CN209855995U

CN209855995U - Compressor amortization structure and have its compressor

Info

Publication number: CN209855995U
Application number: CN201920434814.4U
Authority: CN
Inventors: 陈恩峥; 蓝榕江; 蓝国嘉
Original assignee: Gree Electric Appliances Inc of Zhuhai; Zhuhai Landa Compressor Co Ltd
Current assignee: Gree Electric Appliances Inc of Zhuhai; Zhuhai Landa Compressor Co Ltd
Priority date: 2019-04-02
Filing date: 2019-04-02
Publication date: 2019-12-27
Anticipated expiration: 2029-04-02

Abstract

The utility model discloses a compressor sound attenuation structure and have its compressor eliminates compressor noise through setting up this sound attenuation structure, and the means is nimble and the scope of action is big, can solve compressor mechanical noise problem basically, and the sound attenuation structure is cyclic annularly, is provided with the Helmholtz resonant cavity on its ring body, the Helmholtz resonant cavity has cavity and resonant cavity export, the volume of cavity is greater than the volume that the resonant cavity exported, the cavity is located the ring body lower part, the resonant cavity export is located ring body upper portion, resonant cavity export and cavity intercommunication. The structure is flexible and various in the position arranged in the compressor, and can eliminate noise in a large frequency range.

Description

Compressor amortization structure and have its compressor

Technical Field

The utility model belongs to the technical field of refrigeration machinery, it is concrete, relate to an amortization structure of compressor and have its compressor.

Background

The refrigerant is discharged from the pump body, passes through the silencer, is discharged into the cavities at the lower ends of the stator and the rotor, passes through the gap between the rotor and the stator and the gap between the stator and the shell, moves into the cavities at the upper ends of the stator and the rotor, and then passes through the exhaust pipe to be discharged out of the compressor. The above refrigerant moving route is only an approximate trend, and in practice, the trajectory and the law of the refrigerant moving in the compressor are quite complex, and cannot be particularly developed.

The motion of refrigerant gas generates noise, and how the noise reduction effect is an important standard for measuring the quality of the compressor, so the noise is an important parameter of the compressor. The main noise elimination means of the conventional compressor is to use a silencer to eliminate noise, the effect is limited in practice, the noise required by customers is lower and lower, the challenge of application in high-end markets is great, and how to reduce the noise of the compressor is a technical bottleneck.

The original shape of the helmholtz resonator is a container with a narrow neck or small opening, and when subjected to sound waves, the air in the neck vibrates and the air in the container exerts a restoring force on it. In the case of a wave length of sound much greater than the geometric dimensions of the resonator, it is believed that the kinetic energy of the air vibration inside the resonator is concentrated in the movement of the air inside the neck, and the potential energy is only related to the elastic deformation of the air inside the container. Thus, the resonator is a one-dimensional vibrating system consisting of the effective mass of air in the neck and the elasticity of the air in the container, and thus has a resonance phenomenon with respect to the applied sound waves.

The noise elimination principle is as follows: the Helmholtz resonant cavity is used for eliminating noise, and the design formula of the resonant cavity is as follows:

resonance frequency:

wherein:

c-speed of sound, m/s;

s-area of neck opening, m²；

V-volume of cavity, m³；

I-effective length of the neck, I ═ I₀+0.85d(m)；

I₀The actual length of the neck, m;

d is the diameter of the neck opening.

The resonant frequency required to eliminate the noise can be designed, and the design size of the resonant cavity can be obtained in the design and adjustment process.

SUMMERY OF THE UTILITY MODEL

In order to solve the problem, the utility model provides a compressor amortization structure, this structure can set up in each part of compressor in a flexible way, and the scope of action is wide, can solve the mechanical noise problem basically.

