CN110360656B - Cross flow wind wheel and air conditioner indoor unit - Google Patents
Cross flow wind wheel and air conditioner indoor unit Download PDFInfo
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- CN110360656B CN110360656B CN201910733572.3A CN201910733572A CN110360656B CN 110360656 B CN110360656 B CN 110360656B CN 201910733572 A CN201910733572 A CN 201910733572A CN 110360656 B CN110360656 B CN 110360656B
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- 230000000149 penetrating effect Effects 0.000 claims abstract description 6
- 239000011358 absorbing material Substances 0.000 claims description 4
- 238000004378 air conditioning Methods 0.000 claims 6
- 238000010521 absorption reaction Methods 0.000 abstract description 37
- 239000007787 solid Substances 0.000 abstract description 4
- 238000013461 design Methods 0.000 description 7
- 230000000694 effects Effects 0.000 description 7
- 238000012360 testing method Methods 0.000 description 7
- 238000000034 method Methods 0.000 description 5
- 230000009286 beneficial effect Effects 0.000 description 2
- 230000001902 propagating effect Effects 0.000 description 2
- 229920000742 Cotton Polymers 0.000 description 1
- 229920005830 Polyurethane Foam Polymers 0.000 description 1
- 238000013459 approach Methods 0.000 description 1
- 230000000052 comparative effect Effects 0.000 description 1
- 230000008094 contradictory effect Effects 0.000 description 1
- 238000002474 experimental method Methods 0.000 description 1
- 230000002452 interceptive effect Effects 0.000 description 1
- 210000001503 joint Anatomy 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 239000011496 polyurethane foam Substances 0.000 description 1
- 239000011148 porous material Substances 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/0007—Indoor units, e.g. fan coil units
- F24F1/0018—Indoor units, e.g. fan coil units characterised by fans
- F24F1/0025—Cross-flow or tangential fans
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/0007—Indoor units, e.g. fan coil units
- F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
- F24F1/0063—Indoor units, e.g. fan coil units characterised by heat exchangers by the mounting or arrangement of the heat exchangers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
- F24F13/20—Casings or covers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
- F24F13/24—Means for preventing or suppressing noise
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
- F24F13/20—Casings or covers
- F24F2013/205—Mounting a ventilator fan therein
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
- F24F13/24—Means for preventing or suppressing noise
- F24F2013/242—Sound-absorbing material
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Soundproofing, Sound Blocking, And Sound Damping (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The invention discloses a cross-flow wind wheel and an air conditioner indoor unit. The cross flow wind wheel comprises two end plates which are oppositely arranged and impellers connected with the two end plates, wherein the impellers comprise a plurality of sections of sub-impellers which are distributed along the length direction of the cross flow wind wheel, and middle section discs connected with two adjacent sections of sub-impellers. The middle section disc is hollow and is provided with sound absorption cavities, the middle section disc is provided with side plates positioned at two sides of the sound absorption cavities, and at least one side plate is provided with sound absorption holes along the length direction of the cross flow wind wheel; or the middle section disc is solid, and sound absorption holes are formed in the middle section disc in a penetrating manner along the length direction of the through-flow wind wheel. The cross flow wind wheel can reduce noise generated by the work of the cross flow wind wheel.
Description
Technical Field
The invention relates to the field of air conditioner indoor units, in particular to a cross-flow wind wheel and an air conditioner indoor unit.
Background
The indoor unit of the air conditioner is generally provided with a cross-flow wind wheel so as to blow cold air or hot air indoors by utilizing the high-speed rotation of the cross-flow wind wheel. Referring to fig. 1 of the drawings, a conventional through-flow wind 10 'generally includes two end plates 100 and an impeller 200 connecting the two end plates 100, and the impeller 200 includes a plurality of sub-impellers 210 arranged along a length direction of the conventional through-flow wind wheel 10', and a middle ring 230 connecting adjacent two sub-impellers 210. The middle ring 230 is arranged in a ring shape and is only used for connecting two adjacent sub-impellers 210, so that the noise reduction function is not provided. This results in the conventional cross-flow wind wheel 10' being prone to generate loud noise when rotating at high speed, interfering with the life and work of the user, and reducing the use experience of using the indoor unit of the air conditioner.
