CN110541842B

CN110541842B - Fan and ducted air conditioner

Info

Publication number: CN110541842B
Application number: CN201810524832.1A
Authority: CN
Inventors: 赵海霞; 项红荧; 范强; 闫茂松; 孙兴朋
Original assignee: Qingdao Haier Smart Technology R&D Co Ltd
Current assignee: Qingdao Haier Smart Technology R&D Co Ltd; Haier Smart Home Co Ltd
Priority date: 2018-05-28
Filing date: 2018-05-28
Publication date: 2021-11-02
Anticipated expiration: 2038-05-28
Also published as: CN110541842A

Abstract

The invention discloses a fan and a duct type air conditioner, and belongs to the technical field of fans. The fan comprises a volute, an impeller and one or more noise reducers, wherein the impeller is arranged between two air inlets on two sides of the volute; each noise reducer comprises an annular shell which is closed and matched with the radial section shape of the volute, a plurality of mutually separated noise reduction cavities which are sequentially arranged along the circumferential direction of the inner circumferential wall of the annular shell are arranged in the annular shell, and each noise reduction cavity is provided with a through hole communicated with the air inlet. The embodiment of the invention solves the problems of complex structure and poor noise reduction effect of the noise reduction assembly adopted when the fan is used for reducing the noise, the fan can reduce the noise of air in the air duct of the volute through the silencing cavities of the noise reducer, and each silencing cavity adopts a structural design similar to a Helmholtz resonator (Helmholtz), so that the transmission of the noise at the air duct of the volute of the fan can be effectively reduced.

Description

Fan and ducted air conditioner

Technical Field

The invention relates to the technical field of fans, in particular to a fan and a duct type air conditioner.

Background

The existing air duct machine indoor unit adopts a centrifugal fan, and the problem of aerodynamic noise such as rotation noise and vortex noise is mainly generated in the operation process of the centrifugal fan, wherein the rotation noise is generated due to the interaction of an asymmetric structure around a blade of an impeller and a circumferentially uneven flow field formed by the rotation of the blade, and the vortex noise is mainly generated due to the fact that a turbulent boundary layer and vortex are split and detached when airflow flows through the blade, and the vortex noise is caused by pressure pulsation on the blade. Whatever the type of noise mentioned above, communication, language, etc. of people in production are obstructed, thus affecting organization and management of production, and seriously damaging physical and mental health of people, thus reducing working efficiency, etc. The noise reduction assembly adopted in the prior art for solving the noise problem of the fan in use is complex in structure and poor in noise reduction effect.

Disclosure of Invention

The invention provides a fan and a ducted air conditioner, and aims to solve the problem of noise generated when the existing fan and a volute are used in a matched mode. The following presents a simplified summary in order to provide a basic understanding of some aspects of the disclosed embodiments. This summary is not an extensive overview and is intended to neither identify key/critical elements nor delineate the scope of such embodiments. Its sole purpose is to present some concepts in a simplified form as a prelude to the more detailed description that is presented later.

According to a first aspect of the embodiments of the present invention, there is provided a fan, including a volute, an impeller disposed between two air inlets on two sides of the volute, and one or more noise reducers disposed in an air duct at the air inlet of the volute; each noise reducer comprises an annular shell which is closed and matched with the radial section shape of the volute, a plurality of mutually separated silencing cavities which are sequentially arranged along the circumferential direction of the inner circumferential wall of the annular shell are arranged in the annular shell, and each silencing cavity is provided with a through hole communicated with the air inlet.

Optionally, each silencing cavity is sector-ring-shaped in cross section.

Optionally, the through hole of each sound-deadening cavity is formed in the inner peripheral wall of the annular housing and faces the center of the annular housing.

Optionally, the through holes of each sound-deadening chamber are arranged equidistantly along the circumferential direction of the inner circumferential wall of the annular housing.

Optionally, two adjacent silencing cavities are separated by a longitudinal partition plate, and each longitudinal partition plate is arranged along the radial direction of the annular shell.

