CN220036934U

CN220036934U - Compressor and air conditioner

Info

Publication number: CN220036934U
Application number: CN202320724603.0U
Authority: CN
Inventors: 郭莉娟; 马英超; 吴允柱
Original assignee: Guangdong Midea Environmental Technologies Co Ltd
Current assignee: Guangdong Midea Environmental Technologies Co Ltd
Priority date: 2023-04-04
Filing date: 2023-04-04
Publication date: 2023-11-17
Anticipated expiration: 2033-04-04

Abstract

An embodiment of the present utility model provides a compressor and an air conditioner, the compressor including: the shell is provided with an air outlet; the compression assembly is arranged in the shell and is provided with a compression cavity and an exhaust port which are communicated with each other; a check valve disposed in the compression assembly, the check valve being movable relative to the compression assembly between a first position and a second position; the resonance structure is arranged on the check valve; wherein, based on the check valve being positioned at the first position, the exhaust port is communicated with the resonance structure and the air outlet; the check valve covers the exhaust port based on the check valve being in the second position. When the compressor exhausts, high-temperature high-pressure gas is discharged through the exhaust port, part of high-temperature high-pressure gas can enter the resonance structure, vibration of air in the resonance structure can be caused, and acoustic energy is consumed in the vibration process, so that exhaust pulsation and exhaust noise generated in the exhaust process of the compressor can be effectively reduced, the overall noise of an air conditioner with the compressor is further reduced, the product quality is improved, and the use experience of a user is improved.

Description

Compressor and air conditioner

Technical Field

The embodiment of the utility model relates to the technical field of compressors, in particular to a compressor and an air conditioner.

Background

At present, the compressor is one of key parts of an air conditioner, and because of the working principle characteristic of the compressor, the noise component is complex, the noise is remarkable in frequency band and the noise control of the compressor directly influences the noise of the whole air conditioner. Specifically, when the compressor is exhausted, the refrigerant enters the top cover through the static disc exhaust port and the back pressure plate and is exhausted through the air outlet on the top cover.

However, the noise of the compressor in the related art is larger during the exhaust, so that the noise of the whole air conditioner is larger, the quality of products is reduced, and the use experience of users is affected.

Disclosure of Invention

Embodiments of the present utility model aim to solve at least one of the technical problems existing in the prior art.

To this end, a first aspect of an embodiment of the present utility model provides a compressor.

A second aspect of an embodiment of the present utility model provides an air conditioner.

In view of this, according to a first aspect of an embodiment of the present utility model, there is provided a compressor including: the shell is provided with an air outlet; the compression assembly is arranged in the shell and is provided with a compression cavity and an exhaust port which are communicated with each other; a check valve disposed in the compression assembly, the check valve being movable relative to the compression assembly between a first position and a second position; the resonance structure is arranged on the check valve; wherein, based on the check valve being positioned at the first position, the exhaust port is communicated with the resonance structure and the air outlet; the check valve covers the exhaust port based on the check valve being in the second position.

The compressor provided by the embodiment of the utility model comprises a shell, a compression assembly, a check valve and a resonance structure, wherein the compression assembly is provided with a compression cavity and an exhaust port, the compression cavity is communicated with the exhaust port, the compression assembly can be understood to comprise a movable disc, a static disc, a crankshaft and a motor, the movable disc and the static disc are enclosed to form the compression cavity, the exhaust port is arranged on the static disc, and the crankshaft is connected with the movable disc and the motor. Specifically, under the drive of the motor, the crankshaft drives the movable disc to rotate relative to the static disc so as to compress the gas in the compression cavity. The compressed high-temperature and high-pressure gas can be discharged through the gas outlet and the gas outlet.

The check valve sets up on compression subassembly, and the check valve can be for compression subassembly motion, and when the check valve moved to the second position, the check valve can the closing cap gas vent, when the compressor shut down, through the check valve closing cap gas vent, can effectively prevent to flow back to the compression intracavity through the gas vent in the high temperature high pressure air flow of compression chamber, and then lead to the problem of compressor reversal.

When the compressor discharges, the high-temperature high-pressure gas pushes the check valve to move away from the discharge port, and when the check valve moves to the first position, the discharge port is opened, and the high-temperature high-pressure gas is discharged from the compression chamber through the discharge port and the gas outlet.

The resonance structure is arranged on the check valve, and when the check valve moves to the first position, the exhaust port is communicated with the resonance structure, that is, when the compressor is exhausted, high-temperature and high-pressure gas is exhausted through the exhaust port, and besides being exhausted through the air outlet, part of high-temperature and high-pressure gas can enter the resonance structure and can cause vibration of air in the resonance structure, and acoustic energy is consumed in the vibration process, so that exhaust pulsation and exhaust noise generated in the exhaust process of the compressor can be effectively reduced, the overall noise of an air conditioner with the compressor is further reduced, the product quality is improved, and the use experience of a user is improved.

It will be appreciated that the resonant structure has a certain muffling frequency, and when the frequency of sound waves generated by the compressor is close to the muffling frequency, the air in the resonant structure will generate larger vibration, so that more sound energy can be consumed, that is, the resonant structure can have a better muffling effect on sound waves close to the frequency.

It should be noted that the resonance structure includes a resonance cavity and a vent, which are connected, that is, the exhaust pulsation and exhaust noise in the exhaust process of the compressor are reduced by utilizing the sound absorption principle of helmholtz resonance. It will be appreciated that different muffling frequencies can be achieved by designing the volume of the resonant cavity, the cross-sectional area of the vent and the axial height of the vent.

Specifically, the formula is:where f is the sound elimination frequency, c is the propagation speed of sound waves in the refrigerant, S is the through-flow sectional area of the vent, L is the axial height of the vent, and V is the volume of the resonant cavity.

