CN117365959A

CN117365959A - Air conditioner, compressor and exhaust silencing structure

Info

Publication number: CN117365959A
Application number: CN202311590942.5A
Authority: CN
Inventors: 刘杨; 武晓昆; 龙忠铿; 张益钦
Original assignee: Gree Electric Appliances Inc of Zhuhai
Current assignee: Gree Electric Appliances Inc of Zhuhai
Priority date: 2023-11-24
Filing date: 2023-11-24
Publication date: 2024-01-09

Abstract

The present disclosure relates to compressors, and particularly to an air conditioner, a compressor, and an exhaust muffler. The exhaust silencing structure comprises an exhaust shell, a first silencing cavity, a second silencing cavity, a first perforation and a second perforation; the exhaust shell is provided with an exhaust inlet and an exhaust outlet which are mutually communicated, an installation cavity channel is arranged between the exhaust inlet and the exhaust outlet, the first silencing cavity and the second silencing cavity are arranged on the periphery of the installation cavity channel and are alternately arranged along the axial direction of the installation cavity channel, the first silencing cavity is communicated with the installation cavity channel through a first perforation, and the second silencing cavity is communicated with the installation cavity channel through a second perforation. The exhaust silencing structure can reduce noise caused by airflow pulsation.

Description

Air conditioner, compressor and exhaust silencing structure

Technical Field

The application relates to the field of compressors, in particular to an air conditioner, a compressor and an exhaust silencing structure.

Background

With the progress of scientific technology, the living standard of people is improved, the variable frequency compressor is favored by people, and higher requirements are put on the performance and noise of the compressor.

Screw compressors are one type of rotary positive displacement compressors that compress and discharge gas by intermeshing two rotors with helical gears. The screw compressor has simple structure, less wearing parts, low exhaust temperature and large pressure ratio, is particularly resistant to liquid and dust compression in gas, and is an oil-injection screw compressor, so that the screw compressor for power technology and refrigeration is rapidly developed at home and abroad.

Due to the periodic communication of air suction and air discharge of the screw compressor, the air flow pulsation of the air discharge cavity is severe, and the attenuation offset of noise in the frequency modulation process of the variable frequency screw compressor aggravates the vibration and noise of the screw compressor.

Disclosure of Invention

The application provides an air conditioner, a compressor and an exhaust silencing structure, so as to reduce noise caused by airflow pulsation of a variable-frequency screw compressor.

In a first aspect, the present application provides an exhaust silencing structure comprising:

the exhaust shell is provided with an exhaust inlet and an exhaust outlet which are communicated with each other, and an installation cavity is arranged between the exhaust inlet and the exhaust outlet;

the first silencing cavity and the second silencing cavity are arranged at the periphery of the mounting cavity channel and are alternately arranged along the axial direction of the mounting cavity channel;

the first perforation and the second perforation, the first perforation intercommunication installation cavity way and first amortization chamber, the second perforation intercommunication installation cavity way and second amortization chamber.

In some embodiments, the first sound attenuation chamber is disposed coaxially with the mounting chamber channel, and the first sound attenuation chamber is radially through the mounting chamber channel;

and/or the second silencing cavity is coaxially arranged with the mounting cavity channel, and the second silencing cavity is radially communicated with the mounting cavity channel;

the air exhaust device further comprises an air exhaust barrel arranged in the mounting cavity, wherein the first through hole penetrates through the barrel wall of the air exhaust barrel, and the second through hole penetrates through the barrel wall of the air exhaust barrel.

In some embodiments, the first sound-deadening chamber and the second sound-deadening chamber are not equal in axial dimension along the mounting channel;

and/or the radial dimension of the first silencing cavity and the second silencing cavity along the mounting cavity channel is unequal.

In some embodiments, the first perforations are uniformly disposed along the axial and/or circumferential direction of the vent;

and/or the second perforations are uniformly arranged along the axial direction and/or the circumferential direction of the exhaust funnel.

In some embodiments, the apertures of the first perforations are not congruent;

and/or the aperture of the second perforation is not congruent.

In some embodiments, the apertures of the first and second perforations are unequal.

In some embodiments, the mounting channels are arranged in parallel with each other in multiple sets, and the exhaust stack, the first sound-deadening chamber, and the second sound-deadening chamber are each arranged in correspondence with the mounting channels.

In some embodiments, the inner wall of the first sound-deadening chamber and/or the second sound-deadening chamber is provided with a sound absorbing hole that absorbs sound waves.

In some embodiments, the inner wall of the first sound-deadening chamber and/or the second sound-deadening chamber is provided with a concave-convex surface that reflects sound waves.

In some embodiments, the mounting channel extends through to one of the exhaust inlet and the exhaust outlet, at the other of which an expansion and sound attenuating structure is provided;

the expansion silencing structure at least comprises a group of expansion silencing cavities for changing the exhaust flow area, and the expansion silencing structure is communicated with the exhaust barrel.

In some embodiments, the expansion silencer structure comprises:

the expansion silencing cavity is arranged on the inner periphery of the exhaust shell and is positioned between the first expansion plate and the second expansion plate;

the first insertion pipe is arranged along the circumferential direction of the first expansion plate and penetrates through and is communicated with two sides of the first expansion plate;

the second intubate sets up along the circumference of second expansion plate, and the second intubate runs through the both sides of intercommunication second expansion plate.

In some embodiments, the first cannula and the second cannula are offset.

In some embodiments, the exhaust housing presents a taper radially tapering from the exhaust inlet to the exhaust outlet near the exhaust outlet end.

In some embodiments, the mounting channel and the exhaust funnel are disposed at one end of the exhaust casing near the exhaust inlet, the expansion silencing structure is disposed at one end of the exhaust casing near the exhaust outlet, and an airflow scattering component for scattering airflow is further disposed between the exhaust funnel and the expansion silencing structure.

In some embodiments, the airflow disruption assembly includes:

the fixed plate is provided with exhaust through holes communicated with two sides of the fixed plate in a penetrating way, and the first end of each exhaust through hole is communicated with the exhaust barrel;

the exhaust cover is arranged on one side of the fixing plate, which is away from the exhaust barrel, and is buckled and communicated with the second end of the exhaust through hole, and a plurality of airflow dispersing holes are formed in the exhaust cover along the circumferential direction.

