JP2023069317A - Air blower and washing machine - Google Patents

Abstract

To provide a sound attenuation structure which is suppressed from decreasing in efficiency for an air blower without entailing an increase in the number of components.SOLUTION: An air blower 22 comprises an electric motor 100, a rotary shaft 101 provided rotatably to the electric motor 100, an impeller 300 provided to the rotary shaft 101, and a casing 500 containing the impeller 300. The impeller 300 has a blade 321, a shroud plate 301 and a hub plate 311, and the blade 321 is sandwiched between the shroud plate 301 and hub plate 311 from both sides in an axial direction Ax of the rotary shaft 101. The casing 500 has at least one or more hollows 94 within a range radially inside a position overlapping with an outer periphery (external diameter R1) of the impeller 300 including the position in a radial direction of the impeller 300.SELECTED DRAWING: Figure 5

Description

TECHNICAL FIELD The present invention relates to an air blower and a washing machine having the same.

Patent Document 1 discloses a rotating tub serving as a drying chamber for storing clothes, a circulation air passage communicating with the inside of the rotating tub, a fan for circulating air in the rotating tub through the circulation air passage, and air circulated by the fan. , an exhaust port for discharging part of the circulated air from the circulating air passage, and an exhaust valve for opening and closing the exhaust port, in which a muffler is connected to the exhaust port configuration is described (see abstract).

In Patent Document 2, regarding the anti-vibration rubber for attaching the electric blower to the main body of the vacuum cleaner, a cavity is provided on the surface side of the anti-vibration rubber that contacts the fan casing, and a small hole corresponding to this cavity on a one-to-one basis is formed in the fan casing. An arrangement is described that opens and connects the cavity to the portion of the flow path from the diffuser to the return guide (see abstract).

JP 2014-133031 A JP-A-2000-120599

The clothes dryer described in Patent Document 1 has a configuration in which a silencer is connected to the exhaust port of the blower to reduce noise. However, the configuration described in Patent Literature 1 requires components other than the blower in order to reduce noise. Such a configuration increases the number of parts and manufacturing costs.

In the electric blower described in Patent Literature 2, the position where the small hole that connects the cavity with the flow path portion is provided is the position where the flow in the electric blower mainly flows. At this location, the flow velocity is high and the pores and cavities create turbulence in the flow. In this case, there is concern that the loss will increase and the efficiency of the electric blower will decrease.

SUMMARY OF THE INVENTION An object of the present invention is to provide a blower with a noise reduction structure that suppresses a decrease in efficiency without increasing the number of parts.

The present invention includes an electric motor, a rotating shaft provided rotatably on the electric motor, an impeller provided on the rotating shaft, and a casing enclosing the impeller, wherein the impeller includes blades and a shroud plate. and a hub plate, wherein the blades are sandwiched between the shroud plate and the hub plate from both sides in the axial direction of the rotating shaft, wherein the casing is arranged in the radial direction of the impeller so that the At least one or more recesses are provided in a range radially inward from a position including a position overlapping the outer periphery of the impeller.

ADVANTAGE OF THE INVENTION According to this invention, it is an air blower.

Problems, configurations, and effects other than those described above will be clarified by the following description of the embodiments.

1 is a longitudinal sectional view showing a washing machine equipped with a blower according to a first embodiment of the present invention; FIG. 1 is an external perspective view showing an air blower according to a first embodiment of the present invention; FIG. FIG. 3 is an exploded perspective view of the blower of FIG. 2 when viewed from the fan cover side; 1 is a perspective view of a diffuser according to a first embodiment of the invention; FIG. FIG. 3 is a cross-sectional view taken along line VV of FIG. 2; 6 is an enlarged view of the vicinity of the outer periphery of the centrifugal impeller of FIG. 5; FIG. 1 is a perspective view showing a schematic structure of a resonator according to a first embodiment of the present invention; FIG. FIG. 5 is a perspective view showing a modification of the resonator according to the first embodiment of the present invention; FIG. 7 is a partial cross-sectional view showing an enlarged cross section near the outer circumference of the centrifugal impeller of the blower according to the second embodiment of the present invention; FIG. 11 is a partial cross-sectional view showing an enlarged cross-section near the outer periphery of a centrifugal impeller of a blower according to a third embodiment of the present invention; FIG. 11 is a partial cross-sectional view showing an enlarged cross section near the outer periphery of a centrifugal impeller of a blower according to a fourth embodiment of the present invention;

BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, embodiments for carrying out the present invention will be described in detail with reference to the drawings.

