Compressor and air conditioning system comprising same

Abstract

The invention provides a compressor and an air conditioning system comprising the same. The compressor includes an exhaust flow passage. The exhaust flow channel comprises an upstream flow channel and two downstream flow channels. The two downstream flow channels are in fluid communication with the upstream flow channel. Each of the two downstream flow channels extends substantially along a straight line or a smooth curve. The upstream flow channel and the downstream flow channel are configured in the mode that when fluid flows into the downstream flow channel from the upstream flow channel, the deflection angle of the flowing direction of the fluid is smaller than 90 degrees. Fluid in the exhaust flow channel flows smoothly, the exhaust pressure loss can be controlled at a very low level, so that the performance of a compressor is improved, the noise of the compressor and an air conditioning system can be reduced, the service life of a pipeline system is prolonged, and the exhaust flow channel is simple and compact in structure and convenient to manufacture.

Description

Technical Field

[0001] Embodiments of the present disclosure generally relate to the field of air conditioning systems, and more particularly to a compressor and an air conditioning system including the compressor. Background Art

[0002] The compressor is an important part of the air conditioning system. Currently, the main application in the industrial field is the twin-screw compressor. The twin-screw compressor gradually compresses the gas refrigerant in the compression chamber of the compressor through the rotation and meshing of the female and male screws. The compressed high-pressure gas refrigerant enters the exhaust chamber of the compressor from the compression chamber through the internal exhaust orifice, and then enters the exhaust pipeline and equipment downstream of the compressor through the exhaust port of the exhaust chamber. Summary of the invention

[0003] According to a first aspect of the present disclosure, the present disclosure provides a compressor. The compressor includes an exhaust flow channel. The exhaust flow channel includes an upstream flow channel and two downstream flow channels. The two downstream flow channels are in fluid communication with the upstream flow channel. Each of the two downstream flow channels extends substantially along a straight line or a smooth curve. The upstream flow channel and the downstream flow channel are configured such that when a fluid flows from the upstream flow channel into the downstream flow channel, the deflection angle of the flow direction of the fluid is less than 90°.

[0004] According to the compressor of the first aspect, the upstream flow passage extends substantially in the first direction and defines the air inlet of the exhaust flow passage. Each of the downstream flow passages includes an inlet end and an outlet end, the inlet end is connected to the upstream flow passage, and the outlet end defines the exhaust port of the exhaust flow passage. Each of the downstream flow passages extends substantially obliquely to the first direction and extends away from the axis of the upstream flow passage, so that in the first direction, the distance D2 between the outlet end of each downstream flow passage and the air inlet is greater than the distance D1 between the inlet end and the air inlet.

[0005] According to the compressor of the first aspect, the two downstream flow passages are symmetrically arranged on opposite sides of the upstream flow passage in the radial direction, and together with the upstream flow passage form the substantially Y-shaped exhaust flow passage.

[0006] According to the compressor of the first aspect, the two downstream flow passages extend along straight lines respectively, and the angle between the center lines of the two downstream flow passages is greater than 85° and less than 125°.

[0007] According to the compressor of the first aspect above, each of the downstream flow channels includes an inlet end section, an outlet end section and a middle section, and the middle section is located in the middle position of the downstream flow channel, wherein the area S1 of the inlet end section is greater than the area S3 of the middle section, and the area S2 of the outlet end section is greater than the area S3 of the middle section.

[0008] According to the compressor of the first aspect, the area S3 of the intermediate cross section and the area S1 of the inlet end cross section satisfy and / or the area S3 of the middle cross section and the area S2 of the outlet cross section satisfy

[0009]

[0010] According to the compressor of the first aspect, the inlet end cross section and / or the outlet end cross section and / or the middle cross section are substantially elliptical, circular or quadrilateral in shape.

[0011] According to the compressor of the first aspect, the shape of the inlet end section and / or the outlet end section and / or the middle section is substantially elliptical, and the major axis of the ellipse is coplanar with the axis of the upstream flow channel and the axis of the downstream flow channel.

[0012] According to the compressor of the first aspect, the compressor further comprises an exhaust section. The exhaust section comprises a shell, a core and an intermediate chamber. The core is arranged on the inner side of the shell and defines the exhaust flow channel. The intermediate chamber is formed between the shell and the core. The shell is provided with an exhaust valve, which communicates with the inner side and the outer side of the shell and is fluidically connected with the downstream flow channel via the intermediate chamber.

