Fan motor

Abstract

A fan motor is disclosed. The fan motor comprises: a shroud; an impeller accommodated in the shroud; a motor connected to the impeller through a rotary shaft; and a motor housing accommodating the motor. The motor housing includes an outer wall portion, an inner wall portion, a cover portion covering the upstream end of the inner wall portion, and a vane disposed between the inner circumferential surface of the outer wall portion and the outer circumferential surface of the inner wall portion. A discharge flow path is formed between the inner wall portion and the outer circumferential surface of a stator. Air in the air pocket formed by the cover portion, the inner wall portion, and the upstream end of the motor is discharged to the discharge flow path by a fast flow rate of air having passed through the vane. Accordingly, air in the air pocket can be discharged to the outside without becoming stagnant.

Description

fan motor

[0001] The present invention relates to a fan motor, and more particularly, to a fan motor capable of improving the cooling performance of the motor.

[0002] The motor can be installed in home appliances such as vacuum cleaners or hair dryers.

[0003] Vacuum cleaners and hair dryers can use motors as a power source to generate rotational force.

[0004] For example, the motor can be connected to a fan. The fan receives power from the motor and rotates at high speed to generate airflow.

[0005] Handy stick vacuum cleaners and hair dryers are operated by the user lifting them with their hands.

[0006] To increase portability and convenience for users, it is necessary to make vacuum cleaners and hair dryers smaller and lighter.

[0007] To increase the work done by a fan, you can either increase the diameter of the fan or increase the rotation speed of the fan.

[0008] To increase the work of a motor, either the diameter of the motor or its axial length can be increased. This increases the motor's capacity.

[0009] Prior patent document KR 10-2023-0072178 A (hereinafter, patent document 1) discloses a fan motor assembly.

[0010] In the case of patent document 1, when the outer diameter of the flow path (diffuser) increases while the diameter of the motor (stator) is fixed, the flow path gap between the outer diameter of the motor and the inner diameter of the flow path increases.

[0011] However, in Patent Document 1, the flow of air discharged from the outlet of the euro section acts as an air curtain, so that the air inside the motor housing cannot be discharged through the euro gap, and a phenomenon occurs in which the flow of air stagnates.

[0012] Due to this, Patent Document 1 has a problem in that the cooling performance of the motor is reduced.

[0013] In addition, in Patent Document 1, the stator is accommodated in a direction close to the impeller inside the motor housing, so the space between the inner surface of the motor housing and the stator is narrow.

[0014] Due to this, there is a problem in that the air between the motor housing and the stator has insufficient volume to absorb the heat generated from the stator, which reduces the cooling performance of the motor.

[0015] In addition, since the area of ​​the stator core exposed to the outside of the motor housing is small, there is a problem of reduced heat dissipation performance.

[0016] Prior patent document KR 10-2021-0153940 A (hereinafter, Patent Document 2) discloses a motor assembly and a vacuum cleaner including the same.

[0017] In the case of Patent Document 2, the motor assembly includes a heat dissipation cover covering the outer surface of the motor. The heat dissipation cover includes an inner cover and an outer cover. The inner cover is spaced apart from the outer surface of the motor.

[0018] The inner cover forms an inner airflow path through the gap. The outer cover is positioned outside the inner cover. An outer airflow path is formed along the outer surface of the outer cover. This allows the inner cover to be positioned adjacent to the outer surface of the motor, allowing external air from the housing to flow into the interior of the housing along the outer surface of the motor through the gap, effectively cooling the motor.

[0019] However, Patent Document 2 has a problem in that a separate heat dissipation cover must be added to form the inner and outer cover passages, which increases the number of parts and the manufacturing cost.

[0020] The purpose of the present invention is to provide a fan motor having a structure capable of solving the above-described problems.

[0021] The first purpose is to provide a fan motor having a structure capable of eliminating stagnation of air flow inside the motor housing.

[0022] The second purpose is to provide a fan motor having a structure that can sufficiently secure cooling performance of the motor by securing a space that can absorb the heat generated from the motor.

[0023] The third purpose is to provide a fan motor having a structure capable of improving heat dissipation performance by increasing the area of ​​the stator core exposed to the outside of the motor housing.

[0024] The fourth purpose is to provide a fan motor having a structure that can effectively cool a motor by forming a reflux flow of air moving from the outside to the inside of a motor housing without adding additional parts, while also reducing the number of parts and manufacturing costs.

[0025] As a result of intensive research, the inventors of the present invention have found that the first to fourth objectives of the present invention can be achieved by the following embodiments of the present invention.

[0026] In order to achieve the first object described above, a fan motor according to the present invention includes a shroud; an impeller accommodated in the shroud and forming a flow of air; a rotating shaft to which the impeller is coupled; a motor housing coupled to a downstream side of the shroud; a rotor accommodated inside the motor housing and coupled to the rotating shaft, and a stator surrounding the rotor, the motor driving the impeller.

[0027] The above motor housing includes an outer wall portion; an inner wall portion arranged radially inside the outer wall portion; and a vane arranged between the inner surface of the outer wall portion and the outer surface of the inner wall portion to guide the flow of air.

[0028] A narrow exhaust path is formed between the inner wall portion and the outer surface of the stator. Air in the air pocket formed on the inner wall of the motor housing is discharged to the outside of the motor housing through the exhaust path due to the rapid flow of air passing through the vane.

[0029] Through this, the air in the air pocket absorbs the heat generated from the motor and is released to the outside of the motor housing without stagnation, thereby improving the cooling performance of the motor.

[0030] The above stator includes a stator core and a stator coil wound around the stator core.

[0031] The gap of the above exhaust passage can be defined as the gap between the inner surface of the inner wall portion and the outer surface of the stator core.

[0032] The spacing of the above exhaust passages may be greater than or equal to the thickness of the inner wall portion and less than or equal to the radial width of the vane. The radial width of the vane may be defined as the length of the vane extending radially from the inner peripheral surface of the outer wall portion to the outer peripheral surface of the inner wall portion.

[0033] Through this, the gap between the exhaust passages is formed to narrow the gap between the vanes and the stator, so that the flow of air passing through the vanes can strike the outer surface of the stator at a high speed.

[0034] The spacing of the above exhaust passages may be 3% to 11% of the outer circumferential diameter of the outer wall portion or the radial outer diameter of the vane.

[0035] If the distance between the discharge channels is smaller than the minimum value of the numerical range, the flow resistance is large, making it difficult for air to be discharged. If the distance between the discharge channels is larger than the maximum value of the numerical range, the flow velocity decreases, which causes a problem in that the suction power of the air pocket for air is reduced.

[0036] To achieve the second and third objectives described above, the height of the air pocket may be defined as the distance between the inner surface of the cover portion covering the upstream end of the inner wall portion and the upstream end of the motor. The height of the air pocket may correspond to the length between the inner surface of the cover portion and the downstream end of the vane.

[0037] Through this, the air pocket can secure a sufficient spatial volume to accommodate air capable of absorbing heat generated from the motor. In addition, by increasing the area of ​​the motor exposed to the outside of the motor housing, the heat dissipation performance of the motor can be improved.

[0038] The height of the above air pocket may be 22% to 42% of the radial outer diameter of the above vane.

[0039] If the height of the air pocket is less than the lowest value of the above numerical range, the volume of air that the air pocket can accommodate is reduced, which may result in a decrease in the cooling performance of the motor. If the height of the air pocket is greater than the highest value of the above numerical range, the size (axial length) of the fan motor increases, which is disadvantageous for miniaturization of the product.

[0040] The value obtained by subtracting the axial distance between the inner surface of the cover part and the upstream end of the stator from the axial distance between the inner surface of the cover part and the downstream end of the vane can be defined as the phase difference.

[0041] The range of the above phase difference may be from “-the protrusion height of the insulator boss” or more to “+the protrusion height of the insulator boss” or less.

[0042] The above insulator boss portion may be formed to protrude in the axial direction of the rotational axis from the insulator covering the upstream end of the stator core.

[0043] If the range of the phase difference is smaller than the “-protrusion height of the insulator boss,” it is disadvantageous for product miniaturization. If the range of the phase difference is larger than the “+protrusion height of the insulator boss,” the amount of air contained in the air pocket may decrease, which may reduce the cooling performance of the motor.

[0044] The downstream end of the above vane and the upstream end of the above stator can be arranged to overlap each other radially. This provides an optimal structure for air cooling the motor.

[0045] To achieve the fourth objective described above, the stator core includes a plurality of teeth protruding radially toward the center of the rotational axis from the inside of the stator core; and a plurality of slots formed between the plurality of teeth, in which the stator coil is wound.

[0046] Air outside the motor housing can pass through the slot on the downstream side of the motor and move to the air pocket to form a reflux flow.

[0047] This maximizes the heat dissipation performance of the motor by increasing the exposed surface area of ​​the motor that can come into contact with air without adding additional components. In addition, the heated air in the air pocket can be replaced by the cool air outside the motor housing by the reflux flow.

[0048] The axial distance between the inner surface of the cover portion and the downstream end of the outer wall portion may be equal to the axial distance between the inner surface of the cover portion and the downstream end of the inner wall portion. Through this, the straightness of the air flow passing through the vane can be improved.

[0049] The axial distance between the inner surface of the cover portion and the downstream end of the inner wall portion may be shorter than the axial distance between the inner surface of the cover portion and the downstream end of the outer wall portion.

[0050] The above vane includes a vane extension portion extending radially so as to cover the thickness surface of the inner wall portion at the downstream end of the vane.

[0051] Optionally, the vane may further include a vane protrusion formed to protrude from the vane extension into the exhaust passage.

[0052] Through this, some of the air passing through the vane can be introduced into the air pocket to cool the motor.

[0053] The above vane may be composed of a single-stage vane or N-stage vanes (N is a natural number greater than or equal to 2) formed to be separated from each other in the direction of the air flow.

[0054] This makes it easy to create veins.