[Example 1]
FIG. 1 is a longitudinal sectional view showing a washing machine S equipped with a blower 22 according to the first embodiment of the invention. In the following description, a vertical washing/drying machine is taken as an example, but the blower according to the present invention is applied to a drum-type washing/drying machine and a drum-type washing/drying machine in which an opening for loading and unloading laundry is formed on the front side. You can also

As shown in FIG. 1, the washing machine S includes an outer frame 1 that is a housing, an outer tub 2 that stores washing water, a rotating tub 3, a drive motor 10, a blower 22, and the like. The outer tub 2 is incorporated in the outer frame 1 and is supported by the outer frame 1 in a vibration-proof manner. The rotating tub 3 is a washing and dehydrating tub that accommodates laundry such as clothes to be washed and dried, and is provided inside the outer tub 2 . Further, the rotating tub 3 is rotatably supported within the outer tub 2 .

A stirring blade 4 for stirring and washing the laundry is rotatably provided at the bottom of the rotary tub 3 . The stirring blade 4 repeats forward/reverse rotation during the washing operation and the drying operation. During the dehydration operation, the rotary tub 3 rotates at high speed to dehydrate the laundry. During the dehydration operation, the stirring blade 4 rotates together with the rotating tank 3 at high speed.

An outer lid 5 is provided on the upper portion of the outer frame 1 . The outer lid 5 is provided on a top cover 6 provided on the upper portion of the outer frame 1 so as to be freely opened and closed. An inner lid 34 is provided on the upper portion of the outer tub 2 so as to be openable and closable. By opening the outer lid 5 and the inner lid 34, the laundry can be put in and taken out of the rotary tub 3.

The washing machine S also has a drying mechanism. This drying mechanism circulates and dehumidifies the drying air for drying the laundry in the rotary tub 3 . Moreover, the drying mechanism mainly includes a drying air circulation path 9 and a blower 22 . The drying air circulation path 9 includes a bottom circulation path 20 connected to the bottom of the outer tub 2 so as to communicate therewith, and a vertical dehumidifying path 21 extending upward from the bottom circulation path 20 .

The suction side of the blower 22 is connected to the upper side of the dehumidifying vertical passage 21 . The discharge side of the blower 22 is connected in communication with the return connection circuit 25 . A drying filter 45 is arranged between the blower 22 and the dehumidifying vertical passage 21 so that foreign matter does not flow into the blower 22 .

The return connection circulation path 25 has an upper bellows hose 23 and is connected to the upper part of the outer tub 2 via the upper bellows hose 23 so as to communicate therewith. The bottom circulation path 20 also has a lower bellows hose 26 and is connected to the bottom of the outer tub 2 via the lower bellows hose 26 so as to communicate therewith.

The lower bellows hose 26 is connected to the bottom drop portion 31 of the outer tub 2 . The bottom recessed portion 31 communicates with the wash water drainage channel 42 and the wash water circulation channel 43 through the lower communication pipe 41 . A drain valve 44 is provided in the washing water drain path 42 . A foreign substance removing trap 32 is provided in the washing water circulation channel 43 .

The drain valve 44 is closed during the washing operation and the drying operation. Further, the drain valve 44 is opened when the washing water is drained, and the washing water accumulated in the outer tub 2 is discharged to the outside of the washing machine S (outside the machine) through the washing water drain path 42 .