Optionally, a plurality of the longitudinal partition plates are equidistantly arranged along the circumferential direction of the inner circumferential wall of the annular shell.

Optionally, the plurality of noise reducers are sequentially stacked in the air duct along the axial direction of the volute.

Optionally, the annular housing is provided with a wind guiding ring at least on one side.

Optionally, the air guide ring and the noise reducer are of an integrated structure, and the air guide ring is arranged on the circumferential edge of the inner circumferential wall of the annular shell.

According to a second aspect of embodiments of the present invention, there is provided a ducted air conditioner comprising one or more of the above-described blowers.

Optionally, the ducted air conditioner further includes a heat exchanger, and when the fans are multiple, the multiple fans are disposed on the same side of the heat exchanger.

The invention adopts the technical scheme and has the beneficial effects that:

the fan provided by the embodiment of the invention is provided with one or more noise reducers in the volute 1 of the volute, the air entering the fan from the air inlet of the volute can reduce the noise of the air in the air duct of the volute through the noise reduction cavities of the noise reducers, each noise reduction cavity adopts a structural design similar to a Helmholtz resonator (Helmholtz), the transmission of the noise in the volute can be effectively reduced, the noise environment of the fan during use is improved, and the problems of complex structure and poor noise reduction effect of a noise reduction assembly of the fan are solved.

It is to be understood that both the foregoing general description and the following detailed description are exemplary and explanatory only and are not restrictive of the invention, as claimed.

Drawings

The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments consistent with the invention and together with the description, serve to explain the principles of the invention.

FIG. 1 is a schematic diagram of a conventional volute, according to an exemplary embodiment;

FIG. 2 is an exploded view of the blower of the present invention shown in accordance with an exemplary embodiment;

FIG. 3 is a cross-sectional view of a noise reducer of the present invention shown in accordance with an exemplary embodiment;

FIG. 4 is a schematic structural diagram of the ducted air conditioner of the present invention shown in accordance with an exemplary embodiment;

FIG. 5 is an exploded view of a blower according to the present invention shown in accordance with another exemplary embodiment;

FIG. 6 is a schematic diagram of the construction of the sound-attenuating chamber of the present invention, shown in accordance with another exemplary embodiment;

FIG. 7 is an elevation view of the sound-attenuating chamber of the present invention shown in accordance with another exemplary embodiment:

FIG. 8 is a schematic illustration of a ducted air conditioner according to the present invention in accordance with another exemplary embodiment.

Description of reference numerals: 1. a volute; 11. an air inlet; 12. a housing wall; 2. a noise reducer; 21. an annular housing; 22. a sound-deadening chamber; 221. a sound-deadening subchamber; 23. a first through hole; 24. a second through hole; 25. a diaphragm plate; 26. a longitudinal partition plate; 27. a through hole; 281. a first outer wall; 282. a second outer wall; 31. a first receptacle portion; 32. a second receptacle portion; 4. provided is an air duct machine.

Detailed Description

The following description and the drawings sufficiently illustrate specific embodiments of the invention to enable those skilled in the art to practice them. Other embodiments may incorporate structural, logical, electrical, process, and other changes. The examples merely typify possible variations. Individual components and functions are optional unless explicitly required, and the sequence of operations may vary. Portions and features of some embodiments may be included in or substituted for those of others. The scope of embodiments of the invention encompasses the full ambit of the claims, as well as all available equivalents of the claims. Embodiments may be referred to herein, individually or collectively, by the term "invention" merely for convenience and without intending to voluntarily limit the scope of this application to any single invention or inventive concept if more than one is in fact disclosed. Herein, relational terms such as first and second, and the like may be used solely to distinguish one entity or action from another entity or action without requiring or implying any actual such relationship or order between such entities or actions. Also, the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a process, method, or apparatus that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such process, method, or apparatus. Without further limitation, an element defined by the phrase "comprising an … …" does not exclude the presence of other like elements in a process, method or apparatus that comprises the element. The embodiments are described in a progressive manner, each embodiment focuses on differences from other embodiments, and the same and similar parts among the embodiments are referred to each other. As for the methods, products and the like disclosed by the embodiments, the description is simple because the methods correspond to the method parts disclosed by the embodiments, and the related parts can be referred to the method parts for description.