[0055] The above motor housing is formed to protrude radially from the inner surface of the inner wall portion so as to surround the outer surface of the stator, and includes a plurality of support portions that extend axially from the downstream end of the inner wall portion to support the stator.

[0056] Through this, the plurality of supports can stably support the motor.

[0057] The plurality of support portions may be spaced apart in a circumferential direction along an outer surface of the stator, and the discharge path may be arranged between the plurality of support portions that are adjacent in the circumferential direction.

[0058] Through this, the exhaust path can improve the accessibility of air passing through the vane to the outer surface of the stator.

[0059] A motor mounting portion is concavely formed on the radially inner surface of the support portion, and the motor mounting portion can align the mounting position of the motor spaced axially from the inner surface of the cover portion.

[0060] Through this, the motor mounting portion can indicate the mounting start point of the motor, thereby facilitating mounting of the motor.

[0061] The motor housing may include a first inner wall portion having a first thickness and formed in a cylindrical shape. The motor housing may further include a second inner wall portion. The second inner wall portion may be connected to a downstream side of the first inner wall portion based on the air flow direction. The second inner wall portion may have a second thickness that is thicker than the first thickness and may be formed in a cylindrical shape.

[0062] The motor housing may further include a channel inner wall portion surrounding the outer surface of the first inner wall portion. The motor housing may further include a channel outer wall portion accommodated on the inner side of the downstream end of the shroud and spaced radially outside the channel inner wall portion.

[0063] The above motor housing may include an outer wall portion connected to the downstream end of the outer wall portion of the euro and spaced radially outside the second inner wall portion.

[0064] The motor housing may include a first vane that extends from the outer circumferential surface of the inner wall portion of the passage to the outer wall portion of the passage. The motor housing may include a second vane that is connected to the downstream end of the first vane and extends from the outer circumferential surface of the second inner wall portion to the outer wall portion to protrude.

[0065] Through this, the first vane and the second vane can be arranged in a structure that is separable from each other on the upstream side and the downstream side based on the direction of air flow. The manufacture of the vane is easy.

[0066] The above outer wall portion can be joined to the downstream end of the shroud. This facilitates the joining of the shroud and the motor housing.

[0067] The motor housing may include a first bearing that is positioned downstream of the impeller based on the direction of air flow and supports the upstream side of the rotation shaft; and a first bearing housing that is positioned in the center of the cover portion and accommodates the first bearing.

[0068] The motor housing may further include a second bearing that is positioned downstream of the motor based on the direction of air flow and supports the downstream side of the rotation shaft; and a second bearing housing that accommodates the second bearing.

[0069] Through this, stable support of the rotation axis is possible.

[0070] The motor housing may include a support portion that protrudes from the inner surface of the inner wall portion toward the rotation axis and supports the outer surface of the stator; a coupling portion that is coupled to a downstream end of the support portion; and a bridge that extends radially to be connected to the outer surface of the second bearing housing and the inner surface of the coupling portion.

[0071] Through this, the coupling part can connect the second bearing housing to the support part.

[0072] The above fan motor may further include a control unit that is disposed on the downstream side of the motor and has a PCB equipped with an IGBT and a capacitor to control the operation of the motor.

[0073] The lead wire electrically connected to the above stator can be connected to a power connection provided on the PCB. Through this, power can be supplied to the stator.

[0074] The above PCB can be arranged to face the air pocket in the axial direction.

[0075] The air discharged from the air pocket through the exhaust passage moves to the PCB, thereby cooling the IGBT and the capacitor.

[0076] Air between the downstream side of the motor and the PCB can pass through an internal passage formed inside the motor and move to the air pocket, forming a reflux flow. Through this, the cooling performance of the control unit and the motor can be improved.

[0077] According to an embodiment of the present invention, the following effects can be achieved.

[0078] First, a motor housing for accommodating a motor includes an outer wall portion, an inner wall portion disposed inside the outer wall portion, and a vane disposed between the outer wall portion and the inner wall portion to guide the flow of air formed by the impeller. An air pocket may be formed inside the motor housing. Air present in the air pocket may absorb heat generated by the motor. An exhaust passage is formed between the inner surface of the inner wall portion and the outer surface of a stator constituting the motor. As the diameter of the inner wall portion of the vane decreases with respect to the outer surface of the stator, the gap between the exhaust passages narrows. Accordingly, air passing through the vane strikes the outer surface of the stator through the exhaust passage. The air moving axially along the outer surface of the stator has a faster flow rate than the air in the air pocket. The fast flow rate of the air flowing along the outer surface of the stator can suck in the air in the air pocket and exhaust it to the outside of the motor housing. Through this, the air inside the air pocket can be discharged to the outside without becoming stagnant.

[0079] Second, if the air pocket space is insufficient, the space for air to absorb the heat generated by the motor is reduced, which may reduce the cooling performance of the motor. Ensuring the air pocket space is important for improving the cooling performance of the motor. There are two ways to increase the air pocket space. One way is to increase the radius of the air pocket. However, if the inner diameter of the inner wall is increased to increase the radius of the air pocket, the gap between the exhaust passages widens, which reduces the flow rate of the air flowing along the outer surface of the stator, making it difficult to exhaust the air in the air pocket to the outside through the exhaust passage. This limits the ability to increase the radius of the air pocket.

[0080] Another approach is to increase the height of the air pocket. This refers to the distance the upstream end of the motor is separated from the inner surface of the motor housing. This allows for a reduction in the exhaust path spacing while still maintaining the air pocket space.

[0081] The optimal motor cooling structure can be achieved when the upstream end of the motor, which is spaced axially from the inner surface of the motor housing, corresponds to the length of the discharge portion of the vane, which extends axially from the inner surface of the motor housing.

[0082] For example, the value obtained by subtracting the axial distance between the inner surface of the motor housing and the upstream end of the vane from the axial distance between the inner surface of the motor housing and the upstream end of the stator core may be defined as a 'phase difference'. When the phase difference is 0 mm, the motor cooling structure can be optimal. In order to improve the cooling performance of the motor, the phase difference is preferably within the range of 0 mm ± the protrusion height of the insulator boss. The insulator boss is a part of the insulator that protrudes axially from the upstream end of the stator core to isolate (electrically insulate) the end of the stator coil from the surroundings.

[0083] In addition, when the phase difference is 0 mm, the area of ​​the stator core exposed to the outside of the motor housing increases, thereby maximizing the effective cooling area of ​​the motor.

[0084] In addition, the outside air of the motor housing can directly cool the outer surface of the stator core by the air flow rate passing through the vane.

[0085] Third, the air passing through the vane increases the velocity of the surrounding air layer of the stator core, thereby sucking in the air in the air pocket, thereby forming a reflux flow in which the outside air of the motor housing is circulated back into the air pocket.

[0086] Through this, the reflux flow can alleviate the thermal dome phenomenon caused by stagnant air in the air pocket. Furthermore, the reflux flow can effectively cool the motor by replacing the heated air in the air pocket with cold air.

[0087] FIG. 1 is a perspective view showing the appearance of a fan motor according to one embodiment of the present invention.

[0088] Figure 2 is an exploded view of the fan motor in Figure 1.

[0089] Fig. 3 is a cross-sectional view illustrating the internal configuration of the fan motor in Fig. 1. Fig. 3(a) is a conceptual diagram showing the initial design of the fan motor, located on the left side of the vertical center line O-O' in Fig. 3. Fig. 3(b) is a conceptual diagram showing the configuration of the fan motor according to an embodiment of the present invention, located on the right side of the vertical center line O-O' in Fig. 3.

[0090] FIG. 4 is a cross-sectional view illustrating the internal configuration of the fan motor in FIG. 1. FIG. 4(a) is a conceptual diagram showing the initial design of the fan motor corresponding to FIG. 3(a). FIG. 4(b) is a conceptual diagram showing the configuration of the fan motor according to one embodiment of the present invention corresponding to FIG. 3(b).

[0091] FIG. 5 corresponds to FIG. 4(b) and is a cross-sectional view showing a fan motor according to an embodiment of the present invention.

[0092] Figure 6 is a conceptual diagram showing the upstream end of the stator core and the discharge surface of the vane positioned radially opposite to each other by enlarging the “VI” portion in Figure 5.

[0093] Figure 7 is a conceptual diagram showing the height at which the boss portion of the insulator protrudes in Figure 1.

[0094] Figure 8 is a conceptual diagram showing the radius and height of an air pocket, as viewed in the direction VIII from Figure 7.

[0095] Fig. 9 is a conceptual diagram showing the reflux flow inside the motor housing according to the embodiment of Fig. 5.

[0096] Figure 10 is a graph showing the temperature trend of the motor according to the settling length (phase difference) of the stator core.

[0097] Figure 11 is a conceptual diagram showing the arrangement relationship between the motor housing and the stator according to the phase difference in Figure 10. Figure 11(a) shows the arrangement relationship between the motor housing and the stator when the phase difference is greater than 0. Figure 11(b) shows the arrangement relationship between the motor housing and the stator when the phase difference is 0.

[0098] Figure 12 is a graph for comparing and explaining the saturation time and saturation temperature of an existing structure and a structure to which an air pocket according to the present invention is applied.

[0099] Hereinafter, a fan motor according to an embodiment of the present invention will be described in detail with reference to the attached drawings.

[0100] In the following description, descriptions of some components may be omitted to clarify the features of the present invention.

[0101] 1. Definition of Terms

[0102] Terms that include ordinal numbers, such as first, second, etc., may be used to describe various components, but the components are not limited by these terms. These terms are used solely to distinguish one component from another.

[0103] When a component is referred to as being "connected" or "connected" to another component, it should be understood that it may be directly connected or connected to that other component, but that there may be other components intervening. Conversely, when a component is referred to as being "directly connected" or "connected" to another component, it should be understood that there are no other components intervening.

[0104] As used herein, singular expressions include plural expressions unless the context clearly indicates otherwise.