[0013] According to the compressor of the first aspect, the compressor is a twin-screw compressor, and the twin-screw compressor further includes a screw segment, and the screw segment includes a compression chamber and a gas outlet, and the upstream flow channel is connected to the compression chamber fluid via the gas outlet.

[0014] According to a second aspect of the present disclosure, the present disclosure provides an air conditioning system, which includes the compressor according to the above first aspect. BRIEF DESCRIPTION OF THE DRAWINGS

[0015] Figure 1 is a schematic block diagram of an air conditioning system according to an embodiment of the present disclosure;

[0016] Figure 2 is a perspective view of a compressor according to one embodiment of the present disclosure;

[0017] Figure 3 yes Figure 2 A three-dimensional diagram of a screw segment in FIG.

[0018] Figure 4A yes Figure 2 A three-dimensional diagram of the exhaust section in FIG.

[0019] Figure 4B yes Figure 2A rear view of the exhaust section in FIG.

[0020] Figure 4C is along Figure 4B The cross-sectional view of line AA in the figure;

[0021] Figure 4D is along Figure 4B The cross-sectional view of line BB in FIG.

[0022] Figure 5 is a schematic diagram of a Y-shaped exhaust flow passage according to an embodiment of the present disclosure;

[0023] Figure 6 is a cross-sectional view of an exhaust section according to a comparative example;

[0024] Fig. 7A is a fluid simulation result of a Y-shaped exhaust flow channel according to an embodiment of the present disclosure;

[0025] Figure 7B It is the fluid simulation result of a T-shaped exhaust flow channel according to a comparative example.

[0026] It should be understood that the accompanying drawings are not necessarily drawn to scale. In some cases, details that are not necessary for understanding the present invention or that make other details difficult to perceive may be omitted. Where appropriate, similar or identical reference numerals are used to represent similar or identical parts. DETAILED DESCRIPTION

[0027] Various specific embodiments of the present disclosure will be described below with reference to the accompanying drawings that form a part of this specification. It should be understood that although terms indicating directions, such as "front", "rear", "upper", "lower", "left", "right", "top", "bottom", etc., are used in the present disclosure to describe various example structural parts and elements of the present disclosure, these terms are used here only for the purpose of convenience of description and are determined based on the example orientations shown in the accompanying drawings. Since the embodiments of the present disclosure can be set in different directions, these terms indicating directions are only for illustration and should not be regarded as limitations. In addition, it should be understood that certain features, structures or characteristics in one or more embodiments of the present disclosure may be appropriately combined.

[0028] Figure 1 is a schematic block diagram of an air conditioning system 100 according to an embodiment of the present disclosure. Figure 1As shown, the air conditioning system 100 includes a compressor 110, a condenser 120, a throttling device 130 and an evaporator 140, which are connected to form a closed system through pipelines, and a heat transfer fluid, such as a refrigerant, is filled in the system. The heat transfer fluid flows through the compressor 110, the condenser 120, the throttling device 130 and the evaporator 140 in sequence, so that the air conditioning system 100 can cool or heat the outside.

[0029] Specifically, the high-pressure gas refrigerant discharged from the compressor 110 flows into the condenser 120, releases heat in the condenser 120 and is condensed into a high-pressure liquid refrigerant, then flows into the throttling device 130, is throttled into a low-pressure liquid refrigerant in the throttling device 130, then flows into the evaporator 140, absorbs heat in the evaporator 140 and is evaporated into a low-pressure gas refrigerant, and finally flows back into the compressor 110, completing the refrigerant cycle.

[0030] Figure 2 FIG. 1 is a schematic diagram of the structure of a compressor 110 according to an embodiment of the present disclosure. The compressor 110 is a twin-screw compressor. Figure 2 As shown, the compressor 110 includes a motor 210, a screw section 220 and an exhaust section 230. The motor 210 is used to drive the screw of the screw section 220 to rotate, the screw section 220 is used to compress the gas refrigerant, and the exhaust section 230 is used to discharge the compressed high-pressure gas refrigerant to the exhaust pipeline and equipment (such as the condenser 120) downstream of the compressor 110.

[0031] Figure 3 yes Figure 2 Schematic diagram of the structure of the screw segment 220 of the compressor 110. Figure 3 As shown, the screw section 220 includes a male screw 310, a female screw 320, a compression chamber 330 and a gas outlet 340. The gas refrigerant from the upstream of the compressor 110 enters the compression chamber 330 from the suction port (not shown) arranged diagonally with the gas outlet 340, and is compressed by the rotational engagement of the male screw 310 and the female screw 320. The compressed high-pressure gas refrigerant is discharged to the exhaust section 230 of the compressor 110 via the gas outlet 340.