As shown in fig. 1, a volute 1 in the prior art mainly includes an outer wall 12 formed by bending at the outer side and two side walls 13 respectively connected to the outer wall 11, the outer wall 12 and the two side walls 13 together enclose a volute-shaped cylindrical structure, wherein the volute-shaped cylindrical structure has an air duct inside, the cross-sectional area of the air duct gradually increases from the tail end to the head end, and the head end is an air outlet of the air duct; the casing wall 12 encloses a hollow circular space adjacent to the tail end, the hollow circular space can be used as a receiving space for an impeller of the fan, and an annular opening is formed along the circumference of the circular space and is an air inlet of the volute 1.

When the impeller of the fan rotates, fluid such as air and the like can be extracted from two axial sides of the impeller, the fluid flows into the air inlet of the volute 1 along the radial direction, then the fluid flows along the air channel, and finally the fluid is blown out from the air outlet at the head end.

In this embodiment, the flow direction of the fluid in the air duct is defined by the shape of the air duct, which is defined by the bending direction of the volute 1 itself, here, we can define the center line a of the air duct as the set curve of the air duct molding, and the center line is formed by sequentially connecting the center points of each section of the air duct along the extending molding direction thereof; for example, in the air duct shown in fig. 1, the cross section along the direction of extension is rectangular, and the set curve is formed by connecting the intersections of the diagonals of each rectangular cross section.

The line segment composition of the curves of different types of volutes 1 and the curvature of each line segment are different, and are determined according to the design requirements of the actual volutes 1.

Here, the scroll cylindrical structure of the scroll casing 1 includes not only a curved section near the trailing end side but also a straight section near the leading end; here, for convenience of description of the technical solution of the embodiment of the present invention, the center line of the straight pipe section is used as an integral part of the set curve.

The volute 1 provided by the invention is an improvement based on the structure of the conventional volute 1, so that the problem of noise generated when the existing fan is used is solved.

Example one

According to a first aspect of the embodiments of the present invention, another fan is provided, as shown in fig. 2-3, including a volute 1 and an impeller disposed between two air inlets 11 at two sides of the volute 1, and further including one or more noise reducers 2, each noise reducer 2 being disposed in an air duct at an air inlet 11 of the volute 1; each noise reducer 2 comprises an annular shell 21 which is closed and matched with the radial section shape of the volute 1, a plurality of mutually separated silencing cavities 22 which are sequentially arranged along the circumferential direction of the inner circumferential wall of the annular shell 21 are arranged in the annular shell 21, and each silencing cavity 22 is provided with a through hole 27 communicated with the air inlet 11.

In one embodiment of the present invention, the casing of the volute 1 has a volute shape in a radial cross section, where the radial direction is a radial direction of a hollow circular space surrounded by the casing of the volute 1, and the radial direction is parallel to a plane where the set curve is located. Each noise reducer 2 has an annular housing 21, the annular housing 21 is a closed structure and is also designed as a volute with a radial cross-sectional shape adapted to the volute 1, the cross-sectional area of the annular housing 21 is slightly smaller than that of the volute 1, so that the annular housing and the volute 1 can be set in a sleeved manner, a first outer wall 281 of the annular housing 21 abuts against an outer inner wall of the casing wall 12 of the volute 1, and a second outer wall 282 is also enclosed to form a hollow structure adapted to the hollow circular space of the volute 1, and the second outer wall 282 is exposed to the air outlet of the volute 1.