[0105] The term “fan motor” used in the following description can be understood as a concept meaning a device that sucks in or blows air by rotating a fan using power such as an electric motor.

[0106] “Axial” as used in the following description means the longitudinal direction of the axis of rotation.

[0107] As used in the following description, “radial direction” means the longitudinal direction of a line segment from the center of a circle or cylinder to a point on the circumference (circumference).

[0108] As used in the following description, “circumferential” means the direction of the circumference of a circle.

[0109] 2. Description of the configuration of a fan motor according to one embodiment of the present invention

[0110] FIG. 1 is a perspective view showing the appearance of a fan motor according to one embodiment of the present invention.

[0111] Figure 2 is an exploded view of the fan motor in Figure 1.

[0112] FIG. 3 is a cross-sectional view illustrating the internal configuration of the fan motor in FIG. 1. FIG. 3(a) is a conceptual diagram showing the initial design of the fan motor, located on the left side of the vertical center line O-O' in FIG. 3. FIG. 3(b) is a conceptual diagram showing the configuration of the fan motor according to one embodiment of the present invention, located on the right side of the vertical center line O-O' in FIG. 3.

[0113] FIG. 4 is a cross-sectional view illustrating the internal configuration of the fan motor in FIG. 1. FIG. 4(a) is a conceptual diagram showing the initial design of the fan motor corresponding to FIG. 3(a). FIG. 4(b) is a conceptual diagram showing the configuration of the fan motor according to one embodiment of the present invention corresponding to FIG. 3(b).

[0114] FIG. 5 corresponds to FIG. 4(b) and is a cross-sectional view showing a fan motor according to an embodiment of the present invention.

[0115] The fan motor of the present invention can be applied to home appliances such as handy stick vacuum cleaners.

[0116] The fan motor can be largely composed of a casing, an impeller (113), and a motor (117).

[0117] The casing forms the exterior of the fan motor. The casing includes a shroud (100), a first housing, and a second housing. Here, the first housing may be referred to as a motor housing (109) in the sense that it houses a motor (117) therein. The casing may be formed of a plastic material.

[0118] The shroud (100) has a space to accommodate an impeller (113) therein. In addition, the space of the shroud (100) can accommodate a portion of a vane (135) to be described later, a portion of a motor housing (109), or a first bearing (107).

[0119] The passage for the air generated by the impeller (113) can be formed in the space between the shroud (100) and the impeller (113), and in the flow path section described later.

[0120] The shroud (100) may be formed in a cylindrical shape. However, the shroud (100) may be formed with a different diameter along the length of the cylinder.

[0121] Looking at the detailed configuration of the shroud (100), the shroud (100) can be configured to include an intake port (101), an inclined portion (102), and a straight portion (103). The detailed components of the shroud (100) described above can be divided in order from the upstream side to the downstream side of the shroud (100) based on the direction of air flow.

[0122] The suction port (101) is located at the upstream end of the shroud (100). The suction port (101) is formed in a cylindrical shape. The suction port (101) has a relatively small diameter and a short length compared to other detailed components of the shroud (100). The suction port (101) may be formed to penetrate in the axial direction. One end of the impeller (113) may be accommodated inside the suction port (101).

[0123] Through this, air is sucked in through the intake port (101) by the rotation of the impeller (113).

[0124] The inclined portion (102) is provided on the downstream side of the suction port (101). The inclined portion (102) is formed to be inclined with respect to the rotation axis (106) so that the diameter gradually increases from the upstream side to the downstream side of the shroud (100).

[0125] The inclined portion (102) may be formed in a cone shape along the circumference of the suction port (101). The inclined portion (102) may be formed in a curved shape. The inclined portion (102) may be formed with different curvatures as it moves from the suction port (101) toward the straight portion (103) described later. Some of the inclined portions (102) having different curvatures may have curvatures in opposite directions.

[0126] A reinforcing portion may be formed at the corner where the suction port (101) and the inclined portion (102) are connected. The reinforcing portion may extend in the circumferential direction. The reinforcing portion may prevent the thickness of the shroud (100) from decreasing at the connection between the suction port (101) and the inclined portion (102) and may reinforce the strength of the shroud (100) by adding thickness to the shroud (100).

[0127] The straight section (103) is formed in a cylindrical shape. The straight section (103) is configured to connect the downstream end of the inclined section (102) and the straight section (103) described later.

[0128] The shroud (100) is coupled to the motor housing (109). For example, a portion of the shroud (100) may be coupled by wrapping a portion of the motor housing (109).

[0129] Alternatively, a portion of the shroud (100) may be connected to a portion of the motor housing (109) described later and fastened by a fastening member such as a screw.

[0130] The shroud (100) may further include a first fastening portion (104).

[0131] The first fastening portion (104) may be provided at the downstream end of the shroud (100). The first fastening portion (104) is configured to be coupled to the second fastening portion (134) of the motor housing (109) to be described later.

[0132] The first fastening portion (104) can extend radially outward from the downstream side of the straight portion (103). The first fastening portion (104) extends circumferentially along the downstream perimeter of the straight portion (103). A plurality of first fastening holes are formed to penetrate the first fastening portion (104) in the axial direction. The plurality of first fastening holes are arranged spaced apart from each other along the circumferential direction.

[0133] A protrusion (105) may be formed to protrude axially from the outer end of the first fastening portion (104). The protrusion (105) may extend circumferentially along the outer periphery of the first fastening portion (104). The protrusion (105) is formed to surround the outer circumference of the second fastening portion (134) to be described later.

[0134] A rotation axis (106) is provided at the center of the casing. The rotation axis (106) is formed to extend along an axial direction passing through the center of the casing.

[0135] One end of the rotation shaft (106) is accommodated inside the shroud (100). An impeller (113) is rotatably mounted on one end of the rotation shaft (106).

[0136] The impeller (113) includes a hub (114) and a plurality of blades (116). The impeller (113) can be implemented in the form of a diagonal fan.

[0137] The hub (114) is formed in a cone shape with an inclined shape so that its diameter increases along the axial direction. The diameter of the hub (114) gradually increases from the upstream end to the downstream end of the hub (114) based on the direction of air movement.

[0138] An axial coupling groove (115) may be formed inside the center of the upstream side of the hub (114) so ​​that one end of the rotation shaft (106) is coupled to the center of the hub (114). The inner diameter of the axial coupling groove (115) is formed to correspond to the diameter of the rotation shaft (106), so that the axial coupling groove (115) and the rotation shaft (106) can be press-fit coupled.

[0139] Through this, the upstream end of the shaft coupling groove (115) can be formed with a diameter smaller than the diameter of the rotation shaft (106) so that the upstream end of the rotation shaft (106) is caught in the thrust direction.

[0140] A coupling hole may be formed at the upstream end of the hub (114) and the shaft coupling groove (115) so that the hub (114) and the rotation shaft (106) are coupled.

[0141] The blade (116) may be formed to protrude at a predetermined angle with respect to the radial direction from the outer surface of the hub (114). The blade (116) may extend in a spiral shape along the outer surface of the hub (114).

[0142] A plurality of blades (116) are provided. The plurality of blades (116) are arranged at predetermined intervals along the circumference of the hub (114).

[0143] According to this, the impeller (113) can rotate together with the rotation shaft (106). A plurality of blades (116) that rotate at high speed together with the hub (114) rotate the air in the internal space of the shroud (100), thereby sucking external air into the interior of the shroud (100) through the intake port (101).

[0144] The motor housing (109) is placed on the downstream side of the shroud (100). The motor housing (109) may be configured to include a first bearing housing (110), a cover portion (112), and a flow path portion.

[0145] The rotation shaft (106) can be rotatably supported by a first bearing (107) and a second bearing (108). The first bearing (107) can be placed on one side of the rotation shaft (106), for example, on the upstream side of the rotation shaft (106) based on the air flow direction.

[0146] The second bearing (108) may be placed on the other side of the rotation shaft (106), for example, on the downstream side of the rotation shaft (106) based on the air flow direction.

[0147] The first bearing (107) can be placed on the downstream side of the hub (114) adjacent to the impeller (113).

[0148] The bearings (107, 108) can be implemented as ball bearings or air bearings, etc.

[0149] A rotor (118) and a stator (119) constituting a motor (117) to be described later can be placed between the first bearing (107) and the second bearing (108).

[0150] A first bearing support portion may be formed on one side of the rotation shaft (106). A first bearing (107) may be press-fitted to the first bearing support portion.

[0151] A first bearing (107) is accommodated in a first bearing housing (110). The first bearing housing (110) may be formed in a cylindrical shape. The first bearing housing (110) may be formed to protrude toward the hub (114) from the inner surface of a cover portion (112) to be described later (see FIG. 3) or to protrude axially toward the motor (117) (see FIGS. 4(b) and 5). The first bearing housing (110) extends along the circumferential direction so as to surround the outer surface of the first bearing (107).

[0152] A first stopper (111) is formed to protrude radially inwardly at one axial end of the first bearing housing (110), for example, at the upstream end. The first stopper (111) can restrict movement of the first bearing (107) in the thrust direction while it is accommodated in the first bearing housing (110).

[0153] For example, when the impeller (113) rotates, air is sucked into the inside of the shroud (100) through the intake port (101), moves along the inner surface of the shroud (100), and flows into the flow path section to be described later.

[0154] At this time, when the air moves in the first axial direction from the intake port (101) of the shroud (100) toward the first fastening portion (104), thrust is generated in the second axial direction opposite to the first axial direction by the law of action-reaction. The thrust can act on the rotation shaft (106) and the impeller (113).

[0155] According to this, the first stopper (111) restricts the first bearing (107) coupled to the rotation shaft (106) from moving in the thrust direction due to the thrust.

[0156] The cover portion (112) may be formed in a circular shape. The cover portion (112) extends radially from the outer circumference of the first bearing housing (110) toward the upstream end of the inner wall portion (130) of the flow path portion, which will be described later. The cover portion (112) may extend circumferentially along the outer circumference of the first bearing housing (110).