In a second aspect, the present application provides a compressor comprising a main casing and any one of the above exhaust silencing structures, the exhaust casing being sealingly attached to an exhaust end of the main casing.

In a third aspect, the present application provides an air conditioner, and the compressor is applied.

Compared with the prior art, the technical scheme provided by the embodiment of the application has the following advantages: the exhaust silencing structure is sealed and attached to the main shell of the variable frequency screw compressor through an exhaust shell, a slide valve of the variable frequency screw compressor is connected with an exhaust inlet to support exhaust of the compressor, and the compressor is conveyed to an exhaust pipe of the compressor through an exhaust outlet after flowing through an exhaust barrel arranged in the mounting cavity; when the exhaust gas flows through the mounting cavity, part of the exhaust gas enters the first silencing cavity along the first perforation and enters the second silencing cavity along the second perforation; the first perforation is matched with the mounting cavity and the first silencing cavity to form a first Helmholtz silencer; the second perforation is matched with the mounting cavity and the second silencing cavity to form a second Helmholtz silencer; the multi-band silencing is realized by means of the first Helmholtz silencer and the second Helmholtz silencer, and exhaust noise of the compressor is remarkably reduced. The exhaust silencing structure is not only suitable for variable frequency screw compressors, but also suitable for non-variable frequency compressors and non-screw compressors.

Drawings

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

In order to more clearly illustrate the embodiments of the present application or the technical solutions in the prior art, the drawings that are required to be used in the description of the embodiments or the prior art will be briefly described below, and it will be obvious to those skilled in the art that other drawings can be obtained from these drawings without inventive effort.

One or more embodiments are illustrated by way of example and not limitation in the figures of the accompanying drawings, in which like references indicate similar elements, and in which the figures of the drawings are not to be considered limiting, unless expressly stated otherwise.

Fig. 1 is a front sectional view of a compressor provided in an embodiment of the present application;

FIG. 2 is a top cross-sectional view of a compressor provided in an embodiment of the present application;

FIG. 3 is a pulsating gas flow muffling path of the exhaust muffling structure of FIG. 2;

FIG. 4 is a schematic view of the exhaust stack of FIG. 3;

FIG. 5 is a schematic diagram of the silencing of the first or second silencing chambers in combination with the exhaust stack;

FIG. 6 is a schematic view of the expansion silencer structure of FIG. 3;

FIG. 7 is a schematic view of the airflow disruption assembly of FIG. 3.

Reference numerals illustrate:

10-a main housing; 11-rotor; 20-an exhaust end bearing seat; 30-an exhaust end bearing; 40-slide valve; 50-an exhaust housing; 51-an exhaust inlet; 52-an exhaust outlet; 53-a first sound deadening chamber; 54-a second sound deadening chamber; 55-an expansion sound deadening chamber; 60-exhaust pipe; 61-first perforations; 62-a second perforation; 70-a first expansion plate; 71-a first cannula; 80-a second expansion plate; 81-a second cannula; 90-fixing plates; 91-exhaust hood; 911-gas flow dispersion holes.

Detailed Description

For the purposes of making the objects, technical solutions and advantages of the embodiments of the present application more clear, the technical solutions of the embodiments of the present application will be clearly and completely described below with reference to the drawings in the embodiments of the present application, and it is apparent that the described embodiments are some embodiments of the present application, but not all embodiments. All other embodiments, which can be made by one of ordinary skill in the art without undue burden from the present disclosure, are within the scope of the present application based on the embodiments herein.

The following disclosure provides many different embodiments, or examples, for implementing different structures of the application. In order to simplify the disclosure of the present application, the components and arrangements of specific examples are described below. Of course, they are merely examples and are not intended to limit the present application. Furthermore, the present application may repeat reference numerals and/or letters in the various examples. This repetition is for the purpose of simplicity and clarity and does not in itself dictate a relationship between the various embodiments and/or configurations discussed.

For ease of description, spatially relative terms, such as "inner," "outer," "lower," "upper," "above," "front," "rear," and the like, may be used herein to describe one element's or feature's relative positional relationship or movement to another element's or feature as illustrated in the figures. Such spatially relative terms are intended to encompass different orientations of the device in use or operation in addition to the orientation depicted in the figures. For example, if the device in the figure experiences a position flip or a change in attitude or a change in state of motion, then the indications of these directivities correspondingly change, for example: an element described as "under" or "beneath" another element or feature would then be oriented "over" or "above" the other element or feature. Thus, the example term "below … …" may include both upper and lower orientations. The device may be otherwise oriented (rotated 90 degrees or in other directions) and the spatial relative relationship descriptors used herein interpreted accordingly.

In order to solve the noise problem that the air current pulse of variable frequency screw compressor causes among the prior art, this application provides an air conditioner, compressor and exhaust amortization structure, can show the noise that reduces different frequency channels to reduce compressor impulse exhaust noise. The axial direction or the radial direction defined in the application refer to the rotor of the compressor, the axial direction coincides with or is parallel to the axial direction of the rotor, and the radial direction coincides with or is parallel to the radial direction of the rotor.

The embodiment of the present application provides an exhaust silencing structure, as shown in fig. 1 to 3, including an exhaust housing 50, a first silencing chamber 53, and a second silencing chamber 54. The exhaust housing 50 is generally hollow in structure and has an exhaust inlet 51 and an exhaust outlet 52 that are in communication with each other through its hollow structure. The discharge casing 50 can be sealingly abutted against the main casing 10 of the compressor, i.e. the compression chamber outer casing, to form the outer casing portion of the compressor such that the discharge inlet 51 communicates with the slide valve 40 at the discharge end of the compression chamber. The hollow structure between the exhaust inlet 51 and the exhaust outlet 52 of the exhaust housing 50 includes a hollow installation cavity passage, the first sound deadening chamber 53 communicates with the installation cavity passage through a first perforation 61, and the second sound deadening chamber 54 communicates with the installation cavity passage through a second perforation 62.

