JP2017214900A - Air blowing device and air conditioning device including the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an air blowing device that can restrain the generation of noise around a suction port without impairing air volume-static pressure characteristics.SOLUTION: An air blowing device 100 comprises: an impeller 130 supported rotatably on a rotating shaft 131 and provided with a plurality of blades 132 along a circumferential direction; and a casing 110 that internally houses the impeller 130. The casing 110 comprises: a front plate 111 arranged opposite to one side in a direction of the rotating shaft 131 of the impeller 130 and in which a suction port 115 is formed; and a back plate 112 arranged opposite to another side in the direction of the rotating shaft 131 of the impeller 130. In the front plate 111, a peripheral portion of the suction port 115 is a sound absorbing structure 10.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a blower and an air conditioner equipped with the blower.

  Conventionally, in a blower used in an air conditioner or the like, a thin sheet-like sound absorbing material made of a soft porous material is coupled to the inner wall of the curved flow path of the blower to reduce noise caused by air flow. The intended one is known (for example, see Patent Document 1).

Japanese Patent Laid-Open No. 05-240193

  However, in the air blower in which the wall portion of the casing that houses the impeller is disposed on both sides in the rotation axis direction of the impeller and the suction port is formed on one side in the rotation axis direction of the impeller, A part of the air flow blown to the outer periphery of the impeller may return to the suction port side, collide again with the rotating impeller, and a vortex may be formed around the suction port to generate noise. Moreover, in the air blower having such a configuration, since the wall surface of the casing is formed in parallel on both sides in the rotation axis direction of the impeller, the generated noise is likely to resonate and the noise is likely to increase further.

  As shown in Patent Document 1, it is difficult to suppress noise generated around the suction port and resonating in the casing only by providing a sound absorbing material on the inner wall of the curved flow path of the blower. is there. Moreover, since the thing of patent document 1 sticks and arranges the sound-absorbing material on the inner wall of the casing, the flow path width is narrowed and the pressure loss increases, and the air volume-static pressure characteristics of the blower are remarkably increased. It will decline. Furthermore, the sound absorbing material is easily peeled off by the high-speed air flow, and it is difficult to obtain a noise reduction effect in the long term.

  The present invention has been made to solve such a problem, and wall portions of a casing for accommodating the impeller are disposed on both sides in the rotation axis direction of the impeller, and the rotation shaft of the impeller is provided. In a blower device in which a suction port is formed on one side of the direction, a blower device capable of suppressing the generation of noise around the suction port without impairing the air volume-static pressure characteristics, and an air conditioner equipped with the blower device Is what you get.

  An air blower according to the present invention includes an impeller that is supported rotatably about a rotation shaft and includes a plurality of blades along a circumferential direction, and a casing that houses the impeller inside. The casing is disposed to face one side of the impeller in the rotational axis direction, and is disposed to face the front plate in which a suction port is formed and the other side of the impeller in the rotational axis direction. And the front plate has a structure in which a peripheral portion of the suction port is a sound absorbing structure.

  Moreover, in the air conditioner provided with the air blower according to the present invention, the air blower having the above-described configuration, the suction port and the air outlet are formed, and the air path leading from the air inlet to the air outlet is formed therein. And a heat exchanger provided in the air passage of the casing.

  In the air blower according to the present invention and the air conditioner including the air blower, there is an effect that generation of noise around the suction port can be suppressed without impairing the air volume-static pressure characteristics.

It is a longitudinal cross-sectional view of the air blower which concerns on Embodiment 1 of this invention. It is a cross-sectional view of the air blower according to Embodiment 1 of the present invention. It is a fragmentary sectional view of the sound absorption structure with which the air blower concerning Embodiment 1 of this invention is provided. It is a figure explaining the sound absorption structure with which the air blower which concerns on Embodiment 1 of this invention is provided, and the example of a characteristic of a comparison object. It is sectional drawing of the air conditioning apparatus provided with the air blower which concerns on Embodiment 1 of this invention. It is a figure explaining an example of the spectral characteristic of the air blower which concerns on Embodiment 1 of this invention, and a comparison object.