In addition, the compressor provided by the technical scheme of the utility model has the following additional technical characteristics:

in one possible embodiment, the resonant structure comprises a resonant cavity and at least one vent, wherein the at least one vent communicates with the resonant cavity.

In the technical scheme, the resonance structure is limited to comprise a resonance cavity and at least one vent, specifically, the at least one vent is communicated with the resonance cavity, namely, exhaust pulsation and exhaust noise generated in the exhaust process of the compressor are reduced by utilizing the Helmholtz resonance principle, so that the overall noise of an air conditioner with the compressor is reduced, the product quality is improved, and the use experience of a user is improved.

It can be understood that when the compressor is exhausted, the high-temperature and high-pressure gas is exhausted from the exhaust port, part of the high-temperature and high-pressure gas enters the at least one air vent, so that the air in the at least one air vent vibrates, and the air in the resonant cavity is equivalent to an air spring which generates restoring force on the vibrating air in the at least one air vent, so that vibration is generated, sound energy is consumed in the process of air vibration in the resonant cavity and air mutual vibration in the at least one air vent, and the purpose of silencing is achieved.

It will be appreciated that different muffling frequencies can be obtained by designing the volume V of the resonant cavity, the through-flow cross-sectional area S of the vent, and the axial height L of the vent. The resonance structure can be designed aiming at sound waves of different frequency bands, so that the optimal silencing effect is achieved.

In one possible embodiment, the number of the air vents is plural, and the plural air vents are disposed at intervals.

In this technical scheme, be equipped with a plurality of air vents on the check valve, and a plurality of air vents interval setting each other, can understand that the quantity of air vents is a plurality of, and the through-flow cross-sectional area of air vent increases promptly, and according to the formula, corresponding noise elimination frequency increases, that is to say, through setting up a plurality of air vents, can improve the noise elimination effect to the sound wave of higher frequency channel, especially the noise reduction effect of intermediate frequency sound wave, and then reduces the noise of the air conditioner complete machine that has this compressor.

In one possible technical solution, the check valve comprises a valve body and a baffle, wherein the baffle is connected with the valve body and encloses with the valve body to form a resonant cavity, and at least one vent is provided in the valve body or the baffle.

In this technical scheme, it includes valve body and baffle to have limited the check valve, specifically, the baffle is connected with the valve body, and the baffle encloses with the valve body and closes and form the resonant cavity, that is to say, the resonant cavity is sealed cavity, at least one vent and resonant cavity intercommunication, open a little mouth at a sealed cavity promptly to utilize the sound absorption principle of helm hertz resonance, effectively reduce the exhaust noise of compressor exhaust in-process, and through designing the size of resonant cavity and at least one vent, can reach the purpose that reduces the medium frequency noise of compressor exhaust in-process, promote the user and experience the air conditioner that has this compressor.

At least one vent can be arranged on the valve body or the baffle plate, and can be specifically arranged according to actual needs.

It is worth mentioning that the at least one vent is arranged towards the exhaust port, in particular, when the at least one vent is arranged on the valve body, the baffle is arranged on the side of the valve body facing away from the exhaust port. When at least one vent is provided in the baffle, the baffle is positioned between the exhaust port and the valve body.

In one possible technical scheme, the sum S of the through-flow cross-sectional areas of the plurality of air vents and the cross-sectional area a of the baffle plate meet the condition that S/a is more than or equal to 0.005 and less than or equal to 0.3.

In this embodiment, the ratio of the sum of the through-flow cross-sectional areas of the plurality of vents to the cross-sectional area of the baffle is between 0.005 and 0.3, i.e., the vent hole penetration rate is defined to be between 0.5% and 30%. Through limiting the perforation rate of the vent to between 0.5 and 30 percent, the exhaust pulsation and exhaust noise generated in the exhaust process of the compressor can be effectively reduced, especially the medium-frequency noise generated in the exhaust process of the compressor can be effectively reduced, the overall noise of the air conditioner with the compressor can be further reduced, the product quality can be improved, and the use experience of a user can be improved.

Furthermore, it will be appreciated that the cross-sectional areas of the flow through the vents are defined according to the formula, and accordingly the muffling frequency range of the resonant structure.

In one possible technical scheme, the diameter d of at least one vent hole is 0.5mm less than or equal to d less than or equal to 5mm; and/or along the axial direction of the valve body, the height L of at least one vent and the height H of the valve body are between 0.1mm and L and H.

In this solution, the diameter of at least one vent is between 0.5mm and 5mm, and according to the formula, the through-flow cross-sectional area S of the vent is defined, correspondingly defining the muffling frequency range of the resonant structure. The diameter of the at least one vent is limited to be between 0.5mm and 5mm, so that exhaust pulsation and exhaust noise generated in the exhaust process of the compressor can be effectively reduced, particularly medium-frequency noise generated in the exhaust process of the compressor can be reduced, and the overall noise of an air conditioner with the compressor can be further reduced.

The height of at least one vent is greater than or equal to 0.1mm and less than or equal to the height of the valve body in the axial direction of the valve body, and according to the formula, the range of the axial height L of the vent is limited, and accordingly the silencing frequency of the resonant structure can be limited. That is, by sizing the at least one vent, discharge pulsation and discharge noise generated during compressor discharge, particularly mid-frequency noise generated during compressor discharge, can be effectively reduced.

In one possible technical scheme, along the axial direction of the valve body, the depth n of the resonant cavity and the height H of the valve body are between 2mm and n and less than or equal to 0.9H.

In this solution, along the axial direction of the valve body, the depth of the resonant cavity is between 2mm and 0.9H, according to the formula, i.e. the range of the volume V of the resonant cavity is defined, and accordingly the muffling frequency of the resonant structure can be defined. That is, by designing the size of the resonant cavity, the discharge pulsation and discharge noise generated in the discharge process of the compressor, particularly the mid-frequency noise generated in the discharge process of the compressor, can be effectively reduced.