In the present embodiment, a circular hollow space defined by the housing of the scroll casing 1 is defined as a first accommodating portion 3131, and the air inlet is opened along the circumferential direction of the inner circumferential wall of the first accommodating portion 31; the annular housing 21 defines a second accommodating portion 32 with a hollow center, and the second accommodating portion 32 and the first accommodating portion 31 have the same radius and are coaxially arranged. The first accommodating portion 31 is disposed at two axial sides of the accommodating recess, and the second accommodating portion 32 is disposed at an air inlet of the first accommodating portion 31.

Here, a plurality of mutually separated silencing cavities 22 are defined in the annular shell 21 and are sequentially arranged along the set curve direction, and each silencing cavity 22 is provided with a through hole 27 communicated with the air inlet of the volute 1; each silencing cavity 22 is similar to a helmholtz resonator in structure, the through holes 27 are passages for air flowing into the silencing cavity 22, and the silencing cavity 22 can be used as a resonance structure and can absorb noise within a set frequency.

The plurality of sound-deadening chambers 22 are sequentially arranged along the set curve direction, so that the sound-deadening chambers 22 are also arranged around the periphery of the air inlet of the casing of the volute 1, therefore, at least part of air entering the air duct from any radial direction can flow into the sound-deadening chambers 22 corresponding to the radial direction, and the air flowing in along any radial direction can be silenced.

In an alternative embodiment, to improve the sound-damping effect, as shown in fig. 3, the through hole 27 of each sound-damping chamber 22 is disposed on the inner peripheral wall of the second impeller portion 32 and is aligned with the center of the second accommodating portion 32, i.e. the center of the through hole 27 and the corresponding radial direction, so that the through hole 27 can face the air flow flowing in the radial direction, and the sound wave of the air flow can directly enter the sound-damping chamber 22.

Alternatively, one or more through holes 27 may be provided for each sound-deadening

chamber

22, and 2 through holes 27 are provided for each sound-deadening chamber 22, the 2 through holes 27 being provided at intervals in the axial direction.

Here, the principle of silencing by silencing chamber 22 is: when the noise sound wave flows to the silencing cavity 22 through the through hole 27, the air in the axial channel of the through hole 27 with a certain thickness vibrates, when the frequency of the sound wave is consistent with the self-vibration frequency of the silencing cavity 22, resonance occurs, the sound wave excites the resonance sound absorption structure to generate vibration, the amplitude is maximized, the sound energy is consumed, and therefore the effect of weakening or even eliminating the noise sound wave can be achieved.

The structural design of different noise reducers 2 is designed and determined according to the frequency of the noise which needs to be absorbed actually, and the aperture, the axial length and the volume of the sound attenuation cavity 22 of the through hole 27 can influence the frequency of the noise which can be eliminated.

Alternatively, the hole diameters of the through holes 27 of the plurality of sound-deadening chambers 22 and the lengths of the axial passages may be the same or different. In the illustrated embodiment, the diameters of the through holes 27 of the plurality of sound-deadening chambers 22 and the lengths of the axial passages may be the same, and the volumes of the plurality of sound-deadening chambers 22 may be changed or not changed in accordance with the direction of the set curve, so that the frequency of the noise corresponding to each sound-deadening chamber 22 may be determined in accordance with the calculation of the resonance frequency of the helmholtz resonator.

Specifically, the resonance frequency of the helmholtz resonator is calculated as follows:

wherein f is₀Is the resonance frequency of the helmholtz resonator, c is the sound velocity, S is the cross-sectional area of the opening, d is the diameter of the opening, l is the length of the opening, and V is the volume of the container.

Here, the cross-sectional area S and the diameter of the through hole 27 of each sound-deadening chamber 22 can be obtained according to the aperture of the air intake, the length l is the length of the circumferential passage of the through hole 27, and V is the volume of the sound-deadening chamber 22, so that the natural frequency of each sound-deadening chamber 22 can be determined separately.