[0157] The cover part (112) is configured to connect the first bearing housing (110) and the flow path part. The radially inner side of the cover part (112) is configured to surround the outer surface of the first bearing housing (110). The radially outer side of the cover part (112) is connected to one end of the inner wall part (130) of the flow path part.

[0158] Here, the radially inner side of the cover part (112) means one end of the cover part (112) that faces the rotation axis (106) in the radial direction. The radially outer side of the cover part (112) means the other end of the cover part (112) that faces the opposite direction to the rotation axis (106) in the radial direction.

[0159] The cover part (112) can form one side of the motor receiving part to be described later, for example, the inner side of the motor housing (109) that faces the rotor (118) and stator (119) of the motor (117) in the axial direction.

[0160] The motor housing (109) can form a flow path including an inner wall portion (130), an outer wall portion (133), and a vane (135).

[0161] The inner wall portion (130) is formed in a cylindrical shape having a first diameter. One axial end of the inner wall portion (130) is connected to the outer end of the cover portion (112). Here, the axial direction of the inner wall portion (130) means the longitudinal direction of the inner wall portion (130).

[0162] The inner wall portion (130) can form a motor receiving portion on the inside together with the cover portion (112). The motor receiving portion can be arranged on the inside of the inner wall portion (130), and the flow path portion can be arranged on the outside of the inner wall portion (130).

[0163] The outer wall portion (133) is arranged radially apart from the outer surface of the inner wall portion (130). The outer wall portion (133) is formed in a cylindrical shape with a second diameter that is larger than the first diameter.

[0164] The upstream end of the outer wall portion (133) can be accommodated inside the downstream end of the shroud (100). The upstream end of the outer wall portion (133) and the downstream end of the shroud (100) can be coupled to each other.

[0165] The outer wall portion (133) may further include a second fastening portion (134).

[0166] The second fastening portion (134) may be formed to protrude radially outward from the upstream end of the outer wall portion (133). The second fastening portion (134) extends circumferentially along the outer perimeter of the outer wall portion (133). A plurality of second fastening holes are formed to penetrate the second fastening portion (134) in the axial direction.

[0167] A plurality of second fastening holes are arranged spaced apart from each other in the circumferential direction in the second fastening portion (134). The first fastening hole and the second fastening hole are arranged to overlap in the axial direction. A fastening member such as a screw can be fastened by passing through the first fastening hole and the second fastening hole.

[0168] The outer wall (133) can form the exterior of the fan motor together with the shroud (100).

[0169] An airflow path is formed between the outer wall (133) and the inner wall (130). The path is positioned on the downstream side of the shroud (100). When looking at the shroud (100) and the motor housing (109) in the axial direction, the path is positioned on the inner side of the shroud (100).

[0170] Air sucked by the impeller (113) moves from the shroud (100) to the flow path. The flow of air moving to the flow path can be called the main flow.

[0171] A plurality of vanes (135) are provided between the inner wall portion (130) and the outer wall portion (133). The vanes (135) are formed to protrude radially from the outer surface of the inner wall portion (130) to the inner surface of the outer wall portion (133). The vanes (135) may be formed to be inclined at a preset angle with respect to the axial direction between the inner wall portion (130) and the outer wall portion (133).

[0172] One radial end of the vane (135) is connected to the outer surface of the inner wall (130), and the other radial end of the vane (135) is connected to the inner surface of the outer wall (133).

[0173] The vane (135) is formed in a curved shape inclined with respect to the axial direction along the outer surface of the inner wall portion (130) or the inner surface of the outer wall portion (133). The curvature of the vane (135) may vary along the axial direction. For example, the curvature of the vane (135) may increase from the upstream side to the downstream side of the flow path portion.

[0174] Through this, the vane (135) guides the flow of air generated by the impeller (113) in one direction. For example, a plurality of vanes (135) can convert the rotational flow of air rotating in the circumferential direction of the impeller (113) into the axial direction to maintain a smooth flow of air.

[0175] The vane (135) can be implemented as a single-stage vane or an N-stage vane (N is a natural number greater than or equal to 2) from the upstream side to the downstream side of the motor housing (109) based on the direction of air flow.

[0176] A single-stage vane means that the vanes (135) are formed integrally in the axial direction along the outer surface of the inner wall portion (130) or the inner surface of the outer wall portion (133). An N-stage vane means that a plurality of vanes (135) are formed axially and separately from each other along the outer surface of the inner wall portion (130) or the inner surface of the outer wall portion (133).

[0177] In this embodiment, it is shown as implemented with a two-stage vane (135).

[0178] The second vane (135) may be composed of a first vane (1352) positioned on the upstream side of the euro section and a second vane (1353) positioned on the downstream side of the euro section.

[0179] Here, the euro portion refers to the portion where the vane (135) is formed. The axial length of the euro portion may refer to the axial length of the vane (135).

[0180] The flow path section can be configured to be separated into a first flow path section and a second flow path section. The first flow path section is positioned upstream of the flow path section based on the air flow direction. A plurality of first vanes (1352) are provided on the inside of the first flow path section.

[0181] The second flow section is positioned downstream of the flow section based on the direction of air flow. A plurality of second vanes (1353) are provided on the inside of the second flow section.

[0182] The radial widths of the first and second flow sections can be maintained constant along the axial direction or formed differently. In this embodiment, the radial width (W) of the flow section is maintained constant.

[0183] The thickness of the inner wall portion (130) may vary along the axial direction. The inner wall portion (130) may be divided into a first inner wall portion (131) and a second inner wall portion (132) depending on the position of the flow path portion. The first inner wall portion (131) is arranged in the first flow path portion.

[0184] The second inner wall portion (132) is arranged in the second flow portion. For example, the thickness of the first inner wall portion (131) is thinner than the thickness of the second inner wall portion (132).

[0185] The sum of the thicknesses of the first inner wall portion (131) and the inner wall portion (136) of the euro housing to be described later can be formed to correspond to the thickness of the second inner wall portion (132).

[0186] The motor housing (109) may further include a euro housing.

[0187] The euro housing is arranged in the first euro section. The euro housing can form the first euro section. The euro housing includes an inner euro wall section (136), an outer euro wall section (137), and a first vane (1352).

[0188] The inner wall portion (136) of the flow path is formed in a cylindrical shape. The inner wall portion (136) has an axial length corresponding to the axial length of the first inner wall portion (131). The inner wall portion (136) extends circumferentially along the outer perimeter of the first inner wall portion (131).

[0189] The inner wall portion (136) surrounds the outer surface of the first inner wall portion (131). The inner surface of the inner wall portion (136) and the outer surface of the first inner wall portion (131) are joined to each other so that they are in contact with each other. The inner wall portion (136) and the first inner wall portion (131) are arranged to overlap each other in the radial direction.

[0190] The outer surface of the inner wall portion (136) and the outer surface of the second inner wall portion (132) can form the same surface along the longitudinal direction (axial direction) of the inner wall portion (136) and the second inner wall portion (132). Through this, air flow resistance can be minimized.

[0191] A bend (138) is formed at the upstream end of the inner wall portion (136) of the euro so as to be bent toward the outer periphery of the cover portion (112). A concave groove (139) is formed at the corner portion of the cover portion (112) to which the first inner wall portion (131) is connected. The concave groove (139) is formed concavely radially inward from the outer periphery of the cover portion (112).

[0192] Through this, the bending portion (138) can be joined to the concave groove (139). The inner surface of the inner wall portion (136) of the flow path and the outer surface of the first inner wall portion (131) can be joined while being in close contact with each other. The bending portion (138) is arranged adjacent to the downstream end of the hub (114), and the hub (114) and the bending portion (138) can form a streamlined curved surface. The flow resistance can be minimized during the process of moving from the hub (114) to the bending portion (138).

[0193] The outer wall portion (137) of the flow path is formed in a cylindrical shape. The outer wall portion (137) of the flow path has an axial length corresponding to the axial length of the inner wall portion (136). The outer wall portion (137) of the flow path is arranged radially outward from the outer surface of the inner wall portion (136) at a predetermined interval.

[0194] The outer wall portion (137) of the flow path extends circumferentially along the outer perimeter of the plurality of first vanes (1352). The thickness of the outer wall portion (137) of the flow path may be formed thinner than the thickness of the straight portion (103) of the shroud (100). The thickness of the outer wall portion (137) of the flow path may be formed thinner than the thickness of the outer wall portion (133).

[0195] The outer wall portion (137) of the euro can be joined to the inner surface of the straight portion (103) of the shroud (100). To this end, a joining groove is formed concavely radially outward on the inner surface of the straight portion (103). The joining groove extends circumferentially along the inner perimeter of the straight portion (103).

[0196] Through this, the outer wall portion (137) of the euro can be restricted from moving in the thrust direction by being caught in the joining groove. The euro housing can be supported by being joined between the first inner wall portion (131) of the motor housing (109) and the straight portion (103) of the shroud (100).

[0197] The inner surface of the outer wall portion (137) and the inner surface of the outer wall portion (133) can form the same surface along the longitudinal direction of the outer wall portion (137) and the outer wall portion (133).

[0198] A plurality of first vanes (1352) are arranged between the inner wall portion (136) and the outer wall portion (137). The plurality of first vanes (1352) are arranged spaced apart from each other in the circumferential direction along the outer surface of the inner wall portion (136) or the inner surface of the outer wall portion (137). The inner side of the first vane (1352) is connected to the inner wall portion (136), and the outer side of the first vane (1352) is connected to the outer wall portion (137).

[0199] The first vane (1352) is formed in a curved shape inclined to the axial direction along the outer surface of the inner wall of the euro (136) or the inner surface of the outer wall of the euro (137).

[0200] The inner wall (136), outer wall (137) and first vane (1352) of the euro housing can form a first euro section.

[0201] The second inner wall portion (132), the outer wall portion (133), and the second vane (1353) can form a second flow path portion.