In order to realize the above-mentioned purpose, the utility model discloses a compressor amortization structure, amortization structure are arc or cyclic annular, are provided with the Helmholtz resonant cavity on its ring body, the Helmholtz resonant cavity has cavity and resonant cavity export, the volume of cavity is greater than the volume that the resonant cavity exported, the cavity is located the ring body lower part, the resonant cavity export is located ring body upper portion, resonant cavity export and cavity intercommunication.

Furthermore, a plurality of cavities can be arranged on the ring body, and connecting grooves are formed in the lower portion of the ring body and connect the cavities.

Further, the number of the cavities is not less than 2, and the number of the resonant cavity outlets is less than the number of cavities.

Furthermore, a plurality of Helmholtz resonant cavities are arranged on the ring body, and the number of the Helmholtz resonant cavities is not less than 2.

Further, the ring bodies are mutually overlapped, and Helmholtz resonant cavities on the ring bodies are also mutually overlapped.

Further, the volume of the cavity in the helmholtz resonator may be set to be different according to the desired noise reduction effect.

A compressor comprises a shell, a stator, a rotor and a silencer, wherein a silencing structure of the compressor is arranged in a refrigerant air channel inside the compressor.

Furthermore, the compressor silencing structure is arranged at a refrigerant air outlet of the silencer.

Further, the compressor silencing structures are respectively installed at the upper part and the lower part of the rotor.

Further, the compressor silencing structures are respectively installed at the upper and lower parts of the stator.

Further, the compressor silencing structure is installed on a shell of the compressor.

The utility model has the advantages as follows:

1. according to the refrigerant flow route of the compressor, the Helmholtz resonant cavity is used for eliminating the noise of the compressor. The method has flexible and various action positions and can eliminate noise in a large frequency range.

2. Aiming at a plurality of noise elimination frequency bands, a plurality of Helmholtz resonant cavities are arranged in different shapes, so that multi-band noise reduction is realized.

3. A plurality of Helmholtz resonant cavities are arranged and connected in series for use, so that the noise elimination effect is enhanced.

4. A plurality of Helmholtz resonant cavities are arranged and used in parallel, different resonant cavities have different functions, the noise elimination frequency domain is enlarged, and the space is saved.

Drawings

FIG. 1 is a schematic cross-sectional view of a sound attenuating structure;

FIG. 2 is a schematic view of the overall structure of the compressor;

FIG. 3 is a first top view of a sound attenuating structure;

FIG. 4 is a second top view of the sound attenuating structure;

FIG. 5 is a third top view of the noise dampening structure;

FIG. 6 is a schematic cross-sectional view of a series connection of the silencing structures;

shown in the figure: 1-a ring body; 2-helmholtz resonator; 3-a cavity; 4-resonant cavity outlet; 5-connecting grooves; 6-a shell; 7-a stator; 8-a rotor; 9-silencer.

Detailed Description

In order to make the purpose, technical solution and advantages of the present invention more clearly understood, it is right to combine the drawings and the embodiments below, the present invention discloses a noise reduction structure of a compressor and a compressor having the same. Further detailed description is made; it should be understood that the specific embodiments described herein are for purposes of illustration only and are not intended to limit the invention.

As shown in fig. 1, a sound-deadening structure of a compressor is arc-shaped or annular, a helmholtz resonator 2 is disposed on a ring body 1 of the sound-deadening structure, the helmholtz resonator 2 has a cavity 3 and a resonator outlet 4, the volume of the cavity 3 is greater than the volume of the resonator 4, the cavity 3 is located at a lower portion of the ring body 1, the resonator outlet 4 is located at an upper portion of the ring body 1, and the resonator outlet 4 is communicated with the cavity 3. The outlet area of the outlet 4 of the resonant cavity is the neck area S, and the volume of the cavity is V. The Helmholtz resonant cavity is used for eliminating noise, and the design formula of the resonant cavity is as follows:

resonance frequency:

wherein:

c-speed of sound, m/s;

s-area of neck opening, m²；

V-volume of cavity, m³；

I-effective length of the neck, I ═ I₀+0.85d(m)；

I₀The actual length of the neck, m;

d is the diameter of the neck opening.