In the present embodiment, since the volumes of the sound-deadening chambers 22 are along the direction of the set curve, and the design mode that the volumes gradually increase from the tail end to the head end is selected, the sound-deadening chambers 22 can be compatible with a wide range of sound wave frequencies, and therefore, the noise reducer 2 of the present invention can eliminate noise in a wide frequency range, thereby greatly improving the universality and compatibility of the noise reducer 2.

Therefore, by adjusting the aperture of the air inlet, the axial length (i.e., the structural wall thickness), the volume of the muffling chamber 22, and other factors, the muffling chamber 22 can be adapted to noise cancellation at different frequencies, and the design parameters of the specific factors are modified accordingly according to actual needs.

Preferably, in an alternative embodiment, the through holes 27 of each sound-deadening chamber 22 are arranged equidistantly in the circumferential direction of the inner circumferential wall of the second accommodating portion 32. The through holes 27 of the plurality of silencing cavities 22 are uniformly distributed on the inner peripheral wall of the second accommodating part 32, so that the radial air inlet directions can be covered, and meanwhile, air flow of the air inlet can uniformly enter the through holes 27 of the silencing cavities 22, and the problem of poor silencing effect caused by overlarge local air volume is solved.

In an alternative embodiment, as shown in fig. 3, the through-holes 27 are circular holes. In other embodiments, the through holes 27 may also be square holes, elliptical holes, diamond holes, etc.

In an alternative embodiment, as shown in fig. 3, two adjacent muffling chambers 22 are separated by a longitudinal partition 26, and two ends of the longitudinal partition 26 are respectively connected to the first outer wall 281 and the second outer wall 282, so as to enclose each muffling chamber 21 into a semi-closed structure that only retains one outward passage of the through hole 27.

Preferably, as shown in fig. 3, each longitudinal partition 26 is arranged along the radial direction of the second housing portion 32;

alternatively, in other embodiments not shown, each longitudinal partition 26 may be disposed in a non-radial direction.

Preferably, the connection ends of the plurality of longitudinal separators 26 to the second accommodating portion 32 are equidistantly arranged in the circumferential direction of the inner circumferential wall of the second accommodating portion 32.

Alternatively, in other embodiments not shown, the plurality of longitudinal partitions 26 may be arranged in a non-equidistant manner.

In an alternative embodiment, a plurality of noise reducers 2 are sequentially stacked in the air duct along an axial direction of the volute 1, which is an axial direction of a hollow circular space enclosed by the housing of the volute 1, and the axial direction is perpendicular to a plane where the set curve is located. The specific number of the noise reducers 2 can be determined according to the axial width of each noise reducer 2 and the axial width of the volute 1, the sum of the axial widths of the noise reducers 2 should be smaller than the axial width of the volute 1, and of course, the influence of factors such as wall thickness and the like should be considered during calculation.

The horizontal and vertical partitions of the diaphragm 25 and the vertical partition 26 mentioned in the first embodiment are named in the view directions of fig. 2 and 3.

According to a second aspect of the second embodiment of the present invention, another ducted air conditioner 4 is provided, which includes one or more of the above-mentioned fans.

In an alternative embodiment, as shown in fig. 4, the ducted air conditioner 4 further includes a heat exchanger, and when there are a plurality of fans, the fans are disposed on the same side of the heat exchanger. The fan sets up the promotion that helps tuber pipe machine's radiating effect in the homonymy of heat exchanger.

Example two

The first aspect of the embodiment of the present invention provides another fan, as shown in fig. 5 to 7, including a volute 1, an impeller disposed between two air inlets 11 at two sides of the volute 1, and one or more noise reducers 2, where each noise reducer 2 is disposed in an air duct at an air inlet 11 of the volute 1; each noise reducer 2 comprises an annular shell 21 which is closed and is matched with the radial section shape of the volute 1, a plurality of mutually separated silencing cavities 22 which are sequentially arranged along the circumferential direction of the inner circumferential wall of the annular shell 21 are arranged in the annular shell 21, and each silencing cavity 22 is provided with a first through hole 23 communicated with the air inlet 11; each sound-deadening cavity 22 is divided into two or more sound-deadening subchambers 221 by one or more transverse partition plates 25 which are arranged at intervals in the direction away from the first through hole 23; each diaphragm 25 is provided with a second through hole 24 communicating with the adjacent silencing sub-cavities 221, and the opening position of the second through hole 23 of each diaphragm 25 is distributed in a staggered manner with the adjacent first through hole 23 or second through hole 24.