In the washing machine S, the centrifugal impeller 300 (see FIG. 2) of the blower 22 rotates to cause drying air to flow through the rotary tub 3, thereby drying the laundry in the rotary tub 3. Also, the electric heater 24 (see FIG. 3) of the blower 22 reheats the drying air in which the moisture is condensed in the dehumidifying area and flows through the rotary tub 3, further evaporating the moisture of the laundry. The laundry is dried by repeating this moisture removal by circulation of the drying air.

FIG. 2 is an external perspective view showing the blower 22 according to the first embodiment of the invention.
As shown in FIG. 2, the blower 22 includes a casing 500, an electric motor 100, a centrifugal impeller (impeller) 300, a diffuser 400 (see FIG. 3), and an electric heater 24 (see FIG. 3). . The casing 500 is composed of a fan cover 51 and a fan casing 52, and when the blower 22 is mounted on the washing machine S (see FIG. 1), for example, the fan cover 51 of the blower 22 faces substantially downward. It is installed in the outer frame 1 (see FIG. 1).

A suction port 57 and a discharge port 58 are formed in the fan cover 51 . The suction port 57 is connected to the dehumidification vertical passage 21 (see FIG. 1) through a dry filter 45 (see FIG. 1). The outlet 58 is connected to the return connection circuit 25 (see FIG. 1) of the drying air circuit.

FIG. 3 is an exploded perspective view of the blower 22 of FIG. 2 when viewed from the fan cover 51 side.
As shown in FIG. 3, the fan cover 51 has an elongated shape in one direction, with an intake port 57 formed in one longitudinal direction and an exhaust port 58 formed in the other longitudinal direction. The suction port 57 is a circular through hole and faces the center of the suction opening 302 (suction portion) of the centrifugal impeller 300 .

The outlet 58 is a circular through hole located downstream of the electric heater 24 . Also, the diameter of the discharge port 58 is formed to be larger than the diameter of the suction port 57 . In addition, the suction port 57 and the discharge port 58 are formed facing substantially the same direction.

In addition, a plurality of screw fixing portions 91 that are screw-fixed to the fan casing 52 are formed in the peripheral portion of the fan cover 51 .

The fan casing 52 has a shape corresponding to the fan cover 51 . The fan casing 52 and the fan cover 51 are configured to form a space between the fan cover 51 and the fan casing 52 in which the centrifugal impeller 300, the diffuser 400 and the electric heater 24 are arranged when combined. It is That is, a casing 500 composed of the fan cover 51 and the fan casing 52 contains the centrifugal impeller 300, the diffuser 400 and the electric heater 24. As shown in FIG.

The electric heater 24 has many fins and heats the passing air. The electric heater 24 is arranged at a position through which the air flowing out from the scroll flow path 70 passes.

A shaft insertion hole 80 into which the rotating shaft 101 of the electric motor 100 is inserted is formed in the fan casing 52 . Further, a screw insertion portion 92 through which a screw (not shown) is inserted is formed at a position corresponding to the screw fixing portion 91 of the fan cover 51 on the outer peripheral edge portion of the fan casing 52 .

Further, in the fan casing 52, screw holes 93 for fixing the diffuser 400 to the fan casing 52 are formed at a plurality of locations (four locations in this embodiment) between the shaft insertion hole 80 and the scroll passage 70. ing. These screw holes 93 are formed so as to surround the shaft insertion hole 80 .

A circular depression 94 is provided in a substantially circular shape on the surface of the fan casing 52 where the screw hole 93 is formed.

The electric motor 100 has a rotating shaft 101 rotatably provided and is attached to the fan casing 52 . A centrifugal impeller 300 is coupled to the rotating shaft 101 at its radial center. The electric motor 100 also has a rotor fixed to the rotating shaft 101, a stator provided around the rotor, and bearings supporting the rotating shaft 101 so as to be rotatable. The electric motor 100 also has a substantially cylindrical case 102 that houses the rotor, stator, and bearings.