In addition, the depth of the resonant cavity is less than or equal to 0.9H, so that the structural strength of the valve body can be ensured, the problem that the check valve is damaged due to long-term use due to the fact that high-temperature and high-pressure gas impacts the check valve when the compressor is exhausted can be prevented, and the service life of the check valve is prolonged.

In one possible technical solution, the thickness b of the baffle plate in the axial direction of the valve body is 0.1 mm.ltoreq.b.ltoreq.5 mm.

In this technical scheme, along the axial direction of valve body, the thickness of baffle is between 0.1mm to 5mm to can ensure the structural strength of baffle.

It will be appreciated that when at least one vent is provided in the baffle, the range of values for the thickness of the baffle, i.e. the range of values for the axial height of the vent, is defined. Therefore, the structure strength of the baffle is ensured while the silencing effect of the exhaust process of the compressor is ensured, the baffle is prevented from being damaged under the impact of high-temperature and high-pressure gas for a long time, and the service life of the baffle is prolonged.

When at least one vent setting is on the valve body, the baffle deviates from the gas vent setting, through limiting the value range of baffle thickness, can guarantee the leakproofness that resonant cavity deviates from vent one end when guaranteeing baffle structural strength.

In one possible technical solution, the valve body comprises a bottom and a side, wherein the side is circumferentially arranged at the bottom and connected with the bottom; at least one vent is provided in the bottom or side.

In this technical solution, it is defined that the valve body comprises a bottom and a side, in particular, the side is arranged on the bottom in the circumferential direction, and the side is connected with the bottom, at least one vent can be arranged on the bottom, also on the side, in particular according to the actual need.

It will be appreciated that the compression assembly further comprises a back pressure plate connected to one side of the stationary plate facing away from the movable plate, the back pressure plate being provided with a mounting cavity, the check valve being disposed within the mounting cavity and being movable within the mounting cavity between a first position and a second position. If the height of the mounting cavity is smaller than the height of the check valve in the axial direction of the compression assembly, i.e. when the check valve is in the first position, a portion of the check valve is exposed to the mounting cavity, at this time at least one vent may be provided at the side of the valve body.

In one possible technical scheme, the resonant cavity is an annular cavity, and D1 is less than or equal to D-2mm between the outer diameter D of the valve body and the outer diameter D1 of the annular cavity.

In the technical scheme, the outer diameter of the resonant cavity is smaller than or equal to the outer diameter of the valve body minus 2mm, that is, the wall thickness of the side part of the valve body positioned in the resonant cavity is required to be larger than or equal to 2mm, that is, the side part of the valve body positioned in the resonant cavity is required to have a certain thickness, so that the structural strength of the valve body is ensured, the check valve is prevented from being damaged under the long-term impact of high-temperature high-pressure airflow, and the service life of the check valve is further prolonged.

In one possible solution, the compressor further comprises a sound absorbing member, which is arranged in the resonance chamber.

In this solution, it is defined that the compressor further comprises a sound absorbing member, in particular arranged in the resonant cavity. Through set up the sound absorbing member in resonant cavity, can further reduce the exhaust noise of compressor exhaust in-process, and then reduce the complete machine noise of the air conditioner that has this compressor, improve product quality, promote user's use experience.

In practical applications, the sound absorbing member may be a sound absorbing material or a wire mesh or the like. The setting can be specifically performed according to actual needs.

In one possible technical scheme, the compression assembly comprises a movable disc, a static disc and a back pressure plate, wherein the static disc is arranged on the movable disc and surrounds the movable disc to form a compression cavity, the static disc is provided with an exhaust port, the back pressure plate is connected with one side of the static disc, which is away from the movable disc, the back pressure plate is provided with an exhaust channel, a mounting cavity and a through hole, the exhaust channel is communicated with the air outlet, the through hole is communicated with the air outlet and the mounting cavity, and the check valve is arranged in the mounting cavity and can move in the mounting cavity; based on the check valve being in the first position, the exhaust port is in communication with the resonating structure and the exhaust channel; the check valve covers the exhaust port based on the check valve being in the second position.

In this technical scheme, it includes movable tray, quiet dish and back of the body clamp plate to inject the compression subassembly, and specifically, quiet dish encloses with the movable tray and closes and form the compression chamber, and it is understood that the compression subassembly still includes bent axle and motor, and the bent axle links to each other with movable tray and motor. Specifically, under the drive of the motor, the crankshaft drives the movable disc to rotate relative to the static disc so as to compress the gas in the compression cavity.

The back pressure plate sets up in the quiet dish one side that deviates from the movable plate, and the back pressure plate is equipped with the exhaust passage, and the one end of exhaust passage can communicate with the gas vent, and the other end and the gas outlet intercommunication of exhaust passage, that is to say, the gas vent passes through exhaust passage and gas outlet intercommunication. When the compressor discharges, the compressed high-temperature and high-pressure gas can be discharged through the exhaust port, the exhaust channel and the air outlet.

The back pressure plate is also provided with a mounting cavity and a through hole which are communicated, the through hole is communicated with the air outlet, the check valve is arranged in the mounting cavity, and the check valve can move between a first position and a second position in the mounting cavity. Specifically, when the compressor is exhausted, the check valve is pushed to move in a direction away from the exhaust port by high-temperature high-pressure gas, when the check valve moves to the first position, the exhaust port is opened, the high-temperature high-pressure gas is exhausted through the exhaust channel and the air outlet, and part of the high-temperature high-pressure gas enters at least one air vent, so that air vibration in the at least one air vent and the resonant cavity is caused, acoustic energy is consumed in the vibration process, and exhaust pulsation and exhaust noise in the compressor exhaust process are reduced.

When the compressor is stopped, the check valve can move towards the direction close to the exhaust port due to gravity, in addition, high-temperature and high-pressure gas exhausted from the air outlet can impact the check valve through the through hole, so that the check valve can rapidly move towards the direction of the exhaust port to cover the exhaust port, and therefore when the compressor is stopped, the high-temperature and high-pressure gas can be effectively prevented from flowing back into the compression cavity through the exhaust port, and the problem of reverse rotation of the compressor is further caused.

