CN113982946B

CN113982946B - Compressor and refrigeration equipment

Info

Publication number: CN113982946B
Application number: CN202111263199.3A
Authority: CN
Inventors: 张肃; 邓志强; 叶容君
Original assignee: Guangdong Meizhi Compressor Co Ltd; Guangdong Meizhi Precision Manufacturing Co Ltd
Current assignee: Guangdong Meizhi Compressor Co Ltd; Guangdong Meizhi Precision Manufacturing Co Ltd
Priority date: 2021-10-28
Filing date: 2021-10-28
Publication date: 2023-02-21
Anticipated expiration: 2041-10-28
Also published as: CN113982946A

Abstract

The invention discloses a compressor and refrigeration equipment, wherein the compressor comprises a compression assembly and a sound absorption structure, and the compression assembly is provided with an exhaust port; the sound absorbing structure is located the compression component outside, the sound absorbing structure is equipped with first passageway and second passageway, the first passageway with the second passageway is crooked passageway, the air inlet of first passageway with the air inlet of second passageway set up side by side and with the gas vent intercommunication, the gas outlet of first passageway with the gas outlet of second passageway sets up side by side, forms the binary channels structure, and the air current is discharged from the gas outlet behind first passageway and second passageway, makes the sound wave of pneumatic noise can produce mutual interference at the gas outlet to consume the energy of sound wave, reduce the noise external radiation, and then reduce the noise of compressor, the noise reduction effect preferred, sound absorbing structure does not shelter from the exhaust of gas vent, and air resistance is less, and is less to compressor performance influence.

Description

Compressor and refrigeration equipment

Technical Field

The invention relates to the technical field of electric appliances, in particular to a compressor and refrigeration equipment.

Background

Both the motor assembly and the compression assembly in the inner cavity of the compressor can generate noise, and particularly, the periphery of a discharge valve plate of the compression assembly has large discharge noise. In the related art, in order to reduce the noise of the medium-high frequency gas flow, a silencer is generally disposed in an inner cavity of the compressor, and the noise is attenuated by the silencer, which may deteriorate the performance of the compressor.

Disclosure of Invention

The present invention is directed to solving at least one of the problems of the prior art. Therefore, the compressor provided by the invention can consume the energy of sound waves, effectively reduce the noise in the compressor, has a good noise reduction effect and does not influence the performance of the compressor.

The invention also provides refrigeration equipment comprising the compressor.

A compressor according to an embodiment of the first aspect of the present invention includes:

a compression assembly provided with an exhaust port;

the sound absorption structure is arranged outside the compression assembly, the sound absorption structure is provided with a first channel and a second channel, the first channel and the second channel are both bending channels, the air inlet of the first channel and the air inlet of the second channel are arranged side by side and communicated with the air outlet, and the air outlet of the first channel and the air outlet of the second channel are arranged side by side.

The compressor provided by the embodiment of the invention has at least the following beneficial effects:

through increase sound absorbing structure in the compressor, sound absorbing structure is provided with first passageway and second passageway, first passageway and second passageway are the crooked passageway, set up the air inlet of first passageway and the air inlet of second passageway side by side, and the gas outlet of first passageway and the gas outlet of second passageway side by side, form the binary channels structure, the exhaust of gas vent can enter into first passageway and second passageway through the air inlet, the air current is discharged from the gas outlet behind first passageway and second passageway, the sound wave that makes aerodynamic noise can produce mutual interference at the gas outlet, thereby consume the energy of sound wave, reduce the noise external radiation, and then reduce the noise of compressor, the noise reduction effect preferred, sound absorbing structure does not shelter from the exhaust of gas vent, the air current resistance is less, it is less to compressor performance influence.

According to some embodiments of the invention, the first channel and the second channel are both helical channels and are arranged side by side.

According to some embodiments of the invention, the sound absorbing structure comprises an annular body provided, in radial sequence from inside to outside, with an inner wall and an outer wall defining between them the first channel and the second channel.

According to some embodiments of the invention, the inner wall defines a third passage along a radially inner side of the annular body, the third passage extending through the sound absorbing structure in an axial direction of the annular body.

According to some embodiments of the invention, a projection area of the sound absorption structure along the axial direction is S, opening areas of the air inlet of the first channel and the air inlet of the second channel are both S1, and S1 is greater than or equal to 0.2S and less than or equal to 0.5S.

According to some embodiments of the invention, an outer contour of a projection plane of the first channel and the second channel in an axial direction of the annular body is circular or elliptical.