Centrifugal impeller 300 provided on rotating shaft 101 is configured by combining shroud plate 301 , hub plate 311 , and blades 321 . The shroud plate 301 has a circular suction opening 302 formed in the center in the radial direction. Hub plate 311 is formed with a shaft hole (not shown) for fixing rotating shaft 101 . The blade 321 is configured by sandwiching the shroud plate 301 and the hub plate 311 from both sides in the axial direction Ax. That is, centrifugal impeller 300 has blades 321, shroud plate 301, and hub plate 311, and blades 321 are sandwiched between shroud plate 301 and hub plate 311 from both sides in axial direction Ax of rotating shaft 101. there is

FIG. 4 is a perspective view of a diffuser 400 according to a first embodiment of the invention.
As shown in FIG. 4, the diffuser 400 has a circular bottom plate 400a facing the axial direction Ax surface (hub plate 311) of the centrifugal impeller 300 (see FIG. 3). A plurality of screw insertion holes 430 through which screws (not shown) for fixing the diffuser 400 to the fan casing 52 are inserted are formed in the bottom plate 400a. The screw insertion hole 430 is formed at a position corresponding to (facing) the screw hole 93 (see FIG. 3) of the fan casing 52 .

Further, the diffuser 400 is formed with a recess 430a around the periphery of the screw insertion hole 430 so that the head of the screw (not shown) does not protrude from the surface of the bottom plate 400a.

A circular through hole 440 is formed in a substantially circular shape in the bottom plate 400a. The through-holes 440 are formed in the same number as the recesses 94 (see FIG. 3) at positions corresponding to (opposing to) the recesses 94 (see FIG. 3) of the fan casing 52 and have a hole diameter smaller than the opening of the recesses 94 .

A diffuser outer bottom surface (side wall) 400c formed one step higher than the bottom plate 400a in the axial direction Ax is formed on the entire outer peripheral edge of the bottom plate 400a. Diffuser vanes 401 are formed at regular intervals along the circumferential direction on the upper surface of the diffuser outer bottom surface portion 400c in the axial direction Ax (the surface on the side of the fan cover 51). Form.

A diffuser lid (side wall) 460 is provided above the diffuser vane 401 in the axial direction Ax.

FIG. 5 is a cross-sectional view taken along line VV of FIG.

A scroll flow path 70 is formed on the outer peripheral side of the diffuser 400 . The scroll flow path 70 is formed to have a cross-sectional shape of letter C in a cross section passing through the rotating shaft 101 and parallel to the rotating shaft 101 . In other words, the scroll flow path 70 is formed so as to surround both sides in the axial direction Ax (the shroud plate 301 side and the hub plate 311 side) of the outer peripheral edge of the diffuser 400 and the outer peripheral side surface of the diffuser 400 . .

In the blower 22, the centrifugal impeller 300 rotates in the W direction (see FIG. 3), so that air (fluid) is drawn from the outer periphery of the centrifugal impeller 300 after the air is sucked from the suction opening 302 through the suction port 57. is discharged. The discharged air passes through the diffuser channel 410 and flows into the scroll channels 70 provided on both sides of the diffuser 400 in the axial direction Ax. The air that has flowed through the scroll flow path 70 passes through the electric heater 24 (see FIG. 3) and flows to the discharge port 58 (see FIG. 3).

At this time, the blades 321 of the centrifugal impeller 300 periodically approach the diffuser vanes 401 as they rotate. At this time, the flow from the centrifugal impeller 300 interferes with the diffuser vanes 401, causing a frequency difference depending on the rotational speed of the centrifugal impeller 300 and the number of blades 321 between the centrifugal impeller 300 and the diffuser vanes 401. A pressure fluctuation occurs, and the sound wave is emitted to the outside of the blower 22 . A configuration of the present invention for reducing noise caused by sound waves will be described.

FIG. 6 is an enlarged view of the vicinity of the outer periphery of centrifugal impeller 300 of FIG.

