CN214742067U

CN214742067U - Compressor and air conditioning system

Info

Publication number: CN214742067U
Application number: CN202120210999.8U
Authority: CN
Inventors: 胡余生; 魏会军; 孙成龙; 王珺; 吴健; 梁社兵
Original assignee: Gree Green Refrigeration Technology Center Co Ltd of Zhuhai
Current assignee: Gree Green Refrigeration Technology Center Co Ltd of Zhuhai
Priority date: 2021-01-25
Filing date: 2021-01-25
Publication date: 2021-11-16
Anticipated expiration: 2031-01-25

Abstract

The utility model provides a compressor and an air conditioning system, wherein the compressor comprises a pump body and an air inlet assembly, and the pump body comprises a crankshaft and an air cylinder; the air inlet assembly comprises a filtering part, an air inlet pipe, a main pipe and a branch pipe, wherein the air inlet pipe, the main pipe and the branch pipe are sequentially connected, the filtering part is arranged in the air inlet pipe, and the branch pipe is communicated with an inlet of the air cylinder. Adopt this scheme, replaced the knockout among the traditional compressor through the subassembly that admits air, intake pipe, house steward and branch pipe are the tubulose spare, compare the diameter with the knockout and reduce greatly. Therefore, the resonance point of the refrigerant air inlet flow path can be effectively improved, the total noise value in a low frequency band is reduced, and the sound radiation area is reduced because the diameter of the main pipe is greatly reduced compared with that of the traditional liquid distributor, so that the radiation noise is reduced. Meanwhile, because the pressure pulsation of fluid turbulence in a large space of the liquid distributor component is eliminated, the fluid noise during the operation of the compressor (particularly during high-frequency operation) can be effectively reduced. Therefore, the noise of the compressor can be reduced under the condition of not influencing the performance of the compressor by the scheme.

Description

Compressor and air conditioning system

Technical Field

The utility model relates to a compressor technical field particularly, relates to a compressor and air conditioning system.

Background

With the increasing of the capacity range and the miniaturization requirement of a refrigerating system, the variable frequency rotor compressor is gradually and widely applied due to the characteristics of simple structure, relatively low cost, high energy efficiency and the like, and the core competitiveness of the rotor compressor is the application of a broadband technology aiming at the market requirement. Along with the continuous improvement of the requirements of miniaturization and high speed, the noise level of the compressor faces a serious challenge, for example, the noise of the compressor in 1500Hz is greatly increased due to the influence of the natural frequency of a liquid distributor component when the liquid distributor component runs at a high rotating speed, the noise reduction effect is difficult to realize through the prior art means, and simultaneously, the radiation noise and the pulsation noise of fluid are also greatly deteriorated due to the large occupied volume, and the product experience of a user is seriously influenced.

For the inverter compressor (especially at high frequency) under the application condition of the broadband technology, how to solve the problem of severe noise caused by the liquid separator without influencing the performance of the compressor is one of the technical bottlenecks to be solved urgently in the field.

SUMMERY OF THE UTILITY MODEL

The utility model provides a compressor and air conditioning system to reduce the noise of compressor.

In order to achieve the above object, according to an aspect of the present invention, the present invention provides a compressor, including: a pump body including a crankshaft and a cylinder; the air inlet assembly comprises a filtering part and an air inlet pipe, a header pipe and a branch pipe which are sequentially connected, wherein the filtering part is arranged in the air inlet pipe, and the branch pipe is communicated with an inlet of the cylinder.

Further, the pump body comprises one cylinder, the displacement of the pump body is Vcc, and the inner diameter of the manifold is Dcm; wherein V is more than or equal to 7cc and less than or equal to 15cc, and V/D is more than or equal to 2.8 and less than or equal to 12.5.

Further, V/D is more than or equal to 3.5 and less than or equal to 9.38.

Further, the pump body comprises two cylinders, the displacement of the pump body is Vcc, and the inner diameter of the header pipe is Dcm; wherein V is more than or equal to 14cc and less than or equal to 40cc, and V/D is more than or equal to 5.6 and less than or equal to 34.