According to some embodiments of the invention, the air outlet of the first channel and the air outlet of the second channel are oriented in line with the direction of the air flow of the air outlet.

According to some embodiments of the invention, the number of spiral turns of the first channel and the second channel is n, and n ≧ 3 is satisfied.

According to some embodiments of the invention, the compression assembly comprises a cylinder and bearings, the bearings being provided on both sides of the cylinder in an axial direction, the bearings on either side being provided with the exhaust port, the first passage and the second passage each extending in the axial direction.

The refrigeration equipment according to the second aspect embodiment of the invention comprises the compressor of the first aspect embodiment.

The refrigeration equipment adopts all the technical solutions of the compressor of the above embodiment, and therefore, at least all the advantages brought by the technical solutions of the above embodiments are achieved.

Additional features and advantages of the invention will be set forth in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention.

Drawings

The above and/or additional aspects and advantages of the present invention will become apparent and readily appreciated from the following description of the embodiments, taken in conjunction with the accompanying drawings of which:

fig. 1 is a schematic sectional view of a compressor according to an embodiment of the present invention;

FIG. 2 is a schematic top view of a sound absorbing structure according to an embodiment of the present invention;

FIG. 3 is a cross-sectional perspective view of a sound absorbing structure according to one embodiment of the present invention;

FIG. 4 is a cross-sectional elevation structural schematic view of a sound absorbing structure according to an embodiment of the present invention;

fig. 5 is a comparison graph of the noise reduction effect of the simulation test of the sound absorbing structure according to the embodiment of the present invention.

Reference numerals are as follows:

a compressor 1000;

a housing 100; a cavity 110;

a motor assembly 200; a crankshaft 210;

a compression assembly 300; a cylinder 310; an upper bearing 320; an exhaust port 321; a lower bearing 330;

a sound absorbing structure 400; a body 410; an inner wall 411; an outer wall 412; a first channel 420; a first air inlet 421; a first air outlet 422; a second channel 430; a second air inlet 431; a second outlet 432; a third channel 440.

Detailed Description

Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like reference numerals refer to the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are illustrative only for the purpose of explaining the present invention, and are not to be construed as limiting the present invention.

In the description of the present invention, it is to be understood that the terms upper, lower, etc. indicate orientations or positional relationships based on those shown in the drawings only for convenience in describing the present invention and simplifying the description, but do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus should not be construed as limiting the present invention.

In the description of the present invention, if there are first and second descriptions for distinguishing technical features, they are not interpreted as indicating or implying relative importance or implicitly indicating the number of indicated technical features or implicitly indicating the precedence of the indicated technical features.

In the description of the present invention, it should be noted that the terms such as setting, installing, connecting, etc. should be understood broadly, and those skilled in the art can reasonably determine the specific meaning of the terms in the present invention by combining the specific contents of the technical solutions.

In the description of the present invention, the description of some embodiments, specific embodiments, etc. means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the present invention. In this specification, the schematic representations of the terms used above do not necessarily refer to the same implementation or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.

It can be understood that, during the operation of the compressor, both the internal motor assembly and the compression assembly vibrate to generate noise, and particularly around the discharge valve plate of the compression assembly, the high-speed airflow generated by the discharge generates large aerodynamic noise, and the noise sound waves can radiate outwards through the shell and other components. In order to reduce aerodynamic noise, a silencer is generally disposed in an inner cavity of the compressor, and the silencer is used to attenuate noise, but the silencer easily affects exhaust of the compression assembly, thereby deteriorating performance of the compressor.

In addition, the noise generated by the compressor is mainly medium and low frequency noise, the wavelength of the medium and low frequency noise is relatively long, long wave noise is different from short wave noise, the penetration force of the short wave noise is poor, and the noise can be quickly attenuated along with the distance or encountering an obstacle; the long wave noise has strong penetrating power, that is, the low frequency sound wave has strong propagation penetrating power and high attenuation difficulty, and generally needs a large-mass and large-size structure to attenuate the low frequency sound wave. However, because the volume of the compressor is small, the noise reduction structure with large mass and large size is not suitable for reducing noise of the compressor, and therefore how to effectively reduce noise in a narrow space is a problem to be solved urgently in practical application of the compressor.

