Compressor and heat exchange system

Abstract

A compressor and a heat exchange system. The compressor comprises a housing (1) and a rotor pair, wherein a compression flow channel has an air intake section, and the air intake section has an air-intake communication state in which the air intake section is in communication with an air intake cavity (11) and an air-intake disconnection state in which the air intake section is disconnected from the air intake cavity (11). Performing oil returning by means of the pressure difference between the pressure of a first low-pressure cavity (14) and the evaporation pressure of an evaporator or the pressure of an exhaust-side bearing (4) can ensure the oil returning efficiency of the compressor.

Description

Compressor and heat exchange system

[0001] Cross-references to related applications

[0002] This disclosure is based on and claims priority to a Chinese application with application number 202311165688.4 and filing date September 11, 2023. The disclosure content of the Chinese application is hereby introduced into this disclosure as a whole. Technical Field

[0003] The present disclosure relates to the technical field of compression equipment, and in particular to a compressor and a heat exchange system. Background Art

[0004] The screw compressor is a positive displacement refrigeration compressor that uses a pair of meshing female and male rotors to rotate in the body cavity, periodically changing the volume between each pair of rotor teeth to complete the suction, compression and exhaust processes.

[0005] Most screw refrigeration compressors use oil injection lubrication. The oil lubricates the bearings and seals the rotors during operation. Currently, the oil used to lubricate the compressor's exhaust-side bearings mixes with the refrigerant at the exhaust pressure, resulting in high-pressure oil. Therefore, this oil is routed to the suction chamber to lubricate the suction-side bearings. After lubricating the suction-side bearings, the oil returns to the suction chamber and is discharged as the rotors compress, forming a circulation system.

[0006] It is currently found during use that when the screw compressor is operating with a very small pressure difference or is operating under light load, there is a problem of poor oil return effect, and the reliable operation of the compressor cannot be guaranteed.

[0007] Summary of the Invention

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

[0009] a housing, wherein an air suction chamber, a rotor chamber and a first oil supply passage are formed in the housing;

[0010] The rotor pair is disposed in the rotor cavity, and the rotor pair and the rotor cavity together form at least one compression flow channel; the compression flow channel has an intake section, the intake section has an intake connection state in which the intake section is connected to the intake cavity and an intake disconnection state in which the intake section is disconnected from the intake cavity; the intake section is configured to, during a process of switching from the intake connection state to the intake disconnection state, together with the inner wall of the rotor cavity to enclose a first low-pressure chamber, the first low-pressure chamber being in communication with the first oil supply channel; and

[0011] The suction side bearing is configured to support the rotor pair. The suction side bearing is disposed in the housing, and a lubricating oil inlet of the suction side bearing is communicated with the first low-pressure chamber.

[0012] In some embodiments, the rotor pair includes a male rotor rotatably disposed in a rotor cavity. The male rotor is provided with at least two anode meshing teeth, an anode tooth slot is formed between two adjacent anode meshing teeth, and part of the anode tooth slot forms an air intake section.

[0013] In some embodiments, an intake communication port is formed between the intake chamber and the rotor chamber. When the intake section is in an intake connection state, part of the anode tooth slots are located at the intake communication port and are connected to the intake communication port; when the intake section is in an intake disconnection state, the anode tooth slots are staggered with the intake communication port.

[0014] In some embodiments, the rotor pair further includes a negative rotor, which is provided with at least two cathode meshing teeth, a cathode tooth slot is formed between two adjacent cathode meshing teeth, each anode meshing tooth is meshed with a cathode tooth slot, and some cathode tooth slots form an intake section.

[0015] In some embodiments, an intake communication port is formed between the intake chamber and the rotor chamber. When the intake section is in an intake connection state, part of the cathode tooth slots are located at the intake communication port and are connected to the intake communication port; when the intake section is in an intake disconnection state, the cathode tooth slots are staggered with the intake communication port.

[0016] In some embodiments, the compressor also includes an exhaust side bearing, one end of the first oil supply channel is connected to the lubricating oil outlet of the exhaust side bearing, and the other end constitutes the outlet; or, one end of the first oil supply channel is connected to the lubricating oil supply mechanism, and the other end constitutes the outlet.

[0017] In some embodiments, an exhaust cavity is formed in the housing, and the compression flow passage has an exhaust section, which has an exhaust connection state in which the exhaust cavity is connected, and an exhaust disconnection state in which the exhaust cavity is disconnected. The exhaust section is configured to, during a switching process from the exhaust disconnection state to the exhaust connection state, enclose a second low-pressure cavity together with an inner wall of the rotor cavity.

[0018] Wherein, a second oil supply channel is provided in the shell, and the second oil supply channel is communicated with the second low-pressure chamber;

[0019] The compressor further includes an exhaust side bearing for supporting the rotor pair. The exhaust side bearing is arranged in the shell, and a lubricating oil inlet of the exhaust side bearing is communicated with the second low-pressure chamber.