In an alternative embodiment, as shown in FIG. 6, each muffling chamber 22 is sector-annular in cross-section. The cross-section of the muffling chamber 22 is formed in a fan-like shape according to the shape of the housing of the noise reducer 2.

In an alternative embodiment, as shown in fig. 7, the first through hole 23 of each sound-deadening chamber 22 is provided on the inner peripheral wall of the annular housing 21 and faces the center of the annular housing 21. That is, the center of the first through hole 23 is aligned with the corresponding radial direction, so that the first through hole 23 can face the air flow flowing in along the radial direction, the sound wave of the air flow can directly enter the sound-deadening chamber 22, and the sound-deadening effect is improved.

The second through hole 24 of each diaphragm 25 is also directed toward the center of the second impeller receiving portion 32.

In an alternative embodiment, as shown in fig. 5, the first through holes 23 of each sound-deadening chamber 22 are arranged equidistantly in the circumferential direction of the inner circumferential wall of the annular housing 21. The through holes of the plurality of silencing cavities 22 are uniformly distributed on the inner peripheral wall of the second impeller accommodating part 32, so that the radial air inlet directions can be covered, and meanwhile, air flow of the air inlet can uniformly enter the first through holes 23 of the silencing cavities 22, and the problem of poor silencing effect caused by overlarge local air volume is solved.

In an alternative embodiment, as shown in fig. 6, the diaphragms 25 are arc-shaped plates, and the diaphragms 25 of each sound-deadening chamber 21 are numbered as a first diaphragm, … … and an nth diaphragm in sequence according to the distance from the first through hole 23 from small to large; all diaphragm plates 25 of the muffling chamber 22, which are numbered identically, are located on the same circumference, and this circumference is coaxial with the second impeller accommodation 32.

Optionally, the diaphragms 25 of the plurality of muffling chambers 22, which are numbered as the first diaphragms 25, are located on the same circumference; the diaphragms 25, numbered as second diaphragms 25, are located on the same circumference.

In an alternative embodiment, two adjacent sound-deadening chambers 22 are separated by a longitudinal partition 26, and each longitudinal partition 26 is arranged along the radial direction of the annular housing 21. The diaphragm 26 is connected at both ends to the first and second

outer walls

281 and 282, respectively, to enclose each muffling chamber 22 in a semi-closed structure that retains only one through-hole for external passage.

Preferably, each longitudinal partition 26 is disposed radially of second wheel receptacle 32.

Preferably, the connection ends of the plurality of vertical partition plates 26 to the second impeller housing portion 32 are equidistantly provided in the circumferential direction of the inner circumferential wall of the second impeller housing portion 32.

In an alternative embodiment, a plurality of noise reducers 2 are sequentially stacked in the air duct in the axial direction of the scroll casing 1. In an alternative embodiment, the noise reducers 2 are stacked in the air duct in sequence along an axial direction of the volute 1, which is an axial direction of a hollow circular space enclosed by the housing of the volute 1, and the axial direction is perpendicular to a plane where the set curve is located. The specific number of the noise reducers 2 may be determined according to the axial width of each noise reducer 2 and the axial width of the housing of the volute 1, the sum of the axial widths of the plurality of noise reducers 2 should be smaller than the axial width of the volute 1, and of course, the influence of factors such as the wall thickness should be considered in the calculation.

In an alternative embodiment, the annular housing 21 is provided with a wind deflector on at least one side. The induced air ring can play the effect of induced air, improves the air inlet efficiency of fan.