  DESCRIPTION OF EMBODIMENTS Embodiments of the present invention will be described with reference to the accompanying drawings. In the drawings, the same or corresponding parts are denoted by the same reference numerals, and overlapping descriptions are simplified or omitted as appropriate. The present invention is not limited to the following embodiments, and various modifications can be made without departing from the spirit of the present invention.

Embodiment 1 FIG.
1 to 2 relate to Embodiment 1 of the present invention, FIG. 1 is a longitudinal sectional view of a blower, FIG. 2 is a transverse sectional view of the blower, and FIG. 3 is a sound absorbing structure provided in the blower. FIG. 4 is a diagram for explaining a characteristic example of a sound absorbing structure and a comparison target included in the blower, FIG. 5 is a cross-sectional view of an air conditioner including the blower, and FIG. 6 is a spectrum of the blower and the comparison target. It is a figure explaining an example of a characteristic.

  As shown in FIGS. 1 and 2, the air blower 100 according to Embodiment 1 of the present invention includes a casing 110, an impeller 130, and an electric motor 140. An impeller 130 is accommodated in the casing 110. The impeller 130 includes a rotating shaft 131 and a blade 132. The impeller 130 has a substantially cylindrical outer shape. The impeller 130 is provided with a rotation shaft 131 at the center of a substantially cylindrical shape. The impeller 130 is provided with a plurality of blades 132 along the circumferential direction of a substantially cylindrical shape. For example, about 40 blades 132 are provided at equal intervals along the circumferential direction.

  An electric motor 140 is connected to one end side of the rotating shaft 131 of the impeller 130. The electric motor 140 is a power source that rotationally drives the impeller 130 around the rotation shaft 131. By rotating the impeller 130 by the electric motor 140, a boosting air blowing action is obtained. The impeller 130 is supported inside the casing 110 so as to be rotatable about the rotation shaft 131.

  The casing 110 is formed so as to surround the impeller 130 and has a substantially cylindrical shape whose outer shape is larger than that of the impeller 130. The casing 110 includes a front plate 111, a back plate 112, and a side plate 113. The front plate 111 is disposed to face one side of the impeller 130 in the direction of the rotation shaft 131. The back plate 112 is disposed to face the other side of the impeller 130 in the direction of the rotation shaft 131. Here, the one side in the direction of the rotation shaft 131 of the impeller 130 on which the front plate 111 is disposed is the same side as the one end side of the rotation shaft 131 to which the electric motor 140 is connected. The side plate 113 is provided between the front plate 111 and the back plate 112. The side plate 113 is disposed so as to surround a part of the outer periphery of the impeller 130.

  A suction port 115 and an air outlet 121 are formed in the casing 110. The suction port 115 is an opening for taking air outside the casing 110 into the casing 110. The suction port 115 is formed in the front plate 111. The suction port 115 has a substantially circular shape concentric (coaxial) with the rotation shaft 131 of the impeller 130.

  A bell mouth 114 is provided around the portion of the front plate 111 where the suction port 115 is formed. The bell mouth 114 is for guiding the air taken into the casing 110 from the suction port 115 to the impeller 130. The inner peripheral surface of the bell mouth 114 has a curved shape whose inner diameter decreases from the front plate 111 side toward the back plate 112 side. Further, the outer peripheral surface of the bell mouth 114 has a curved shape whose outer diameter decreases from the front plate 111 side toward the back plate 112 side.

  The air outlet 121 is an opening for discharging the air inside the casing 110 to the outside of the casing 110. The blower outlet 121 opens in a direction orthogonal to the rotation shaft 131 of the impeller 130. The casing 110 is provided with a duct portion 120. The duct part 120 connects the housing part of the impeller 130 of the casing 110 and the outlet 121.

  In portions other than the duct portion 120 of the casing 110, the side plate 113 is arranged in a circular shape around the impeller 130. On the other hand, in the duct part 120 of the casing 110, the side wall part is linearly arranged. The duct part 120 is provided integrally with the other part of the casing 110.

