Screw compressor and air conditioner

Abstract

A screw compressor and an air conditioner. The screw compressor comprises a gas discharging bearing seat, an oil separation tank, and a perforated tube. The gas discharging bearing seat is connected to a compressor body and used for supporting a screw rod. The oil separation tank is connected to the compressor body and is fitted over the outer side of the gas discharging bearing seat. The oil separation tank and the gas discharging bearing seat define a gas discharging cavity. The gas discharging cavity is provided with a gas discharging inlet and a gas discharging outlet. Compressed gas flows from the gas discharging inlet to the gas discharging outlet. The perforated tube comprises a tube body and a plurality of through holes distributed in the tube body. The perforated tube is arranged in the gas discharging cavity and located between the gas discharging inlet and the gas discharging outlet. According to the screw compressor, the perforated tube is arranged between the gas discharging inlet and the gas discharging outlet, and the through holes are formed in the tube body of the perforated tube, so that the compressed gas can flow through the through holes on the perforated tube in the process of flowing from the gas discharging inlet to the gas discharging outlet such that the compressed gas flowing through the outer side of the perforated tube and air on the inner side of the perforated tube resonate, and resonance friction is generated at the through holes, thereby consuming sound energy to reduce noise.

Description

Screw compressors and air conditioners

[0001] CROSS-REFERENCE TO RELATED APPLICATIONS

[0002] This disclosure is based on and claims priority to an application with CN application number 202311759706.1 and filing date December 20, 2023. The disclosure content of this CN application is hereby incorporated into this disclosure as a whole. Technical Field

[0003] The present disclosure relates to the technical field of compressors, and in particular to a screw compressor and an air conditioner. Background Art

[0004] The greater the compressor's cooling capacity, the greater the amount of gas compressed per unit time. Due to the periodic connection between the intake and exhaust phases of a screw compressor, the airflow pulsates violently within the exhaust chamber, causing significant vibration and noise. Therefore, reducing compressor vibration and noise is an urgent issue.

[0005] It should be noted that the statements in this background technology section only provide background technology related to the present disclosure and do not necessarily constitute prior art.

[0006] Summary of the Invention

[0007] The present disclosure provides a screw compressor and an air conditioner to reduce noise.

[0008] A first aspect of the present disclosure provides a screw compressor, comprising:

[0009] body;

[0010] An exhaust bearing seat is connected to the machine body and is used to support the screw;

[0011] An oil separator barrel is connected to the engine body and sleeved on the outside of the exhaust bearing seat. The oil separator barrel and the exhaust bearing seat enclose an exhaust cavity, and the exhaust cavity has an exhaust inlet and an exhaust outlet. The compressed gas flows from the exhaust inlet to the exhaust outlet; and

[0012] The perforated pipe comprises a pipe body and a plurality of through holes distributed on the pipe body. The perforated pipe is arranged in the exhaust cavity and is located between the exhaust inlet and the exhaust outlet.

[0013] In some embodiments, the axial direction of the perforated tube is arranged in the same direction as the flow path of the compressed gas.

[0014] In some embodiments, the exhaust inlet and the exhaust outlet are arranged opposite to each other in the same direction.

[0015] In some embodiments, the screw compressor also includes an exhaust tube, which is arranged in the exhaust chamber and close to the exhaust outlet. An air outlet is provided on the wall of the exhaust tube, and the air outlet is connected to the exhaust chamber. The compressed air enters the exhaust tube through the air outlet and is discharged through the exhaust outlet.

[0016] In some embodiments, at least a portion of the perforated tube extends into the interior of the exhaust chimney.

[0017] In some embodiments, a plurality of air outlet holes are arranged at intervals on the wall of the exhaust pipe.

[0018] In some embodiments, the screw compressor includes at least two damping chambers spaced apart in the circumferential direction of the perforated tube, the damping chamber is formed on the wall of the oil separator barrel, and the damping chamber has a perforation communicating with the exhaust chamber gas.

[0019] In some embodiments, the screw compressor includes at least two damping chambers spaced apart in the axial direction of the perforated tube.

[0020] In some embodiments, the wall of the oil separator barrel has a channel that runs through in the thickness direction of the wall, and the screw compressor includes a perforated cover plate arranged on the inner end surface of the channel and a closed cover plate arranged on the outer end surface of the channel, and the perforated cover plate is provided with through holes.