Optionally, the induced air ring and the noise reducer 2 are of an integrated structure, and the induced air ring is disposed on a circumferential edge of an inner circumferential wall of the annular housing 21. The integral structure of the air guide ring and the noise reducer 2 is arranged to be beneficial to installation, and the arrangement position of the air guide ring is close to the edge mainly for inducing air to a greater degree.

In the present embodiment, a circular hollow space defined by the housing of the volute casing 1 is defined as a first impeller accommodating portion 31, and the air inlet is opened along the circumferential direction of the inner circumferential wall of the first impeller accommodating portion 31; the annular housing 21 defines a second impeller receptacle 32 with a hollow center, the second impeller receptacle 32 being arranged coaxially with and having the same radius as the first impeller receptacle 31. The first impeller accommodating portion 31 is disposed at two axial sides of the accommodating space, and the second impeller accommodating portion 32 is disposed at an air inlet of the first impeller accommodating portion 31.

Here, a plurality of mutually separated sound-deadening chambers 22 are defined in the annular housing 21, which are sequentially arranged along the aforementioned set curve direction, and each sound-deadening chamber 22 has a first through hole 23 communicated with the air inlet of the scroll casing 1; the structure of each silencing cavity 22 is similar to an F-P cavity, the first through hole 23 is the air inflow of the silencing cavity 22, and the silencing cavity 22 can be used as a resonance structure and can play a role in absorbing noise.

Here, each sound-deadening chamber 22 in the air passage region of the air passage above the set air passage width is partitioned into two or more sound-deadening subchambers 221 by one or more cross partitions 25 spaced apart in the direction away from the first through hole 23. In a specific embodiment, when the width of the tail end portion of the duct is small, the diaphragm 25 is not disposed in the sound-deadening chamber 22 at the tail end; whereas the width of the middle and head end portions is larger, so that the diaphragm 25 is mainly disposed in the sound-deadening chambers 22 of the middle and head ends. The design mainly considers that sound waves need a certain distance length to play a sound wave attenuation effect when being transmitted among the plurality of silencing sub-cavities 221, so that for the silencing cavity 22 in the air channel area below the set air channel width, if the transverse partition plate 25 is arranged, the distance among the plurality of silencing sub-cavities is too small, and the silencing effect cannot be played; when the width of the tail end part of the air duct is not much different from the width of the head end part of the air duct, as shown in fig. 2 of the annular shell 21, the size of each sound-deadening chamber 22 is the same, and the structure of the sound-deadening chamber 22 is as shown in fig. 3 and 4, so that the noise reduction effect of the whole noise reducer can be more uniform.

Each diaphragm 25 is provided with a second through hole 24 communicating with the adjacent silencing sub-cavities 221, and the opening position of the second through hole 24 of each diaphragm 25 is not on the same side as the adjacent first through hole 23 or second through hole 24.

Taking one of the sound-deadening chambers 22 as an example, the sound-deadening chamber 22 is divided into two sound-deadening subchambers 221 by a diaphragm 25, and a first through hole 23 of the sound-deadening chamber is opened in a position of the second outer wall 282 of the annular housing 21 near the left-side longitudinal diaphragm 26, and a second through hole 24 of the sound-deadening chamber 25 is opened in a position of the diaphragm 25 near the right-side longitudinal diaphragm 26.

Taking another sound-deadening chamber 22 as an example, the sound-deadening chamber 22 is divided into three sound-deadening subchambers 221 by two diaphragms 25, and the first through hole 23 is opened in the second outer wall 282 of the annular casing 21 at a position close to the left-side longitudinal partition 26, the second through hole 24 in the diaphragm 25 close to the second outer wall 282 is opened in the diaphragm 25 at a position close to the right-side longitudinal partition 26, and the second through hole 24 in the diaphragm 25 far from the second outer wall 282 is opened in the diaphragm 25 at a position close to the left-side longitudinal partition 26, and so on.