  In the casing 110, parts other than the suction port 115 and the blower outlet 121 are closed by the front plate 111, the back plate 112, the side plate 113, and the duct part 120. As described above, the suction port 115 opens in a direction parallel to the rotation shaft 131 of the impeller 130, and the air outlet 121 opens in a direction orthogonal to the rotation shaft 131 of the impeller 130. That is, the air blower 100 according to the first embodiment is configured in a form generally called a sirocco fan.

  As shown in FIG. 2, the front plate 111 is configured by the sound absorbing structure 10 at least around the suction port 115. The peripheral part of the suction inlet 115 here is a part including at least the bell mouth 114. FIG. 2 shows an example in which the entire front plate 111 is configured by the sound absorbing structure 10. Further, the back plate 112 is constituted by the sound absorbing structure 10. FIG. 2 shows an example in which the entire back plate 112 is configured by the sound absorbing structure 10.

  Further, as shown in FIG. 1, at least a peripheral portion of the air outlet 121 in the casing 110 is constituted by the sound absorbing structure 10. In FIG. 1, the example which comprised the duct part 120 of the casing 110 with the sound-absorbing structure 10 is shown. That is, in this example, the portion where the side wall portion of the casing 110 is linearly arranged in FIG.

  Next, the configuration of the sound absorbing structure 10 will be described with reference to FIG. FIG. 3 is a partial cross-sectional view of the sound absorbing structure 10, schematically showing a cross section cut in the thickness direction. The sound absorbing structure 10 is configured by stacking a plurality of layers, and includes a sound absorbing layer 11 and a surface layer 12.

  The surface layer 12 is arrange | positioned at both surfaces of the outer side of the thickness direction, respectively. The surface layer 12 is obtained by compressing a sound absorbing material serving as a base material. In other words, the surface layer 12 is composed of a compressed sound absorbing material.

  The sound absorbing layer 11 is a layer provided inside the surface layer 12, that is, between the two surface layers 12. The sound absorbing layer 11 is configured using a sound absorbing material as a base material without being compressed. Therefore, the sound absorbing material constituting the sound absorbing layer 11 is softer than the sound absorbing material constituting the surface layer 12. In other words, since the sound absorbing material constituting the surface layer 12 is compressed, it is harder than the sound absorbing material constituting the sound absorbing layer 11.

  The sound-absorbing material constituting the sound-absorbing layer 11 and the sound-absorbing material as the base material of the surface layer 12 may be the same type of material or different materials. When using the same kind of material, for example, a pulp fiber sound absorbing material may be specifically used as the sound absorbing material. At this time, as the pulp fiber, for example, a natural material typified by bioplastic can be used. And the sound absorption layer 11 is comprised using as it is, without compressing a pulp-type fiber sound-absorbing material. The surface layer 12 is formed by compression molding a pulp-based fiber sound absorbing material.

  On the other hand, when different types of materials are used, for example, a fiber composite material (fiber-based resin composite material) can be used as the surface layer 12. The fiber composite material used in this case is a composite of fiber such as glass fiber, carbon fiber, and aramid fiber and a resin.

  As described above, the sound absorbing structure 10 in which the sound absorbing layer 11 and the surface layer 12 are laminated and integrated can be manufactured, for example, by the following method. First, as a first method example, one type of pulp fiber is used, and a method of forming by heating and pressing in a state where the inner surface temperature of the male mold and the female mold of the molding mold is different is considered. . As a second method example, a sound absorbing material molded in an uncompressed state in advance and a sound absorbing material molded by compression are prepared, and the non-compressed sound absorbing material is sandwiched between the compressed sound absorbing material and heated and pressed. A way to do this is considered.