[0032] Figure 4A-4D yes Figure 2 A schematic diagram of the structure of the exhaust section 230 of the compressor 110. Figure 4A is a perspective view of the exhaust section 230, Figure 4B is a rear view of the exhaust section 230, Figure 4C is along Figure 4B The cross-sectional view of line AA in the figure, Figure 4D is along Figure 4B Cross-sectional view of line BB in . Figure 5 yes Figure 4A-4DA simplified schematic diagram of the exhaust flow passage 430 in FIG.

[0033] like Figure 4A-4D and Figure 5 As shown, the exhaust section 230 includes a shell 410, a core 420, an exhaust flow passage 430, and an intermediate chamber 440. The core 420 is disposed inside the shell 410 and defines the exhaust flow passage 430. The intermediate chamber 440 is formed between the shell 410 and the core 420.

[0034] The exhaust flow passage 430 includes an air inlet 431, two exhaust ports 432, an upstream flow passage 433, and two downstream flow passages 434. The inlet end 510 of the upstream flow passage 433 defines the air inlet 431. The air inlet 431 is fluidly connected to the gas outlet 340 of the screw segment 220, so that the upstream flow passage 433 is fluidly connected to the compression chamber 330 via the gas outlet 340 to receive the compressed high-pressure gas refrigerant discharged from the compression chamber 330. The inlet end 520 of each downstream flow passage 434 is fluidly connected to the upstream flow passage 433, and the outlet end 530 of each downstream flow passage 434 defines the exhaust port 432. The downstream flow passage 434 is fluidly connected to the intermediate chamber 440 via the exhaust port 432.

[0035] The housing 410 is provided with an exhaust valve 450, for example, disposed at one end of the housing 410 away from the screw section 220. The exhaust valve 450 communicates with the intermediate chamber 440 inside the housing 410 and the exhaust pipeline (not shown) outside the housing 410, so that the two exhaust ports 432 are fluidly connected to the exhaust pipeline and equipment downstream of the compressor 110 through one exhaust valve 450, so as to simplify the structure and facilitate connection.

[0036] Therefore, after the high-pressure gas refrigerant discharged from the screw section 220 of the compressor 110 flows into the exhaust flow channel 430 through the air inlet 431, it first flows along the upstream flow channel 433, and then is divided into two parts. The two parts flow along two downstream flow channels 434 respectively, and then flow into the intermediate chamber 440 through the exhaust port 432, and finally are discharged to the exhaust pipeline and equipment downstream of the compressor 110 through the exhaust valve 450.

[0037] In the twin-screw compressor 110, due to the rotational meshing of the male screw 310 and the female screw 320, the elementary volume between the relative tooth surfaces of the male screw 310 and the female screw 320 is periodically connected to the gas outlet 340, causing the flow of the gas refrigerant to be a periodic pulsed flow, generating air flow pulsation, and the induced pneumatic noise becomes the main noise source of the compressor 110. In addition, the air flow pulsation during the exhaust process of the compressor 110 will also stimulate the pipeline system to generate vibration radiation noise when propagating downstream, and even cause destructive consequences such as fatigue fracture of the pipeline system.

[0038] In a conventional twin-screw compressor, the exhaust flow channel is a single exhaust flow channel, and all high-pressure gas refrigerant flowing into the exhaust flow channel from the screw section of the compressor flows along the single exhaust flow channel to a single exhaust port, and then flows out of the compressor from the single exhaust port.

[0039] In contrast, the exhaust flow channel 430 of the embodiment of the present disclosure adopts a dual exhaust structure, that is, two forked downstream flow channels 434 are provided, so that the high-pressure gas refrigerant is divided into two parts, which flow along the two downstream flow channels 434 to the two exhaust ports 432 respectively. Therefore, compared with the conventional single exhaust flow channel, the two forked downstream flow channels 434 can use pipelines with smaller diameters, so that the pipeline wall stiffness is relatively high and the sound radiation surface area of ​​the pipeline is relatively small. Therefore, under the same excitation force, the vibration response magnitude of the pipeline wall is relatively low, and the sound radiation energy of the pipeline is relatively low, which can reduce the noise of the compressor 110 and the air-conditioning system 100, improve the service life of the pipeline system, and achieve a shorter and simpler exhaust layout.