In one possible technical solution, the compressor further comprises a check groove, the check groove is arranged on one side of the check valve facing the back pressure plate, and the check groove is communicated with the through hole.

In this technical scheme, it still includes the check groove to have defined the compressor, specifically, the check groove sets up on the one side of check valve orientation back pressure board, and check groove and through-hole intercommunication, when the compressor shut down, the check valve can be to the direction motion that is close to the gas vent because of gravity's reason, in addition, it can strike the check groove of check valve through the through-hole to have not yet reached from the gas outlet exhaust high temperature high pressure gas, make the check valve can be fast to the direction motion of gas vent, in order to seal the lid gas vent, thereby when the compressor shut down, can effectively prevent high temperature high pressure gas back flow to the compression intracavity through the gas vent, and then lead to the problem of compressor reversal.

It can be appreciated that if the baffle is set towards the back pressure plate, the baffle is provided with an avoidance port, and the through hole is communicated with the check groove through the avoidance port.

According to a second aspect of the present utility model, an air conditioner is provided, which includes the compressor provided by any one of the above technical schemes, so that all the beneficial technical effects of the compressor are provided, and the description thereof is omitted.

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

Drawings

The foregoing and/or additional aspects and advantages of the utility model will become apparent and may be better understood from the following description of embodiments taken in conjunction with the accompanying drawings in which:

FIG. 1 illustrates a partial structural schematic view of a compressor according to an embodiment of the present utility model;

FIG. 2 shows an enlarged view of the compressor of the embodiment of FIG. 1 at A;

FIG. 3 shows one of the structural schematic diagrams of the check valve according to one embodiment of the present utility model;

FIG. 4 shows a second schematic structural view of a check valve according to an embodiment of the present utility model;

FIG. 5 shows a third schematic structural view of a check valve according to an embodiment of the present utility model;

FIG. 6 shows a fourth schematic structural view of a check valve according to one embodiment of the present utility model;

FIG. 7 shows a schematic structural view of a valve body according to one embodiment of the utility model;

fig. 8 illustrates a structural schematic view of a compressor according to an embodiment of the present utility model.

The correspondence between the reference numerals and the component names in fig. 1 to 8 is:

100 compressors, 110 casings, 111 air outlets, 120 compression assemblies, 121 compression chambers, 122 air outlets, 123 movable disks, 124 static disks, 125 back pressure plates, 126 air outlet channels, 127 installation chambers, 128 through holes, 130 check valves, 131 valve bodies, 1311 bottoms, 1312 side parts, 132 baffles, 140 resonance structures, 141 resonance chambers, 142 air vents, 150 check grooves, 160 sound absorbers.

Detailed Description

In order that the above-recited objects, features and advantages of the present utility model will be more clearly understood, a more particular description of the utility model will be rendered by reference to the appended drawings and appended detailed description. It should be noted that, without conflict, the embodiments of the present utility model and features in the embodiments may be combined with each other.

In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present utility model, however, the present utility model may be practiced otherwise than as described herein, and therefore the scope of the present utility model is not limited to the specific embodiments disclosed below.

A compressor 100 and an air conditioner provided according to some embodiments of the present utility model are described below with reference to fig. 1 to 8.

In one embodiment according to the present utility model, as shown in fig. 1, 2 and 8, there is provided a compressor 100, the compressor 100 including: a housing 110, the housing 110 being provided with an air outlet 111; the compression assembly 120 is arranged in the shell 110, and the compression assembly 120 is provided with a compression cavity 121 and an exhaust port 122 which are communicated with each other; a check valve 130 disposed in the compression assembly 120, the check valve 130 being movable relative to the compression assembly 120 between a first position and a second position; a resonance structure 140 provided at the check valve 130; wherein, based on the check valve 130 being in the first position, the exhaust port 122 communicates with the resonant structure 140 and the air outlet 111; based on the check valve 130 being in the second position, the check valve 130 covers the exhaust port 122.

The compressor 100 provided by the embodiment of the utility model includes a casing 110, a compression assembly 120, a check valve 130 and a resonance structure 140, specifically, the compression assembly 120 is provided with a compression cavity 121 and an exhaust port 122, and the compression cavity 121 is communicated with the exhaust port 122, it can be understood that the compression assembly 120 includes a movable disc 123, a static disc 124, a crankshaft and a motor, the movable disc 123 and the static disc 124 enclose to form the compression cavity 121, the exhaust port 122 is arranged on the static disc 124, and the crankshaft is connected with the movable disc 123 and the motor. Specifically, the crankshaft drives the movable plate 123 to rotate relative to the stationary plate 124 under the driving of the motor to compress the gas in the compression chamber 121. The compressed high-temperature and high-pressure gas can be discharged through the gas outlet 122 and the gas outlet 111.

The check valve 130 is disposed on the compression assembly 120, and the check valve 130 is capable of moving relative to the compression assembly 120, when the check valve 130 moves to the second position, the check valve 130 can cover the discharge port 122, when the compressor 100 is stopped, the discharge port 122 is covered by the check valve 130, so that the high-temperature and high-pressure air flowing out of the compression chamber 121 can be effectively prevented from flowing back into the compression chamber 121 through the discharge port 122, and the reverse rotation problem of the compressor 100 is caused.

When the compressor 100 discharges, the high temperature and high pressure gas pushes the check valve 130 to move away from the discharge port 122, and when the check valve 130 moves to the first position, the discharge port 122 is opened, and the high temperature and high pressure gas is discharged from the compression chamber 121 through the discharge port 122 and the discharge port 111.