  Next, the sound absorbing performance of the sound absorbing structure 10 configured as described above will be described with reference to FIG. 4 in comparison with other sound absorbing materials. FIG. 4 shows an example of the sound absorbing performance of each sound absorbing material including the sound absorbing structure 10 of the present embodiment. FIG. 4 shows the sound absorption rates of the following five types of sound absorbing materials a) to e). In addition, all of these five types of sound absorbing materials a) to e) have a thickness of 10 mm.

a) General glass wool b) Non-compression molded sound-absorbing material with pulp fiber c) Compression-molded sound-absorbing material with pulp fiber d) Sound-absorbing material in which uncompressed and compressed sound-absorbing material is integrated with pulp fiber (sound absorbing structure of this embodiment) Configuration of body 10)
e) General resin (ABS, PP, etc.)

  As can be seen from FIG. 4, the sound absorption rate increases in the order of e << c <a <d <b, particularly in a band where the frequency is higher than about 600 Hz. The pulp fiber-based sound absorbing material b has a sound deadening space between fibers as in the case of other sound absorbing materials, and a plurality of air holes are formed inside the fiber, so that a higher sound absorption rate than that of glass wool a is obtained. Can do. In addition, although the sound absorption coefficient of the pulp fiber compression molded sound absorption material of c is lower than that of b, the sound absorption coefficient is higher than that of a general ABS or PP resin e.

  The sound absorbing structure 10 of d is configured to include a sound absorbing layer 11 having a thickness b of about 9 mm and a surface layer 12 made of c having a thickness of about 1 mm only on the surface. For this reason, a sound absorption rate higher than a can be obtained. Further, the sound absorbing structure 10 of d is characterized in that the sound absorption rate is higher than other a, b, c and e, particularly in a low frequency range where the frequency is lower than around 600 Hz. This is considered to be due to the membrane vibration absorption effect of the surface layer 12.

  Next, the operation of the blower 100 configured as described above will be described with reference to FIGS. 1 and 2 again. When the impeller 130 is rotated by the electric motor 140, air is sucked into the casing 110 from the suction port 115 of the bell mouth 114, as indicated by the solid line arrow in FIG. The sucked air flows into the impeller 130 from the front plate 111 side in the axial direction of the rotating shaft 131 toward the rear plate 112 side along the rotating shaft 131 direction.

  The inflowing air passes through the gap between the blades 132 and flows out while being accelerated from the impeller 130 radially outward. As shown by the solid line arrow in FIG. 1, the outflowed air flows along the inner peripheral wall (side plate 113) of the casing 110, passes through the duct portion 120 integral with the casing 110, and then flows out from the air outlet 121. leak.

  Next, noise generated in the casing 110 during the operation of the blower 100 will be described with reference to FIGS. 1 and 2. As indicated by the solid arrows in FIG. 2, the airflow that has flowed out radially outward of the impeller 130 along the surface of the rotating blade 132 collides with the inner peripheral wall (side plate 113) of the casing 110.

  A part of the air flow that collided with the inner peripheral wall (side plate 113) of the casing 110 returns to the front plate 111 as shown by the broken arrow in FIG. 2, and the bell mouth 114 around the suction port 115, etc. Wrap around. Then, the sneak-in air collides with another blade 132 of the impeller 130 and a vortex is generated around the suction port 115.

  Flowing noise is generated in the casing 110 by the vortex generated in this way. Further, when the air flow that flows out of the impeller 130 and returns to the front plate 111 collides with the front plate 111, the front plate 111 is vibrated to generate vibration noise. Further, the flow noise and vibration noise are amplified by the resonance phenomenon in the inside of the casing 110, particularly in a space formed between two parallel plate surfaces such as the front plate 111 and the back plate 112. Thus, during the operation of the blower 100, fluid noise and vibration noise and resonance phenomena of these noises occur.

  On the other hand, according to the air blower 100 which concerns on Embodiment 1 of this invention, as for the front board 111, the peripheral part of the suction inlet 115 is the sound-absorbing structure 10. FIG. For this reason, the flow noise caused by the vortex generated around the suction port 115 can be effectively attenuated and suppressed by the sound absorbing structure 10. Further, vibration noise and resonance phenomenon caused by the collision of the air flow with the front plate 111 can be effectively attenuated and suppressed by the sound absorbing structure 10 around the suction port 115. Furthermore, since the front plate 111 itself is the sound absorbing structure 10, the air volume-static pressure performance is maintained without causing narrowing of the flow path, and the sound absorbing structure 10 does not fall off the casing 110 for a long period of time. Noise can be suppressed over.