[0040] Continue to refer to Figure 4A-4D and Figure 5 , the upstream flow channel 433 of the exhaust flow channel 430 extends substantially along the first direction X, that is, extends along the direction of the axis OA of the upstream flow channel 433. Each downstream flow channel 434 extends substantially along a straight line. The upstream flow channel 433 and the downstream flow channel 434 are configured so that when a fluid (e.g., a gas refrigerant) flows from the upstream flow channel 433 into the downstream flow channel 434, the deflection angle α of the flow direction of the fluid is less than 90°.

[0041] Specifically, each downstream flow channel 434 extends substantially obliquely to the first direction X and extends away from the axis OA of the upstream flow channel 433. For example, the angle between the center lines OB and OC of the two downstream flow channels 434 is greater than 85° and less than 125°, so that in the first direction X, the distance D2 between the outlet end 530 of each downstream flow channel 434 and the air inlet 431 is greater than the distance D1 between the inlet end 520 of the downstream flow channel 434 and the air inlet 431. The two downstream flow channels 434 are symmetrically arranged on opposite sides of the upstream flow channel 433 in the radial direction, and together with the upstream flow channel 433, form a substantially "Y"-shaped exhaust flow channel 430.

[0042] Each downstream flow channel 434 includes an inlet end section 501 located at the inlet end 520, an outlet end section 502 located at the outlet end 530, and a middle section 503 located at the middle position of the downstream flow channel 434. Figure 5 In the orientation shown, the intermediate section 503 passes through the center point D on the upper boundary and the center point E on the lower boundary of the downstream flow channel 434.

[0043] The cross section of the downstream flow channel 434 shows a trend of first decreasing and then increasing. Specifically, the area S1 of the inlet end cross section 501 is designed to be larger than the area S3 of the middle cross section 503. For example, the area S1 of the inlet end cross section 501 and the area S3 of the middle cross section 503 satisfy The area S2 of the outlet cross section 502 is designed to be larger than the area S3 of the middle cross section 503. For example, the area S2 of the outlet cross section 502 and the area S3 of the middle cross section 503 satisfy The downstream flow channel 434 gradually transitions from the inlet end section 501 to the middle section 503 , and gradually transitions from the middle section 503 to the outlet end section 502 .

[0044] The shape of the inlet end section 501 and / or the outlet end section 502 and / or the middle section 503 is generally an ellipse, and the major axis of the ellipse is coplanar with the axis OA of the upstream flow channel 433 and the axes OB and OC of the downstream flow channel 434, that is, the major axis of the ellipse is along Figure 5 In other embodiments, the inlet end cross section 501 and / or the outlet end cross section 502 and / or the middle cross section 503 are substantially circular or quadrilateral with rounded corners.

[0045] The structure between the exhaust flow channel and the downstream exhaust pipeline has a great influence on the exhaust pressure loss, especially for a small rotor and high-speed screw compressor. In order to pursue high performance and achieve the goals of energy saving and emission reduction, it is particularly important to control the pressure loss of the exhaust flow channel at a very low level in a compact structure. The exhaust flow channel 430 according to the embodiment of the present disclosure is optimized to make the gas flow in the flow channel smoother, which can reduce the local loss coefficient in the exhaust flow channel 430 and improve the performance of the compressor 110.

[0046] As a comparison, Figure 6 is a cross-sectional view of an exhaust section 600 according to a comparative example. Figure 6 As shown, the exhaust section 600 of the comparative example includes a shell 610, a core 620, an exhaust flow channel 630 and an intermediate chamber 640. The core 620 is disposed inside the shell 610 and defines the exhaust flow channel 630. The intermediate chamber 640 is formed between the shell 610 and the core 620. The exhaust flow channel 630 includes an air inlet 631, two exhaust ports 632, an upstream flow channel 633 and two downstream flow channels 634. The upstream flow channel 633 defines the air inlet 631, and the two downstream flow channels 634 are respectively in fluid communication with the upstream flow channel 633 and respectively define two exhaust ports 632. The downstream flow channel 634 is in fluid communication with the intermediate chamber 640 via the exhaust ports 632.