Disclosure of Invention
The invention mainly aims to provide a cross-flow wind wheel, which aims to reduce noise generated by the work of the cross-flow wind wheel.
In order to achieve the above purpose, the invention provides a cross-flow wind wheel, which comprises two end plates oppositely arranged and an impeller connected with the two end plates, wherein the impeller comprises a plurality of sections of sub-impellers distributed along the length direction of the cross-flow wind wheel, and a middle section of disc connected with two adjacent sections of the sub-impellers. The middle section disc is hollow and is provided with sound absorption cavities, the middle section disc is provided with side plates positioned at two sides of the sound absorption cavities, and at least one side plate is provided with sound absorption holes along the length direction of the cross flow wind wheel; or the middle section disc is solid, and sound absorption holes are formed in the middle section disc in a penetrating manner along the length direction of the through-flow wind wheel.
Optionally, only one of the side plates is perforated with a plurality of sound absorbing holes, and the thickness of the side plate perforated with the sound absorbing holes is smaller than that of the other side plate.
Optionally, a plurality of sound absorbing holes are formed in each of the two side plates; the sound absorbing cavity is internally provided with a sound insulating plate, the sound insulating plate divides the sound absorbing cavity into two sub-cavities, and the two sub-cavities are respectively communicated with sound absorbing holes on the two side plates.
Optionally, the two side plates are all provided with a plurality of sound absorbing holes in a penetrating way, and the sound absorbing holes on one side plate and the sound absorbing holes on the other side plate are arranged in a staggered way.
Optionally, the thickness of the side plate through which the sound absorbing holes are formed is not less than 0.1mm and not more than 2mm.
Alternatively, the porosity of the side plate through which the sound absorbing holes are formed is not less than 0.1% and not more than 20%.
Optionally, the depth of the sound absorbing cavity in the length direction of the cross flow wind wheel is not less than 1mm and not more than 100mm.
Optionally, the sound absorbing holes are round holes, square holes or strip slits.
Optionally, when the sound-absorbing hole is a circular hole or a square hole, the aperture of the sound-absorbing hole is not less than 0.1mm and not more than 2.5mm; or when the sound absorbing holes are strip slits, the width of the sound absorbing holes is not less than 0.1mm and not more than 2.5mm.
Optionally, the sound absorbing cavity is filled with a sound absorbing material.
Optionally, the end plate is provided with a plurality of sound absorbing holes.
The invention also provides an air conditioner indoor unit which comprises a shell, a heat exchanger and a cross flow wind wheel. Wherein, the casing be equipped with the air intake and with the air outlet of air intake intercommunication. The heat exchanger is mounted in the housing. The cross flow wind wheel is arranged on the air outlet side of the heat exchanger.
The cross flow wind wheel comprises two end plates which are oppositely arranged and impellers connected with the two end plates, wherein the impellers comprise a plurality of sections of sub-impellers which are distributed along the length direction of the cross flow wind wheel, and middle section discs connected with two adjacent sections of sub-impellers. The middle section disc is hollow and is provided with sound absorption cavities, the middle section disc is provided with side plates positioned at two sides of the sound absorption cavities, and at least one side plate is provided with sound absorption holes along the length direction of the cross flow wind wheel; or the middle section plate is solid, and sound absorption holes are formed in the middle section plate along the length direction of the cross flow wind wheel in a penetrating way
Optionally, the air conditioner indoor unit is a wall-mounted air conditioner indoor unit or a floor-mounted air conditioner indoor unit.