The resonance structure 140 is disposed on the check valve 130, and when the check valve 130 moves to the first position, the air outlet 122 is in communication with the resonance structure 140, that is, when the compressor 100 is exhausting, high-temperature and high-pressure air is exhausted through the air outlet 122, and besides being exhausted through the air outlet 111, part of the high-temperature and high-pressure air enters the resonance structure 140 and can cause vibration of air in the resonance structure 140 and consume acoustic energy in the vibration process, thereby effectively reducing exhaust pulsation and exhaust noise generated in the exhaust process of the compressor 100, further reducing the noise of the whole air conditioner with the compressor 100, improving the product quality and improving the use experience of users.

It will be appreciated that the resonant structure 140 has a certain muffling frequency, and when the frequency of the sound wave at the time of the compressor 100 exhaust is close to the muffling frequency, the air in the resonant structure 140 will generate larger vibration, so that more sound energy can be consumed, that is, the resonant structure 140 can have a better muffling effect on the sound wave close to the frequency.

It should be noted that the resonant structure 140 includes a resonant cavity 141 and a vent 142 that are in communication, that is, the sound absorption principle of helmholtz resonance is utilized to reduce exhaust pulsation and exhaust noise during the exhaust process of the compressor 100. It will be appreciated that by designing the volume of the resonant cavity 141, the cross-sectional area of the vent 142, and the axial height of the vent 142, different frequencies of muffling may be achieved.

Specifically, the formula is:where f is the muffling frequency, c is the propagation velocity of sound waves in the refrigerant, S is the through-flow cross-sectional area of the vent 142, L is the axial height of the vent 142, and V is the volume of the resonant cavity 141.

As shown in fig. 2, 3, 4, 5 and 6, further, on the basis of the above embodiment, the resonant structure 140 includes a resonant cavity 141 and at least one vent 142, wherein the at least one vent 142 communicates with the resonant cavity 141.

In this embodiment, the resonant structure 140 is defined to include a resonant cavity 141 and at least one air vent 142, specifically, the at least one air vent 142 is in communication with the resonant cavity 141, that is, exhaust pulsation and exhaust noise generated in the exhaust process of the compressor 100 are reduced by using the helmholtz resonance principle, so that the overall noise of an air conditioner with the compressor 100 is reduced, the product quality is improved, and the use experience of a user is improved.

It will be appreciated that when the compressor 100 is exhausted, the high-temperature and high-pressure gas is exhausted from the exhaust port 122, part of the high-temperature and high-pressure gas enters the at least one air port 142, so that the air in the at least one air port 142 vibrates, and the air in the resonant cavity 141 is equivalent to an "air spring" which generates restoring force to the vibrating air in the at least one air port 142, so that vibration is generated, and acoustic energy is consumed in the process of mutually vibrating the air in the resonant cavity 141 and the air in the at least one air port 142, thereby achieving the purpose of silencing.

Specifically, the formula is:where f is the muffling frequency, c is the propagation velocity of sound waves in the refrigerant, S is the through-flow cross-sectional area of the vent 142, L is the axial height of the vent 142, and V is the resonant cavity 141 Is a volume of (c) a (c).

It will be appreciated that by designing the volume V of the resonant cavity 141, the through-flow cross-sectional area S of the vent 142, and the axial height L of the vent 142, different muffling frequencies can be obtained. The resonant structure 140 can be designed according to the sound waves of different frequency bands, so that the optimal silencing effect is achieved.

As shown in fig. 3 and 6, further, the number of the air vents 142 is plural, and the plural air vents 142 are spaced apart from each other.

In this embodiment, the check valve 130 is provided with a plurality of air vents 142, and the plurality of air vents 142 are spaced apart from each other, it can be understood that the number of air vents 142 is plural, that is, the through flow cross-sectional area of the air vents 142 is increased, and according to the formula, the corresponding noise elimination frequency is increased, that is, by providing a plurality of air vents 142, the noise elimination effect of the sound wave in the higher frequency band, especially the noise reduction effect of the sound wave in the middle frequency band can be improved, and thus the noise of the air conditioner with the compressor 100 can be reduced.

As shown in fig. 2, 3, 4, 5 and 6, further, based on the above embodiment, the check valve 130 includes a valve body 131 and a baffle 132, where the baffle 132 is connected to the valve body 131 and encloses a resonant cavity 141 with the valve body 131, and at least one vent 142 is provided in the valve body 131 or the baffle 132.

In this embodiment, the check valve 130 is defined to include the valve body 131 and the baffle 132, specifically, the baffle 132 is connected with the valve body 131, and the baffle 132 and the valve body 131 enclose to form the resonant cavity 141, that is, the resonant cavity 141 is a sealed cavity, and the at least one vent 142 is communicated with the resonant cavity 141, that is, a small opening is formed in one sealed cavity, so that the exhaust noise in the exhaust process of the compressor 100 is effectively reduced by using the helm hertz resonance sound absorption principle, and the purpose of reducing the medium frequency noise in the exhaust process of the compressor 100 can be achieved by designing the sizes of the resonant cavity 141 and the at least one vent 142, so that the use experience of a user on the air conditioner with the compressor 100 is improved.

The at least one vent 142 may be disposed on the valve body 131 or on the baffle 132, and may be specifically disposed according to actual needs.

It should be noted that the at least one vent 142 is disposed toward the exhaust port 122, and in particular, when the at least one vent 142 is disposed on the valve body 131, the baffle 132 is disposed on a side of the valve body 131 facing away from the exhaust port 122. When at least one vent 142 is provided on the baffle 132, the baffle 132 is positioned between the exhaust port 122 and the valve body 131.

In a specific embodiment, further, between the sum S of the through-flow cross-sectional areas of the plurality of air vents 142 and the cross-sectional area a of the baffle 132, 0.005S/a 0.3 is satisfied.