According to the refrigerant characteristics, the resonant frequency of the noise to be eliminated is designed, and the design size of the resonant cavity can be obtained in the design and adjustment process.

As shown in fig. 5, a plurality of cavities 3 may be provided on the ring body 1, as shown in fig. 3 and 4, a connecting groove 5 is provided at the lower portion of the ring body 1, the connecting groove 5 connects the cavities 3, i.e., the cavities are connected in parallel, the volumes of the cavities 3 may be set to be different according to the needs, different resonant cavities have different functions, the muffling frequency domain is enlarged, and the space is saved.

As shown in fig. 6, the ring body 1 can be stacked on each other, and the helmholtz resonant cavities 2 on the ring body 1 are also stacked on each other, so that the helmholtz resonant cavities 2 are connected in series, thereby further enhancing the noise elimination effect.

As shown in fig. 2, the refrigerant flow path of a compressor commonly available in the market is roughly as follows: the refrigerant is discharged from the pump body, passes through the muffler 9, is discharged into the cavities at the lower ends of the stator 7 and the rotor 8, passes through the gap between the rotor 8 and the stator 7 and the gap between the stator 7 and the shell 6, moves to the cavities at the upper ends of the stator 7 and the rotor 8, and then is discharged out of the compressor through the exhaust pipe.

The silencing structure can be installed in the respective refrigerant circulation areas inside the compressor, according to the refrigerant flow path, and most commonly, it is installed at the refrigerant outlet of the silencer 9, or at the upper and lower portions of the rotor 8, or at the upper and lower portions of the stator 7, or at the casing 6 of the compressor.

Claims

1. The utility model provides a compressor sound attenuation structure, its characterized in that, sound attenuation structure are arc or cyclic annular, are provided with Helmholtz resonance chamber (2) on its ring body (1), Helmholtz resonance chamber (2) have cavity (3) and resonance chamber export (4), the volume of cavity (3) is greater than the volume of resonance chamber export (4), cavity (3) are located ring body (1) lower part, resonance chamber export (4) are located ring body (1) upper portion, resonance chamber export (4) and cavity (3) intercommunication.

2. Compressor sound attenuation structure according to claim 1, characterized in that the number of the cavities (3) on the ring body (1) can be multiple, and the lower part of the ring body (1) is provided with the connecting slots (5), and the connecting slots (5) connect the cavities (3).

3. A compressor sound-deadening structure according to claim 2, wherein the number of the cavities (3) is not less than 2, and the number of the resonance chamber outlets (4) is less than the number of the cavities (3).

4. Compressor sound-damping structure according to claim 1, characterized in that a plurality of helmholtz resonator chambers (2) are provided in said ring body (1), said helmholtz resonator chambers (2) being not less than 2 in number.

5. Compressor sound-damping arrangement according to claim 1, characterised in that the ring bodies (1) overlap each other, and that the helmholtz resonator cavities (2) in the ring bodies (1) also overlap each other.

6. Compressor silencing structure according to any of claims 2-5, characterized in that the volume of the cavity (3) on the Helmholtz resonance chamber (2) can be set differently depending on the desired silencing effect.

7. A compressor comprising a shell (6), a stator (7), a rotor (8) and an upper silencer (9), characterized in that it comprises a compressor silencing structure as claimed in any one of the preceding claims, said compressor silencing structure being mounted in the compressor interior refrigerant air passage.

8. A compressor according to claim 7, characterized in that the compressor silencing structure is mounted at the refrigerant outlet of the silencer (9).

9. A compressor according to claim 7, characterized in that the compressor sound-deadening structures are respectively mounted on the upper and lower portions of the rotor (8).

10. A compressor according to claim 7, characterized in that the compressor sound-deadening structures are mounted respectively in the upper and lower parts of the stator (7).

11. A compressor according to claim 7, characterized in that the compressor sound-dampening structure is mounted on the shell (6) of the compressor.