A resonator 600 is formed by a through-hole 440 provided in the diffuser 400 and a recess 94 provided in the fan casing 52 below the centrifugal impeller 300 in the axial direction Ax. When periodic pressure fluctuations occur between the centrifugal impeller and the diffuser vanes 410, the air inside the through-holes 40 vibrates accordingly. At that time, the air in the depression 94 acts as a spring against vibration of the air in the through hole 40 . The spring effect of the depressions 94 dampens vibrations in the through-holes 40 and, in turn, dampens periodic pressure fluctuations that occur between the centrifugal impeller and the diffuser vanes 410 . This makes it possible to reduce noise.

Further, the resonator 600 is formed below the centrifugal impeller 300 in the axial direction Ax and inside the outer diameter R1 of the centrifugal impeller 300 . That is, the blower 22 of this embodiment includes a diffuser 400 having diffuser vanes 401 arranged downstream of the centrifugal impeller 300 and a bottom plate 400a provided with the diffuser vanes 401 and facing the hub plate 311. The bottom plate 400a is provided with the same number of through-holes 440 as the recesses 94 corresponding to the positions of the recesses 94. As shown in FIG.

At least one recess 94 forming the resonator 600 is provided in a radially inner range from a position including a position overlapping the outer circumference of the centrifugal impeller 300 in the radial direction of the centrifugal impeller 300 .

Although the depression 94 is provided on the fan casing 52 side in this embodiment, it may be provided on the fan cover 51 side. That is, recesses 94 are provided in at least one of casing 500 on the side of centrifugal impeller 300 facing shroud plate 301 and casing 500 on the side facing hub plate 311 of centrifugal impeller 300 .

Inside the blower 22, a high-speed flow flows from the centrifugal impeller 300 into the diffuser flow path 410, but the position where the resonator 600 is provided is not a region where the high-speed flow flows, but a region where the high-speed flow flows. is the slow region. Therefore, the flow disturbance caused by the through hole 440 is small, and the loss due to the provision of the resonator 600 can be reduced.

FIG. 7 is a perspective view schematically showing the structure of the resonator 600 according to the first embodiment of the invention.
In order to reduce the noise, it is necessary to match the resonance frequency f of the resonator 600 with the frequency of the noise to be reduced. Let L1 be the depth of the through-hole 440, A1 be the opening area, L2 be the depth of the recess 94, A2 be the opening area, and c be the speed of sound.
f=(c/2π)×(A1/(L1×A2×L2))̂0.5
Therefore, although the through hole 440 and the depression 94 are formed cylindrical in this embodiment, they may be formed as shown in FIG.

FIG. 8 is a perspective view showing a modification of the resonator 600 according to the first embodiment of the invention.
Various shapes, such as a rectangular parallelepiped resonator 600b as shown in FIG.

Also, the through holes 440 and the recesses 94 need not all have the same dimensions. That is, the through-holes 440 and the recesses 94 may be provided in a plurality and in two or more sizes. By setting the dimensions of the through-hole 440 and the depression 94 so as to obtain a plurality of resonance frequencies f, noise of a plurality of frequencies can be reduced.

As described above, the blower 22 of the first embodiment includes the electric motor 100, the rotating shaft 101 rotatably provided on the electric motor 100, the centrifugal impeller 300 provided on the rotating shaft 101, and the downstream of the centrifugal impeller 300. and a diffuser 400 provided with a through hole 440 inside the outer diameter R1 of the centrifugal impeller 300, and a casing 500 provided with a recess 94 at a position corresponding to the through hole 440.

That is, the blower 22 of this embodiment includes an electric motor 100, a rotating shaft 101 rotatably provided on the electric motor 100, an impeller 300 provided on the rotating shaft 101, and a casing 500 enclosing the impeller 300. , the impeller 300 has blades 321, a shroud plate 301 and a hub plate 311, and the blades 321 are sandwiched between the shroud plate 301 and the hub plate 311 from both sides in the axial direction Ax of the rotating shaft 101. , the casing 500 has at least one or more depressions 94 in the radial direction of the impeller 300, including a position overlapping the outer circumference (outer diameter R1) of the impeller 300, and in a range radially inward from the position.