The first helmholtz silencer is formed by the first silencing cavity 53, the first perforation 61 and the mounting cavity, the second helmholtz silencer is formed by the second silencing cavity 54, the second perforation 62 and the mounting cavity, and when the exhaust gas of the compression cavity flows through the mounting cavity, noise in different frequency bands is silenced and reduced by the first helmholtz silencer and the second helmholtz silencer, so that broadband noise reduction is realized, and noise caused by airflow pulsation of the compressor is reduced.

In some embodiments, the exhaust silencing structure further includes an exhaust funnel 60, where the first silencing cavity 53 and the second silencing cavity 54 are all communicated with the mounting cavity along the radial direction of the mounting cavity. The exhaust pipe 60 is fixed in the exhaust housing 50 by the mounting channel, and the exhaust pipe 60 has a hollow cylindrical structure, and the axial direction thereof is preferably parallel to the axial direction of the exhaust housing 50. The shape of the exhaust pipe 60 is matched with the shape of the mounting cavity, in other words, if the cross section of the mounting cavity is square, the exhaust pipe 60 is a square pipe matched with the mounting cavity; if the mounting channel is circular in cross-section, the vent cartridge 60 is a circular cartridge that fits into the mounting channel.

The hollow portion of the exhaust housing 50 further includes a first sound deadening chamber 53 and a second sound deadening chamber 54 formed at the outer periphery of the installation chamber passage, the first sound deadening chamber 53 and the second sound deadening chamber 54 being alternately arranged in the axial direction of the installation chamber passage, and the inner periphery of the first sound deadening chamber 53 being communicated with the installation chamber passage. That is, after the exhaust pipe 60 is fixed to the mounting cavity, the outer surface of the exhaust pipe 60 contacts the first sound-deadening cavity 53 and forms a certain seal with the first sound-deadening cavity 53. Similarly, the inner periphery of the second silencing chamber 54 is communicated with the mounting chamber channel, that is, after the exhaust pipe 60 is fixed to the mounting chamber channel, the outer surface of the exhaust pipe 60 contacts with the second silencing chamber 54 and forms a certain seal with the second silencing chamber 54.

At this time, the first through holes 61 and the second through holes 62 correspondingly penetrate through the wall of the exhaust funnel 60, the first through holes 61 and the second through holes 62 are both provided with a plurality of holes, the first through holes 61 are correspondingly provided with the first silencing cavities 53, and the second through holes 62 are correspondingly provided with the second silencing cavities 54. The first perforation 61 serves to communicate the inner circumference of the exhaust pipe 60 with the first sound deadening chamber 53, and the second perforation 62 serves to communicate the inner circumference of the exhaust pipe 60 with the second sound deadening chamber 54. The air flow passage, the first through hole 61 and the first sound deadening chamber 53 of the inner periphery of the exhaust pipe 60 cooperate to form a first helmholtz muffler; the airflow passage in the inner periphery of the exhaust pipe 60, the second through hole 62, and the second sound deadening chamber 54 cooperate to form a second helmholtz muffler. When the compressor discharge gas flows through the discharge tube 60, a small portion of the gas flows through the first perforated holes 61 to the first muffling chamber 53, and a small portion of the gas flows through the second perforated holes 62 to the second muffling chamber 54. The helmholtz resonance sound absorption/noise elimination principle is utilized to reduce noise of exhaust gas of the compressor, and noise in different frequency bands is eliminated.

The above-described structure for sealing the first sound-deadening chamber 53 or the second sound-deadening chamber 54 is not limited to the one set of the exhaust pipe 60, and two sets of the exhaust pipes 60 may be provided to seal the first sound-deadening chamber 53 and the second sound-deadening chamber 54, respectively, and the first through hole 61 and the second through hole 62 may be provided in different exhaust pipes, respectively. Of course, the structure for sealing the first sound-deadening chamber 53 and the second sound-deadening chamber 54 is not limited to a complete cylindrical structure, and a spliced bush structure may be adopted, and the first through hole 61 and the second through hole 62 may be formed in corresponding bush structures.

The helmholtz silencer can effectively suppress noise with a specific frequency, and the structure and the silencing principle of the helmholtz silencer formed by the first perforation 61, the second perforation 62, the first silencing chamber 53 and the second silencing chamber 54 in combination with the exhaust pipe 60 can be seen in fig. 5. The helmholtz silencer consists of a main pipeline, a neck and a back cavity, the exhaust funnel 60 forms the main pipeline of the helmholtz silencer, the first perforation 61 and the second perforation 62 which are arranged on the exhaust funnel 60 form the neck of the helmholtz silencer, and the first silencing cavity 53 and the second silencing cavity 54 form the back cavity of the helmholtz silencer. In fig. 5, the letter c indicates the flow rate of the air flow in the main pipe, i.e., the exhaust funnel 60, d indicates the diameter of the neck, i.e., the first perforation 61 or the second perforation 62, L indicates the depth of the neck, i.e., the first perforation 61 or the second perforation 62, and V indicates the volume of the back chamber. The muffling frequency of the helmholtz muffler is related to the flow rate c of the air flow in the main pipe, the diameter d of the neck, the depth L of the neck and the volume V of the back chamber, as well as to the shape of the back chamber.

For the exhaust structure provided in this embodiment, the exhaust pipe 60, the first perforation 61 and the first helmholtz silencer formed by the first silencing cavity 53 are utilized, and for the second helmholtz silencer formed by the exhaust pipe 60, the second perforation 62 and the second silencing cavity 54, noise elimination of different frequency bands by the first helmholtz silencer and the second helmholtz silencer can be ensured only by setting the size difference of the first perforation 61 and the second perforation 62 or setting the shape and the size difference of the first silencing cavity 53 and the second silencing cavity 54. Even if the dimensions of the first perforation 61 and the second perforation 62 are identical, and the shapes and dimensions of the first muffling chamber 53 and the second muffling chamber 54 are identical, since the first muffling chamber 53 and the second muffling chamber 54 are disposed in an axial direction of the installation cavity, the air flow is disturbed when flowing through one set of helmholtz silencers in the exhaust funnel 60, so that the speed of the air flow when flowing through the second set of helmholtz silencers actually changes to some extent, thereby ensuring that the first helmholtz silencers and the second helmholtz silencers mute noises in different frequency bands.