[0202] The outer wall portion (133) is placed on the downstream side of the outer wall portion (137). The outer wall portion (133) is placed at a predetermined interval on the outer side of the second inner wall portion (132).

[0203] The sum of the axial lengths (heights) of the outer wall portion (137) and the outer wall portion (133) is equal to the sum of the axial lengths (heights) of the first inner wall portion (131) and the second inner wall portion (132) based on the inner surface of the motor housing (109), i.e., the inner surface of the cover portion (112) (see FIGS. 4(b) to 5 and 9), or may be extended longer than the sum of the axial lengths (heights) of the first inner wall portion (131) and the second inner wall portion (132) (see FIGS. 3, 7 and 8).

[0204] Referring to FIGS. 4(b) to 5 and 9, when the sum of the axial lengths of the first inner wall portion (131) and the second inner wall portion (132) is equal to the sum of the axial lengths of the outer wall portion (137) and the outer wall portion (133), the axial straightness of the air guided through the vane (135) can be improved. In addition, it is more effective in the reflux flow described later.

[0205] Referring to FIGS. 3, 7 and 8, when the sum of the axial lengths of the first inner wall portion (131) and the second inner wall portion (132) is shorter than the sum of the axial lengths of the outer wall portion (137) and the outer wall portion (133) with respect to the inner surface of the cover portion (112), an opening may be formed radially at the downstream end of the second inner wall portion (132). Through the opening, a vane extension portion (140) and a vane protrusion portion (141) may be further provided in the second vane (1353).

[0206] The vane extension (140) may extend radially inward from the downstream end (1351) of the second vane (1353) to cover the thickness surface of the downstream end of the second inner wall portion (132). The vane protrusion (141) may be formed to protrude radially further inward than the inner surface of the second inner wall portion (132) from the inner end of the vane extension (140).

[0207] The vane extension (140) and the vane protrusion (141) can change the flow direction of air discharged from the discharge end (1351), which is the downstream end of the second vane (1353), from the axial direction to the radial inward direction toward the upstream space of the motor (117). Through this, the flow resistance of the air discharged from the discharge end of the second vane (1353) can be minimized.

[0208] A second fastening portion (134) is formed to protrude radially outward from the upstream end of the outer wall portion (133). The second fastening portion (134) extends circumferentially along the outer perimeter of the outer wall portion (133). The first fastening portion (104) and the second fastening portion (134) are arranged to overlap in the axial direction.

[0209] A second fastening hole is formed to penetrate the second fastening portion (134) in the axial direction. A plurality of second fastening holes are provided in the second fastening portion (134). The plurality of second fastening holes are arranged to be spaced apart from each other in the circumference along the periphery of the second fastening portion (134). The second fastening holes are arranged to overlap the first fastening holes in the axial direction.

[0210] Through this, fastening members such as screws are penetrated and connected to the first fastening portion (104) and the second fastening portion (134) through the first fastening hole and the second fastening hole. The second fastening portion (134) is connected to the downstream side of the first fastening portion (104). The shroud (100) and the motor housing (109) can be connected by a plurality of fastening members.

[0211] A plurality of second vanes (1353) are arranged between the second inner wall portion (132) and the outer wall portion (133). The number of first vanes (1352) and the number of second vanes (1353) may be different. The inner side of the second vane (1353) is connected to the second inner wall portion (132), and the outer side of the second vane (1353) is connected to the outer wall portion (133).

[0212] The first and second euro sections are axially connected to each other.

[0213] The downstream end of the first vane (1352) and the upstream end of the second vane (1353) can be spaced apart from each other with a gap. This allows the air moving along the first vane (1352) and the air moving along the second vane (1353) to flow continuously and smoothly without interruption.

[0214] The motor receiving portion, in which the motor (117) is received, is provided on the radially inner side of the inner wall portion (130).

[0215] In order to support the motor (117), a support member (142) is provided on the inner surface of the inner wall member (130). The support member (142) is formed to protrude radially inward from the inner surface of the inner wall member (130).

[0216] A plurality of support members (142) are provided on the inner surface of the inner wall (130). The plurality of support members (142) can be arranged at predetermined intervals in the circumferential direction along the inner surface of the inner wall (130). In the present embodiment, three support members (142) are arranged at equal intervals of 120 degrees.

[0217] A discharge path (144) is formed between a plurality of adjacent support members (142) in the circumferential direction. The discharge path (144) may be formed to penetrate radially through the downstream end of the motor housing (109). The discharge path (144) may be connected to the flow path portion in communication with it.

[0218] Through this, the stator core (120) can be exposed to the outside of the motor housing (109) through the exhaust passage (144). In addition, the stator core (120) can come into contact with air passing through the vane (135) through the exhaust passage (144) or with the outside air of the motor housing (109), thereby releasing heat generated in the stator core (120).

[0219] The support member (142) extends axially from the inner circumferential surface of the inner wall member (130).

[0220] The support member (142) may extend so as to protrude along the axial direction from the downstream end of the second inner wall member (132). The support member (142) is formed to surround the outer circumferential surface of the stator core (120) to be described later.

[0221] The axial length of the support member (142) is longer than the axial length of the stator core (120).

[0222] The motor (117) may be configured to include a rotation shaft (106), a rotor (118), and a stator (119).

[0223] The rotation axis (106) is positioned at the center of each of the shroud (100), the motor housing (109), and the second housing to be described later. The rotation axis (106) extends along a center line that passes axially through the centers of the shroud (100), the motor housing (109), and the second housing.

[0224] A first bearing support part is formed on one side of the rotation shaft (106) into which a first bearing (107) is press-fitted. A second bearing support part is formed on the other side of the rotation shaft (106) into which a second bearing (108) is press-fitted.

[0225] The rotor (118) is disposed between the first bearing support and the second bearing support. The rotor support is disposed between the first bearing support and the second bearing support. The rotor (118) includes a permanent magnet. The rotor (118) may optionally further include a rotor core.

[0226] The permanent magnet may be coupled to the rotation shaft (106) or to the rotor core. In this embodiment, the rotor core is omitted to miniaturize the motor (117), and the permanent magnet is shown coupled to the rotor support of the rotation shaft (106).

[0227] The stator (119) is configured to surround the rotor (118), for example, a permanent magnet. The permanent magnet is rotatably mounted and spaced apart from the stator (119) in the radial direction by a preset air gap.

[0228] The stator (119) includes a stator core (120) and a stator coil (123). The stator core (120) includes a back yoke, a plurality of teeth (121), and a plurality of slots (122). The back yoke may be formed in an annular shape.

[0229] A plurality of teeth (121) may be formed to protrude radially inwardly toward the rotation axis (106) from the inner surface of the back yoke. The plurality of teeth (121) are arranged spaced apart from each other in the circumferential direction along the inner surface of the back yoke. A slot (122) is formed between two teeth (121) adjacent to each other in the circumferential direction.

[0230] A slot (122) is formed to penetrate the stator core (120) along the axial direction. A plurality of teeth (121) and a plurality of slots (122) are arranged alternately in the circumferential direction.

[0231] The stator coil (123) may be composed of a plurality of three-phase coils. The stator coil (123) is wound on a tooth (121). An insulator (124) is provided between the stator coil (123) and the stator core (120) for electrical insulation.

[0232] The slot (122) can form an internal passage for cooling the motor (117). Air can flow through the internal passage to cool the motor (117).

[0233] A lead wire (125) that applies power to one side of the stator coil (123) can extend in the axial direction. The lead wire (125) can receive external power through a power connection part (126) to be described later.

[0234] According to this configuration, when a power source such as an AC current is applied to the stator coil (123), a magnetic field is generated around the stator coil (123). The rotor (118) rotates relative to the stator (119) due to the electromagnetic interaction between the rotor (118) and the stator (119). The permanent magnet and the rotation shaft (106) rotate together to generate rotational force.

[0235] The impeller (113) coupled to one side of the rotation shaft (106) rotates by the rotational force transmitted through the rotation shaft (106).

[0236] The stator core (120) is press-fitted and joined to a plurality of support members (142). Through this, the plurality of support members (142) can support the stator (119).

[0237] A motor mounting portion (143) is provided on the inner surface of the support portion (142). The motor mounting portion (143) is formed radially concavely on the inner surface of the support portion (142). The circumferential width of the support portion (142) is smaller than the mutual spacing between the plurality of support portions (142).

[0238] The inner surface of the motor mounting portion (143) can be formed into a curved shape having a curvature corresponding to the outer surface of the stator core (120).

[0239] Through this, the motor mounting portion (143) can be in surface contact with the outer surface of the stator core (120) by surrounding it. A step is formed at one axial end of the motor mounting portion (143), for example, at one upstream end of the motor mounting portion (143). The step is formed to align the axial position of the stator core (120).

[0240] The step portion forms a radial step surface at the boundary line between the support portion (142) and the motor mounting portion (143). The step portion may cover a portion of an axial end of the stator core (120).

[0241] Through this, when the stator core (120) is press-fitted between a plurality of support members (142), one axial end of the stator core (120) can be caught on the step member. The step member can restrict the stator core (120) from moving in the thrust direction while being coupled to the support members (142). Accordingly, the coupling position of the stator core (120) can be aligned by the step member.

[0242] The second housing is positioned downstream of the motor housing (109). The second housing includes a second bearing housing (145), a bridge (147), and a coupling portion (148).

[0243] A second bearing (108) is accommodated in a second bearing housing (145). The second bearing housing (145) may be formed in a cylindrical shape. The second bearing housing (145) extends along the circumferential direction so as to surround the outer surface of the second bearing (108).

[0244] A second stopper (146) is formed to protrude radially inward from one axial end of the second bearing housing (145). Here, the axial end of the second bearing housing (145) means the first axial end in the air flow direction among the two axial ends of the second bearing housing (145).

[0245] Through this, the second stopper (146) can limit the movement of the second bearing (108) in the first axial direction while it is accommodated in the second bearing housing (145).