According to the embodiment of the invention, the sound absorption structure is additionally arranged in the inner cavity of the compressor, the sound absorption structure is provided with the first channel and the second channel, both the first channel and the second channel are bent channels to form a double-channel structure, exhaust of the exhaust port can enter the first channel and the second channel through the air inlet, air flow is exhausted from the air outlet after passing through the first channel and the second channel, and sound waves of air flow noise can generate mutual interference at the air outlet, so that the energy of the sound waves is consumed, the outward radiation of the noise is reduced, the noise of the compressor is reduced, the noise reduction effect is better, the sound absorption structure does not shield the exhaust of the exhaust port, the air flow resistance is smaller, and the influence on the performance of the compressor is smaller; and the noise reduction problem of a narrow space in the compressor can be effectively solved through the sound absorption structure.

A compressor 1000 according to an embodiment of the present invention is described with reference to fig. 1 to 5, the compressor 1000 being a rotary compressor, and the compressor 1000 will be described below with a specific example.

Referring to fig. 1, a compressor 1000 according to an embodiment of the present invention includes a casing 100, an inner cavity is disposed in the casing 100, a motor assembly 200 and a compression assembly 300 are installed in the inner cavity, the motor assembly 200 is disposed above the compression assembly 300, and the motor assembly 200 is connected to the compression assembly 300 through a crankshaft 210.

Referring to fig. 1, the compression assembly 300 includes a cylinder 310 and two bearings, the two bearings are respectively located at two sides of the cylinder 310 along an axial direction, and define a compression cavity in the cylinder 310, the bearing at the upper end of the cylinder 310 is an upper bearing 320, the bearing at the lower end is a lower bearing 330, a piston is disposed in the cylinder 310, the upper end of the crankshaft 210 is connected with the rotating shaft assembly, the lower end of the crankshaft 210 is connected with the piston, so that the motor assembly 200 drives the piston to rotate in the compression cavity through the crankshaft 210, and the crankshaft 210 is supported through the upper bearing 320 and the lower bearing 330, so that the crankshaft 210 is limited, and the structure is stable and reliable.

Wherein, the upper bearing 320 is provided with an exhaust valve seat, the exhaust valve seat is provided with an exhaust port 321, and exhaust is performed through the exhaust port 321; and a discharge valve sheet and a stopper (not shown in the drawings) are provided on the discharge valve seat, the discharge valve sheet is located between the stopper and the discharge port 321, and the discharge port 321 can be opened or closed by the discharge valve sheet. It can be understood that, during the operation of the compressor 1000, the motor assembly 200 and the compression assembly 300 may vibrate to generate noise, especially, the high-speed airflow generated by the exhaust valve seat during the exhaust may generate large aerodynamic noise, and the exhaust valve sheet may periodically flap the stopper, so that the stopper generates large vibration, and the vibration may be transmitted to the housing 100 of the compressor 1000, etc., so as to radiate noise outwards, resulting in large operation noise of the compressor 1000. Therefore, the sound absorption structure 400 is added in the compressor 1000 according to the embodiment of the present invention, so that an effective noise reduction effect can be achieved.

Referring to fig. 1, specifically, a cavity 110 is formed in the inner cavity of the housing 100 and spaced between the motor assembly 200 and the upper bearing 320, the cavity 110 is communicated with an exhaust port 321, and a high-pressure air flow exhausted along the exhaust port 321 enters the cavity 110. Embodiments of the present invention dispose the sound absorbing structure 400 in the cavity 110, and use the sound absorbing structure 400 to muffle noise sound waves. The sound absorbing structure 400 includes a body 410, a first channel 420 and a second channel 430 are disposed on the body 410, the first channel 420 and the second channel 430 are disposed independently of each other, and the first channel 420 and the second channel 430 are both provided with an air inlet and an air outlet, wherein ports at two ends of the first channel 420 are a first air inlet 421 and a first air outlet 422, and ports at two ends of the second channel 430 are a second air inlet 431 and a second air outlet 432, respectively. It can be appreciated that, as the sound absorbing structure 400 is placed within the cavity 110, the first air inlet 421 and the first air outlet 422 of the first passage 420 are both in communication with the cavity 110, and the second air inlet 431 and the second air outlet 432 of the second passage 430 are both in communication with the cavity 110.

In an embodiment, the first air outlet 422 and the second air outlet 432 are arranged side by side to form a double-channel structure, and the first air inlet 421 and the second air inlet 431 are both close to the air outlet 321, that is, the air outlet 321 is communicated with the first air inlet 421 and the second air inlet 431 through the cavity 110, air flow discharged from the air outlet 321 can enter the first channel 420 and the second channel 430 from the first air inlet 421 and the second air inlet 431 respectively, because the first channel 420 and the second channel 430 are arranged independently, a part of air flow is discharged from the first air outlet 422 after passing through the first channel 420, and a part of air flow is discharged from the second air outlet 432 after passing through the second channel 430.