A resonator 600 is formed by the through hole 440 and the recess 94, and the resonator 600 attenuates periodic pressure fluctuations generated between the centrifugal impeller and the diffuser vane 410, thereby enabling noise reduction. .

In addition, the resonator 600 is provided radially inward from the position including the position overlapping the outer circumference (outer diameter R1) of the centrifugal impeller, and is a region where the flow is slow. Loss due to flow turbulence can be reduced.

In addition, since the resonator 600 can be formed by drilling the diffuser 400 and the casing 500, no additional parts are required, and an increase in manufacturing cost can be suppressed.

Also, the blower 22 of the first embodiment is provided in the washing machine S. As shown in FIG. As a result, noise can be reduced, so that the number of noise countermeasure parts such as sound absorbing materials can be reduced, and the washing machine S can be made low-noise and low-cost.

[Example 2]
FIG. 9 is a partial cross-sectional view showing an enlarged cross section near the outer periphery of the centrifugal impeller 300 of the blower 22b according to the second embodiment of the present invention. Similar to FIG. 6, FIG. 9 is an enlarged view of the vicinity of the outer periphery of centrifugal impeller 300, showing only centrifugal impeller 300, diffuser 400 and casing 500. FIG.

In the air blower 22b, the cross-sectional shape of the scroll flow path 70 is formed to be circular.

It is desirable that the position where the resonator 600 is provided be as close as possible to the source of the noise. In the blower 22b, since the scroll flow path 70 is not formed to surround the outer peripheral side of the diffuser 400, the opening of the through hole 440 and the depression 94 can be provided at the same position as the outer diameter R1 of the centrifugal impeller 300. can. Since the source of the noise is between the centrifugal impeller 300 and the diffuser 400, the resonator 600 can be provided near the source of the noise, thereby further reducing the noise.

As in this embodiment, the through-holes 440 and the recesses 94 may be provided at positions overlapping the outer circumference (outer diameter R1) of the impeller 300 when viewed from the axial direction Ax of the rotating shaft 101 . This is synonymous with providing through-hole 440 and depression 94 at positions overlapping the outer periphery (outer diameter R1) of impeller 300 in the radial direction.

Since the flow emitted from the centrifugal impeller 300 cannot be bent 90 degrees and directed directly below and above the outer circumference (outer diameter R1) of the centrifugal impeller 300, the resonator 600 is arranged as in this embodiment. However, the flow turbulence generated by the resonator 600 can be reduced.

[Example 3]
FIG. 10 is a partial cross-sectional view showing an enlarged cross-section near the outer circumference of the centrifugal impeller 300 of the blower 22c according to the third embodiment of the present invention.

The air blower 22c has a configuration in which the diffuser 400 is removed from the air blower 22b of the second embodiment. Since the diffuser 400 is not provided in this embodiment, the bottom plate 400 a of the diffuser 400 is not present between the impeller 300 and the casing 500 . Therefore, the through hole 440 is not provided in the depression 94 provided in the casing 500 on the side (lower side) facing the hub plate 311 . In this case, by appropriately providing the depth L2 of the depression 94, it is possible to reduce the noise of the specific frequency.

A sound wave incident on the depression 94 is reflected within the depression 94 and radiated again from the depression 94 . Assuming that the wavelength of noise to be reduced is λ, the depth L2 of the recess 94 is set so that L2=λ/4. It becomes a phase, and the effect of canceling out the noise is obtained. Due to this effect, noise can be reduced even when the through hole 440 does not exist.

If the through hole 440 is required for setting the resonance frequency f, a member having the through hole 440 at the opening of the recess 94 may be provided.

[Example 4]
FIG. 11 is a partial cross-sectional view showing an enlarged cross section near the outer circumference of the centrifugal impeller of the blower according to the fourth embodiment of the present invention.