Further, V/D is more than or equal to 7 and less than or equal to 25.

Further, the pump body comprises two cylinders, the displacement of the pump body is Vcc, and the inner diameter of the header pipe is Dcm; wherein V is more than 40cc and less than or equal to 60cc, and V/D is more than 16 and less than or equal to 50.

Further, 20 is less than or equal to V/D is less than or equal to 37.5.

Further, the pump body comprises two cylinders, the displacement of the pump body is Vcc, and the inner diameter of the header pipe is Dcm; wherein V is more than 60cc and less than or equal to 80cc, and V/D is more than 24 and less than or equal to 67.

Further, V/D is more than or equal to 30 and less than or equal to 50.

Further, the inner diameter of the header pipe is D, and the outer diameter of the filter part is D1; wherein D1 is more than or equal to D.

Further, the pump body comprises one cylinder, the inner diameter of the main pipe is D, and the inner diameter of the branch pipe is D

Wherein,

further, the pump body includes two cylinders, the number of the branch pipes is two, two the branch pipes andtwo cylinders are communicated in one-to-one correspondence, the inner diameter of the main pipe is D, and the inner diameters of the branch pipes are D

Wherein,

further, the wall thickness of the main pipe is 1mm to 3mm, and the wall thickness of the branch pipe is 1mm to 3 mm.

According to the utility model discloses an on the other hand provides an air conditioning system, air conditioning system includes heat exchanger and compressor, the compressor is foretell compressor, the intake pipe of compressor with the heat exchanger intercommunication.

The technical scheme of the utility model is applied to provide a compressor, which comprises a pump body and an air inlet component, wherein the pump body comprises a crankshaft and an air cylinder; the air inlet assembly comprises a filtering part, an air inlet pipe, a main pipe and a branch pipe, wherein the air inlet pipe, the main pipe and the branch pipe are sequentially connected, the filtering part is arranged in the air inlet pipe, and the branch pipe is communicated with an inlet of the air cylinder. Adopt this scheme, replaced the knockout among the traditional compressor through the subassembly that admits air, intake pipe, house steward and branch pipe are the tubulose spare, compare the diameter with the knockout and reduce greatly. Therefore, the resonance point of the refrigerant air inlet flow path can be effectively improved, the total noise value in a low frequency band is reduced, and the sound radiation area is reduced because the diameter of the main pipe is greatly reduced compared with that of the traditional liquid distributor, so that the radiation noise is reduced. Meanwhile, because the pressure pulsation of fluid turbulence in a large space of the liquid distributor component is eliminated, the fluid noise during the operation of the compressor (particularly during high-frequency operation) can be effectively reduced. Therefore, the noise of the compressor can be reduced under the condition of not influencing the performance of the compressor by the scheme.

Drawings

The accompanying drawings, which form a part of the present application, are included to provide a further understanding of the invention, and are incorporated in and constitute a part of this specification, illustrate embodiments of the invention and together with the description serve to explain the invention and not to limit the invention. In the drawings:

fig. 1 shows a schematic structural diagram of a compressor provided by an embodiment of the present invention;

FIG. 2 shows a schematic structural view of the intake assembly of FIG. 1;

fig. 3 is a schematic structural diagram illustrating an air intake assembly in a compressor according to another embodiment of the present invention;

fig. 4 is a schematic structural diagram illustrating an air intake assembly in a compressor according to another embodiment of the present invention;

fig. 5 is a schematic structural diagram illustrating an air intake assembly in a compressor according to another embodiment of the present invention;

FIG. 6 is a schematic view showing the structure of the intake duct and the filter portion of FIG. 1;

FIG. 7 shows another view of the pump body of FIG. 1;

fig. 8 shows a comparison of the compressor of fig. 1 with a 1500Hz total noise value for a prior art compressor.

Wherein the figures include the following reference numerals:

10. a pump body; 11. a crankshaft; 12. a cylinder; 20. an air intake assembly; 21. an air inlet pipe; 22. a header pipe; 23. a branch pipe; 24. and a filtering part.