In this embodiment, the ratio of the sum of the through-flow cross-sectional areas of the plurality of vents 142 to the cross-sectional area of the baffle 132 is between 0.005 and 0.3, i.e., defines a porosity of between 0.5% and 30% of the vents 142. By limiting the perforation rate of the air vent 142 to between 0.5% and 30%, exhaust pulsation and exhaust noise generated in the exhaust process of the compressor 100, particularly mid-frequency noise generated in the exhaust process of the compressor 100, can be effectively reduced, thereby reducing the overall noise of an air conditioner with the compressor 100, improving the product quality and improving the use experience of users.

Further, it will be appreciated that the cross-sectional areas of the flow through the plurality of vents 142 are defined according to the formula, and correspondingly the muffling frequency range of the resonant structure 140.

In another specific embodiment, further, the diameter d of the at least one vent 142 satisfies 0.5 mm.ltoreq.d.ltoreq.5 mm; and/or along the axial direction of the valve body 131, the height L of the at least one vent 142 is between the height H of the valve body 131 and L.ltoreq.H of 0.1 mm.

In this embodiment, the diameter of the at least one vent 142 is between 0.5mm and 5mm, and according to the formula, the through-flow cross-sectional area S of the vent 142 is defined, which in turn defines the muffling frequency range of the resonant structure 140. By limiting the diameter of the at least one vent 142 to between 0.5mm and 5mm, it is possible to effectively reduce the discharge pulsation and discharge noise generated during the discharge of the compressor 100, particularly the mid-frequency noise generated during the discharge of the compressor 100, thereby reducing the overall noise of the air conditioner having the compressor 100.

The height of the at least one vent 142 is greater than or equal to 0.1mm and less than or equal to the height of the valve body 131 in the axial direction of the valve body 131, and according to the formula, i.e., defining the range of the axial height L of the vent 142, the muffling frequency of the resonant structure 140 can be defined accordingly. That is, by sizing the at least one vent 142, the discharge pulsation and discharge noise generated during the discharge of the compressor 100, particularly mid-frequency noise generated during the discharge of the compressor 100, can be effectively reduced.

In still another specific embodiment, further, between the depth n of the resonant cavity 141 and the height H of the valve body 131 in the axial direction of the valve body 131, 2mm n 0.9H is satisfied.

In this embodiment, the depth of the resonant cavity 141 is between 2mm and 0.9H in the axial direction of the valve body 131, and according to the formula, i.e., the range of the volume V of the resonant cavity 141 is defined, the muffling frequency of the resonant structure 140 can be defined accordingly. That is, by designing the size of the resonant cavity 141, it is possible to effectively reduce the discharge pulsation and the discharge noise generated during the discharge of the compressor 100, particularly the mid-frequency noise generated during the discharge of the compressor 100.

In addition, the depth of the resonant cavity 141 is less than or equal to 0.9H, so that the structural strength of the valve body 131 can be ensured, the problem that the check valve 130 is damaged due to long-term use due to the impact of high-temperature and high-pressure gas on the check valve 130 when the compressor 100 is discharged can be prevented, and the service life of the check valve 130 can be prolonged.

Further, on the basis of the above embodiment, the thickness b of the baffle 132 in the axial direction of the valve body 131 satisfies 0.1 mm.ltoreq.b.ltoreq.5 mm.

In this embodiment, the thickness of the baffle 132 is between 0.1mm and 5mm in the axial direction of the valve body 131, so that the structural strength of the baffle 132 can be ensured.

It will be appreciated that when at least one vent 142 is provided on the baffle 132, the range of values defining the thickness of the baffle 132, i.e., the range of values defining the axial height of the vent 142, is defined. Thereby ensuring the noise elimination effect of the compressor 100 in the exhaust process, ensuring the structural strength of the baffle 132, preventing the baffle 132 from being damaged under the impact of high-temperature and high-pressure gas for a long time, and prolonging the service life of the baffle 132.

When at least one vent 142 is disposed on the valve body 131, the baffle 132 is disposed away from the exhaust port 122, and by limiting the range of the thickness of the baffle 132, the tightness of the end of the resonant cavity 141 away from the vent 142 can be ensured while the structural strength of the baffle 132 is ensured.

As shown in fig. 4, in addition to any of the above embodiments, the valve body 131 further includes a bottom 1311 and a side 1312, where the side 1312 is circumferentially disposed on the bottom 1311 and connected to the bottom 1311; at least one vent 142 is provided in either the bottom 1311 or the side 1312.

In this embodiment, it is defined that the valve body 131 includes a bottom 1311 and a side 1312, specifically, the side 1312 is disposed on the bottom 1311 in a circumferential direction, and the side 1312 is connected to the bottom 1311, and at least one vent 142 may be disposed on the bottom 1311 or on the side 1312, specifically, may be disposed according to actual needs.

It will be appreciated that the compression assembly 120 further includes a back pressure plate 125, the back pressure plate 125 being connected to a side of the stationary plate 124 facing away from the movable plate 123, the back pressure plate 125 being provided with a mounting cavity 127, a check valve 130 being disposed within the mounting cavity 127, and the check valve 130 being movable within the mounting cavity 127 between a first position and a second position. If the height of the mounting chamber 127 is smaller than the height of the check valve 130 in the axial direction of the compression assembly 120, i.e., when the check valve 130 is in the first position, a portion of the check valve 130 is exposed to the mounting chamber 127, at least one vent 142 may be provided at the side 1312 of the valve body 131.

In addition, when the compressor 100 is exhausted, the high-temperature and high-pressure gas is exhausted through the exhaust port 122, and besides being exhausted through the air outlet 111, part of the high-temperature and high-pressure gas can enter the resonance structure 140, and can cause the vibration of air in the resonance structure 140, and consume sound energy in the vibration process, so that exhaust pulsation and exhaust noise generated in the exhaust process of the compressor 100 can be effectively reduced, the overall noise of an air conditioner with the compressor 100 is further reduced, the product quality is improved, and the use experience of a user is improved.