According to the technical scheme, the middle section disc is adopted to connect the adjacent two sub-impellers, and the sound-absorbing cavity and/or the sound-absorbing hole are formed in the middle section disc, so that noise generated during operation of the sound-absorbing cavity and/or the sound-absorbing Kong Xishou cross-flow wind wheel is utilized, the noise is further reduced, and noise reduction is achieved. The finer the sound absorption holes on the middle section disc, the larger the sound resistance of the middle section disc, the smaller the sound mass of the middle section disc, and the higher the ratio of the sound resistance to the sound mass of the middle section disc, so that the middle section disc has good high-frequency broadband sound absorption performance. If the resonance frequency of the absorption peak is controlled by the sound absorption cavity of the middle section disc, the middle section disc has high-frequency sound absorption and low-frequency sound absorption performances, and the noise reduction effect is obvious.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings that are required in the embodiments or the description of the prior art will be briefly described, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and other drawings may be obtained according to the structures shown in these drawings without inventive effort for a person skilled in the art.
FIG. 1 is a schematic structural view of a conventional cross-flow wind turbine;
FIG. 2 is a schematic view of an embodiment of a cross-flow rotor according to the present invention;
FIG. 3 is an enlarged view of the portion P 1 of FIG. 2;
FIG. 4 is a front view of the cross flow rotor of FIG. 2;
FIG. 5 is a cross-sectional view of the cross-flow wind turbine of FIG. 4 taken along line A-A;
FIG. 6 is an enlarged view of the portion P 2 of FIG. 5;
FIG. 7 is a cross-sectional view of the cross-flow wind turbine of FIG. 4 taken along line B-B;
FIG. 8 is a front view of another embodiment of a cross-flow rotor of the present invention;
FIG. 9 is a cross-sectional view of the cross-flow wind turbine of FIG. 8 taken along line C-C;
FIG. 10 is an enlarged view of the portion P 3 of FIG. 9;
FIG. 11 is a front view of yet another embodiment of a cross-flow rotor of the present invention;
FIG. 12 is a cross-sectional view of the cross-flow rotor of FIG. 11 taken along line D-D;
FIG. 13 is an enlarged view of the portion P 4 of FIG. 12;
FIG. 14 is a schematic view of the sound absorbing chamber of FIG. 13 with baffles disposed therein;
fig. 15 is a graph of air volume versus noise for a cross flow rotor of the present invention versus a conventional cross flow rotor.
Reference numerals illustrate:
The achievement of the objects, functional features and advantages of the present invention will be further described with reference to the accompanying drawings, in conjunction with the embodiments.
Detailed Description
The following description of the embodiments of the present invention will be made clearly and fully with reference to the accompanying drawings, in which it is evident that the embodiments described are only some, but not all embodiments of the invention. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
It should be noted that, if directional indications (such as up, down, left, right, front, and rear … …) are included in the embodiments of the present invention, the directional indications are merely used to explain the relative positional relationship, movement conditions, etc. between the components in a specific posture (as shown in the drawings), and if the specific posture is changed, the directional indications are correspondingly changed.
In addition, the technical solutions of the embodiments may be combined with each other, but it is necessary to base that the technical solutions can be realized by those skilled in the art, and when the technical solutions are contradictory or cannot be realized, the combination of the technical solutions should be considered to be absent and not within the scope of protection claimed in the present invention.
Referring to fig. 2 and 3, in an embodiment of the cross-flow wind wheel 10 of the present invention, the cross-flow wind wheel 10 includes two end plates 100 disposed opposite to each other and an impeller 200 connecting the two end plates 100. Impeller 200 includes a plurality of sub-impellers 210 arranged along the length of cross-flow rotor 10 and a middle section 220 connecting adjacent sub-impellers 210.
Specifically, the end plate 100 is provided with a rotation shaft 110, and the rotation shaft 110 is used for being connected with a motor to drive the rotation shaft 110 to rotate the impeller 200 by the motor. The impeller 200 may include two or more sections of impeller 210, where multiple sections of impeller 210 are all arranged in concentric rings, and two adjacent sections of impeller 210 are separated by a middle section plate 220, so that the inner cavity of each section of impeller 210 is separated from the inner cavities of the other impeller 210. Each of the sub-impellers 210 includes a plurality of blades (see fig. 3 and 7) annularly arranged along the circumference of the cross-flow wind wheel 10, and a blade gap for passing air flow is formed between any two adjacent blades.