Detailed Description

The technical solution in the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present invention. It is to be understood that the embodiments described are only some embodiments of the invention, and not all embodiments. The following description of at least one exemplary embodiment is merely illustrative in nature and is in no way intended to limit the invention, its application, or uses. Based on the embodiments in the present invention, all other embodiments obtained by a person skilled in the art without creative efforts belong to the protection scope of the present invention.

As shown in the drawings, embodiments of the present invention provide a compressor, including: a pump body 10, the pump body 10 including a crankshaft 11 and a cylinder 12; the air inlet assembly 20 comprises a filtering portion 24, an air inlet pipe 21, a header pipe 22 and a branch pipe 23 which are sequentially connected, wherein the filtering portion 24 is arranged in the air inlet pipe 21, and the branch pipe 23 is communicated with an inlet of the cylinder 12.

Adopt this scheme, replaced the knockout in the traditional compressor through air intake assembly 20, because air intake pipe 21, house steward 22 and branch pipe 23 of air intake assembly 20 are the tubulose spare, compare the diameter with original knockout and reduce greatly, can effectively promote the resonance point of refrigerant inlet flow path like this, reduce the noise total value in the low-frequency channel, reduce by a wide margin because of the diameter of above-mentioned house steward 22 relative traditional knockout again, the acoustic radiation area reduces to can reduce the radiated noise. Meanwhile, the scheme eliminates the pressure pulsation of fluid turbulence in a large space of the liquid distributor component, and can effectively reduce the fluid noise during the operation of the compressor (particularly during high-frequency operation). Therefore, the noise of the compressor can be reduced under the condition of not influencing the performance of the compressor by the scheme.

In the present embodiment, the pump body 10 comprises one cylinder 12, i.e. for a single cylinder compressor, the displacement of the pump body 10 is Vcc and the internal diameter of the manifold 22 is Dcm; wherein V is more than or equal to 7cc and less than or equal to 15cc, and V/D is more than or equal to 2.8 and less than or equal to 12.5. This reduces the noise and cost of the compressor.

For the single-cylinder compressor, more preferably, V/D is more than or equal to 3.5 and less than or equal to 9.38. This further improves the performance of the compressor.

In another embodiment, the pump body 10 includes two cylinders 12, i.e., for a two cylinder compressor, the displacement of the pump body 10 is Vcc and the internal diameter of the manifold 22 is Dcm; wherein V is more than or equal to 14cc and less than or equal to 40cc, and V/D is more than or equal to 5.6 and less than or equal to 34. That is, when V is not less than 40cc and the displacement V of the pump body 10 is not less than 14cc, V/D is not less than 5.6 and not more than 34 with respect to the inner diameter of the main pipe 22.

More preferably, i.e., for a two-cylinder compressor, the displacement V and the internal diameter of the manifold 22 are defined as 7V/D25.

In another embodiment, the pump block 10 includes two cylinders 12, i.e., for a two cylinder compressor, the pump block 10 includes two cylinders 12, the displacement of the pump block 10 is Vcc, and the internal diameter of the manifold 22 is Dcm; wherein V is more than 40cc and less than or equal to 60cc, and V/D is more than 16 and less than or equal to 50. That is, when the displacement volume of the pump body 10 is 40cc < V.ltoreq.60 cc, the displacement volume V and the inner diameter of the manifold 22 are limited to 16 < V/D.ltoreq.50.

More preferably, for the above two-cylinder compressor, 20 ≤ V/D ≤ 37.5. This further improves the performance of the compressor.

In another twin cylinder compressor, the pump body 10 comprises two cylinders 12, the displacement of the pump body 10 is Vcc, and the internal diameter of the manifold 22 is Dcm; wherein V is more than 60cc and less than or equal to 80cc, and V/D is more than 24 and less than or equal to 67. That is, when the displacement of the pump body 10 is 60cc < V.ltoreq.80 cc, the displacement V and the inner diameter of the manifold 22 are limited to 24 < V/D.ltoreq.67.