[0047] The exhaust section 600 of the comparative example is Figure 4A-Figure 5The main difference of the exhaust section 230 shown is that the two downstream flow passages 634 of the comparative example are substantially perpendicular to the upstream flow passage 633, thereby forming a substantially "T"-shaped exhaust flow passage 630 together with the upstream flow passage 633. There are multiple cross-sectional mutations and recirculation areas in the T-shaped exhaust flow passage 630, and when the compressor speed increases and the flow rate increases, there will be obvious pressure loss.

[0048] Fig. 7A FIG. 4 shows a CFD fluid simulation result of a simplified model of a Y-shaped exhaust runner according to an embodiment. Figure 7B The CFD fluid simulation results of a simplified model of a T-shaped exhaust runner according to a comparative example are shown.

[0049] like Figure 7B As shown, after the high-temperature and high-pressure gas refrigerant compressed by the screw section flows into the T-shaped exhaust flow channel, the high-speed airflow will hit the bottom of the flow channel (according to Figure 7B The air flows to both sides (as shown in the direction). During the collision and bifurcation of high-speed airflow, the flow of the fluid is relatively chaotic and many vortices are generated. In this case, a large energy loss of the fluid will be caused, resulting in a large pressure loss and reducing the performance of the compressor.

[0050] In contrast, Fig. 7A As shown, the Y-shaped exhaust flow channel does not have the 90° bend in the T-shaped exhaust flow channel. The gas in the flow channel flows smoothly, there is no obvious high-speed area, and there is no airflow impact loss like in the T-shaped exhaust flow channel, thereby greatly reducing the pressure loss of the fluid in the exhaust flow channel and improving the performance of the compressor.

[0051] Table 1 shows the fluid pressure loss in a simplified model of a Y-shaped exhaust flow passage according to an embodiment, calculated using CFD fluid simulation, and the fluid pressure loss in a simplified model of a T-shaped exhaust flow passage according to a comparative example. Table 2 shows the fluid pressure loss in a simplified model of a T-shaped exhaust flow passage according to a comparative example, calculated using CFD fluid simulation. Figure 4A-Figure 5 The fluid pressure loss in the actual product model of the Y-shaped exhaust flow channel of the embodiment shown, and the Figure 6 The fluid pressure loss in the actual product model of the T-shaped exhaust flow channel of the comparative example shown. From the simulation results of Table 1 and Table 2, it can be seen that the pressure loss of the Y-shaped exhaust flow channel is reduced by more than 70% compared with the T-shaped exhaust flow channel.

[0052] Table 1 Fluid pressure loss of simplified model

[0053] Runner type Pressure loss(kPa) Y-shaped flow channel 6.9 T-shaped flow channel 32.5

[0054] Table 2 Fluid pressure loss of actual product model

[0055] Runner type Pressure loss(kPa) Y-shaped flow channel 0.5 T-shaped flow channel 2.2

[0056] It is worth noting that despite the above Figure 4A-4D and Figure 5 The illustrated embodiment shows a specific structure of the exhaust flow channel 430. However, those skilled in the art will appreciate that, under the principles of the present disclosure, other variations are possible. For example, in other embodiments, the two downstream flow channels 434 may be asymmetrically arranged, and / or one or both of the two downstream flow channels 434 may generally extend along a smooth curve, and / or the axis of one or both of the two downstream flow channels 434 may not be in the same plane as the axis of the upstream flow channel 433, etc. As long as the exhaust flow channel 430 has a smooth configuration and the flow direction deflection angle α when the fluid flows from the upstream flow channel 433 into the downstream flow channel 434 is less than 90°, it will be sufficient.

[0057] According to the embodiment of the present disclosure, the exhaust flow channel of the compressor includes an upstream flow channel and two downstream flow channels, each downstream flow channel generally extends along a straight line or a smooth curve, and the upstream flow channel and the downstream flow channel are constructed so that when the fluid flows from the upstream flow channel into the downstream flow channel, the deflection angle of the flow direction of the fluid is less than 90°, so that the fluid flow in the exhaust flow channel is relatively smooth, and the exhaust pressure loss can be controlled at a very low level, thereby improving the performance of the compressor, and can reduce the noise of the compressor and the air-conditioning system, and increase the service life of the pipeline system. The structure of the exhaust flow channel is simple and compact, and it is easy to manufacture.