Referring to fig. 2 and 4 in combination, in one embodiment provided herein, the cross section of the mounting channel is circular, the exhaust pipe 60 is a cylindrical shell, the first silencing chamber 53 is located at the periphery of the end of the mounting channel near the exhaust inlet 51, and the second silencing chamber 54 is located at the periphery of the end of the mounting channel near the exhaust outlet 52. The first silencing cavity 53 preferably adopts a circular annular cavity, the second silencing cavity 54 can also adopt a circular annular cavity, the first silencing cavity 53 can be coaxially arranged with the mounting cavity, and the second silencing cavity 54 can be coaxially arranged with the mounting cavity. The first sound deadening chamber 53 is radially penetrated by the mounting chamber channel, and the second sound deadening chamber 54 is radially penetrated by the mounting chamber channel. I.e. the first sound-deadening chamber 53 is in annular communication with the mounting channel and the second sound-deadening chamber 54 is in annular communication with the mounting channel.

In this way, symmetry of the silencing structure formed by the first perforation 61 and the first silencing cavity 53 in the circumferential direction of the exhaust funnel 60 is ensured, airflow is enabled to uniformly enter all parts in the circumferential direction of the first silencing cavity 53 along the radial direction of the exhaust funnel 60, irregular disturbance to airflow in the exhaust funnel 60 is reduced, and meanwhile noise silencing of the first specific frequency band is ensured to be achieved by the first silencing cavity 53. Similarly, the second silencing cavity 54 and the mounting cavity or the coaxial arrangement of the second silencing cavity and the exhaust barrel 60 ensure the symmetry of the silencing structure formed by the second through holes 62 in the axial direction of the exhaust barrel 60 and the second silencing cavity 54, so that the air flow uniformly enters all parts in the circumferential direction of the second silencing cavity 54 along the radial direction of the exhaust barrel 60, irregular disturbance to the air flow in the exhaust barrel 60 is reduced, and meanwhile, the second silencing cavity 54 is ensured to realize noise silencing of a second specific frequency band.

As shown in fig. 1 to 3, in some embodiments, the dimensions of the first sound-deadening chamber 53 and the second sound-deadening chamber 54 in the axial direction of the mounting chamber channel are set to be unequal. Illustratively, the width of the first silencing cavity 53 along the axial direction of the mounting cavity is set to a first size, the width of the second silencing cavity 54 along the axial direction of the mounting cavity is set to a second size, and the second size is set to be larger than the first size, so that the size of the second silencing cavity 54 along the axial direction of the mounting cavity is larger than the first silencing cavity 53, and therefore the silencing frequency band of the second helmholtz silencer formed by the second silencing cavity 54 and the second perforation 62 matched with the exhaust funnel 60 is distinguished from the silencing frequency band of the first helmholtz silencer formed by the first silencing cavity 53 and the first perforation 61 matched with the exhaust funnel 60, and the silencing frequency band of the exhaust silencing structure provided by the embodiment of the application is enlarged.

In addition, the first sound-deadening chamber 53 and the second sound-deadening chamber 54 may also be provided to be unequal in size in the radial direction of the mounting chamber passage. Illustratively, the depth of the first silencing cavity 53 along the radial direction of the mounting cavity is set to a third size, the depth of the second silencing cavity 54 along the radial direction of the mounting cavity is set to a fourth size, and the fourth size is set to be larger than the third size, so that the depth of the second silencing cavity 54 along the radial direction of the mounting cavity is larger than the first silencing cavity 53, and therefore the silencing frequency band of the second helmholtz silencer formed by the second silencing cavity 54 and the second perforation 62 matched with the exhaust funnel 60 is distinguished from the silencing frequency band of the first helmholtz silencer formed by the first silencing cavity 53 and the first perforation 61 matched with the exhaust funnel 60, and the silencing frequency band of the exhaust silencing structure provided by the embodiment of the application is enlarged.

In some embodiments, the first perforations 61 are uniformly formed along the axial direction of the exhaust pipe 60, and the first perforations 61 are also uniformly formed along the circumferential direction of the exhaust pipe 60, that is, the first perforations 61 are uniformly formed along the wall surface of the exhaust pipe 60 corresponding to the area of the first silencing chamber 53. The second perforations 62 are uniformly formed along the axial direction of the exhaust pipe 60, and the second perforations 62 are also uniformly formed along the circumferential direction of the exhaust pipe 60, that is, the second perforations 62 are uniformly formed along the surface of the wall of the exhaust pipe 60 corresponding to the area of the second silencing chamber 54. The first perforation 61 and the second perforation 62 are uniformly arranged, so that the first silencing cavity 53 is matched with the corresponding exhaust tube 60 section and the first perforation 61 to form a plurality of first helmholtz silencers, the second silencing cavity 54 is matched with the corresponding exhaust tube 60 section and the second perforation 62 to form a plurality of second helmholtz silencers, and the noise reduction effect of the exhaust silencing structure is improved. Meanwhile, the arrangement mode that the first perforation 61 and the second perforation 62 are uniformly arranged along the surface of the exhaust funnel 60 improves the symmetry of the exhaust silencing structure, and reduces irregular disturbance to the airflow when the airflow flows through the inner periphery of the exhaust funnel 60.

It is contemplated that the sound attenuation and noise reduction band of a helmholtz silencer is related not only to the shape and size of the back cavity, but also to the size of the neck, such as the diameter of the neck. The exhaust silencing structure provided by one embodiment of the present application sets the diameters of the first perforation 61 and the second perforation 62 to be unequal, thereby expanding the silencing frequency band of the helmholtz silencer. If the diameter of the second perforation 62 is set to be larger than or equal to the diameter of the first perforation 61, other dimensions of the first helmholtz silencer and the second helmholtz silencer may be kept the same or different as required, eventually making the silencing frequency bands of the first helmholtz silencer and the second helmholtz silencer different.