More preferably, for the above two-cylinder compressor, V/D is 30 ≤ and 50.

In the present embodiment, the inner diameter of the manifold 22 is D, and the outer diameter of the filter portion 24 is D1; wherein D1 is more than or equal to D.

For a single-cylinder compressor, i.e. the pump body 10 comprising a cylinder 12, the internal diameter of the manifold 22 is D and the internal diameter of the branch 23 is D

Wherein,

specifically, the wall thickness of the header pipe 22 is 1mm to 3mm, and the wall thickness of the branch pipes 23 is 1mm to 3 mm. The thickness and strength of the pipe itself affects its own mode shape. Limiting the wall thickness of the main pipe 22 and branch pipes 23 to the above size range further reduces vibration and noise.

For a two-cylinder compressor, i.e., the pump body 10 includes two cylinders 12, the number of branch pipes 23 is two, the two branch pipes 23 are in one-to-one correspondence with the two cylinders 12, the inner diameter of the header pipe 22 is D, and the inner diameter of the branch pipes 23 is D

Wherein,

alternatively, for a single cylinder compressor, the manifold 22 and branch 23 are integrally formed tubes. Or the main pipe 22 and the branch pipes 23 are connected by different pipes. For a twin cylinder compressor, the manifold 22 and one of the branch pipes 23 below are integrally formed as a tube, and the other branch pipe 23 is connected to the manifold 22. Alternatively, the header 22 and the two branch pipes 23 may be different pipes, and the two branch pipes 23 may be connected to the header 22.

Of course, the scheme can also be used for multi-cylinder compressors such as three cylinders and the like.

Another embodiment of the utility model provides an air conditioning system, air conditioning system include heat exchanger and compressor, and the compressor is foretell compressor, the intake pipe 21 and the heat exchanger intercommunication of compressor. Adopt this scheme, replaced the knockout in the traditional compressor through air intake assembly 20, because air intake pipe 21, house steward 22 and branch pipe 23 of air intake assembly 20 are the tubulose spare, compare the diameter with original knockout and reduce greatly, can effectively promote the resonance point of refrigerant inlet flow path like this, reduce the noise total value in the low-frequency channel, reduce by a wide margin because of the diameter of above-mentioned house steward 22 relative traditional knockout again, the acoustic radiation area reduces to can reduce the radiated noise. Meanwhile, the scheme eliminates the pressure pulsation of fluid turbulence in a large space of the liquid distributor component, and can effectively reduce the fluid noise during the operation of the compressor (particularly during high-frequency operation). This reduces the noise of the air conditioning system and improves performance.

To facilitate understanding of the present solution, the following is further described.

The compressor in the prior art can excite the inherent mode of a conventional liquid distributor when a variable-frequency compressor based on a wide-frequency technology operates (particularly when the variable-frequency compressor operates at a high frequency), can excite an abnormal noise peak value near 1500Hz, is difficult to solve the noise in a low-frequency range by the conventional noise reduction means, and has large radiation area due to large surface area of the liquid distributor, so that the conditions of the pulsation noise and the radiation noise of the fluid of the compressor are greatly deteriorated, and the user experience is seriously influenced.

In this scheme, be provided with motor element and pump body subassembly from top to bottom in the sealed casing of compressor, the casing outer joint has the subassembly that admits air. Wherein, pump body subassembly includes: the air cylinder with certain compression cavity space inside, the middle partition board of the air cylinder (for double cylinders or multiple cylinders), the crankshaft with transmission function, the upper bearing and the lower bearing which can support the crankshaft, and the roller which compresses the refrigerant. In the compression process, the head surface of the sliding vane is always contacted with the outer circular surface of the roller, so that a suction cavity and a compression cavity are separated in the cylinder, the sum of the volumes of the suction cavity and the compression cavity is called the volume of a working cavity, and the sum of the volumes of the working cavities of all cylinders of the compressor is called the displacement V (cc) of the compressor. The inner wall and the outer wall of the air cylinder are penetrated through by an air suction passage, refrigerant steam flows out from an outlet of the air inlet assembly and enters the air cylinder through the air suction passage to be compressed, the compressed refrigerant steam is discharged from an air outlet at the end face of the air cylinder to enter a shell inner closed space, flows out through an exhaust pipe of the shell upper cover assembly to enter a condenser to dissipate heat, then flows into the evaporator to absorb heat, and superheated steam at the moment enters the air inlet assembly and further flows into the compressor to complete a refrigeration cycle.