  At this time, as described above, the sound absorbing structure 10 includes the sound absorbing layer 11 and the surface layer 12. The sound absorbing layer 11 can efficiently reduce acoustic energy components accompanying noise propagating in the air flow path inside the casing 110. In the surface layer 12, the surface exposed to the air flow path inside the casing 110 is a smooth surface having no unevenness as compared with the sound absorbing layer 11. For this reason, it is possible to suppress the generation of vortices and the increase in pressure loss due to friction when the air flow collides without deteriorating the air flow characteristics in the casing 110.

  That is, the flow noise, the resonance sound inside the casing 110, and the fluid vibration sound can be suppressed for a long time without reducing the aerodynamic performance while maintaining a high air volume-static pressure performance. .

  Moreover, since the surface layer 12 has few unevenness | corrugations, it can improve water repellency. In addition, since the unevenness in the air passage can be reduced, it is possible to obtain the sound absorbing structure 10 and the air blower 100 with high reliability that are less likely to accumulate dust and the like.

  Furthermore, as described above, the surface layer 12 of the sound absorbing structure 10 also has a property as a coating. Therefore, the surface layer 12 is vibrated by the collision of the sound wave or the air flow, and the vibration of the surface layer 12 is suppressed by the elasticity of the fibers constituting the surface layer 12. For this reason, it is possible to reduce the amount of vibration accompanying vibration when the air flow collides, and to suppress the generation of vibration noise. In addition, since the surface layer 12 is formed outside so that the sound absorbing layer 11 is not exposed to the outside, scattering of pulp fibers and the like of the sound absorbing layer 11 inside the sound absorbing structure 10 can be prevented, and the sound absorbing structure 10 reliability can be improved.

  In this case, when a fiber composite material (fiber-based resin composite material) is used for the surface layer 12, the generation of vibration noise due to fluid excitation is further reduced by taking advantage of the high elasticity and high strength of the composite material. be able to. In addition, since the fibers are mesh-like on the surface exposed to the flow path of the surface layer 12, a fine uneven shape is formed on the surface exposed to the flow path, and the size of the vortex generated due to fluid disturbance is reduced. Therefore, the flow noise can be suppressed.

  Moreover, according to the air blower 100 which concerns on Embodiment 1 of this invention, the backplate 112 is the sound-absorbing structure 10. FIG. For this reason, the resonance phenomenon which generate | occur | produces especially in the space formed between the front board 111 and the back board 112 can further be suppressed. Therefore, noise generated during operation of the blower 100 can be further attenuated and suppressed.

  Next, as shown by the solid line arrow in FIG. 1, the air that has flowed radially outward from the impeller 130 swirls along the inner peripheral wall (side plate 113) of the casing 110, and then passes through the duct portion 120. It flows out from the blower outlet 121. When proceeding from the turn along the side plate 113 of the casing 110 to the duct portion 120, the air flow changes.

  At the portion where the air flow inside the casing 110 changes, that is, at the connecting portion of the casing 110, the side plate 113 and the duct portion 120, the air flow collides with the inner wall of the duct portion 120, and the duct portion around the outlet 121. At 120, a vortex is generated. The generated vortex causes flow noise in the duct portion 120 of the casing 110. Further, when the air flow collides with the inner wall of the duct part 120, vibration noise is generated by exciting the duct part 120.

  On the other hand, according to the air blower 100 according to Embodiment 1 of the present invention, the duct portion 120 that is the peripheral portion of the air outlet 121 is the sound absorbing structure 10. For this reason, the flow noise caused by the vortex generated around the air outlet 121 can be effectively attenuated and suppressed by the sound absorbing structure 10. Further, vibration noise and resonance phenomenon caused by the collision of the air flow with the duct portion 120 can also be effectively attenuated and suppressed by the sound absorbing structure 10 in the peripheral portion of the air outlet 121 (duct portion 120). .