[0021] In some embodiments, a plurality of through holes are provided on the perforated cover plate, wherein the plurality of through holes are evenly distributed on the perforated cover plate; or, the plurality of through holes include a first through hole group and a second through hole group located at different positions of the perforated cover plate, wherein the distribution density of the through holes in the first through hole group is greater than the distribution density of the through holes in the second through hole group.

[0022] A second aspect of the present disclosure provides an air conditioner comprising the above-mentioned screw compressor.

[0023] Based on the technical solution provided by the present disclosure, the screw compressor includes a body, an exhaust bearing seat, an oil separator barrel and a perforated pipe. The exhaust bearing seat is connected to the body and is used to support the screw. The oil separator barrel is connected to the body and is sleeved on the outside of the exhaust bearing seat. The oil separator barrel and the exhaust bearing seat enclose an exhaust chamber. The exhaust chamber has an exhaust inlet and an exhaust outlet. The compressed gas flows from the exhaust inlet to the exhaust outlet. The perforated pipe includes a pipe body and a plurality of through holes distributed on the pipe body. The perforated pipe is arranged in the exhaust chamber and is located between the exhaust inlet and the exhaust outlet. The screw compressor of the embodiment of the present disclosure is provided with a through hole on the pipe body by arranging a perforated pipe between the exhaust inlet and the exhaust outlet. The compressed gas flows through the through holes on the perforated pipe in the process of flowing from the exhaust inlet to the exhaust outlet, so that the compressed gas flowing through the outside of the perforated pipe and the air inside the perforated pipe resonate, and resonant friction is generated at the through holes, thereby consuming sound energy and reducing noise.

[0024] Other features and advantages of the present disclosure will become apparent from the following detailed description of exemplary embodiments of the present disclosure with reference to the accompanying drawings. BRIEF DESCRIPTION OF THE DRAWINGS

[0025] The drawings described herein are used to provide a further understanding of the present disclosure and constitute a part of this application. The illustrative embodiments of the present disclosure and their descriptions are used to explain the present disclosure and do not constitute an improper limitation of the present disclosure. In the drawings:

[0026] FIG1 is a schematic cross-sectional view of the exhaust chamber of a screw compressor according to an embodiment of the present disclosure.

[0027] FIG2 is a schematic cross-sectional structural diagram of another cross section of the exhaust chamber of the screw compressor according to an embodiment of the present disclosure.

[0028] FIG3 is a schematic structural diagram of a damping chamber of a screw compressor according to an embodiment of the present disclosure.

[0029] FIG4 is a schematic structural diagram of the perforated cover plate of the attenuation cavity shown in FIG3 .

[0030] FIG5 is a structural principle diagram of a Helmholtz resonator. DETAILED DESCRIPTION

[0031] The following will be combined with the drawings in the embodiments of the present disclosure to clearly and completely describe the technical solutions in the embodiments of the present disclosure. Obviously, the described embodiments are only part of the embodiments of the present disclosure, rather than all the embodiments. The following description of at least one exemplary embodiment is actually only illustrative and is in no way intended to limit the present disclosure and its application or use. Based on the embodiments in the present disclosure, all other embodiments obtained by ordinary technicians in this field without making creative work are within the scope of protection of the present disclosure.

[0032] Unless otherwise specifically stated, the relative arrangement of the parts and steps, numerical expressions and numerical values ​​set forth in these embodiments do not limit the scope of the present disclosure. At the same time, it should be understood that, for ease of description, the sizes of the various parts shown in the drawings are not drawn according to actual proportional relationships. The technology, methods and equipment known to those of ordinary skill in the relevant art may not be discussed in detail, but in appropriate cases, the technology, methods and equipment should be considered as part of the specification. In all examples shown and discussed here, any specific value should be interpreted as being merely exemplary, rather than as a limitation. Therefore, other examples of the exemplary embodiments may have different values. It should be noted that similar numbers and letters represent similar items in the following figures, and therefore, once an item is defined in one figure, it does not need to be further discussed in subsequent figures.

[0033] For ease of description, spatially relative terms such as "above", "above", "on the upper surface of", "above", etc. may be used herein to describe the spatial positional relationship of a device or feature to other devices or features as shown in the figures. It should be understood that spatially relative terms are intended to include different orientations of the device in use or operation in addition to the orientation described in the figures. For example, if the device in the drawings is inverted, the device described as "above other devices or structures" or "above other devices or structures" will be subsequently positioned as "below other devices or structures" or "below other devices or structures". Thus, the exemplary term "above" can include both "above" and "below". The device may also be positioned in other different ways, and the spatially relative descriptions used herein are interpreted accordingly.