[0246] The bridge (147) extends radially from the outer surface of the second bearing housing (145) toward the inner surface of the connecting portion (148) to be described later. A plurality of bridges (147) may be provided. A plurality of bridges (147) may be arranged to be spaced apart from each other in the circumferential direction along the outer periphery of the second bearing housing (145). Through this, the bridges (147) can connect the second bearing housing (145) and the connecting portion (148).

[0247] The connecting portion (148) may be formed to protrude from the outer end of the bridge (147) toward the downstream end of the support portion (142). The connecting portion (148) may be connected to the downstream end of the support portion (142). The connecting portion (148) may be formed to surround the downstream end of the support portion (142). For example, a supporting portion receiving groove (149) may be formed concavely in the axial direction at one end of the connecting portion (148).

[0248] The support receiving groove (149) may include a first surface, a second surface, and a third surface. The first surface of the support receiving groove (149) may be formed to face the downstream end of the support (142) in the axial direction.

[0249] The second side of the support receiving groove (149) may be arranged to face one of the two circumferentially opposed side surfaces of the support (142) by extending axially from one end of the first side. The third side of the support receiving groove (149) may be arranged to face the other of the two circumferentially opposed side surfaces of the support (142).

[0250] The downstream end of the support member (142) is inserted into and joined to the support member receiving groove (149) of the coupling member (148). Optionally, the support member (142) and the coupling member (148) may be joined by a fastening member such as a screw.

[0251] A control unit may be placed on the downstream side of the second housing. The control unit is configured to control the overall operation of the fan motor, such as the motor (117). The control unit includes a printed circuit board (153), an IGBT (128), and a capacitor (129).

[0252] A power connection part (126) is provided on a printed circuit board (153). The power connection part (126) is formed to protrude from the printed circuit board (153) so as to be connectable to a lead wire (125). A plurality of power connection parts (126) are provided to correspond to the lead wire (125). The power connection parts (126) are connected to an external power source.

[0253] Through this, external power can be applied to the stator coil (123) through the power connection (126) and the lead wire (125).

[0254] The outer surface of the stator core (120) and the inner surface of the inner wall portion (130) are radially spaced apart at a predetermined interval by the radial thickness of the support portion (142). The predetermined interval can form a discharge path (144).

[0255] The exhaust passage (144) is a passage for discharging air from the air pocket (150) described later to the outside of the motor housing (109). The exhaust passage (144) can be connected in communication with the passage section.

[0256] The size of the gap between the above exhaust passages (144) can be an important factor influencing the cooling performance of the motor (117).

[0257] This is because, if the above gap is too large (wide), the air passing through the second vane (1353) acts as an air curtain, causing a problem in which the air in the motor housing stagnates inside the motor housing (109). In addition, if the above gap is too small (narrow), the flow resistance increases, causing a problem in which the air in the motor housing cannot be discharged to the outside through the exhaust passage (144).

[0258] To solve this problem, the minimum gap of the discharge passage (144) may be formed to be equal to or greater than the thickness of the inner wall portion (130) or the outer wall portion (133). In addition, the maximum gap of the discharge passage (144) may be formed to be equal to or smaller than the gap between the outer surface of the inner wall portion (130) and the inner surface of the outer wall portion (133).

[0259] At this time, the thickness of the inner wall portion (130) and the outer wall portion (133) may be the same. The thickness of the inner wall portion (130) and the outer wall portion (133) may be smaller than or equal to the passage gap between the outer surface of the inner wall portion (130) and the inner surface of the outer wall portion (133).

[0260] Except in cases where the first inner wall portion (131) and the second inner wall portion (132) are separately distinguished in this specification, the description of the inner wall portion (130) can be commonly applied to the first inner wall portion (131) and the second inner wall portion (132).

[0261] The outer diameter (D) of the motor (17) according to the comparative examples of Fig. 3(a) and Fig. 4(a) o ) and the outer diameter (d) of the motor (117) according to the present embodiment of FIG. 3(b) and FIG. 4(b) o ) are equal to each other. The radial width of the vane (35) according to the comparative examples of FIGS. 3(a) and 4(a) and the radial width of the vane (135) according to the present embodiment of FIGS. 3(b) and 4(b) are equal to each other.

[0262] However, the inner diameter of the inner wall portion (130) of the motor housing (109) according to the present embodiment of FIGS. 3(b) and 4(b) is smaller than the inner diameter of the inner wall portion (30) of the motor housing (9) according to the comparative example of FIGS. 3(a) and 4(a). The outer diameter of the outer wall portion (133) of the motor housing (109) according to the present embodiment of FIGS. 3(b) and 4(b) is smaller than the outer diameter of the outer wall portion (33) of the motor housing (9) according to the comparative example of FIGS. 3(a) and 4(a).

[0263] FIG. 3(a) and FIG. 4(a) are comparative examples for explanation in comparison with FIG. 3(b) and FIG. 4(b) of the present invention. Referring to FIG. 3(a) and FIG. 4(a), the gap (G1) of the discharge path (44) according to the comparative example is shown to be larger than the gap (G2) between the outer surface of the inner wall portion (30) and the inner surface of the outer wall portion (33).

[0264] The velocity of air passing through the vane (135) is faster than the velocity of air inside the motor housing (109). According to Bernoulli's equation, if the velocity of air is faster, the pressure of the air decreases.

[0265] However, when the gap (G1) of the exhaust passage (44) is too large, as in the comparative example, even if the velocity of the air passing through the vane (35) is fast, the velocity of the air flow layer adjacent to the outer surface of the stator core (20) is relatively low compared to the velocity of the air passing through the vane (35).

[0266] Due to this, the low velocity of the air flow layer adjacent to the outer surface of the stator core (20) has a limitation in generating a low pressure that can suck the air inside the motor housing (9) to the outside of the motor housing (9).

[0267] On the other hand, the minimum gap (g1) of the exhaust passage (144) according to FIG. 3(b) and FIG. 4(b) according to the present embodiment may be equal to or greater than (≥; equal to or greater than) the thickness (t) of the inner wall portion (130) or the outer wall portion (133). In addition, the maximum gap (g1) of the exhaust passage (144) may be equal to or less than (≤; less than or equal to) the gap (g2) between the outer surface of the inner wall portion (130) and the inner surface of the outer wall portion (133). The maximum gap (g1) of the exhaust passage (144) may be equal to or less than (≤; less than or equal to) the radial width (g2) of the vane (135).

[0268] In this embodiment, the gap of the exhaust path (144), i.e., the gap (d1) between the outer surface of the stator core (120) and the inner surface of the inner wall portion (130), is preferably 3% to 11% of the outer diameter of the outer wall portion (133) of the motor housing (109).

[0269] Because, if the gap of the above discharge path (144) is less than 3% of the outer diameter of the outer wall portion (133), there is a problem that air cannot be discharged smoothly due to the flow resistance of the discharge path (144). If the gap of the above discharge path (144) exceeds 11%, the flow velocity of the air flow layer adjacent to the outer surface of the stator core (120) decreases, causing a problem that the suction power of the air through the discharge path (144) decreases.

[0270] According to this embodiment, since the gap of the exhaust passage (144), i.e., the gap between the outer surface of the stator core (120) and the inner surface of the inner wall portion (130), is reduced, the velocity of the air flow layer adjacent to the outer surface of the stator core (120) is significantly faster than the velocity of the air inside the motor housing (109).

[0271] Accordingly, as the pressure of the air adjacent to the outer surface of the stator core (120) is significantly lower than the pressure of the air inside the motor housing (109), the air inside the motor housing (109) can be sucked in and discharged to the outside of the motor housing (109) through the exhaust passage (144).

[0272] In addition, the low pressure of the air adjacent to the outer surface of the stator core (120) provides suction power to suck in the air inside the motor housing (109), which can become a power source for the reflux flow described later.

[0273] In addition, the thermal dome phenomenon in which the hot air flow on the upstream side of the motor (117) stagnates can be eliminated.

[0274] FIG. 6 is a conceptual diagram showing the upstream end (1201) of the stator core (120) and the discharge surface of the vane (135) positioned to correspond to each other in the radial direction by enlarging the “VI” portion in FIG. 5.

[0275] Fig. 7 is a conceptual diagram showing the height at which the boss portion of the insulator (124) protrudes in Fig. 1.

[0276] Figure 8 is a view viewed in the direction VIII in Figure 7, and is a conceptual diagram showing the radius (r) and height of the air pocket (150).

[0277] The upstream end (1201) of the motor (117) is arranged axially spaced apart from the inner surface of the motor housing (109) at a preset interval. Here, the inner surface of the motor housing (109) refers to the inner surface of the cover part (112). The inner surface of the motor housing (109) is arranged axially facing the upstream end (1201) of the motor (117). In addition, the upstream end (1201) of the motor (117) refers to the upstream end (1201) of the stator coil (123) and / or the stator core (120).

[0278] The insulator (124) includes an insulator end portion (1241, 1242) and an insulator boss portion (1243, 1244). The insulator end portion (1241, 1242) includes a first insulator end portion (1241) covering an upstream end portion (1201) of the stator core (120) and a second insulator end portion (1242) covering a downstream end portion of the stator core (120).

[0279] The insulator end portion (1241, 1242) can be formed in a disc shape.

[0280] Insulator boss parts (1243, 1244) are provided in multiple numbers in each of the first insulator end part (1241) and the second insulator end part (1242). Insulator boss parts (1243, 1244) can be provided in multiple numbers on the inner and outer sides of the insulator end parts (1241, 1242) with the stator coil (123) interposed therebetween.

[0281] The plurality of insulator boss portions (1243, 1244) may include a plurality of inner insulator boss portions (1243) that protrude axially from the radially inner side of the insulator end portions (1241, 1242), and a plurality of outer insulator boss portions (1244) that protrude axially from the radially outer side of the insulator end portions (1241, 1242).