When the cross-flow wind wheel 10 works, the impeller 200 rotates at a high speed and drives air flow to enter the inner cavity of the cotyledon wheel 210 from the blade gap at one side of the cotyledon wheel 210, then rotates and extrudes in the inner cavity of the cotyledon wheel 210, and finally is thrown out from the blade gap at the other side of the cotyledon wheel 210, so that the air flow is driven to flow. In this process, the noise generated by each of the cotyledon wheels 210 is blocked by a corresponding one of the intermediate disks 220 while propagating along the axial direction thereof.
In view of this, a sound deadening structure may be provided on the middle panel 220 to improve the effect of the middle panel 220 in absorbing noise. For the middle node 220, the middle node 220 is a circular plate unlike the conventional middle ring 230. The noise reduction structure of the middle panel 220 has two design modes:
referring to fig. 4 to 6, the first design method of the middle panel 220 is as follows: the middle section plate 220 is hollow to form a sound absorbing cavity 2201, the middle section plate 220 is provided with side plates positioned at two sides of the sound absorbing cavity 2201, and at least one side plate is provided with sound absorbing holes 2202 along the length direction of the cross-flow wind wheel 10.
The sound absorbing cavity 2201 is a cavity, and the sound absorbing hole 2202 is a through hole communicating with the sound absorbing cavity 2201. Noise generated during operation of cross-flow wind wheel 10 enters sound absorbing cavity 2201 through sound absorbing hole 2202, and noise sound wave resonates in sound absorbing cavity 2201 and is absorbed. In this process, the sound energy of the noise is gradually reduced, and the noise is gradually absorbed by the sound absorbing holes 2202 and the sound absorbing cavities 2201, thereby reducing the noise and realizing noise reduction.
Referring to fig. 8 to 10, a second design method of the middle panel 220 is as follows: the middle section plate 220 is solid, and the middle section plate 220 is provided with sound absorption holes 2202 along the length direction of the cross-flow wind wheel 10. That is, the sound absorbing cavities 2201 are not necessary, and the sound absorbing holes 2202 directly penetrate through both side surfaces of the middle panel 220. This approach may result in a longer length of the sound-absorbing hole 2202, which may be equivalent to extending the path along which noise propagates within the sound-absorbing hole 2202, and in the process of propagating, the acoustic energy of the noise may also be gradually reduced, thereby achieving noise reduction.
According to the technical scheme, the middle section plate 220 is adopted to connect two adjacent sub-impellers 210, and the sound-absorbing cavity 2201 and/or the sound-absorbing hole 2202 are arranged on the middle section plate 220, so that noise generated when the cross-flow wind wheel 10 works is absorbed by the sound-absorbing cavity 2201 and/or the sound-absorbing hole 2202, and further the noise is reduced, and noise reduction is achieved. The finer the sound absorbing holes 2202 on the middle section plate 220, the larger the acoustic resistance of the middle section plate 220, the smaller the acoustic mass of the middle section plate 220, and the higher the ratio of the acoustic resistance to the acoustic mass of the middle section plate 220, so that the middle section plate 220 has good high-frequency broadband sound absorbing performance. If the resonant frequency of the absorption peak is controlled by the sound absorption cavity 2201 of the middle section plate 220, the middle section plate 220 has both high-frequency sound absorption and low-frequency sound absorption, and the noise reduction effect is remarkable.
As described above, the structure of the middle panel 220 has two design modes, and the design can be correspondingly designed according to the production difficulty and cost in practical application, and the invention is not limited thereto. In order to avoid redundancy, the following embodiments will describe the first design manner in detail, and the second design manner can be executed with reference to the following embodiments.
Referring to fig. 4 to 6, in an embodiment, only one of the side plates is provided with a plurality of sound absorbing holes 2202, and the thickness of the side plate provided with the sound absorbing holes 2202 is smaller than that of the other side plate. For ease of explanation, the two side plates of the node plate 220 in this definition are a first side plate 221 and a second side plate 222, respectively. Wherein, the first side plate 221 is provided with a plurality of sound absorbing holes 2202, and the thickness of the first side plate 221 is smaller than that of the second side plate 222. As shown in fig. 6, H 1 is represented as the thickness of the first side plate 221, and H 2 is represented as the thickness of the second side plate 222.