It should be noted that the first channel 420 and the second channel 430 are both curved channels, that is, the first channel 420 and the second channel 430 are both provided with bending sections, and the number of the bending sections is at least one, for example, the first channel 420 and the second channel 430 may be channels with wave shapes, oval shapes, circular shapes, and the like. The crooked passageway can increase the sound wave and propagate the stroke in sound-absorbing structure 400, be favorable to consuming the energy of sound wave, for straight passageway, the crooked passageway more saves installation space, can set up the multistage section of bending on body 410, can understand, first passageway 420 and second passageway 430 the section of bending are more, it is more effective to the weakening effect of sound wave, can the inside narrow space of make full use of compressor 1000 through sound-absorbing structure 400, effectively promote the sound absorption effect, the problem of making an uproar falls in narrow space can be solved to the realization adoption small-size structure.

It can be understood that the first air inlet 421 and the second air inlet 431 are disposed side by side, so that the incident angles of the air flows of the first channel 420 and the second channel 430 are substantially the same, and the first air outlet 422 and the second air outlet 432 are also disposed side by side, so that the exit angles of the air flows at the air outlets of the first channel 420 and the second channel 430 are substantially the same, and thus after the sound wave of the aerodynamic noise passes through the first channel 420 and the second channel 430, the sound wave at the first air outlet 422 interferes with the sound wave at the second air outlet 432, so that the sound wave is weakened, thereby consuming a part of the energy of the sound wave, achieving the purpose of reducing the noise, reducing the aerodynamic noise caused by high flow velocity, and further facilitating reduction of the overall noise of the compressor 1000.

It should be noted that, the sound absorbing structure 400 adopted in the embodiment is disposed in the cavity 110, the sound absorbing structure 400 does not affect the exhaust of the exhaust port 321, and the resistance of the dual-channel structure to the air flow is small, the influence on the ventilation resistance performance is small, and a good noise reduction effect can be achieved, so that the influence on the performance of the compressor 1000 is reduced.

In some embodiments, a silencer is disposed on the upper bearing 320, the silencer covers the exhaust port 321, and the sound absorption structure 400 may be disposed inside the silencer, so that aerodynamic noise may be effectively reduced by the sound absorption structure 400, and the silencer is combined to perform sound insulation and silencing on noise, thereby further reducing overall noise.

It should be noted that, in some embodiments, the air outlet 321 may be disposed on the lower bearing 330, and at this time, the sound absorbing structure 400 may be disposed on the lower bearing 330, and both the first channel 420 and the second channel 430 extend along the axial direction.

Referring to fig. 2 and 3, in some embodiments, the first channel 420 and the second channel 430 are each arranged in a spiral, and the two channels are arranged side by side to form a double spiral channel structure. It can be understood that the first channel 420 extends spirally along the axial direction of the body 410 to form a spiral channel, the first air inlet 421 faces the air outlet 321, and the first air outlet 422 faces the motor assembly 200; similarly, the second channel 430 extends spirally along the axial direction of the body 410 to form a spiral channel, and the arrangement of the second channel 430 and the first channel 420 side by side can be understood as two spiral channels surrounding together side by side, and the two spiral channels are independent of each other, so that the spiral loops of the first channel 420 and the second channel 430 can be overlapped, and the two channels are tightly matched to form a double-spiral structure. The second air inlet 431 faces the air outlet 321, the second air outlet 432 faces the motor assembly 200, so that the first air inlet 421 and the second air inlet 431 are both located at the bottom end of the body 410, and the first air outlet 422 and the second air outlet 432 are both located at the top end of the body 410.

It can be understood that the air flow can enter the first channel 420 and the second channel 430 through the air inlet, so that the air flow in the two channels can advance along the spiral channel, the structural design is reasonable, the stroke of the air flow can be increased through the double-spiral structure, the purpose of reducing the flow speed is achieved, the sound wave is effectively weakened, and the pneumatic noise is reduced; and the double-helix structure can greatly reduce the space required by the structure, and under the condition of fully utilizing the internal space of the compressor 1000, the problem of noise reduction in the narrow space of the compressor 1000 can be effectively solved, so that the double-helix structure has higher use value.