[0034] The screw compressor includes an exhaust bearing seat. The exhaust bearing seat is used to support the screw arranged in the compressor housing. The noise of the screw compressor includes exhaust noise. As the rotor rotates, the gas from different tooth grooves is discharged periodically, and the exhaust pressure also fluctuates, thereby generating periodic exhaust noise. It should be noted that this application does not impose any restrictions on the screw compressor and the screw, and it can be any structure that can realize the function of the compressor, and therefore, the specific description and illustration of the structure of the screw compressor and the screw are omitted here.

[0035] In order to reduce exhaust noise, the present disclosure proposes to set a perforated tube in the exhaust chamber of the screw compressor. The pulsating airflow continuously flows through the through holes on the perforated tube, forming a long-term resonance, generating vibration friction on the wall of the hole, consuming sound energy, and thus reducing noise.

[0036] The structure and working process of the screw compressor of some embodiments of the present disclosure are described in detail below with reference to Figures 1 to 4.

[0037] 1 and 2 , the screw compressor provided by the embodiment of the present disclosure includes a body (not shown in the figures), an exhaust bearing seat 10, an oil separator barrel 20 and a perforated tube 50. The exhaust bearing seat 10 is connected to the body and is used to support the screw. The oil separator barrel 20 is connected to the body and is sleeved on the outside of the exhaust bearing seat 10. The oil separator barrel 20 and the exhaust bearing seat 10 enclose an exhaust chamber 40. The exhaust chamber 40 has an exhaust inlet 410 and an exhaust outlet 420. The compressed gas flows from the exhaust inlet 410 to the exhaust outlet 420. The perforated tube 50 includes a tube body and a plurality of through holes distributed on the tube body. The perforated tube 50 is arranged in the exhaust chamber 40 and is located between the exhaust inlet 410 and the exhaust outlet 420.

[0038] The screw compressor of the embodiment of the present disclosure arranges a perforated tube 50 between the exhaust inlet 410 and the exhaust outlet 420, and a through hole is provided on the tube body of the perforated tube 50. In this way, the compressed gas flows through the through holes on the perforated tube 50 in the process of flowing from the exhaust inlet 410 to the exhaust outlet 420, so that the compressed gas flowing through the outside of the perforated tube 50 and the air inside the perforated tube 50 resonate, and resonant friction is generated at the through holes, thereby consuming sound energy and reducing noise.

[0039] [Corrected 08.11.2024 according to Rule 91] Referring to Figure 5, the principle of the Helmholtz resonator is to use the resonance of the air flow outside the cavity and the air inside the cavity to generate resonant friction at the opening, thereby achieving the effect of consuming sound energy. As shown in Figure 5, the resonant frequency Among them, L K =t + 0.8d, where c is the speed of sound, V is the cavity volume, d is the diameter of the through-hole, S is the area of ​​the through-hole, and t is the wall thickness. Wall thickness refers to the thickness of the cavity wall separating the inside and outside of the cavity. The through-hole extends through the thickness of the cavity wall, so the wall thickness t also represents the axial length of the through-hole. Based on this principle, by rationally arranging the size and density of the through-holes in the perforated tube 50, a series Helmholtz resonator is formed to eliminate low-frequency noise.

[0040] In some embodiments, the through holes on the perforated tube 50 are circular holes.

[0041] Referring to Figure 1 , in some embodiments, the perforated tube 50 has a cylindrical body. Multiple, evenly distributed through-holes are provided on the cylindrical body. The axial end faces of the perforated tube 50 are sealed. The circumferential wall of the perforated tube 50 is provided with through-holes, thereby forming a resonant cavity. As the compressed gas flows through the outer surface of the perforated tube 50, it resonates with the air inside the perforated tube at the through-holes, generating resonant friction at the through-holes, thereby dissipating acoustic energy.

[0042] In some embodiments, the perforated tube 50 is provided with multiple through-hole groups spaced apart in the axial direction. Each through-hole group includes multiple through-holes arranged in the circumferential direction. The multiple through-holes in each through-hole group are located at the same axial position, forming a through-hole ring around the axis of the perforated tube 50. This allows the multiple through-hole groups of the perforated tube 50 to form a series-connected Helmholtz resonator, thereby eliminating noise.