  Next, the air conditioning apparatus 200 including the blower 100 configured as described above will be described with reference to FIG. As shown in FIG. 5, the air conditioning apparatus 200 includes a box-shaped housing 210. An air conditioner suction port 211 and an air conditioner blower outlet 212 are formed in the casing 210. The air conditioner suction port 211 is an opening for taking in air from the outside to the inside of the housing 210. The air conditioner outlet 212 is an opening for exhausting air from the inside of the housing 210 to the outside.

  Inside the casing 210, an air passage 213 that leads from the air conditioner inlet 211 to the air conditioner outlet 212 is formed. A heat exchanger 220 is installed in the air path 213 of the casing 210. The heat exchanger 220 exchanges heat between the air flowing through the air passage 213 and, for example, a refrigerant flowing through the heat exchanger 220, and cools or heats the air flowing through the air passage 213.

  A drain pan 230 is installed below the heat exchanger 220. The drain pan 230 is for receiving condensed water (drain water) generated by cooling the air in the heat exchanger 220.

  In addition, the blower 100 having the configuration described above is installed inside the casing 210. In the example illustrated in FIG. 5, the air blower 100 is disposed on the upstream side of the heat exchanger 220 in the air path 213 of the casing 210.

  Here, if the heat exchanger 220 and the air blower 100 are arranged close to each other in the air conditioner 200, the air blower 100 is affected by a temperature change caused by the heat exchanger 220 and the occurrence of condensation. As described above, the sound absorbing structure 10 used in the blower 100 is provided with the surface layer 12. And, since the surface of the surface layer 12 is less uneven, even if condensation occurs on the surface of the surface layer 12, it is possible to suppress the condensed water from being absorbed into the sound absorbing structure 10, Deterioration or the like of the blower 100 can be suppressed. Therefore, the heat exchanger 220 and the blower 100 can be disposed close to each other in the air conditioner 200, and the size of the air conditioner 200 can be reduced.

  Moreover, the air blown out from the air conditioning apparatus 200 is often blown directly to humans. For this reason, when the air blower 100 is in operation, durability that prevents parts from being peeled off and scattered from the air blower 100 is required. As described above, the sound absorbing structure 10 used in the blower device 100 includes the sound absorbing layer 11 and the surface layer 12, and the surface layer 12 can prevent the sound absorbing layer 11 from being peeled off and scattered. Therefore, it can be preferably used for the air conditioner 200.

  FIG. 6 shows a noise reduction effect together with a comparative example when the air blower 100 is applied to the air conditioner 200 as shown in FIG. 5 described above. The “Example” indicated by the solid line in FIG. 6 is an example in which the air blower 100 according to Embodiment 1 of the present invention is applied to the air conditioner 200. A “comparative example” indicated by a broken line is an example in which a conventional blower that does not include the sound absorbing structure 10 is applied to an air conditioner.

  FIG. 6A shows the attenuation band of the vibration noise component due to both the sound absorbing layer 11 and the surface layer 12. That is, in the band A, the noise component in the low frequency band generated due to the fluid excitation is reduced by the synergistic effect of the elasticity of the sound absorbing layer 11 and the surface layer 12 having a high sound absorption rate. 6B shows the attenuation band of the vibration noise component by the sound absorbing layer 11. FIG. That is, in the B band, the high frequency band where the flow noise is dominant is effectively reduced by the sound absorbing layer 11 having a high sound absorption coefficient. Then, when these A and B are combined, it can be seen that the embodiment achieves noise attenuation of 5 to 10 dB or more in a wide frequency band as shown in FIG.