Further, the first plurality of perforations 61 may also be sized not all the same and the second plurality of perforations 62 may be sized not all the same. Illustratively, the first perforations 61 and the second perforations 62 are uniformly distributed along the axial direction and the circumferential direction of the exhaust funnel 60, the diameters of the first perforations 61 located on the same circumference of the exhaust funnel 60 are set to be equal, and the diameters of the first perforations 61 in the same row along the axial direction of the exhaust funnel 60 may be set to be gradually increased from the end of the exhaust funnel 60 near the exhaust inlet 51 to the end of the exhaust funnel 60 near the exhaust outlet 52. Similarly, the diameters of the plurality of second perforations 62 located on the same circumference of the exhaust funnel 60 may be set to be equal, and the diameters of the same row of first perforations 61 in the axial direction of the exhaust funnel 60 may be set to be gradually increased from the end of the exhaust funnel 60 near the exhaust inlet 51 to the end of the exhaust funnel 60 near the exhaust outlet 52.

While setting the maximum diameter of the first perforation 61 smaller than the minimum diameter of the second perforation 62; or the maximum diameter of the first perforation 61 is smaller than the maximum diameter of the second perforation 62, the minimum diameter of the first perforation 61 is smaller than the minimum diameter of the second perforation 62, the sizes of the first perforation 61 are differently arranged along the axial direction of the exhaust tube 60, so that the silencing frequency ranges of a plurality of formed first Helmholtz silencers are different, and the silencing frequency ranges of the first Helmholtz silencers formed by the cooperation of the first perforation 61 are increased; the silencing frequency bands of the second Helmholtz silencers are different, and the silencing frequency bands of the second Helmholtz silencers formed by the cooperation of the second perforations 62 are increased, so that the total silencing frequency band of the exhaust silencing structure is increased.

The above-described embodiment adjusts the muffling frequency band of the exhaust muffling structure only from the diameter differential setting of the first perforation 61 and the second perforation 62, that is, adjusts the corresponding muffling frequency band by adjusting the diameter of the neck portion of the helmholtz muffler. In specific implementation, the length/depth of the neck of the helmholtz silencer can be adjusted to adjust the silencing frequency band, that is, the depth of the first perforation 61 and the second perforation 62 along the radial direction of the exhaust funnel 60 is adjusted, at this time, the exhaust funnel 60 does not adopt a uniform-wall-thickness shell, a variable-thickness shell with gradually increased thickness along the axial direction of the exhaust funnel 60 can be adopted, or the exhaust funnel 60 is formed by splicing shells with different thicknesses. The exhaust pipe 60 is formed by splicing a first cylinder shell and a second cylinder shell, wherein the first cylinder shell and the second cylinder shell are all shells with equal wall thickness, and the wall thickness of the second cylinder shell is larger than that of the first cylinder shell. The first silencing cavity 53 may be correspondingly disposed on the outer periphery of the first cylinder shell, and the first through hole 61 is formed in a partial section of the first cylinder shell corresponding to the first silencing cavity 53; the second silencing cavity 54 is correspondingly arranged on the periphery of the second cylinder shell, and the second perforation 62 is formed in a partial section of the second cylinder shell corresponding to the second silencing cavity 54.

With further reference to fig. 2 and 3, in one embodiment provided herein, the mounting channels may be provided with multiple sets, and the exhaust cartridges 60 are disposed in the mounting channels in a one-to-one correspondence. The first and second silencing cavities 53 and 54 are disposed at the outer circumferences of the corresponding mounting channels and are communicated with the mounting channels, and each exhaust pipe 60 is provided with a first perforation 61 for communicating the inner circumference of the exhaust pipe 60 with the first silencing cavity 53 and a second perforation 62 for communicating the inner circumference of the exhaust pipe 60 with the second silencing cavity 54. The drawing illustrates two sets of mounting channels, which are arranged parallel to each other between the exhaust inlet 51 and the exhaust outlet 52 of the exhaust housing 50.

The sizes of the first and second muffling chambers 53 and 54 corresponding to the different exhaust shafts 60 and 60 may be set to be unequal, the sizes of the first and second muffling chambers 53 and 54 corresponding to the same exhaust shaft 60 may be set to be unequal, or the sizes of the different exhaust shafts 60 may be set to be unequal. Meanwhile, the sizes of the first through holes 61 on the different exhaust barrels 60 may also be differently set, the sizes of the second through holes 62 on the different exhaust barrels 60 may be differently set, and the sizes of the first through holes 61 and the second through holes 62 of the same exhaust barrel 60 may be differently set. The arrangement of the plurality of groups of exhaust drums 60 forms a plurality of Helmholtz silencers with different silencing frequency bands, so that the multi-frequency band silencing of noise caused by exhaust pulse is realized.

It will be appreciated that the above-described configuration is equally applicable to more than three sets of mounting channels and exhaust cartridges 60. In addition, in addition to the use of multiple sets of mounting channels in parallel between the exhaust inlet 51 and the exhaust outlet 52 of the exhaust housing 50. The structure that the multiple groups of installation cavity channels are mutually connected in series can also be adopted, the periphery of each installation cavity channel is not limited to the structure of the first silencing cavity 53 and the second silencing cavity 54, and when the axial sizes of the exhaust shell 50 and the installation cavity channels meet the requirements and the silencing frequency bands meet the requirements, a third silencing cavity and even a fourth silencing cavity can be further arranged along the periphery of the installation cavity channel. The exhaust pipe 60 is correspondingly provided with a third perforation which is communicated with the inner periphery of the exhaust pipe 60 and the third silencing cavity, and a fourth perforation which is communicated with the fourth silencing cavity and the inner periphery of the exhaust pipe 60.

In order to improve the noise reduction effect of the first noise reduction cavity 53, the second noise reduction cavity 54 and other noise reduction cavities, in addition to the noise reduction material coated on the inner walls of the first noise reduction cavity 53 and the second noise reduction cavity 54, the embodiment of the application may also set the inner walls of the first noise reduction cavity 53 and the second noise reduction cavity 54 to a porous structure or a concave structure or a sound absorption structure such as a sound absorption wedge structure. By forming sound absorbing holes in the inner walls of the first and second sound absorbing chambers 53 and 54, noise generated by pulsation of the air flow is absorbed. By providing the concave-convex surfaces on the inner walls of the first and second sound-deadening chambers 53 and 54, noise entering the first and second sound-deadening chambers 53 and 54 can be reflected, and sound-deadening and noise reduction can be achieved by mutual interference of sound waves.