Specifically, the thickness of the first side plate 221 is smaller than that of the second side plate 222, so that the first side plate 221 forms a sound absorbing microporous sheet. When the noise sound wave resonates in the sound absorbing chamber 2201, the noise reducing microporous sheet resonates, and the noise energy can be further absorbed. When noise enters the sound-absorbing cavity 2201 through the sound-absorbing holes 2202 on the first side plate 221, the sound-absorbing holes 2202 and the sound-absorbing cavity 2201 absorb the noise so that the sound energy thereof is reduced. To reduce this, the thickness of the first side plate 221 is limited to be smaller than that of the second side plate 222, so as to increase the acoustic resistance of the second side plate 222, so that the noise is difficult to penetrate the second side plate 222 and propagate outwards, and the noise reduction efficiency is improved.
Referring to fig. 11 to 13, in another embodiment, the difference from the above embodiment is that: a plurality of sound-absorbing holes 2202 are formed through both the side plates (the first side plate 221 and the second side plate 222), and the sound-absorbing holes 2202 on one side plate and the sound-absorbing holes 2202 on the other side plate are arranged in a staggered manner. That is, the first side plate 221 and the second side plate 222 each have a plurality of sound absorbing holes 2202 formed therethrough. This allows the middle joint plate 220 to simultaneously reduce noise generated by the rotation of the two sub-impellers 210 located at both sides thereof.
Because the sound absorbing holes 2202 on the first side plate 221 are offset from the sound absorbing holes 2202 on the second side plate 222, the noise sound waves passing through the sound absorbing holes 2202 on the first side plate 221 cannot directly penetrate out from the sound absorbing holes 2202 on the second side plate 222, but are blocked by the plate surfaces without the sound absorbing holes 2202 on the second side plate 222, stop at the sound absorbing cavities 2201, and finally are absorbed by the sound absorbing cavities 2201.
Referring to fig. 14, in yet another embodiment, the difference from the above embodiment is that: a plurality of sound absorbing holes 2202 are formed through both the side plates (the first side plate 221 and the second side plate 222); still be equipped with the acoustic celotex board 223 in the sound absorbing cavity 2201, the acoustic celotex board 223 separates the sound absorbing cavity 2201 into two subcavities, two subcavities respectively with the sound absorbing hole 2202 intercommunication on the curb plate.
For ease of illustration, the two subcavities are a first subcavity 2201a and a second subcavity 2201b, respectively, the first subcavity 2201a being connected to the sound absorbing aperture 2202 on the first side plate 221 and the second subcavity 2201b being connected to the sound absorbing aperture 2202 on the second side plate 222. Noise sound waves passing through the sound absorbing holes 2202 on the first side plate 221 enter the first sub-cavity 2201a, and are blocked by the sound insulating plate 223, and the noise is difficult to penetrate through the sound insulating plate 223 and propagate to the other side of the middle panel 220, and finally can only be absorbed by the first sub-cavity 2201 a. Similarly, noise on the other side of the middle panel 220 is absorbed by the second subcavity 2201 b.
Referring to fig. 4 to 6, according to any of the above embodiments, for a side plate through which sound absorbing holes are formed (i.e., a sound absorbing microporous sheet), the relative acoustic impedance of a single sound absorbing hole is related to the thickness of the side plate. The greater the thickness of the side plate, the greater the acoustic impedance, the less the acoustic mass, and the higher the ratio of acoustic resistance to acoustic mass, the better the high frequency broadband sound absorption performance of the middle panel 220. However, the larger the thickness of the side plate, the smaller the volume of the sound absorbing cavity 2201 will be under the condition that the middle section plate 220 is fixed, which is not beneficial to noise reduction.