In a specific embodiment, further, the resonant cavity 141 is an annular cavity, and D1 is less than or equal to D-2mm between the outer diameter D of the valve body 131 and the outer diameter D1 of the annular cavity.

In this embodiment, the outer diameter of the resonant cavity 141 is less than or equal to the outer diameter of the valve body 131 minus 2mm, that is, the wall thickness of the side portion 1312 of the valve body 131 on the resonant cavity 141 needs to be greater than or equal to 2mm, that is, the side portion 1312 of the valve body 131 on the resonant cavity 141 needs to have a certain thickness to ensure the structural strength of the valve body 131, prevent the check valve 130 from being damaged under long-term impact of high-temperature and high-pressure airflow, and further prolong the service life of the check valve 130.

Further, the compressor 100 further includes a sound absorbing member 160, and the sound absorbing member 160 is disposed in the resonant cavity 141.

In this embodiment, it is defined that the compressor 100 further includes a sound absorbing member 160, and in particular, the sound absorbing member 160 is disposed within the resonant cavity 141. Through set up sound absorber 160 in resonant cavity 141, can further reduce the exhaust noise in the compressor 100 exhaust process, and then reduce the complete machine noise that has this compressor 100's air conditioner, improve the product quality, promote user's use experience.

In practical applications, the sound absorbing member 160 may be a sound absorbing material or a wire mesh, or the like. The setting can be specifically performed according to actual needs.

As shown in fig. 1, 2 and 8, further, on the basis of the above embodiment, the compression assembly 120 includes a movable disc 123, a static disc 124 and a back pressure plate 125, wherein the static disc 124 is disposed on the movable disc 123 and encloses with the movable disc 123 to form a compression chamber 121, the static disc 124 is provided with an exhaust port 122, the back pressure plate 125 is connected with one side of the static disc 124 away from the movable disc 123, the back pressure plate 125 is provided with an exhaust passage 126, a mounting chamber 127 and a through hole 128, the exhaust passage 126 is communicated with the air outlet 111, the through hole 128 is communicated with the air outlet 111 and the mounting chamber 127, and the check valve 130 is disposed in the mounting chamber 127 and can move in the mounting chamber 127; based on the check valve 130 being in the first position, the exhaust port 122 communicates with the resonant structure 140 and the exhaust passage 126; based on the check valve 130 being in the second position, the check valve 130 covers the exhaust port 122.

In this embodiment, the compression assembly 120 is defined to include a movable plate 123, a stationary plate 124, and a back pressure plate 125, and in particular, the stationary plate 124 encloses the movable plate 123 to form a compression chamber 121, it being understood that the compression assembly 120 further includes a crankshaft and a motor, the crankshaft being coupled to the movable plate 123 and the motor. Specifically, the crankshaft drives the movable plate 123 to rotate relative to the stationary plate 124 under the driving of the motor to compress the gas in the compression chamber 121.

The back pressure plate 125 is disposed on a side of the stationary plate 124 facing away from the movable plate 123, and the back pressure plate 125 is provided with an exhaust passage 126, one end of the exhaust passage 126 can be communicated with the exhaust port 122, and the other end of the exhaust passage 126 is communicated with the air outlet 111, that is, the exhaust port 122 is communicated with the air outlet 111 through the exhaust passage 126. When the compressor 100 discharges, the compressed high-temperature and high-pressure gas can be discharged through the discharge port 122, the discharge passage 126, and the discharge port 111.

The back pressure plate 125 is further provided with a mounting cavity 127 and a through hole 128 in communication, the through hole 128 being in communication with the air outlet 111, a check valve 130 being disposed within the mounting cavity 127, and the check valve 130 being movable within the mounting cavity 127 between a first position and a second position. Specifically, when the compressor 100 discharges, the high temperature and high pressure gas pushes the check valve 130 to move in a direction away from the discharge port 122, and when the check valve 130 moves to the first position, the discharge port 122 is opened, the high temperature and high pressure gas is discharged through the discharge passage 126 and the discharge port 111, and a part of the high temperature and high pressure gas enters the at least one vent 142, thereby causing air vibration in the at least one vent 142 and the resonant cavity 141, and consuming acoustic energy during the vibration, thereby reducing discharge pulsation and discharge noise during the discharge of the compressor 100.

When the compressor 100 is stopped, the check valve 130 can move in a direction close to the discharge port 122 due to gravity, and in addition, the high-temperature and high-pressure gas discharged from the discharge port 111 can impact the check valve 130 through the through hole 128, so that the check valve 130 can rapidly move in a direction of the discharge port 122 to cover the discharge port 122, thereby effectively preventing the high-temperature and high-pressure gas from flowing back into the compression chamber 121 through the discharge port 122 when the compressor 100 is stopped, and further causing a problem of reverse rotation of the compressor 100.

As shown in fig. 7, further, the compressor 100 further includes a check groove 150, the check groove 150 being provided at a side of the check valve 130 facing the back pressure plate 125, the check groove 150 communicating with the through hole.

In this embodiment, it is defined that the compressor 100 further includes a check groove 150, specifically, the check groove 150 is provided on a side of the check valve 130 facing the back pressure plate 125, and the check groove 150 communicates with the through hole, when the compressor 100 is stopped, the check valve 130 can move toward the direction close to the discharge port 122 due to gravity, and furthermore, the high temperature and high pressure gas discharged from the discharge port 111 can not reach the check groove 150 of the check valve 130 through the through hole, so that the check valve 130 can move rapidly toward the discharge port 122 to cover the discharge port 122, thereby effectively preventing the high temperature and high pressure gas from flowing back into the compression chamber 121 through the discharge port 122 when the compressor 100 is stopped, thereby causing a problem of reverse rotation of the compressor 100.

It will be appreciated that if the baffle 132 is disposed toward the back pressure plate 125, the baffle 132 is provided with a relief port, and the through hole 128 communicates with the check groove 150 through the relief port.