[0043] Referring to Figures 1 and 2, in some embodiments, the axial direction of the perforated tube 50 is arranged in the same direction as the flow path of the compressed gas. That is, the axial direction of the perforated tube 50 is in the same direction as the flow path of the compressed gas. As shown in Figure 1, the axial direction of the perforated tube 50 is arranged along a horizontal line. Similarly, the compressed gas flowing from the exhaust inlet 410 to the exhaust outlet 420 is also arranged along a horizontal line. In this way, the compressed gas entering the exhaust chamber from the exhaust inlet 410 will pass through the perforated tube 50 on the way to the exhaust outlet 420, thereby causing the compressed gas to resonate in the resonator formed by the perforated tube 50, thereby eliminating noise. In some embodiments not shown in the figures, for example, if the flow path of the compressed gas is not a straight line but a curved type, then the axial direction of the perforated tube 50 can also be set to a curved type arranged in the same direction as the flow path of the compressed gas. In this case, the perforated tube is a curved tube.

[0044] In some embodiments, the exhaust inlet 410 and the exhaust outlet 420 are arranged relative to each other in the same direction. The phrase "exhaust inlet 410 and exhaust outlet 420 are arranged relative to each other in the same direction" here refers to the exhaust inlet 410 and exhaust outlet 420 being located in the same direction. For example, in the embodiment shown in FIG1 , the exhaust inlet 410 and exhaust outlet 420 are both horizontal. This results in a straight flow path for the compressed gas. Placing the exhaust inlet 410 and exhaust outlet 420 in the same direction ensures that all gas is discharged only through the resonance silencing effect of the perforated tube, thereby improving the silencing effect.

[0045] Referring to FIG. 1 , in some embodiments, an exhaust chamber is formed by enclosing an oil separator barrel 20 and an exhaust bearing housing 10 . The oil separator barrel 20 includes a first segment and a second segment arranged in the axial direction. The cross-sectional area of ​​the first segment is larger than that of the second segment, and the second segment is retracted inward relative to the first segment. This forms the exhaust chamber 40 as a cavity communicating from the exhaust inlet 410 to the exhaust outlet 420 . The perforated tube 50 is disposed within the cavity, thereby causing the compressed gas to flow through the perforated tube 50 through resonance, thereby reducing noise.

[0046] In order to further improve the noise reduction effect, referring to Figures 1 and 2, in some embodiments, the screw compressor further includes an exhaust pipe 30. The exhaust pipe 30 is arranged in the exhaust chamber 40 and is arranged near the exhaust outlet 420. The first end of the perforated tube 50 is connected to the oil separator barrel 20, and the second end of the perforated tube 50 is connected to the exhaust pipe 30. An air outlet 310 is provided on the wall of the exhaust pipe 30. The air outlet 310 is connected to the exhaust chamber 40. In this way, the compressed gas that has been subjected to vibration and noise reduction through the perforated tube 50 enters the exhaust pipe 30 through the air outlet 310 and is discharged through the exhaust outlet 420. The arrangement of the exhaust pipe 30 ensures that all air flows need to pass through the air outlet 310 on the exhaust pipe 30 to enter the exhaust pipe 30 before being discharged through the exhaust outlet 420. This slows down the speed of gas outflow, thereby deepening the resonance effect of the air flow through the perforated tube 50, and further improving the noise reduction effect.

[0047] As shown in Figures 1 and 2 , the first end of the exhaust pipe 30 is sealed with the perforated tube 50. The second end of the exhaust pipe 30 is connected to the oil separator barrel 20. The first end of the exhaust pipe 30 is sealed with the perforated tube 50, and the second end of the exhaust pipe 30 is open and communicates with the exhaust outlet 420. As shown in Figures 1 and 2 , the inner wall of the oil separator barrel 20 is provided with an annular boss for engaging the exhaust pipe 30. The exhaust end of the exhaust pipe 30 is engaged with the annular boss of the exhaust pipe 30.

[0048] 1 , in some embodiments, at least a portion of the perforated tube 50 extends into the exhaust pipe 30. This allows the compressed gas entering the exhaust pipe 30 through the air outlet 310 to resonate and reduce noise through the through holes in the portion of the perforated tube 50 that extends into the exhaust pipe 30, further reducing noise.

[0049] Referring to Figures 1 and 2 , in some embodiments, a plurality of air outlet holes 310 are spaced apart on the wall of the exhaust cylinder 30. Providing multiple air outlet holes 310 connects the exhaust chamber and the exhaust outlet, thereby preventing excessive pressure caused by gas accumulation in the exhaust chamber and inability to be discharged, thereby improving operational reliability. Specifically, the air outlet holes 310 are circular holes.