In some embodiments, the exhaust silencing structure further includes an expansion silencing structure disposed between the exhaust inlet 51 and the exhaust outlet 52 of the exhaust housing 50, the expansion silencing structure including an expansion silencing chamber 55, and the compressed air flow is consumed in the expansion silencing chamber 55 by diffusion, collision wall reflection and mutual interference by changing the exhaust flow area, and the noise is reduced and discharged into the compressor discharge pipe. Wherein, the installation cavity is arranged at one end of the exhaust shell 50 near the exhaust inlet 51 or the exhaust outlet 52 in a penetrating way, the expansion silencing structure is arranged at the other end of the exhaust shell 50 near the exhaust inlet 51 and the exhaust outlet 52, and the exhaust barrel 60 is communicated through a hollow structure between the exhaust inlet 51 and the exhaust outlet 52 of the exhaust shell 50. The illustrated embodiment of the present application preferably provides the mounting channel and exhaust stack 60 at the end of the exhaust housing 50 adjacent the exhaust inlet 51 and the expansion and sound deadening structure at the end of the exhaust housing 50 adjacent the exhaust outlet 52.

Exhaust gas of a compression cavity of the compressor enters an exhaust inlet 51 of an exhaust shell 50 through a slide valve 40, flows to different mounting cavities and exhaust drums 60 after being split at the exhaust inlet 51, forms a Helmholtz silencer at the position of the exhaust drum 60 through a first silencing cavity 53, a second silencing cavity 54, a first perforation 61 and a second perforation 62 which are matched with the exhaust drum 60 to realize silencing and noise reduction, then flows along a hollow structure of the exhaust shell 50 to one end of an exhaust outlet 52, flows through an expansion silencing structure and an expansion silencing cavity 55 thereof, and is discharged to an exhaust pipe of the compressor from the exhaust outlet 52.

In one embodiment, as shown in fig. 2, 3 and 6, the expansion and noise reducing structure includes a first expansion plate 70 and a second expansion plate 80 fixed in a hollow structure of the exhaust housing 50, and the first expansion plate 70 and the second expansion plate 80 are disposed in parallel with a set gap therebetween. The expansion and noise reduction chamber 55 is formed between the first expansion plate 70 and the second expansion plate 80 and is located at the inner periphery of the exhaust housing 50, wherein the first expansion plate 70 is located at a side of the expansion and noise reduction chamber 55 facing away from the exhaust outlet 52, and the second expansion plate 80 is located at a side of the expansion and noise reduction chamber facing the exhaust outlet 52. The first expansion plate 70 is provided with a plurality of sets of first cannulas 71 in the circumferential direction, and the first cannulas 71 are in penetrating communication with both sides of the first expansion plate 70. The second expansion plate 80 is provided with a plurality of sets of second insertion pipes 81 in the circumferential direction, and the second insertion pipes 81 are connected through both sides of the second expansion plate 80.

Exhaust gas from the compression chamber of the compressor enters the exhaust shell 50, passes through the common silencing action of the exhaust tube 60, the first perforation 61, the second perforation 62, the first silencing chamber 53 and the second silencing chamber 54, enters the silencing expansion chamber from the first insertion tube 71, is diffused, reflected and interfered in the silencing expansion chamber, flows from the second insertion tube 81 on the second expansion plate 80 to the exhaust outlet 52, and finally is discharged through the exhaust outlet 52.

In order to improve the sound attenuation and noise reduction effect of the expansion sound attenuation structure, the first insertion tube 71 and the second insertion tube 81 are preferably arranged in a staggered manner in the embodiment of the present application. Illustratively, the number of first and second cannulas 71, 81 may be set to be unequal such that at least a portion of first and second cannulas 71, 81 are circumferentially offset to enhance the number of reflections and interference effects of the airflow within expansion and sound attenuation chamber 55, avoiding the airflow being expelled directly from first cannula 71 into second cannula 81. In addition, the first cannula 71 and the second cannula 81 may be arranged in a radially offset manner, for example, the axes of the first expansion plate 70 and the second expansion plate 80 are aligned, the circle centers of all the openings for fixing the first cannula 71 on the first circumference in the circumferential direction of the first expansion plate 70, and the circle centers of all the openings for fixing the second cannula 81 on the second circumference in the circumferential direction of the second expansion plate 80 are located on the first circumference, and the diameter of the first circumference is larger than that of the second circumference. In this way, the first cannula 71 is generally distributed on the periphery of the second cannula 81, and meanwhile, the staggered arrangement of the first cannula 71 and the second cannula 81 is realized by combining the differentiated arrangement of the number of the first cannula 71 and the number of the second cannula 81, so that the reflection times of the air flow entering the expansion and noise reduction cavity 55 from the first cannula 71 in the expansion and noise reduction cavity 55 are increased, and the interference and noise reduction effect is increased.

In some embodiments, two or more sets of expansion and noise reduction chambers 55 are provided, for example, two sets are illustrated, and the expansion and noise reduction structure further includes a third expansion plate, wherein the third expansion plate is disposed on one side of the second expansion plate 80 near the exhaust outlet 52, and the third expansion plate and the second expansion plate 80 are disposed with a set gap. The other expansion silencing cavity 55 is formed between the second expansion plate 80 and the third expansion plate, the second expansion plate 80 and the first expansion plate 70 are coaxially arranged, a plurality of third insertion pipes are arranged on the third expansion plate along the circumferential direction, and the third insertion pipes are communicated with two sides of the third expansion plate in a penetrating mode. The third insertion tube is preferably arranged in a staggered manner with the second insertion tube 81, that is, the third insertion tube can be not only staggered with the second insertion tube 81 in the circumferential direction, but also staggered with the second insertion tube 81 in the radial direction, so that the air flow and noise of the expansion silencing cavity 55 between the second expansion plate 80 and the third expansion plate are diffused, reflected and interfered in the expansion cavity as much as possible, and the silencing and noise reducing effects are improved.

