support part 112 of the rotating shaft 110 adjacent to the impeller 120, the rotation shaft 110 due to the unilateral load of the impeller 120 during high-speed rotation. warpage can be prevented. Also, by increasing the thickness of the first support part 112 , the allowable speed limit of the rotation shaft 110 may be increased.

For example, the diameter of the first support part 112 may be larger than the diameter of the impeller coupling part 111 of the rotation shaft 110 to which the impeller 120 is coupled.

In addition, the diameter of the first support part 112 may be formed to be larger than the diameter of the permanent magnet mounting part 113 of the rotation shaft 110 on which the permanent magnet 141 is mounted.

Also, the diameter of the first support part 112 may be larger than the diameter of the second support part 114 supported by the second bearing.

The rotating shaft 110 passes through the rotor receiving hole formed inside the stator core 131 after the stator 130 is pre-assembled on the inside of the shroud 100 and the first receiving part 102 of the shroud 100 and It is assembled to be disposed on the same center line of the second accommodating portion 104 .

In order for the first support part 112 to pass through the rotor receiving hole to be coupled to the inner circumferential surface of the first bearing, the diameter of the first support part 112 is preferably smaller than the inner diameter of the stator core 131 .

In addition, the inner diameter of the first bearing is formed smaller than the inner diameter of the stator core 131 , so that assembly of the rotating shaft 110 and the like can be secured.

Moreover, the air bearing 180 is not disposed in the suction passage, the expansion passage 103, and the cooling passage 105, which are the main passages of the fan motor, and the impeller 120 accommodates the first bearing in which the air bearing 180 is accommodated. By being disposed to cover the part 151 , it is possible to block the inflow of foreign substances such as dust into the air bearing 180 .

In addition, a first O-ring mounting groove 182 is formed on the outer wall of the first O-ring holder 181 surrounding the air bearing 180 , and a plurality of first O-rings 183 are formed in the plurality of first O-ring mounting grooves 182 . ) is mounted, the rotation shaft 110 can be aligned along the axial direction on the center line of the shroud 100 .

In addition, the first O-ring 183 may be formed of an elastic material to attenuate an impact transmitted from the outside to the first bearing.

On the other hand, the ball bearing 190 may be applied as a second bearing supporting the second support part 114 of the rotation shaft 110 positioned opposite to the impeller 120 with respect to the permanent magnet mounting part 113 .

Since the second support part 114 of the rotating shaft 110 located opposite to the impeller 120 is less affected by the load on one side of the impeller 120 , the axial diameter of the second support part 114 is the first support part 112 . ) may be smaller than the shaft diameter.

For this reason, the ball bearing 190 may be applied to the second support part 114 . The ball bearing 190 is cheaper than the air bearing 180 . Therefore, it is advantageous in terms of cost to apply one air bearing 180 and one ball bearing 190 than to apply two air bearings 180 as bearings supporting both sides of the rotation shaft 110 .

In addition, when using two bearings with only the air bearing 180, a thrust bearing, which is an essential element, must be used. However, if one air bearing 180 and one ball bearing 190 are applied, the thrust bearing is not required. It can greatly contribute to the miniaturization and weight reduction of the fan motor.

In addition, the first vane hub 160 and the second vane hub 163 are arranged on the downstream side of the impeller 120 based on the flow direction of the air generated by the impeller 120 in a straight line with each other, The cooling flow path 105 formed between the wood 100 and the first and second vane hubs 163 has the same diameter and is formed in a straight line without bending, so that the flow resistance of air can be minimized, and the air motor can increase the cooling efficiency.

In addition, a plurality of second vanes 164 are formed to protrude into the cooling passage 105 on the outer peripheral surface of the second vane hub 163 , and the plurality of second vanes 164 not only guide the flow of air but also air By extending the heat exchange area of the and stator 130, it is possible to maximize the cooling performance of the motor.

Moreover, the plurality of first fastening portions 154 protrude downward in the axial direction from the first bearing housing 150 . A plurality of second fastening portions 165 protrude upward in the axial direction from the second vane hub 163 . The first fastening part 154 and the second fastening part 165 are disposed to overlap in a radial direction with the first vane hub 160 interposed therebetween. By fastening a fastening member such as a screw through the first fastening part 154 of the first bearing housing 150 , the first vane hub 160 and the second fastening part 165 of the second bearing housing 170 , , the first bearing housing 150, the first vane hub 160, and the second vane hub 163 disposed along the axial direction can be firmly fastened to each other, and the fastening structure is simple and compact. It can greatly contribute to the miniaturization and weight reduction of the motor.

100: shroud 101: intake
102: first accommodating part 103: expansion passage
104: second accommodating part 105: cooling flow path
106: outlet 107: confirmation window
110: rotation shaft 111: impeller coupling part
112: first support part 113: permanent magnet mounting part
114: second support 120: impeller
121: hub 122: blade
130: stator 131: stator core
132: back yoke 133: teeth
134: stator coil 135: connection ring
136: bus bar 137: insulator
140: rotor 141: permanent magnet
142: end cap 150: first bearing housing
151: first bearing receiving part 152: first axial movement limiting part
153: first snap ring receiving groove 154: first fastening part
155: second fastening hole 160: first vane hub
161: first vane 162: first fastening hole
163: second vane hub 164: second vane
165: second fastening part 166: third fastening hole
170: second bearing housing 171: second bearing receiving part
172: bridge 173: second axial movement limiting part
174: second snap ring receiving groove 180: air bearing
181: first O-ring holder 182: first O-ring mounting groove
183: first O-ring 190: ball bearing
191: second O-ring holder 192: second O-ring mounting groove
193: 2nd O-ring