The horizontal and vertical partitions of the diaphragm 25 and the vertical partition 26 mentioned in the second embodiment are named in the view directions of fig. 6 and 7.

Here, the principle of silencing by silencing chamber 22 is: an F-P cavity in the prior art is mainly applied to optical equipment such as a laser and the like and can be used for realizing light interference; both sound and light are in the form of waves, and the F-P cavity actually has the capacity of interfering with the existence of most wave forms; therefore, the silencing cavity of the embodiment of the invention adopts a design similar to an F-P cavity, sound waves can be reflected back and forth in the silencing cavity and the silencing sub-cavity in the silencing cavity after entering the silencing cavity through the first through hole, and the energy of the sound waves is gradually consumed in the reflection process, so that the effects of silencing and reducing noise are realized.

According to a second aspect of the embodiments of the present invention, there is provided a ducted air conditioner 4 including one or more of the above-described blowers.

In an alternative embodiment, as shown in fig. 8, the ducted air conditioner 4 further includes a heat exchanger, and when there are a plurality of fans, the fans are disposed on the same side of the heat exchanger. The fan sets up the promotion that helps tuber pipe machine's radiating effect in the homonymy of heat exchanger.

EXAMPLE III

In the third embodiment, the invention further provides a fan, which includes a volute 1, an impeller arranged between two air inlets 11 at two sides of the volute 1, and one or more noise reducers 2, where the plurality of noise reducers 2 include at least one noise reducer 2 provided in the first embodiment and at least one noise reducer 2 provided in the second embodiment, and the plurality of noise reducers 2 are sequentially stacked in an air duct along an axial direction of the volute 1.

Therefore, the purpose of reducing the noise of the fan can be achieved by utilizing the two noise reducers 2 respectively disclosed in the two embodiments, and the setting number and the overlapping mode of the two noise reducers 2 can be adjusted according to the actual noise reduction requirement.

According to a third aspect of the third embodiment of the present invention, there is provided a ducted air conditioner including one or more of the above-described fans.

It is to be understood that the present invention is not limited to the procedures and structures described above and shown in the drawings, and that various modifications and changes may be made without departing from the scope thereof. The scope of the invention is limited only by the appended claims.

Claims

1. A fan comprises a volute and an impeller arranged between two air inlets on two sides of the volute, and is characterized by further comprising one or more noise reducers, wherein the one or more noise reducers are arranged in an air channel at the air inlet of the volute; each noise reducer comprises an annular shell which is closed and is matched with the radial section shape of the volute, a plurality of mutually-separated silencing cavities which are sequentially arranged along the circumferential direction of the inner circumferential wall of the annular shell are arranged in the annular shell, the volume of the silencing cavities is gradually increased from the tail end to the head end along the circumferential direction of the inner circumferential wall of the annular shell, and each silencing cavity is provided with a through hole communicated with the air inlet; wherein, the through-hole is located the internal perisporium of annular housing, and orientation the centre of a circle of annular housing, the through-hole is followed the circumference equidistance setting of the internal perisporium of annular housing.

2. The fan according to claim 1, wherein adjacent two of the muffling chambers are separated by a longitudinal partition, and each longitudinal partition is arranged along a radial direction of the annular shell.

3. The fan of claim 2 wherein a plurality of the longitudinal partitions are disposed circumferentially equidistant along the inner circumferential wall of the annular housing.

4. The fan according to claim 1, wherein a plurality of the noise reducers are sequentially stacked in the air duct in an axial direction of the scroll.

5. The fan of claim 1, wherein the annular housing is provided with a wind deflector on at least one side.

6. The fan of claim 5, wherein the inducer is integral with the noise reducer, and the inducer is disposed at a circumferential edge of an inner circumferential wall of the annular housing.

7. A ducted air conditioner comprising one or more blowers according to any of claims 1-6.

8. The ducted air conditioner according to claim 7, further comprising a heat exchanger, and when the fan is plural, the plural fans are disposed on the same side of the heat exchanger.