The end of the exhaust casing 50 near the exhaust outlet 52 may be configured as a tapered structure, specifically, the radial dimension of the tapered structure is gradually reduced along the direction from the exhaust inlet 51 to the exhaust outlet 52, and the tapered structure at the end of the exhaust casing 50 near the exhaust outlet 52 is convenient for interfacing with the compressor discharge pipe. Correspondingly, the sizes of the first expansion plate 70, the second expansion plate 80 and the third expansion plate are also gradually reduced along the direction from the exhaust inlet 51 to the exhaust outlet 52, and the first insertion tube 71 and the second insertion tube 81 are radially arranged in a staggered manner, so that all the second insertion tubes 81 are positioned at the inner periphery of the axle center connecting line circle of all the first insertion tubes 71; the second cannulas 81 and the third cannulas are radially arranged in a staggered manner, so that all the third cannulas are located at the inner periphery of the axis connecting line circle of all the second cannulas 81.

Referring to fig. 1, 2 and 7, the exhaust silencing structure according to the embodiment of the present application further includes an airflow scattering component disposed between the exhaust pipe 60 and the expansion silencing structure. The mounting cavity and the exhaust tube 60 are disposed at one end of the exhaust housing 50 near the exhaust inlet 51, the expansion silencing structure is disposed at one end of the exhaust housing 50 near the exhaust outlet 52, and the airflow scattering assembly is disposed therebetween and used for scattering the airflow discharged from the exhaust tube 60 along the circumferential direction, so that the airflow uniformly flows to the first insertion tube 71 of the first expansion plate 70 along the circumferential direction, i.e. the airflow scattering assembly plays a role in scattering, carding and consuming the acoustic energy.

In one embodiment, the airflow scattering component may be configured in a structure that the fixing plate 90 is matched with the exhaust hood 91, and the fixing plate 90 is provided with an exhaust through hole in a penetrating manner, and the exhaust through hole is communicated with two sides of the fixing plate 90. The fixing plate 90 is attached to the mounting cavity, so that the first end of the exhaust through hole is communicated with the exhaust barrel 60, and the exhaust cover 91 is fastened and fixed on one side of the fixing plate 90, which is away from the exhaust barrel 60. The exhaust hood 91 is in a closed hood-shaped structure as a whole, a cavity formed between the exhaust hood 91 and the fixing plate 90 is communicated with the second end of the exhaust through hole, a plurality of airflow dispersing holes 911 are formed in a circumferential shell of the exhaust hood 91, and the airflow dispersing holes 911 are preferably uniformly and alternately formed along the circumferential direction of the exhaust hood 91.

The air flow scattering components are arranged in one-to-one correspondence with the exhaust barrels 60, when the exhaust barrels 60 are arranged in two groups, the air flow scattering components are also arranged in two groups, and each group of air flow scattering components is arranged by attaching the fixing plate 90 to the exhaust barrels 60. In this way, the exhaust gas of the compression chamber of the compressor enters the exhaust casing 50 through the slide valve 40, flows into different exhaust drums 60 after being split, flows to the cavity between the fixed plate 90 and the exhaust hood 91 through the exhaust through holes after being subjected to noise elimination and noise reduction through the helmholtz silencer structures formed at the different exhaust drums 60, is uniformly dispersed and conveyed to the first insertion pipe 71 in the circumferential direction of the first expansion plate 70 along the axial direction of the exhaust hood 91 through the airflow dispersing holes 911, enters the expansion noise reduction cavity 55 between the first expansion plate 70 and the second expansion plate 80 through the first insertion pipe 71, is discharged from the second insertion pipe 81 in the circumferential direction of the second expansion plate 80 after being subjected to diffusion, reflection and interference noise elimination and noise reduction, and is finally discharged to the exhaust pipe of the compressor through the exhaust outlet 52 of the exhaust casing 50.

It should be understood that the above-mentioned airflow dispersing assembly is mainly used for dispersing the airflow of the exhaust pipe relatively uniformly along the circumferential direction, so that the exhaust gas of the exhaust pipe 60 can flow to the first insertion pipes 71 at circumferentially different positions of the first expansion plate 70 relatively uniformly, the specific structure is not limited to the structure that the fixing plate 90 fixes the exhaust cover 91, and an inserting structure may be provided at the opening end of the exhaust cover 91, so that the exhaust cover 91 is inserted and fixed in the exhaust pipe 60 through the inserting structure. When the airflow scattering assembly adopts the structure of the fixing plate 90 and the exhaust hood 91, and the exhaust silencing structure is applied to the compressor, the fixing plate 90 may be a bearing seat cover plate of the exhaust end bearing seat 20 of the compressor. The exhaust silencing structure is not only suitable for silencing and noise reduction of the exhaust of the compressor, but also suitable for silencing and noise reduction of the exhaust of other exhaust devices.

The embodiment of the present application also provides a compressor, as shown in fig. 1 and 2, including a main casing 10, a rotor 11, a discharge end bearing 30, a discharge end bearing housing 20, a slide valve 40, and the discharge silencing structure provided by the above embodiment. The main casing 10 is provided with a compressor inlet, a compression chamber is formed inside the main casing 10, an air flow is compressed by rotation of a rotor 11, i.e., a screw, in the compression chamber, the rotor 11 is supported by a discharge end bearing 30, and the discharge end bearing 30 is fixed to a discharge end of the main casing 10 through a discharge end bearing housing 20. The compression chamber is provided with a slide valve 40 at the discharge end, and the discharge amount of the compressor is adjusted by the opening degree of the slide valve 40. The exhaust silencing structure is formed by sealing and attaching an exhaust casing 50 and an exhaust end of a main casing 10, the exhaust casing 50 and the main casing 10 together form a casing part of the compressor, an exhaust inlet 51 of the exhaust casing 50 is communicated with a slide valve 40, and a bearing seat cover plate of an exhaust end bearing seat 20 serves as a fixing plate 90 of an airflow dispersing assembly for fixing an exhaust hood 91. The compressor may be a variable frequency screw compressor, and the exhaust silencing structure is applicable to a non-variable frequency compressor or a non-screw compressor, and other parts of the compressor may be arranged with reference to the prior art.