It should be noted that, referring to fig. 3 and 4, in the embodiment, the first channel 420 and the second channel 430 adopt a side-by-side double-spiral structure, and the cross sections of the two channels are substantially the same, wherein the length of the first channel 420 can be understood as the propagation stroke of the sound wave in the first channel 420, and the length of the second channel 430 can be understood as the propagation stroke of the sound wave in the second channel 430, and the larger the number of spiral loops of the double-spiral structure, the longer the propagation stroke. In the embodiment shown in fig. 2, the number of spiral loops of the first channel 420 and the second channel 430 is n, and n is greater than or equal to 3, that is, the number of spiral loops of the two spiral channels is not less than 3, so that the double-spiral structure has a longer propagation stroke, which is beneficial to improving the noise reduction effect.

It can be understood that when two sound waves with the same frequency, the same vibration direction and the same pace are superposed, an interference phenomenon occurs, and when the phases of the two sound waves are opposite, the superposed amplitude of the two sound waves reduces the sound pressure and weakens the sound pressure, so that the sound waves are weakened. In the embodiment, the lengths of the two spiral channels are set to satisfy that two sound waves can interfere and offset at the air outlet, and are not particularly limited further.

It can be understood that the first air outlet 422 of the first channel 420 and the second air outlet 432 of the second channel 430 are upward along the axial direction and are consistent with the air flow direction of the air outlet 321, after the sound waves pass through the double spiral channel, the sound waves of the two air outlets generate strong interference under the condition that the emitting angles of the first air outlet 422 and the second air outlet 432 are consistent, the sound waves are converted into heat to be dissipated partially, and the aerodynamic noise caused by high flow velocity is reduced, the designed target sound absorption frequency band of the sound absorption structure 400 of the embodiment is distributed in the range of 630Hz to 2000Hz, that is, the sound absorption structure has a better noise reduction effect on the medium frequency noise, and the overall noise energy of the compressor 1000 is reduced by about 2 dB.

Referring to fig. 5, fig. 5 is a comparison diagram of a simulation test noise reduction effect of the sound absorption structure 400 of the embodiment, wherein a solid line curve shown in the drawing is a relation curve of noise and frequency calculated through simulation when the sound absorption structure 400 is not used, and a dashed line curve is a relation curve of noise and frequency calculated through simulation when the sound absorption structure 400 of the double spiral channel of the embodiment is used.

In addition, the sound absorption structure 400 of the embodiment can be understood as a passive sound attenuation structure, the resistance of the double-spiral channel to the air flow is small, the main sound attenuation frequency band is the medium-frequency air flow noise, the sound attenuation bandwidth is wide, a good noise reduction effect can be achieved under the condition that the ventilation resistance performance is not affected, and the influence on the performance of the compressor 1000 is reduced.

Referring to fig. 2 and 3, the body 410 of the sound absorbing structure 400 is annular, a hollow channel is formed at a central position of the annular body 410, the annular body 410 is provided with an inner wall 411 and an outer wall 412 in sequence from inside to outside in a radial direction, a double spiral channel structure is defined between the inner wall 411 and the outer wall 412, that is, the first channel 420 and the second channel 430 both extend spirally around the hollow channel. Between the inner wall 411 and the outer wall 412, the first passage 420 and the second passage 430 are overlapped with each other in the axial direction to form a multi-layered passage.

It can be understood that, as shown in fig. 3 and fig. 4, the channel in the middle of the body 410 is a third channel 440, the third channel 440 is located inside the inner wall 411, and the third channel 440 extends along the axial direction of the body 410, so that the middle of the body 410 forms a hollow structure, and the body 410 is in an annular column shape, so that part of the airflow discharged by the air outlet 321 can pass through the body 410 through the third channel 440, and part of the airflow can advance along the double spiral channel, and the airflow passing resistance is small, so that the sound absorption structure 400 has good ventilation performance, less influence on the ventilation resistance performance, and good sound absorption effect.

In addition, the annular body 410 can match the installation space between the motor assembly 200 and the upper bearing 320 during assembly, and the crankshaft 210 can pass through the third channel 440, so that the sound absorption structure 400 does not affect the installation structure of the motor assembly 200 and the compression assembly 300, the structure is more compact and reliable, the installation is simpler and more convenient, the sound absorption structure 400 can fully utilize the internal space of the compressor 1000, and a better noise reduction effect is realized.