Thus, as defined herein, the thickness of the side plate (first side plate 221 and/or second side plate 222) through which sound-absorbing apertures 2202 are formed is not less than 0.1mm and not more than 2mm, such as but not limited to: 0.2mm, 0.5mm, 0.8mm, 1.0mm, 1.2mm, 1.5mm, 1.8mm, etc. In this case, the single sound-absorbing hole has a better relative acoustic impedance, thereby improving the acoustic impedance of the whole sound-absorbing microporous sheet and improving the normal incidence sound-absorbing coefficient of the sound-absorbing microporous sheet.
The plate surface of the side plate (first side plate 221 and/or second side plate 222) through which the sound absorbing holes 2202 are formed may be formed as a concave arc surface recessed toward the other side plate. By the arrangement, noise waves can enter the sound absorption cavity 2201 from the sound absorption holes 2202 to be absorbed, the plate surfaces of the side plates are consistent with the streamline of the air flow, wind resistance is reduced, and the air flow in the inner cavity of the sub-impeller 210 is guided outwards from the blade gap.
Theoretically, the finer the sound-absorbing holes 2202 on the sound-absorbing micro-porous plate, the better the high-frequency broadband sound-absorbing performance can be obtained for the middle panel 220. Obviously, the shape and size of the sound-absorbing holes 2202 and the density thereof affect the sound-absorbing efficiency. Here, the sound absorbing holes 2202 may have a circular hole, a square hole, or a slit shape, with respect to the shape of the sound absorbing holes 2202.
When the sound-absorbing holes 2202 are circular holes or square holes, the aperture of the sound-absorbing holes 2202 is not less than 0.1mm and not more than 2.5mm, such as but not limited to: 0.2mm, 0.5mm, 0.8mm, 1.0mm, 1.2mm, 1.5mm, 1.8mm, 2.0mm, 2.2mm, 2.4mm, etc. It should be noted that the aperture of the sound absorbing holes 2202 should be understood herein as a diameter.
When the sound absorbing hole 2202 is a strip-shaped slit, a plurality of the strip-shaped slits may be arranged radially from the center of the side plate to the circumferential direction thereof. At this time, the width of the sound-absorbing hole 2202 is not less than 0.1mm and not more than 2.5mm, such as but not limited to: 0.2mm, 0.5mm, 0.8mm, 1.0mm, 1.2mm, 1.5mm, 1.8mm, 2.0mm, 2.2mm, 2.4mm, etc.
For the density of sound absorbing holes on the sound absorbing microporous plate, the sound absorbing holes 2202 cannot be infinitely increased, otherwise, the dense holes damage the structure of the middle section plate 220, and the noise reduction performance of the middle section plate 220 is reduced. To this end, the effect of the porosity of the middle panel 220 on the noise reduction performance was tested. Tests show that when the porosity of the side plate (the first side plate 221 and/or the second side plate 222) of the middle section plate 220, through which the sound absorbing holes 2202 are formed, is not less than 0.1% and not more than 20%, the sound absorbing holes 2202 on the side plate can be uniformly distributed, and a better interval is maintained, so that the middle section plate 220 has better high-frequency broadband sound absorbing performance, and the structure of the middle section plate 220 is ensured not to be damaged by compact holes.
Thus, based on the above-described test, in the embodiment, the porosity of the side plate defining the through-hole 2202 is not less than 0.1% and not more than 20%, for example, but not limited to: 1%, 2%, 5%, 8%, 10%, 12%, 15%, 18%, 20%, etc.
With continued reference to fig. 4-6, further, in view of the fact that the middle panel 220 further absorbs noise by the sound absorbing cavity 2201, the sound absorbing cavity 2201 can absorb and control the resonance frequency of the absorption peak. The larger the sound absorbing cavity 2201 is, the lower the resonance frequency of the noise wave in the sound absorbing cavity 2201 is, so that the middle section plate 220 has high-frequency sound absorption and low-frequency sound absorption performances, and the sound absorption effect is obvious. However, correspondingly, the larger the sound absorbing cavity 2201 is, the larger the volume of the middle section plate 220 is, and the larger space of the cross-flow wind wheel 10 is occupied, so that the wind volume of the cross-flow wind wheel 10 is reduced.