The embodiment of the application also provides an air conditioner, and the compressor that the embodiment provided is applied to, the air conditioner still includes indoor heat exchanger, outdoor heat exchanger, choke valve, switching-over valve, indoor fan and outdoor fan etc. and the relevant part of air conditioner can consult prior art setting, and this application is mainly to the exhaust structure of air conditioner compressor department improves to reduce compressor exhaust noise.

It is to be understood that the terminology used herein is for the purpose of describing particular example embodiments only, and is not intended to be limiting. As used herein, the singular forms "a", "an" and "the" are intended to include the plural forms as well, unless the context clearly indicates otherwise. The terms "comprises," "comprising," "includes," "including," and "having" are inclusive and therefore specify the presence of stated features, steps, operations, elements, and/or components, but do not preclude the presence or addition of one or more other features, steps, operations, elements, components, and/or groups thereof. The method steps, processes, and operations described herein are not to be construed as necessarily requiring their performance in the particular order described or illustrated, unless an order of performance is explicitly stated. It should also be appreciated that additional or alternative steps may be used.

Although the terms first, second, third, etc. may be used herein to describe various elements, components, regions, layers and/or sections, these elements, components, regions, layers and/or sections should not be limited by these terms. These terms may be only used to distinguish one element, component, region, layer or section from another region, layer or section. Terms such as "first," "second," and other numerical terms when used herein do not imply a sequence or order unless clearly indicated by the context. Thus, a first element, component, region, layer or section discussed below could be termed a second element, component, region, layer or section without departing from the teachings of the example embodiments.

The foregoing is merely a specific embodiment of the application to enable one skilled in the art to understand or practice the application. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the generic principles defined herein may be applied to other embodiments without departing from the spirit or scope of the application. Thus, the present application is not intended to be limited to the embodiments shown herein but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.

Claims

1. An exhaust silencing structure, comprising:

the first silencing cavity and the second silencing cavity are arranged on the periphery of the mounting cavity channel and are arranged in an axial direction of the mounting cavity channel in a mutually-spaced mode;

the first perforation is communicated with the mounting cavity and the first silencing cavity, and the second perforation is communicated with the mounting cavity and the second silencing cavity.

2. The exhaust silencing structure according to claim 1, wherein the first silencing chamber is provided coaxially with the installation chamber passage, and the first silencing chamber is radially penetrated with the installation chamber passage; and/or the second silencing cavity is coaxially arranged with the mounting cavity channel, and the second silencing cavity is radially communicated with the mounting cavity channel;

the air exhaust pipe is arranged in the mounting cavity, the first perforation penetrates through the wall of the air exhaust pipe, and the second perforation penetrates through the wall of the air exhaust pipe.

3. The exhaust silencing structure according to claim 2, wherein the first silencing chamber and the second silencing chamber are unequal in axial dimension along the mounting chamber channel;

and/or the radial dimensions of the first silencing cavity and the second silencing cavity along the mounting cavity channel are different.

4. The exhaust silencing structure according to claim 2, wherein the first perforations are uniformly arranged in an axial direction and/or a circumferential direction of the exhaust funnel;

5. The exhaust silencing structure of claim 2, wherein the apertures of the first perforations are not congruent;

and/or the apertures of the second perforations are not congruent.

6. The exhaust silencing structure of claim 2, wherein the apertures of the first perforations and the second perforations are unequal.

7. The exhaust silencing structure according to claim 2, wherein the installation cavities are arranged in parallel with each other in plural groups, and the exhaust pipe, the first silencing cavity, and the second silencing cavity are each arranged corresponding to the installation cavities.

8. The exhaust silencing structure according to any one of claims 1 to 7, wherein an inner wall of the first silencing chamber and/or the second silencing chamber is provided with a sound absorbing hole that absorbs sound waves.

9. The exhaust silencing structure according to any one of claims 1 to 7, wherein an inner wall of the first silencing chamber and/or the second silencing chamber is provided with a concave-convex surface that reflects sound waves.

10. The exhaust silencing structure according to any one of claims 2 to 7, wherein the mounting channel penetrates to one of the exhaust inlet and the exhaust outlet, at which the expansion silencing structure is provided;

11. The exhaust silencing structure according to claim 10, wherein the expansion silencing structure comprises:

the first insertion pipe is arranged along the circumferential direction of the first expansion plate and is communicated with two sides of the first expansion plate in a penetrating manner;

the second cannula is arranged along the circumferential direction of the second expansion plate, and the second cannula is communicated with the two sides of the second expansion plate in a penetrating mode.

12. The exhaust silencer structure of claim 11, wherein the first and second cannulas are offset.

13. The exhaust silencing structure according to claim 10, wherein an end of the exhaust housing near the exhaust outlet exhibits a tapered shape that tapers radially from the exhaust inlet to the exhaust outlet.

14. The exhaust silencing structure according to claim 11, wherein the mounting channel and the exhaust funnel are disposed at one end of the exhaust housing near the exhaust inlet, the expansion silencing structure is disposed at one end of the exhaust housing near the exhaust outlet, and an airflow scattering component for scattering airflow is further disposed between the exhaust funnel and the expansion silencing structure.

15. The exhaust silencing structure of claim 14, wherein the airflow disruption assembly comprises:

the fixed plate is provided with exhaust through holes communicated with two sides of the fixed plate in a penetrating manner, and the first end of each exhaust through hole is communicated with the exhaust barrel;

the exhaust cover is arranged on one side of the fixing plate, which is away from the exhaust barrel, and is buckled and communicated with the second end of the exhaust through hole, and a plurality of airflow dispersing holes are formed in the circumferential direction of the exhaust cover.

16. A compressor comprising a main housing and the exhaust silencing structure of any of claims 1-15, the exhaust housing sealingly engaging an exhaust end of the main housing.

17. An air conditioner, characterized by applying the compressor of claim 16.