Specifically, the intake air flow path assembly includes: the filter comprises an air inlet pipe, a filter screen component (namely a filtering part), a cylinder body (namely a main pipe), a first air inlet branch pipe and a second air inlet branch pipe (namely two branch pipes), wherein the first air inlet branch pipe and the second air inlet branch pipe are respectively connected with air suction ports of an upper cylinder and a lower cylinder, the other end of the air inlet branch pipe is communicated with the cylinder body which is vertically arranged on an air inlet flow path component, and one end of the air inlet of the cylinder body is provided with the filter screen component which is used for filtering impurities flowing out of an evaporator. Optionally, the filter screen assembly and the cylinder body can be designed in a split mode and in an integrated mode, and due to the fact that the diameter of meshes of the filter screen assembly is small, the refrigerant in a gas-liquid coexisting state under certain specific working conditions can also play a role in preliminarily separating the refrigerant oil, the refrigerant oil flows into the cylinder along the cylinder wall, and therefore the oil quantity and the oil film integrity of the compressor are guaranteed.

The air inlet flow path assembly can effectively improve the resonance point of the refrigerant air inlet flow path and reduce the total noise value in a low frequency band because the traditional liquid distributor component is replaced and cancelled, and the sound radiation area is reduced because the area of the cylinder body is greatly reduced compared with the traditional liquid distributor component, thereby reducing the radiation noise. Meanwhile, because the pressure pulsation of fluid turbulence in a large space of the liquid distributor component is eliminated, the fluid noise (particularly high frequency) during the operation of the compressor can be effectively reduced.

In this scheme, through the experiment discovery, carry out optimal design to inlet flow path barrel diameter, can effectively reduce near 1500 Hz's frequency multiplication peak value to can reduce the noise total value within 1500Hz, promote user experience, simultaneously because the utility model discloses inlet flow path subassembly has characteristics such as the path loss is little, the radiation area is little, can further reduce the pressure pulsation etc. of the radiation noise of compressor, fluid production. In addition the utility model discloses can reduce compressor cost.

For the air inlet flow path component for the double-cylinder rotor compressor, the diameter of the cylinder body is D (cm), and the diameter of the first air inlet branch pipe is D (cm)

The diameter of the second air inlet branch pipe is

When the compressor displacement V cc is constant and V is more than or equal to 14cc and less than or equal to 40cc, D satisfies the relation: V/D is more than or equal to 5.6 and less than or equal to 34, particularly more than or equal to 7 and less than or equal to 25; when V is more than 40cc and less than or equal to 60cc, D satisfies the relation: V/D is more than 16 and less than or equal to 50, particularly more than or equal to 20 and less than or equal to 37.5; when V is more than 60cc and less than or equal to 80cc, D satisfies the relation: V/D is more than 24 and less than or equal to 67, and particularly, V/D is more than or equal to 30 and less than or equal to 50;

the relation should be satisfied:

for the air inlet flow path component for the single-cylinder compressor, when the compressor displacement V cc is constant and V is not less than 7cc and not more than 15cc, the diameter D (cm) of the cylinder body meets the relation: V/D is more than or equal to 2.8 and less than or equal to 12.5, particularly more than or equal to 3.5 and less than or equal to 9.38; the diameter of the air inlet branch pipe is

Satisfy the relation:

the diameter of the filter screen assembly is D1(cm), the diameter of the cylinder body is D (cm), in order to reduce the suction loss of the compressor, D1 is required to be more than or equal to D, and the pressure of a low-pressure refrigerant on the suction side of the compressor is increased by the necking principle of the cylinder body after passing through the filter screen assembly, so that the suction loss of the compressor is reduced, and the efficiency of the compressor is improved.