For this reason, the influence of the depth of the sound absorbing cavity 2201 of the middle panel 220 on the noise reduction performance was tested. As shown in fig. 6, S represents the depth of the sound absorbing cavity 2201 in the longitudinal direction of the cross-flow rotor 10. Experiments show that when the depth of the sound absorption cavity 2201 in the length direction of the cross-flow wind wheel 10 is not less than 1mm and not more than 100mm, the resonance frequency of noise sound waves in the sound absorption cavity 2201 is low, the vertical incidence sound absorption coefficient of the sound absorption microporous sheet is large, and the efficiency of the sound absorption cavity 2201 for absorbing noise is greatly improved. In addition, the volume of the middle section plate 220 is moderate, so that the larger space of the cross-flow wind wheel 10 is not occupied.
Thus, in an embodiment, sound-absorbing cavity 2201 is defined to have a depth of no less than 1mm and no more than 100mm in the length direction of cross-flow rotor 10, such as, but not limited to: 5mm, 10mm, 20mm, 30mm, 40mm, 50mm, 60mm, 70mm, 80mm, 90mm, etc. In order to improve the noise reduction effect, the sound absorbing cavity 2201 may be filled with a sound absorbing material. The sound absorbing material may be, but is not limited to: nano multi-layer structural materials, porous materials, sound absorbing cotton, polyurethane foam, and the like.
In order to verify the noise reduction effect of the cross flow wind wheel, the cross flow wind wheel and the conventional cross flow wind wheel are subjected to a comparison test. In the comparative test, the middle section plate of the cross-flow wind wheel is provided with a sound absorption cavity and a sound absorption hole, and other parameters are respectively as follows: the aperture of the sound-absorbing holes is 0.5mm, the thickness of the sound-absorbing microporous sheet is 0.8mm, the sound-absorbing cavity is 25mm, and the porosity is 0.7%. The cross flow wind wheel and the conventional cross flow wind wheel are tested under the same test condition, and an air quantity-noise comparison chart shown in fig. 15 is drawn according to test data. As can be seen from fig. 15, under the same test conditions, compared with the conventional through-flow wind wheel, the noise of the through-flow wind wheel of the present invention can be reduced by 2.3dBA on average, even up to 3dBA.
Based on any of the above embodiments, in addition to the sound absorbing holes 2202 provided on the middle section plate 220 of the cross-flow wind wheel 10, a plurality of sound absorbing holes 2202 may be provided on the end plate 100 of the cross-flow wind wheel 10, so that the sound absorbing holes 2202 on the end plate 100 can absorb the noise at both ends of the cross-flow wind wheel 10, thereby improving the noise reduction efficiency.
The invention also provides an air conditioner indoor unit which comprises a shell, a heat exchanger and a cross-flow wind wheel 10. Wherein, the casing be equipped with the air intake and with the air outlet of air intake intercommunication. The heat exchanger is mounted in the housing. The cross flow wind wheel 10 is installed on the wind outlet side of the heat exchanger. The specific structure of the cross-flow wind wheel 10 refers to the above embodiment, and because the air conditioner indoor unit adopts all the technical solutions of all the embodiments, the air conditioner indoor unit also has all the beneficial effects brought by the technical solutions of the embodiments, and the description is omitted here.
Optionally, the air conditioner indoor unit is a wall-mounted air conditioner indoor unit or a floor-mounted air conditioner indoor unit.
The foregoing description is only of the preferred embodiments of the present invention and is not intended to limit the scope of the invention, and all equivalent structural changes made by the description of the present invention and the accompanying drawings or direct/indirect application in other related technical fields are included in the scope of the invention.