[0050] In order to further improve the noise reduction effect, in some embodiments, the screw compressor includes at least two attenuation chambers 210 spaced apart in the circumferential direction of the perforated tube 50. The attenuation chamber 210 is formed on the barrel wall of the oil separator barrel 20. The attenuation chamber 210 has a through hole connected to the exhaust chamber gas. The attenuation chamber 210 has a through hole to form a Helmholtz resonator. The attenuation chamber 210 and the perforated tube 50 together form a silencer structure. The screw compressor of the embodiment of the present disclosure eliminates low-frequency noise by setting the perforated tube 50, and eliminates high-frequency noise by setting the attenuation chamber 210. In this way, the cooperation of the perforated tube 50 and the attenuation chamber 210 can eliminate noise in different frequency bands, thereby more comprehensively reducing the noise of the screw compressor.

[0051] In some embodiments, the screw compressor includes at least two damping chambers 210 spaced apart in the axial direction of the perforated tube 50. Exhaust gas flows into the exhaust chamber from the exhaust inlet, and the gas sequentially flows through the at least two damping chambers and the perforated tube 50 to improve the noise reduction effect.

[0052] As shown in Figures 3 and 4, in some embodiments, the wall of the oil separator drum 20 has a channel extending through the wall thickness. The screw compressor includes a perforated cover plate 70 disposed on the inner end surface of the channel and a closed cover plate 60 disposed on the outer end surface of the channel. The perforated cover plate 70 is provided with a through hole 710. The inner end surface here refers to the end closest to the exhaust chamber, while the outer end surface refers to the end away from the exhaust chamber. The through hole 710 in the perforated cover plate 70 enables the attenuation chamber to form a Helmholtz resonator.

[0053] 4 , the plurality of through holes 710 on the perforated cover plate 70 have the same size and are evenly distributed on the perforated cover plate 70 .

[0054] In other embodiments not shown in the accompanying drawings, the perforated cover plate is provided with a plurality of through holes. The plurality of through holes includes a first through hole group and a second through hole group located at different positions on the perforated cover plate. The distribution density of the through holes in the first through hole group is greater than the distribution density of the through holes in the second through hole group.

[0055] In some embodiments, the apertures of the through holes in the first through hole group are smaller than the apertures of the through holes in the second through hole group, and the through holes in the first through hole group are evenly distributed. The through holes in the second through hole group are also evenly distributed.

[0056] Furthermore, as shown in FIG3 , multiple channels share the same closed cover plate 60 to form mutually independent attenuation cavities, which can simplify the manufacturing steps and reduce the manufacturing difficulty.

[0057] The present disclosure also provides an air conditioner including the screw compressor. The air conditioner using the screw compressor can reduce noise.

[0058] The structure of a screw compressor according to a specific embodiment of the present disclosure will be described in detail below with reference to FIG. 1 to FIG. 4 .

[0059] As shown in FIG. 1 and FIG. 2 , the screw compressor includes an exhaust bearing housing 10 , an oil separator barrel 20 , a perforated tube 50 and a plurality of attenuation chambers 210 .

[0060] The exhaust bearing housing 10 and the oil separator barrel 20 enclose an exhaust chamber 40. The exhaust chamber 40 has an exhaust inlet 410 and an exhaust outlet 420. The perforated tube 50 is disposed between the exhaust inlet 410 and the exhaust outlet 420. A plurality of attenuation chambers 210 are disposed around the circumference of the perforated tube 50 and arranged along the flow path of the compressed air.

[0061] In this way, the perforated tube 50 and the multiple attenuation chambers 210 of this embodiment together form a silencer for the exhaust chamber. As shown in Figure 1, the exhaust gas flows into the exhaust chamber from the exhaust inlet 410 on the left side, and the gas passes through the multiple attenuation chambers 210 arranged in the axial direction in sequence. The multiple attenuation chambers 210 are arranged in the circumferential direction of the airflow. Under the premise of meeting reliability, the cross-sectional shape of the attenuation chamber can be circular or other shapes for pulsating airflow noise in different frequency bands. The size and number of the attenuation chambers can also be adjusted. At the same time, the size, number and arrangement of the through holes 710 on the perforated cover plate of the attenuation chamber can be adjusted to form a parallel Helmholtz resonator to eliminate noise in a wider frequency band.