It will be appreciated that, since the first and

second channels

420 and 430 are each a spiral channel, the first and

second channels

420 and 430 have a spiral shape along the axial side wall of the body 410, thereby defining the first and

second channels

420 and 430 by the side wall and the inner and

outer walls

411 and 412. The air inlet and the air outlet are located at two ends of the body 410, openings of the air inlet and the air outlet are defined by adjacent side walls, under the condition that end faces at two ends of the body 410 are planar, the air inlet and the air outlet both have certain opening sizes along the axial direction of the body 410, and the sizes of the air inlet and the air outlet can be adjusted by horizontally extending the side walls at the outermost sides of the two ends of the body 410.

Considering that the sizes of the openings of the first and

second air inlets

421 and 431 affect the air flows into the first and

second passages

420 and 430, the opening areas of the first and

second air inlets

421 and 431 are set within a suitable range in the embodiment, and the resistance to the air flow is reduced. Specifically, the body 410 is annular and columnar, and has a projection surface in the axial direction of the body 410, the projection surface is annular, the projection area is the area of the annular projection surface, the projection area is S, the opening area of the first air inlet 421 and the opening area of the second air inlet 431 are both S1, S1 is equal to or greater than 0.2S and is equal to or less than 0.5S, and when S1=0.5S, the opening areas of the first air inlet 421 and the second air inlet 431 each occupy half of the projection area of the body 410, that is, in the embodiment, the opening areas of the first air inlet 421 and the second air inlet 431 are not greater than half of the projection area, and at the same time, the opening areas of the first air inlet 421 and the second air inlet 431 are not less than 0.2 times of the projection area, so that the first air inlet 421 and the second air inlet 431 have sufficiently large openings.

Referring to fig. 2 and 3, in the embodiment, the body 410 is in a circular ring shape, and the circumferential outer contour of the body 410 is in a circular shape, so that the sound absorbing structure 400 can be conveniently installed in the inner cavity of the casing 100, and the sound absorbing structure can be matched with the inner cavity better and can be installed more reliably. It is understood that the first channel 420 and the second channel 430 are spiral and overlapped, in the axial direction of the body 410, the projection surfaces of the first channel 420 and the second channel 430 are both annular, the outer contour line of the projection surfaces is circular, and the spiral contour lines of the first channel 420 and the second channel 430 are cylindrical spiral lines.

In some embodiments, the projection of the outer contours of the first channel 420 and the second channel 430 may be elliptical, that is, the first channel 420 and the second channel 430 surround the third channel 440 in a spiral shape, and each spiral turn is elliptical, such that the spiral contours of the first channel 420 and the second channel 430 are elliptical-cylindrical-spiral shapes. The spiral loops, which may be elliptical, are not uniformly distributed, for example, the spiral loops near two ends of the body 410 in the axial direction are circular, the spiral loops at the middle position are elliptical, and the spiral structure of different forms is selected according to the actual use requirement, which is not further limited herein.

The embodiments of the present invention have been described in detail with reference to the drawings, but the present invention is not limited to the embodiments, and various changes can be made within the knowledge of those skilled in the art without departing from the gist of the present invention.

Claims

1. A compressor, comprising:

a compression assembly provided with an exhaust port;

2. The compressor of claim 1, wherein the first and second passages are each spiral passages and are arranged side-by-side.

3. The compressor of claim 2, wherein the sound absorbing structure includes an annular body having an inner wall and an outer wall in radial sequence from inside to outside, the inner wall and the outer wall defining the first passage and the second passage therebetween.

4. The compressor of claim 3, wherein the inner wall defines a third passage along a radially inner side of the annular body, the third passage extending axially through the sound absorbing structure in the axial direction of the annular body.

5. The compressor of claim 4, wherein a projection area of the sound absorbing structure along the axial direction is S, opening areas of the air inlet of the first channel and the air inlet of the second channel are S1, and S1 is more than or equal to 0.2S and less than or equal to 0.5S.

6. The compressor of claim 3, wherein the first passage and the second passage are circular or elliptical along an outer contour of a plane of projection of the annular body in the axial direction.

7. The compressor of claim 2, wherein the outlet of the first passage and the outlet of the second passage are oriented in a direction coincident with the direction of gas flow at the discharge port.

8. The compressor as claimed in claim 2, wherein the number of the spiral rings of the first passage and the second passage is n, and n ≧ 3 is satisfied.

9. The compressor of claim 2, wherein the compression assembly includes a cylinder and bearings disposed on opposite sides of the cylinder in an axial direction, the bearings on either side being provided with the exhaust port, the first and second passages each extending in the axial direction.

10. A refrigeration apparatus, characterized by comprising a compressor according to any one of claims 1 to 9.