In addition, the resonance structure 140 is disposed on the check valve 130, and when the check valve 130 moves to the first position, the exhaust port 122 is in communication with the resonance structure 140, that is, when the compressor 100 is exhausted, high-temperature and high-pressure gas is exhausted through the exhaust port 122, and besides being exhausted through the air outlet 111, part of the high-temperature and high-pressure gas enters the resonance structure 140 and can cause vibration of air in the resonance structure 140 and consume sound energy in the vibration process, thereby effectively reducing exhaust pulsation and exhaust noise generated in the exhaust process of the compressor 100, further reducing overall noise of an air conditioner with the compressor 100, improving product quality and improving use experience of users.

According to a second aspect of the present utility model, an air conditioner is provided, which includes the compressor 100 provided in any of the above embodiments, so that all the beneficial technical effects of the compressor 100 are provided, and are not described herein.

In practice, compressor 100 includes, but is not limited to, a scroll compressor.

Specifically, as shown in fig. 1 and 2, the compressor 100 includes a housing 110, a compression assembly 120, a check valve 130, and a resonance structure 140, specifically, the compression assembly 120 is provided with a compression chamber 121 and an exhaust port 122, and the compression chamber 121 and the exhaust port 122 are communicated, it can be understood that the compression assembly 120 includes a movable plate 123, a stationary plate 124, a crankshaft, and a motor, the movable plate 123 and the stationary plate 124 enclose to form the compression chamber 121, the exhaust port 122 is provided on the stationary plate 124, and the crankshaft is connected to the movable plate 123 and the motor. Specifically, the crankshaft drives the movable plate 123 to rotate relative to the stationary plate 124 under the driving of the motor to compress the gas in the compression chamber 121. The compressed high-temperature and high-pressure gas can be discharged through the gas outlet 122 and the gas outlet 111.

In the description of the present specification, the terms "connected," "mounted," "secured," and the like are to be construed broadly, and for example, "connected" may be a fixed connection, a removable connection, or an integral connection; can be directly connected or indirectly connected through an intermediate medium. The specific meaning of the above terms in the present utility model can be understood by those of ordinary skill in the art according to the specific circumstances.

In the description of the present specification, the terms "one embodiment," "some embodiments," "particular embodiments," and the like, mean 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 utility model. In this specification, schematic representations of the above terms do not necessarily refer to the same embodiment 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.

The above is only a preferred embodiment of the present utility model, and is not intended to limit the present utility model, but various modifications and variations can be made to the present utility model by those skilled in the art. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present utility model should be included in the protection scope of the present utility model.

Claims

1. A compressor, comprising:

the shell is provided with an air outlet;

the compression assembly is arranged in the shell and is provided with a compression cavity and an exhaust port which are communicated with each other;

a check valve disposed in the compression assembly, the check valve being movable relative to the compression assembly between a first position and a second position;

the resonance structure is arranged on the check valve;

wherein the vent communicates with the resonating structure and the vent based on the check valve being in the first position; the check valve seals the exhaust port based on the check valve being in the second position.

2. The compressor of claim 1, wherein the resonant structure comprises:

a resonant cavity;

at least one vent in communication with the resonant cavity.

3. A compressor according to claim 2, wherein,

the number of the air vents is multiple, and the multiple air vents are arranged at intervals.

4. The compressor of claim 2, wherein the check valve comprises:

a valve body;

the baffle is connected with the valve body and surrounds the valve body to form the resonant cavity, and the at least one air vent is arranged on the valve body or the baffle.

5. The compressor of claim 4, wherein,

the sum S of the through-flow sectional areas of the plurality of air vents and the cross-sectional area a of the baffle plate meet the requirement that S/a is more than or equal to 0.005 and less than or equal to 0.3.

6. The compressor of claim 4, wherein,

the diameter d of at least one vent hole is 0.5mm or less and d or less than or equal to 5mm; and/or

And along the axial direction of the valve body, the height L of at least one vent and the height H of the valve body are between 0.1mm and less than or equal to L and less than or equal to H.

7. The compressor of claim 4, wherein,

along the axial direction of the valve body, the depth n of the resonant cavity and the height H of the valve body are between 2mm and less than or equal to n and less than or equal to 0.9H.

8. The compressor of claim 4, wherein,

Along the axial direction of the valve body, the thickness b of the baffle plate is more than or equal to 0.1mm and less than or equal to 5mm.

9. The compressor of claim 4, wherein the valve body comprises:

a bottom;

the side part is circumferentially arranged at the bottom part and is connected with the bottom part;

wherein at least one of the vents is provided at the bottom or the side.

10. The compressor of claim 4, wherein,

the resonant cavity is an annular cavity, and D1 is less than or equal to D-2mm between the outer diameter D of the valve body and the outer diameter D1 of the annular cavity.

11. The compressor according to any one of claims 2 to 10, further comprising:

and the sound absorption piece is arranged in the resonant cavity.

12. The compressor of any one of claims 4 to 10, wherein the compression assembly comprises:

a movable plate;

the static disc is arranged on the movable disc, surrounds the movable disc to form the compression cavity, and is provided with the exhaust port;

the back pressure plate is connected with one side of the static disc, which is away from the movable disc, and is provided with an exhaust channel, a mounting cavity and a through hole, the exhaust channel is communicated with the air outlet, the through hole is communicated with the air outlet and the mounting cavity, and the check valve is arranged in the mounting cavity and can move in the mounting cavity;

Wherein the exhaust port is in communication with the resonating structure and the exhaust channel based on the check valve being in the first position; the check valve seals the exhaust port based on the check valve being in the second position.

13. The compressor of claim 12, further comprising:

and the check groove is arranged on one side of the check valve, which faces the back pressing plate, and is communicated with the through hole.

14. An air conditioner comprising the compressor according to any one of claims 1 to 13.