Claims (20)

shroud;
a rotation shaft rotatably disposed on a straight line crossing the inner center of the shroud;
an impeller rotatably coupled to one end of the rotation shaft;
a rotor installed on the rotating shaft to be axially spaced apart from the impeller;
an air bearing lubricated with air with an air gap between the rotation shaft and the rotation shaft to rotatably support one side of the rotation shaft;
and a ball bearing coupled to the other end of the rotation shaft opposite to the air bearing with the rotor interposed therebetween and rotatably supporting the other side of the rotation shaft. According to claim 1,
The air bearing is a fan motor disposed between the impeller and the rotor toward a downstream side of the impeller based on a flow direction of the air generated by the impeller. According to claim 1,
The rotating shaft is
a first support part supported by the air bearing;
a second support part supported by the ball bearing; and
and a permanent magnet mounting part disposed between the first support part and the second support part and to which a permanent magnet is mounted. 4. The method of claim 3,
The fan motor in which the first support part has a larger diameter than the second support part. 4. The method of claim 3,
The first support portion is a fan motor having a larger diameter than the permanent magnet mounting portion. According to claim 1,
A stator comprising a stator core formed to surround the rotor with an air gap with the rotor and a stator coil wound around the stator core,
An inner diameter of the air bearing is smaller than an inner diameter of the stator core. According to claim 1,
An inner diameter of the air bearing is formed to be larger than a diameter of the rotor. According to claim 1,
a first O-ring holder mounted on an outer circumferential surface of the air bearing to surround the air bearing; and
and a plurality of first O-rings respectively mounted in the plurality of first O-ring mounting grooves formed in the first O-ring holder. According to claim 1,
a second O-ring holder mounted on an outer circumferential surface of the ball bearing to surround the ball bearing; and
and a plurality of second O-rings respectively mounted in a plurality of second O-ring mounting grooves formed in the second O-ring holder. According to claim 1,
A first bearing housing disposed on the downstream side of the impeller based on the flow direction of the air generated by the impeller and having a first bearing accommodating part for accommodating the air bearing,
The impeller includes a hub and a plurality of blades protruding from an outer circumferential surface of the hub,
The hub is a fan motor disposed to cover an upper portion of the air bearing that is opened toward the impeller. According to claim 1,
a first bearing housing disposed on a downstream side of the impeller based on a flow direction of the air generated by the impeller and having a first bearing accommodating part for accommodating the air bearing;
a first vane hub disposed on a downstream side of the first bearing housing based on the flow direction of the air to cover a part of the first bearing housing and having a plurality of first vanes for guiding the flow of the air; and
and a second vane hub disposed on a downstream side of the first vane hub with respect to the flow direction of the air and having a plurality of second vanes guiding the flow of the air. 12. The method of claim 11,
The first vane hub and the second vane hub are formed in a cylindrical shape having the same diameter, and are disposed in a straight line in the axial direction. 12. The method of claim 11,
A fan motor in which the plurality of first vanes and the plurality of second vanes are coupled to and supported by fitting to an inner circumferential surface of the shroud. 12. The method of claim 11,
A stator comprising a stator core formed to surround the rotor with an air gap with the rotor and a stator coil wound around the stator core,
The stator is coupled to surface contact with the inner peripheral surface of the second vane hub,
A fan motor configured to extend to a heat exchange area between the stator and the air with the second vane hub and the plurality of second vanes. 12. The method of claim 11,
The second vane hub and the plurality of second vanes are formed of a thermally conductive metal material. 12. The method of claim 11,
a first fastening portion formed to protrude downward in the axial direction from the first bearing housing; and
Further comprising a second fastening portion formed to protrude upward in the axial direction from the second vane hub,
The first fastening part and the second fastening part are disposed to overlap in a radial direction with the first vane hub therebetween,
The first bearing housing, the first vane hub, and the second vane hub are fastened by a fastening member penetrating the first fastening part, the first vane hub, and the second fastening part. 12. The method of claim 11,
A second bearing housing disposed on the downstream side of the rotor with respect to the flow direction of the air and having a second bearing accommodating part for accommodating the ball bearing,
The second bearing housing,
and a plurality of bridges protruding from the second bearing accommodating part toward an inner circumferential surface of the second vane hub and connecting the second bearing accommodating part and the second vane hub. shroud;
an impeller rotatably provided inside the shroud to suck air into the shroud;
a rotating shaft having one end coupled to the impeller and disposed to cross the center of the shroud in the axial direction;
a rotor disposed to be spaced apart from the impeller in the axial direction and having a permanent magnet mounted on the rotating shaft;
a stator provided inside the shroud to surround the rotor with a gap with the rotor;
a first vane disposed between the impeller and the stator to guide air sucked in by the impeller to flow toward the stator;
an air bearing disposed between the impeller and the rotor and lubricated with air with an air gap with one side of the rotation shaft to rotatably support one side of the rotation shaft; and
and a ball bearing disposed opposite the impeller with respect to the rotor and rotatably supporting the other side of the rotation shaft. 19. The method of claim 18,
a first O-ring holder mounted on an outer circumferential surface of the air bearing to surround the air bearing;
a plurality of first O-rings respectively mounted in a plurality of first O-ring mounting grooves formed in the first O-ring holder;
a second O-ring holder mounted on an outer circumferential surface of the ball bearing to surround the ball bearing; and
and a plurality of second O-rings respectively mounted in a plurality of second O-ring mounting grooves formed in the second O-ring holder. 19. The method of claim 18,
The air bearing is accommodated in a first bearing receiving portion disposed on the downstream side of the impeller in the flow direction of the air,
An upper side of the first bearing accommodating part opened toward the impeller is disposed to be covered by a hub of the impeller.

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