Through the experiment contrast, the test result sees the attached drawing, adopts the utility model discloses a rotor compressor contrasts with prior art, and the compressor has obvious reduction near 1500Hz noise peak value under same test condition and rotational speed, and especially super high rotational speed falls the noise effect more obvious.

Through getting rid of the knockout structure, the noise problem under wide band operating condition of inverter compressor can effectively be improved according to this scheme to the design of the flow path of admitting air. According to the frequency spectrum within the range of 1000-2000 Hz when the rotating speed of the compressor is 120rps, the frequency spectrum shows that the peak values of the technical scheme of the proposal near 1500Hz are all reduced to a certain extent, and the method is consistent with the expected conclusion. Fig. 8 shows a noise situation of an embodiment of the present technical solution, and from experimental results, compared with the prior art, the present technical solution has a certain improvement effect on noise within 1500Hz for different rotation speeds, so as to improve user experience.

The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention, and various modifications and changes may be made by those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims

1. A compressor, comprising:

a pump body (10), the pump body (10) comprising a crankshaft (11) and a cylinder (12);

air intake assembly (20), air intake assembly (20) include filter house (24) and intake pipe (21), house steward (22) and branch pipe (23) of connecting in proper order, filter house (24) set up in intake pipe (21), branch pipe (23) with the entry intercommunication of cylinder (12).

2. The compressor of claim 1, wherein said pump body (10) includes one said cylinder (12), said pump body (10) has a displacement of Vcc, and said manifold (22) has an internal diameter of Dcm;

wherein V is more than or equal to 7cc and less than or equal to 15cc, and V/D is more than or equal to 2.8 and less than or equal to 12.5.

3. The compressor of claim 2, wherein 3.5 ≦ V/D ≦ 9.38.

4. The compressor of claim 1, wherein the pump body (10) includes two cylinders (12), the pump body (10) has a displacement of Vcc, and the manifold (22) has an internal diameter of Dcm;

wherein V is more than or equal to 14cc and less than or equal to 40cc, and V/D is more than or equal to 5.6 and less than or equal to 34.

5. The compressor of claim 4, wherein 7 ≦ V/D ≦ 25.

6. The compressor of claim 1, wherein the pump body (10) includes two cylinders (12), the pump body (10) has a displacement of Vcc, and the manifold (22) has an internal diameter of Dcm;

wherein V is more than 40cc and less than or equal to 60cc, and V/D is more than 16 and less than or equal to 50.

7. The compressor of claim 6, wherein 20 ≦ V/D ≦ 37.5.

8. The compressor of claim 1, wherein the pump body (10) includes two cylinders (12), the pump body (10) has a displacement of Vcc, and the manifold (22) has an internal diameter of Dcm;

wherein V is more than 60cc and less than or equal to 80cc, and V/D is more than 24 and less than or equal to 67.

9. The compressor of claim 8, wherein 30 ≦ V/D ≦ 50.

10. Compressor according to claim 1, characterized in that the internal diameter of the manifold (22) is D and the external diameter of the filter portion (24) is D1; wherein D1 is more than or equal to D.

11. Root of herbaceous plantCompressor according to claim 1, characterized in that said pump body (10) comprises one of said cylinders (12), said manifold (22) having an internal diameter D and said branch (23) having an internal diameter D

Wherein,

12. compressor according to claim 1, characterized in that the pump body (10) comprises two cylinders (12), the number of branch pipes (23) is two, the two branch pipes (23) and the two cylinders (12) communicate in a one-to-one correspondence, the internal diameter of the manifold (22) is D, and the internal diameter of the branch pipes (23) is D

Wherein,

13. compressor according to claim 1, characterized in that the wall thickness of the header pipe (22) is 1mm to 3mm and the wall thickness of the branch pipe (23) is 1mm to 3 mm.

14. Air conditioning system, characterized in that it comprises a heat exchanger and a compressor according to any one of claims 1 to 13, the intake duct (21) of which communicates with the heat exchanger.