[0058] Although the present disclosure has been described in conjunction with the examples of the embodiments summarized above, various alternatives, modifications, changes, improvements and / or substantially equivalent solutions, whether known or currently or foreseeable in the near future, may be apparent to those of ordinary skill in the art. In addition, the technical effects and / or technical problems described in this specification are exemplary rather than restrictive; so the disclosure in this specification may be used to solve other technical problems and have other technical effects and / or may solve other technical problems. Therefore, the examples of the embodiments of the present disclosure as stated above are intended to be illustrative rather than restrictive. Various changes may be made without departing from the spirit or scope of the present disclosure. Therefore, the present disclosure is intended to include all known or earlier developed alternatives, modifications, changes, improvements and / or substantially equivalent solutions.

Claims

1. A compressor (110), comprising an exhaust flow passage (430), wherein the exhaust flow passage (430) comprises: an upstream flow channel (433); and two downstream flow passages (434), the two downstream flow passages (434) being in fluid communication with the upstream flow passage (433), wherein each of the two downstream flow passages (434) extends substantially along a straight line or a smooth curve; The upstream flow channel (433) and the downstream flow channel (434) are configured such that when the fluid flows from the upstream flow channel (433) into the downstream flow channel (434), the deflection angle (α) of the flow direction of the fluid is less than 90°.

2. The compressor (110) according to claim 1, characterized in that: The upstream flow channel (433) generally extends along a first direction (X) and defines an air inlet (431) of the exhaust flow channel (430); Each of the downstream flow passages (434) includes an inlet end (520) and an outlet end (530), wherein the inlet end (520) is connected to the upstream flow passage (433), and the outlet end (530) defines an exhaust port (432) of the exhaust flow passage (430); and Each of the downstream flow channels (434) generally extends obliquely to the first direction (X) and away from the axis of the upstream flow channel (433), so that in the first direction (X), the distance D2 between the outlet end (530) of each of the downstream flow channels (434) and the air inlet (431) is greater than the distance D1 between the inlet end (520) and the air inlet (431).

3. The compressor (110) according to claim 1 or 2, characterized in that: The two downstream flow passages (434) are symmetrically arranged on two opposite sides of the upstream flow passage (433) in the radial direction, and together with the upstream flow passage (433) form the exhaust flow passage (430) which is substantially Y-shaped.

4. The compressor (110) according to claim 3, characterized in that: The two downstream flow channels (434) extend along straight lines respectively, and the angle between the center lines of the two downstream flow channels (434) is greater than 85° and less than 125°.

5. The compressor (110) according to claim 1, characterized in that: Each of the downstream flow channels (434) includes an inlet end section (501), an outlet end section (502) and a middle section (503), wherein the middle section (503) is located in the middle position of the downstream flow channel (434), wherein the area S1 of the inlet end section (501) is greater than the area S3 of the middle section (503), and the area S2 of the outlet end section (502) is greater than the area S3 of the middle section (503).

6. The compressor (110) according to claim 5, characterized in that: The area S3 of the middle cross section (503) and the area S1 of the inlet end cross section (501) satisfy and / or The area S3 of the middle cross section (503) and the area S2 of the outlet cross section (502) satisfy 7. The compressor (110) according to claim 5, characterized in that: The shape of the inlet end cross section (501) and / or the outlet end cross section (502) and / or the middle cross section (503) is generally elliptical, circular or quadrilateral.

8. The compressor (110) according to claim 5, characterized in that: The shape of the inlet end section (501) and / or the outlet end section (502) and / or the middle section (503) is generally elliptical, and the major axis of the ellipse is coplanar with the axis of the upstream flow channel (433) and the axis of the downstream flow channel (434).

9. The compressor (110) according to claim 1, characterized in that: The compressor (110) further comprises an exhaust section (230), wherein the exhaust section (230) comprises: Housing (410); a core (420) disposed inside the housing (410) and defining the exhaust flow channel (430); and an intermediate chamber (440), the intermediate chamber (440) being formed between the shell (410) and the core (420); The shell (410) is provided with an exhaust valve (450), and the exhaust valve (450) is connected to the inner side and the outer side of the shell (410), and is fluidically connected to the downstream flow channel (434) via the intermediate chamber (440).

10. The compressor (110) according to claim 1, characterized in that: The compressor (110) is a twin-screw compressor, and the twin-screw compressor further includes a screw segment (220), and the screw segment (220) includes a compression chamber (330) and a gas outlet (340), and the upstream flow channel (433) is fluidically connected to the compression chamber (330) via the gas outlet (340).

11. An air conditioning system (100), comprising the compressor (110) according to any one of claims 1 to 10.

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