  According to the air blower 100 according to the embodiment configured as described above, a part of the air passage wall surface in the air blower 100 is configured by the sound absorbing structure 10 formed by the compression sound absorbing material and the non-compression sound absorbing material. Therefore, the flow noise generated in the casing 110 and the duct portion 120 and the vibration noise generated by the vibration of the wall surface of the casing 110 by the high-speed fluid are generated while maintaining the static pressure-air flow performance of the blower 100 high. In addition, the amplification of noise due to the resonance phenomenon inside the casing 110 can also be suppressed.

  Moreover, since the surface layer 12 of the sound absorbing structure 10 is made of a compression sound absorbing material, the sound absorbing performance in the low frequency band can be increased compared to other porous sound absorbing materials, and the sound absorbing layer 11 inside Combined with the sound absorption performance in the high frequency band, a noise reduction effect can be obtained in a wide frequency band.

  In addition, since the surface layer 12 is made of a compression sound absorbing material, the static pressure-air volume performance of the blower 100 is maintained high, and abnormal noise due to pressure loss, a decrease in wind speed, and the like are not caused. Therefore, useless power loss can be suppressed, power consumption during operation of the blower 100 can be suppressed, and energy saving can be achieved.

  Furthermore, even if the surface of the sound absorbing structure 10 is directly exposed to a high-speed fluid by performing a surface treatment with bioplastic based on pulp fibers on the surface layer 12 of the sound absorbing structure 10, the sound absorbing structure 10 Can be prevented from scattering. In addition, by using a natural material typified by bioplastics existing in nature, it can be restored to its original nature by processing such as filling in the ground after product disposal. For this reason, it can process, without generating the dioxin which generate | occur | produces at the time of incineration processing.

  In addition, the noise suppression effect can be acquired, ensuring the rigidity intensity | strength of the casing 110 by comprising a part of the casing 110 containing the duct part 120 with the sound absorption structure 10. FIG. At this time, portions other than the sound absorbing structure 10 may be made of a general resin, or may be made of a composite material of a fiber such as glass fiber, carbon fiber, or aramid fiber and a resin. By using the composite material, a light and high-strength casing 110 can be obtained.

  The sound absorbing structure 10 itself described above is not limited to the sirocco fan type air blower 100 as the first embodiment, but also, for example, an impeller such as a turbo fan type air blower or an axial fan type air blower. As long as it is provided with a casing including a duct portion around it, any of them can be applied.

DESCRIPTION OF SYMBOLS 10 Sound absorption structure 11 Sound absorption layer 12 Surface layer 100 Air blower 110 Casing 111 Front plate 112 Back plate 113 Side plate 114 Bell mouth 115 Inlet 120 Duct part 121 Outlet 130 Impeller 131 Rotating shaft 132 Blade 140 Electric motor 200 Air conditioner 210 Case 211 Air Conditioner Inlet 212 Air Conditioner Outlet 213 Air Path 220 Heat Exchanger 230 Drain Pan

Claims (6)

An impeller that is rotatably supported around a rotation axis and provided with a plurality of blades along the circumferential direction;
A casing that houses the impeller therein,
The casing is
A front plate that is disposed opposite to one side of the impeller in the direction of the rotation axis and in which a suction port is formed,
A back plate disposed opposite to the other side of the impeller in the rotational axis direction,
The front plate is a blower device in which a peripheral portion of the suction port is a sound absorbing structure.   The blower according to claim 1, wherein the back plate is a sound absorbing structure. The sound absorbing structure is
A surface layer obtained by compressing a sound absorbing material as a base material;
The air blower according to claim 1, further comprising: a sound absorbing layer provided inside the surface layer, wherein the sound absorbing material is softer than the surface layer.   The blower according to claim 3, wherein the sound absorbing material is a pulp-based fiber sound absorbing material. The sound absorbing structure is
A surface layer of a fiber composite;
The air blower according to claim 1, further comprising: a sound absorbing layer provided inside the surface layer, wherein the sound absorbing material is softer than the surface layer. A blower device according to any one of claims 1 to 5,
A housing in which an air inlet and an air outlet are formed, and an air passage leading from the air inlet to the air outlet is formed inside;
An air conditioner comprising: a heat exchanger provided in the air passage of the housing.

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