As shown in FIG. 11 , the depression 94 may be provided in the casing 500 on the side (upper side) facing the shroud plate 301 in the axial direction Ax of the centrifugal impeller 300 . That is, recesses 94 may be provided in both casing 500 on the side of impeller 300 facing shroud plate 301 and casing 500 on the side of impeller 300 facing hub plate 311 .

In this embodiment, there is no member covering the recess 94 provided in the casing 500 on the side (upper side) facing the shroud plate 301 , that is, the member corresponding to the bottom plate 400 a of the diffuser 400 . Therefore, the recess 94 provided in the casing 500 on the side (upper side) facing the shroud plate 301 is not provided with the through hole 440 . If the through hole 440 is required for setting the resonance frequency f, a member having the through hole 440 at the opening of the recess 94 may be provided.

By providing the depressions 94 above and below the centrifugal impeller 300 in the axial direction Ax, it is possible to further reduce noise. Further, by making the depth L2 of the recess 94 different between the upper and lower sides, it is possible to reduce noise of a plurality of frequencies.

In each of the above-described embodiments of the present invention, it is possible to provide a low-noise blower while maintaining blower performance without increasing manufacturing costs. Further, by providing a washing machine (washing/drying machine) with the blower of each embodiment, it is possible to provide a low-noise washing machine while maintaining blower performance without increasing manufacturing costs.

It should be noted that the present invention is not limited to the above-described embodiments, and includes various modifications. For example, the above-described embodiments are detailed descriptions for easy understanding of the present invention, and are not necessarily limited to those having all the configurations. In addition, it is possible to replace part of the configuration of one embodiment with the configuration of another embodiment, and it is also possible to add the configuration of another embodiment to the configuration of one embodiment. Moreover, it is possible to add, delete, or replace a part of the configuration of each embodiment with another configuration.

22 blower 94 recess 100 electric motor 101 rotating shaft 300 centrifugal impeller (impeller) 301 shroud plate of centrifugal impeller 300 311 hub plate of centrifugal impeller 300 321 centrifugal Blades of impeller 300 400 diffuser 400a bottom plate of diffuser 400 401 diffuser vane 440 through hole 500 casing Ax axial direction of rotating shaft 101 R1 outer periphery of impeller 300 (outer diameter ), S... Washing machine.

Claims (9)

an electric motor;
a rotating shaft provided rotatably on the electric motor;
an impeller provided on the rotating shaft;
A casing enclosing the impeller,
A fan in which the impeller has blades, a shroud plate and a hub plate, and the blades are sandwiched between the shroud plate and the hub plate from both sides in the axial direction of the rotating shaft,
The blower, wherein the casing has at least one or more recesses in a range radially inward from a position overlapping an outer periphery of the impeller in the radial direction of the impeller. The blower according to claim 1,
A fan according to claim 1, wherein said depressions are provided in a plurality and in two or more sizes. The blower according to claim 1 or 2,
The blower, wherein the recess is provided in at least one of the casing on the side of the impeller facing the shroud plate and the casing on the side of the impeller facing the hub plate. The blower according to claim 1 or 2,
A fan according to claim 1, wherein the recesses are provided in both the casing on the side of the impeller facing the shroud plate and the casing on the side of the impeller facing the hub plate. In the fan according to any one of claims 1 to 4,
The blower according to claim 1, wherein the recess is provided at a position overlapping the outer periphery of the impeller when viewed from the axial direction of the rotating shaft. The blower according to claim 1 or 2,
A diffuser having diffuser vanes arranged downstream of the impeller and a bottom plate provided with the diffuser vanes and facing the hub plate,
A fan according to claim 1, wherein the bottom plate of the diffuser is provided with through-holes corresponding to the positions of the dents, the number of which being the same as that of the dents. The blower according to claim 6,
The blower, wherein the through holes are provided in two or more sizes. In the fan according to claim 6 or 7,
The blower, wherein the through-hole is provided so as to overlap an outer periphery of the impeller when viewed from the axial direction of the rotating shaft. A washing machine comprising the blower according to any one of claims 1 to 8.

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