[0282] A plurality of inner insulator boss parts (1243) and a plurality of outer insulator boss parts (1244) can be arranged spaced apart from each other in the circumferential direction of the insulator end parts (1241, 1242).

[0283] The inner insulator boss (1243) is positioned between the permanent magnet and the stator coil (123). The outer insulator boss (1244) is positioned between the stator coil (123) and the inner wall (130).

[0284] Through this, the insulator boss (1243, 1244) can isolate the stator coil (123) from its surroundings so that the magnetic field generated in the stator coil (123) does not affect the surroundings.

[0285] Based on Figures 7 and 8, the boss portion protrudes upward from the insulator end portion (1241, 1242). The protruding height of the boss portion may vary depending on the amount and thickness of the stator coil (123) wound. For example, the height of the boss portion may be within the range of 2 to 5 mm.

[0286] The axial gap between the inner surface of the motor housing (109) and the upstream end (1201) of the motor (117) is an important factor that determines the cooling performance of the motor (117).

[0287] The air present inside the motor housing (109) can absorb heat generated from the upstream end (1201) of the stator coil (123) and the stator core (120).

[0288] When the radius (r) of the air pocket (150) is constant, the larger (wider) the axial gap between the inner surface of the motor housing (109) and the upstream end (1201) of the motor (117) becomes, the greater the volume of the air pocket (150), which can absorb the heat generated from the motor (117).

[0289] The air pocket (150) forms at least a part of the motor housing. The air pocket (150) may be formed by the inner surface of the cover portion (112) and the inner surface of the inner wall portion (130). The volume V of the air pocket (150) is πr 2 ×h may be. Here, r is the radius (r) of the air pocket (150). h is the height (h) of the air pocket (150).

[0290] The radius (r) of the air pocket (150) refers to the distance from the center line passing along the axial direction through the center of the rotation axis (106) to the inner surface of the inner wall (130). The height (h) of the air pocket (150) refers to the axial distance between the inner surface of the motor housing (109) and the upstream end (1201) of the motor (117).

[0291] More specifically, the height (h) of the air pocket (150) may mean the axial gap between the inner surface of the motor housing (109) and the upstream end (1201) of the stator core (120).

[0292] Therefore, in order to improve the cooling performance of the motor (117), it is desirable to increase the axial gap between the inner surface of the motor housing (109) and the upstream end (1201) of the stator core (120) when the diameter of the air pocket (150) is constant.

[0293] Preferably, the upstream end (1201) of the motor (117) is axially spaced from the inner surface of the motor housing (109) and is positioned to correspond to the discharge portion of the vane (135). The discharge portion of the vane (135) refers to the downstream end (1351) of the vane (135).

[0294] More specifically, the settling length of the stator core (120) corresponds to the axial distance from the inner surface of the motor housing (109) to the downstream end (1351) of the vane (135) (see FIG. 6).

[0295] In this embodiment, the height (h) of the air pocket (150) may be 22% to 42% of the outer diameter of the entire vane (135) or the outer diameter of the outer wall portion (133).

[0296] If the height (h) of the air pocket (150) is too much smaller than 22%, the volume of the air pocket (150) capable of absorbing the heat of the motor (117) is reduced, which may result in a decrease in the cooling performance of the motor (117). If the height (h) of the air pocket (150) is too much larger than 42%, the cooling performance of the motor (117) is increased, but the axial length of the fan motor is increased, which may have a negative effect on the miniaturization of the fan motor.

[0297] In this embodiment, the phase difference (ΔD) means the value obtained by subtracting the axial distance between the inner surface of the motor housing (109) and the downstream end (1351) of the vane (135) from the axial distance between the inner surface of the motor housing (109) and the upstream end (1201) of the stator core (120). When the phase difference (ΔD) is 0 mm, the optimal motor (117) cooling structure can be achieved.

[0298] The range of the phase difference (ΔD) can be greater than or equal to the height of the 0mm+insulator boss portion (1243, 1244) and less than or equal to the height of the 0mm-insulator boss portion (1243, 1244).

[0299] The effective cooling area refers to the area where the flow of air passing through the vane (135) directly hits and cools the outer surface of the motor (117), for example, the stator core (120).

[0300] According to the configuration according to the present embodiment, when the height (h) and the phase difference (ΔD) of the air pocket (150) are each limited to the numerical ranges described above, the effective cooling area is maximized, thereby increasing the cooling effect of the motor (117).

[0301] In addition, the air in the air pocket (150) absorbs the heat source of the motor (117), particularly the upstream end of the stator coil (123) and the upstream end (1201) of the stator core (120), thereby reducing the saturation maximum temperature. That is, the cooling performance is increased.

[0302] In addition, the air in the air pocket (150) can delay the time required to reach the saturated maximum temperature by absorbing the heat source of the motor (117).

[0303] Ultimately, the air in the air pocket (150) prevents a rapid temperature rise of the motor (117), thereby improving the reliability of products such as vacuum cleaners.

[0304] Fig. 9 is a conceptual diagram showing the reflux flow inside the motor housing (109) according to the embodiment of Fig. 5.

[0305] In this embodiment, the air flow can be divided into main flow and reflux flow. The main flow can be referred to as the first flow (①). The reflux flow can be referred to as the second flow (②).

[0306] The main flow is formed by the impeller (113) as described above. As the impeller (113) rotates, outside air is drawn into the interior of the shroud (100) through the intake port (101).

[0307] The air introduced into the shroud (100) moves to the flow path along the flow path between the outer surface of the hub (114) of the impeller (113) and the inner surface of the shroud (100).

[0308] Air flowing along the path formed between the outer surface of the inner wall portion (130) of the euro portion and the inner surface of the outer wall portion (133) is guided by the vane (135) and discharged from the downstream end (1351) of the vane (135), i.e., the discharge portion.

[0309] The air gap between the inner surface of the inner wall (130) and the outer surface of the stator core (120) is very narrow, so that some of the air discharged from the discharge portion of the vane (135) strikes the outer surface of the stator core (120), and the air flowing axially along the outer surface of the stator core (120) has a very fast velocity. Through this, the cooling performance of the motor (117) is increased.

[0310] Another portion of the air discharged from the discharge port of the vane (135) may pass through the outside of the motor (117) and be discharged to the outside of the motor housing (109), or may move to the PCB (127) through the discharge port formed between the bridges (147) of the second housing to cool the PCB (127), IGBT (128), capacitor (129), etc., and be discharged to the outside of the second housing.

[0311] In addition, the external air of the outer wall (133) of the motor housing (109) can strike the outer surface of the stator core (120) together with the main flow due to the rapid flow of air passing through the discharge portion of the vane (135).

[0312] Reflux flow means that some of the air discharged to the outside of the second housing is re-introduced into the air pocket (150) inside the motor housing (109) through the internal flow path of the motor (117) and then discharged through the exhaust flow path (144). The exhaust flow path (144) means the flow path between the outer surface of the stator core (120) and the inner surface of the inner wall portion (130).

[0313] Looking at the path of the reflux flow, when a portion of the air discharged from the discharge portion of the vane (135) strikes the outer surface of the stator core (120), the velocity of the air is significantly faster than the velocity of the air in the air pocket (150). As a result, the pressure in the discharge path (144) is significantly lower than the pressure in the air pocket (150).

[0314] Through this, the air in the air pocket (150) is discharged along the outer surface of the stator core (120) along with a portion of the air discharged from the discharge portion of the vane (135) due to the pressure difference between the discharge path (144) and the air pocket (150).

[0315] According to this reflux flow, some of the air discharged to the outside of the second housing passes through the discharge path (144) via the internal path formed between the discharge port of the second housing, the stator coil (123) of the motor (117), and the air pocket (150), thereby changing the heated air inside the motor (117) to external cold air, thereby improving the cooling performance of the motor (117).

[0316] In addition, the external air of the outer wall portion (133) can move toward the outer surface of the stator core (120) due to the rapid flow of air passing through the vane (135). This can be referred to as the third flow (③). Through this, the external air of the outer wall portion (133) cools the outer surface of the stator core (120), thereby increasing the cooling performance of the motor (117).

[0317] Fig. 10 is a graph showing the temperature trend of the motor (117) according to the settling length (or phase difference) of the stator core (120).

[0318] Fig. 11 is a conceptual diagram showing the arrangement relationship of the motor housing (109) and the stator (119) according to the phase difference in Fig. 10. Fig. 11(a) shows the arrangement relationship of the motor housing (109) and the stator (119) when the phase difference (ΔD) is greater than 0. Fig. 11(b) shows the arrangement relationship of the motor housing (109) and the stator (119) when the phase difference (Δd) is 0.

[0319] Referring to Fig. 10, the case where the settling length of the stator core (120) is short (Fig. 3(a) and Fig. 4(a)) and the case where it is the optimal length (Fig. 3(b) and Fig. 4(b)) and the case where the phase difference (ΔD, Δd = discharge end of vane (135) - upstream end (1201) of stator core (120)) is 6 mm, 3 mm, and 0 mm will be compared and explained.

[0320] An example of a case where the settling length of the stator core (120) is short means a case where the phase difference (ΔD) is 6 mm and 3 mm. An example of a case where the settling length of the stator core (120) is an optimal length means a case where the phase difference (Δd) is 0 mm.

[0321] When the phase difference (ΔD) is 6 mm, the temperature of the motor (117) is 0, and when the phase difference (ΔD) is 3 mm, the temperature of the motor (117) is a value greater than 0 and less than 1, approximately 0.8. When the phase difference (Δd) is 0 mm, the temperature of the motor (117) is -7.6. The reason why the unit of temperature is not limited here is because this temperature value is not limited to this and means a relative value depending on the phase difference (ΔD).

[0322] Through this, it can be seen that when the phase difference (Δd) is 0 mm, the temperature of the motor (117) has the lowest value.