Claims (13)
1. The cross flow wind wheel is characterized by comprising two end plates which are oppositely arranged, an impeller connected with the two end plates, a plurality of sections of sub-impellers which are distributed along the length direction of the cross flow wind wheel, and a middle section disc connected with two adjacent sections of the sub-impellers; wherein,
The middle section disc is hollow and is provided with sound absorbing cavities, the middle section disc is provided with side plates positioned on two sides of the sound absorbing cavities, at least one side plate is provided with sound absorbing holes communicated with the sound absorbing cavities in a penetrating mode along the length direction of the cross flow wind wheel, and the plate surface of the side plate provided with the sound absorbing holes is provided with a concave arc surface which is sunken towards the other side plate.
2. The cross-flow wind wheel according to claim 1, wherein only one of said side plates is perforated with a plurality of sound absorbing holes, and the thickness of the side plate perforated with sound absorbing holes is smaller than the thickness of the other of said side plates.
3. The cross-flow wind wheel according to claim 1, wherein a plurality of sound absorbing holes are formed in each of the two side plates; the sound absorbing cavity is internally provided with a sound insulating plate, the sound insulating plate divides the sound absorbing cavity into two sub-cavities, and the two sub-cavities are respectively communicated with sound absorbing holes on the two side plates.
4. The cross-flow wind wheel according to claim 1, wherein a plurality of sound absorbing holes are formed in both side plates in a penetrating manner, and the sound absorbing holes in one side plate are arranged in a staggered manner with the sound absorbing holes in the other side plate.
5. A through-flow wind wheel according to any one of claims 1 to 4, wherein the thickness of the side plate through which the sound absorbing holes are formed is not less than 0.1mm and not more than 2mm.
6. A cross flow wind wheel according to any one of claims 1 to 4, wherein the porosity of the side plates through which the sound absorbing holes are formed is not less than 0.1% and not more than 20%.
7. The cross-flow wind wheel according to any one of claims 1 to 4, wherein the sound absorbing cavity has a depth of not less than 1mm and not more than 100mm in a length direction of the cross-flow wind wheel.
8. The cross-flow wind wheel according to any one of claims 1 to 4, wherein the sound absorbing holes are circular holes, square holes, or strip slits.
9. The through-flow wind wheel according to claim 8, wherein when the sound-absorbing hole is a circular hole or a square hole, the aperture of the sound-absorbing hole is not less than 0.1mm and not more than 2.5mm; or when the sound absorbing holes are strip slits, the width of the sound absorbing holes is not less than 0.1mm and not more than 2.5mm.
10. A cross flow wind turbine according to any one of claims 1 to 4, wherein the sound absorbing cavity is filled with sound absorbing material.
11. A cross flow wind turbine according to any one of claims 1 to 4, wherein the end plate is perforated with a plurality of sound absorbing apertures.
12. An air conditioning indoor unit, the air conditioning indoor unit comprising:
the shell is provided with an air inlet and an air outlet communicated with the air inlet;
the heat exchanger is arranged in the shell; and
A cross flow wind wheel according to any one of claims 1 to 11, which is mounted on the wind outlet side of the heat exchanger.
13. The air conditioning indoor unit of claim 12, wherein the air conditioning indoor unit is a wall-mounted air conditioning indoor unit or a floor-mounted air conditioning indoor unit.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201910733572.3A CN110360656B (en) | 2019-08-08 | 2019-08-08 | Cross flow wind wheel and air conditioner indoor unit |
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| CN201910733572.3A CN110360656B (en) | 2019-08-08 | 2019-08-08 | Cross flow wind wheel and air conditioner indoor unit |
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| CN110360656A CN110360656A (en) | 2019-10-22 |
| CN110360656B true CN110360656B (en) | 2024-05-28 |
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| CN210373774U (en) * | 2019-08-08 | 2020-04-21 | 广东美的制冷设备有限公司 | Cross flow wind wheel and air conditioner indoor unit |
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| JPH06137295A (en) * | 1992-10-29 | 1994-05-17 | Daikin Ind Ltd | Cross flow fan |
| JPH11280688A (en) * | 1998-03-31 | 1999-10-15 | Toshiba Corp | Transversal flow fan |
| JP2006329099A (en) * | 2005-05-27 | 2006-12-07 | Daikin Ind Ltd | Cross flow fan |
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| CN110360656A (en) | 2019-10-22 |
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