[0062] The two ends of the perforated tube 50 are fixed in the exhaust cavity in an embedded manner. The pulsating airflow continuously flows through the through holes on the perforated tube 50, forming a long-term resonance, generating vibration friction on the wall surface of the hole, consuming sound energy, and reasonably arranging the size and density of the holes in the microporous perforated tube to form a series Helmholtz resonator to eliminate low-frequency noise.

[0063] The exhaust silencer structure composed of perforated tubes and attenuation chambers effectively solves the problem of excessive noise in high-refrigeration-capacity compressors and the vibration problem caused by pulsating airflow. Due to the noise attenuation offset of variable-frequency compressors, this silencer structure is also suitable for variable-frequency screw compressors.

[0064] In some embodiments, a sound absorbing material is disposed in the attenuation cavity.

[0065] The screw compressor of this embodiment forms a combined silencer structure by adding a perforated tube and an attenuation chamber. The attenuation chamber and the perforated tube are reasonably arranged around the air flow path. The pulsating airflow flowing through the perforated tube eliminates low- and high-frequency noise in multiple layers. In conjunction with the attenuation chamber, the natural frequency of the exhaust attenuation chamber is made consistent with the frequency of the exhaust airflow noise, forming resonance, generating vibration friction on the orifice wall, consuming sound energy, and thus achieving a noise reduction effect.

[0066] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present disclosure and not to limit it. Although the present disclosure has been described in detail with reference to the preferred embodiments, ordinary technicians in the relevant field should understand that the specific implementation methods of the present disclosure can still be modified or some technical features can be replaced by equivalents without departing from the spirit of the technical solutions of the present disclosure, which should all be included in the scope of the technical solutions requested for protection in the present disclosure.

Claims

1. A screw compressor, comprising: Body; An exhaust bearing seat (10), connected to the machine body and used to support the screw; an oil separator barrel (20) connected to the machine body and sleeved on the outer side of the exhaust bearing seat (10); the oil separator barrel (20) and the exhaust bearing seat (10) enclose an exhaust chamber (40); the exhaust chamber (40) has an exhaust inlet (410) and an exhaust outlet (420); compressed gas flows from the exhaust inlet (410) to the exhaust outlet (420); and A perforated pipe (50) comprises a pipe body and a plurality of through holes distributed on the pipe body. The perforated pipe (50) is arranged in the exhaust cavity (40) and is located between the exhaust inlet (410) and the exhaust outlet (420).

2. The screw compressor according to claim 1, wherein: The axial direction of the perforated tube (50) is arranged in the same direction as the flow path of the compressed gas.

3. The screw compressor according to claim 1, wherein: The exhaust inlet (410) and the exhaust outlet (420) are arranged opposite to each other in the same direction.

4. The screw compressor according to claim 1, further comprising an exhaust tube (30), wherein the exhaust tube (30) is arranged in the exhaust chamber (40) and close to the exhaust outlet (420), and an air outlet hole (310) is arranged on the tube wall of the exhaust tube (30), wherein the air outlet hole (310) is communicated with the exhaust chamber (40), and compressed air enters into the exhaust tube (30) through the air outlet hole (310) and is discharged through the exhaust outlet (420).

5. The screw compressor according to claim 4, wherein: A plurality of the air outlet holes (310) are arranged at intervals on the wall of the exhaust pipe (30).

6. A screw compressor according to any one of claims 1 to 5, comprising at least two damping chambers (210) spaced apart in the circumferential direction of the perforated tube (50), wherein the damping chamber (210) is formed on the cylinder wall of the oil separation barrel (20), and the damping chamber (210) has a through hole (710) connected to the exhaust chamber gas.

7. The screw compressor according to claim 6, comprising at least two damping chambers (210) spaced apart in the axial direction of the perforated tube (50).

8. The screw compressor according to claim 6, wherein: The barrel wall of the oil separator barrel (20) has a channel that penetrates in the thickness direction of the barrel wall, and the screw compressor comprises a perforated cover plate (70) arranged on the inner end surface of the channel and a closed cover plate (60) arranged on the outer end surface of the channel, and the through hole (710) is arranged on the perforated cover plate (70).

9. The screw compressor according to claim 8, wherein: The perforated cover plate (70) is provided with a plurality of through holes (710), wherein the plurality of through holes (710) are evenly distributed on the perforated cover plate (70); or, the plurality of through holes (710) include a first through hole group and a second through hole group respectively located at different positions of the perforated cover plate (70), wherein the distribution density of the through holes in the first through hole group is greater than the distribution density of the through holes in the second through hole group.

10. An air conditioner comprising the screw compressor according to any one of claims 1 to 9.

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