[0323] Referring to Fig. 11, the phase difference ΔD, Δd is L1-L2. L1 may refer to the axial length of the vane (135) (including the first vane (1352) and the second vane (1353)) based on the inner surface of the motor housing (109). Alternatively, L1 may refer to the axial length of the inner wall portion (130) based on the inner surface of the motor housing (109).

[0324] L2 is the settling length of the stator core (120). The settling length L2 of the motor (117) refers to the axial separation distance of the upstream end (1201) of the stator core (120) based on the inner surface of the motor housing (109).

[0325] When the settling length of the stator core (120) according to the comparative example of Fig. 11(a) is short, for example, when the phase difference (ΔD) is 6 mm or 3 mm, the temperature of the motor (17) was relatively high, as in the case of the temperature of 0 or 0.8 in Fig. 10 described above.

[0326] When the settling length of the stator core (120) according to the present embodiment of Fig. 11(b) is the optimal length, for example, when the phase difference (Δd) is 0 mm, the temperature of the motor (117) was relatively low, as in the case of the temperature being -7.6 in Fig. 10 described above.

[0327] Figure 12 is a graph for comparing and explaining the saturation time and saturation temperature of the existing structure and the structure to which the air pocket (150) according to the present invention is applied.

[0328] Table 1 is a conceptual diagram showing the temperatures of the stator (119), magnet, bearing, etc. according to the core settling length.

[0329] [Table 1]

[0330]

[0331] When an air pocket (150) is applied inside the motor housing (109) according to the present embodiment, the time taken to reach the saturation temperature capable of absorbing the heat of the motor (117) (saturation time 2) is delayed compared to the time taken to reach the saturation temperature when an air pocket (150) is not applied inside the motor housing (109) according to the comparative example (saturation time 1).

[0332] Table 1 shows the results of measuring the temperature (℃) of the upstream end of the stator coil (123) according to the phase difference (ΔD) and the settling length of the stator core (120). In Table 1, coil means stator coil (123), core means stator core (120), magnet means permanent magnet, bearing phase means first bearing (107), and bearing second bearing (108) respectively.

[0333] Referring to Table 1, the phase difference (ΔD) is shown as an example for cases of 6 mm, 3 mm, and 0 mm. The settling length of the stator core (120) according to the phase difference (ΔD) is shown as an example for cases of 12 mm, 15 mm, and 18 mm. As the phase difference (ΔD) decreases, the settling length of the stator core (120) increases.

[0334] When the phase difference (ΔD) decreased from 6 mm to 3 mm, the settling length of the stator core (120) increased from 12 mm to 15 mm, but the maximum temperature of the upper end of the stator coil (123) increased by 0.7°C.

[0335] When the phase difference (ΔD) decreased from 6 mm to 0 mm, the settling length of the stator core (120) increased from 12 mm to 18 mm, and the maximum temperature of the upper end of the stator coil (123) decreased by 7.6°C.

[0336] When the phase difference (ΔD) decreased from 6 mm to 3 mm, the settling length of the stator core (120) increased from 12 mm to 15 mm, but the average temperature of the upper end of the stator coil (123) increased by 0.7°C.

[0337] When the phase difference (ΔD) decreased from 6 mm to 0 mm, the settling length of the stator core (120) increased from 12 mm to 18 mm, and the average temperature of the upper end of the stator coil (123) decreased by 4.9°C.

[0338] When the phase difference (ΔD) according to the present embodiment is 0 mm, it can be confirmed that the average temperature of the stator core (120), the average temperature of the permanent magnet, and the temperature of the first bearing (107) are lower than when the phase difference (ΔD) according to the comparative example is 6 mm and 3 mm.

Claims

1. Shroud; An impeller accommodated in the above shroud and forming a flow of air; A rotating shaft to which the above impeller is coupled; A motor housing coupled to the downstream side of the shroud based on the direction of air flow; A motor is included that is accommodated inside the motor housing and has a rotor coupled to the rotation shaft and a stator surrounding the rotor to drive the impeller. The above motor housing, Exterior wall; An inner wall portion arranged radially inwardly of the outer wall portion; A cover part covering the upstream end of the inner wall part based on the direction of air flow; and A fan motor including a vane that guides the flow of air and is arranged between the inner surface of the outer wall portion and the outer surface of the inner wall portion, an exhaust path is formed between the inner wall portion and the outer surface of the stator, and air in an air pocket formed by the cover portion, the inner wall portion, and the upstream end of the motor is exhausted to the exhaust path by the flow rate of air passing through the vane.

2. In paragraph 1, The above stator includes a stator core and a stator coil wound around the stator core, The above-mentioned discharge path spacing is defined as the spacing between the inner surface of the inner wall portion and the outer surface of the stator core. A fan motor in which the spacing of the above exhaust paths is equal to or greater than the thickness of the inner wall portion and equal to or less than the radial width of the vane, and the radial width of the vane is defined as the length of the vane extending radially from the inner peripheral surface of the outer wall portion to the outer peripheral surface of the inner wall portion.

3. In paragraph 2, A fan motor in which the gap of the above exhaust path is 3% to 11% of the outer circumferential diameter of the outer wall portion or the radial outer diameter of the vane.

4. In paragraph 1, The height of the above air pocket is defined as the gap between the inner surface of the cover part and the upstream end of the motor, A fan motor in which the height of the above air pocket corresponds to the length between the inner surface of the cover part and the downstream end of the vane.

5. In paragraph 4, A fan motor wherein the height of the above air pocket is 22% to 42% of the radial outer diameter of the above vane.

6. In paragraph 2, The value obtained by subtracting the axial distance between the inner surface of the cover part and the upstream end of the stator from the axial distance between the inner surface of the cover part and the downstream end of the vane is defined as the phase difference, The range of the above phase difference is - the protrusion height of the insulator boss portion or more to + the protrusion height of the insulator boss portion or less, and the fan motor in which the insulator boss portion is formed to protrude in the axial direction of the rotation shaft from the insulator covering the upstream end of the stator core.

7. In paragraph 1, A fan motor in which the downstream end of the vane and the upstream end of the stator are arranged to overlap each other in the radial direction.

8. In paragraph 2, The above stator core, A plurality of teeth protruding radially toward the center of the rotation axis from the inside of the stator core; and It includes a plurality of slots formed between the plurality of teeth and in which the stator coil is wound, A fan motor in which air outside the motor housing passes through the slot on the downstream side of the motor and moves to the air pocket to form a reflux flow.

9. In paragraph 1, A fan motor in which the axial distance between the inner surface of the cover portion and the downstream end of the outer wall portion is equal to the axial distance between the inner surface of the cover portion and the downstream end of the inner wall portion.

10. In paragraph 1, The axial distance between the inner surface of the cover portion and the downstream end of the inner wall portion is shorter than the axial distance between the inner surface of the cover portion and the downstream end of the outer wall portion, The above vein, A vane extension extending radially from the downstream end of the vane to cover the thickness surface of the inner wall; and A fan motor further comprising a vane protrusion formed to protrude from the vane extension into the exhaust path.

11. In paragraph 1, The above vane is a fan motor composed of a single-stage vane or N-stage vanes (N is a natural number greater than or equal to 2) formed to be separated from each other in the direction of the air flow.

12. In paragraph 1, The above motor housing, It includes a plurality of support parts that are formed to protrude radially from the inner surface of the inner wall part to surround the outer surface of the stator and extend axially from the downstream end of the inner wall part to support the stator, and the plurality of support parts are spaced apart in the circumferential direction along the outer surface of the stator. The above exhaust path is a fan motor arranged between the plurality of adjacent supports in the circumferential direction.

13. In paragraph 12, A motor mounting portion is concavely formed on the radially inner surface of the above support portion, The above motor mounting portion is a fan motor that aligns the mounting position of the motor spaced axially from the inner surface of the cover portion.

14. In paragraph 1, The above motor housing, A first inner wall portion having a first thickness and formed in a cylindrical shape; A second inner wall portion connected to the downstream side of the first inner wall portion based on the air flow direction, having a second thickness thicker than the first thickness, and formed in a cylindrical shape; A flow inner wall portion surrounding the outer surface of the first inner wall portion; A channel outer wall portion accommodated on the inner side of the downstream end of the shroud and spaced radially outside the channel inner wall portion; An outer wall portion connected to the downstream end of the above outer wall portion and spaced radially outside the second inner wall portion; A first vane extending from the outer surface of the inner wall of the above-mentioned euro to the outer wall of the above-mentioned euro; and A fan motor including a second vane that is connected to the downstream end of the first vane and protrudes from the outer surface of the second inner wall portion to the outer wall portion.

15. In paragraph 1, The above outer wall portion is a fan motor coupled to the downstream end of the shroud.

16. In paragraph 1, The above motor housing, A first bearing positioned downstream of the impeller based on the direction of air flow and supporting the upstream side of the rotation shaft; and A fan motor including a first bearing housing arranged in the central portion of the cover portion and accommodating the first bearing.

17. In paragraph 16, A support portion formed to protrude from the inner surface of the inner wall portion toward the rotation axis and to support the outer surface of the stator; A second bearing positioned downstream of the motor based on the direction of air flow and supporting the downstream side of the rotation shaft; A second bearing housing accommodating the second bearing; A joint part coupled with the downstream end of the above support part; and A fan motor including a bridge extending radially so as to be connected to an outer surface of the second bearing housing and an inner surface of the coupling portion.

18. In paragraph 1, A control unit is provided on the downstream side of the motor and includes a PCB equipped with an IGBT and a capacitor to control the operation of the motor. A fan motor whose lead wire is electrically connected to the stator above is connected to a power connection provided on the PCB above.

19. In paragraph 18, The above PCB is positioned axially facing the air pocket, The air discharged through the exhaust path from the above air pocket moves to the PCB, and a fan motor that cools the IGBT and the capacitor.

20. In paragraph 18, A fan motor in which air between the downstream side of the motor and the PCB passes through an internal passage formed inside the motor and moves to the air pocket to form a reflux flow.

Images