[0020] In some embodiments, the rotor pair includes a male rotor and a female rotor that mesh with each other, the female rotor is provided with at least two cathode meshing teeth, and a cathode tooth slot is formed between two adjacent cathode meshing teeth, and the male rotor is provided with at least two anode meshing teeth, and each anode meshing tooth is meshed with a cathode tooth slot to form a compression flow channel.

[0021] In some embodiments, during the process of the exhaust section switching from the exhaust disconnected state to the exhaust connected state, part of the anode meshing teeth constituting the exhaust section gradually disengage from the cathode tooth slots.

[0022] A second aspect of the present disclosure provides a compressor, comprising:

[0023] a housing, wherein an exhaust cavity, a rotor cavity, and a second oil supply passage are formed in the housing;

[0024] a rotor pair disposed in the rotor cavity and forming at least one compression flow channel within the rotor cavity; the compression flow channel having an exhaust section, the exhaust section having an exhaust connection state in communication with the exhaust cavity and an exhaust disconnection state in which the exhaust cavity is disconnected; the exhaust section being configured to, during a switching process from the exhaust disconnection state to the exhaust connection state, collectively enclose a second low-pressure chamber with an inner wall of the rotor cavity, the second low-pressure chamber being in communication with the second oil supply channel; and

[0025] The exhaust side bearing is configured to support the rotor pair. The exhaust side bearing is disposed in the housing, and a lubricating oil inlet of the exhaust side bearing is communicated with the second low-pressure chamber.

[0026] In some embodiments, the rotor pair includes a male rotor and a female rotor that mesh with each other, the female rotor is provided with at least two cathode meshing teeth, and a cathode tooth slot is formed between two adjacent cathode meshing teeth, and the male rotor is provided with at least two anode meshing teeth, and each anode meshing tooth is meshed with a cathode tooth slot to form a compression flow channel.

[0027] In some embodiments, during the process of switching the exhaust section from the exhaust disconnected state to the exhaust connected state, part of the anode meshing teeth constituting the exhaust section gradually disengage from the cathode tooth slots.

[0028] A third aspect of the present disclosure provides a heat exchange system, comprising the compressor of the above embodiment.

[0029] In some embodiments, the heat exchange system further includes an evaporator, the suction cavity of the compressor is connected to the gaseous outlet of the evaporator, and the first oil supply channel and the second oil supply channel are connected to the oil return port of the evaporator. BRIEF DESCRIPTION OF THE DRAWINGS

[0030] FIG1 is a schematic structural diagram of some embodiments of the compressor disclosed herein;

[0031] FIG2 is a schematic structural diagram of other embodiments of the compressor disclosed herein;

[0032] FIG3 is a partial schematic diagram of point A in FIG2 ;

[0033] FIG4 is a schematic diagram of a compressor provided in an embodiment of the present disclosure.

[0034] In the picture:

[0035] 1. Shell; 11. Intake chamber; 12. Rotor chamber; 14. First low-pressure chamber; 15. First oil supply channel; 3. Intake-side bearing; 24. Male rotor; 241. Anode meshing teeth; 242. Anode tooth grooves; 25. Female rotor; 251. Cathode meshing teeth; 252. Cathode tooth grooves; 4. Exhaust-side bearing; 13. Exhaust chamber; 16. Second low-pressure chamber; 17. Second oil supply channel. DETAILED DESCRIPTION

[0036] In order to make the purpose, technical solutions and advantages of the present disclosure more clearly understood, the present disclosure is further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present disclosure and are not intended to limit the present disclosure.

[0037] In order to enable those skilled in the art to better understand the solutions of the present disclosure, the technical solutions in the embodiments of the present disclosure will be clearly and completely described below in conjunction with the drawings in the embodiments of the present disclosure. Obviously, the embodiments described are only part of the embodiments of the present disclosure, not all of the embodiments. Based on the embodiments of the present disclosure, all other embodiments obtained by ordinary technicians in this field without making creative efforts should fall within the scope of protection of the present disclosure.

[0038] It should be noted that the terms "first," "second," and the like in the specification and claims of the present disclosure and the accompanying drawings are used to distinguish similar objects and are not necessarily used to describe a specific order or precedence. It should be understood that the terms used in this manner are interchangeable where appropriate for the embodiments of the present disclosure described herein. In addition, the terms "including" and "having," and any variations thereof, are intended to cover non-exclusive inclusions. For example, a process, method, system, product, or apparatus comprising a series of steps or units is not necessarily limited to those steps or units explicitly listed, but may include other steps or units that are not explicitly listed or inherent to these processes, methods, products, or apparatuses.

[0039] It should be noted that, in the description of this disclosure, terms such as "upper," "lower," "left," "right," "inner," and "outer" indicating directions or positional relationships are based on the directions or positional relationships shown in the accompanying drawings. These terms are used solely for ease of description and are not intended to indicate or imply that the device or component described must have, be constructed, or operate in a specific orientation. Therefore, they should not be construed as limitations on this disclosure. Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0040] Furthermore, it should be noted that, in the description of this disclosure, unless otherwise expressly specified or limited, the terms "installed," "installed," and "connected" should be understood in a broad sense. For example, they may refer to fixed connections, detachable connections, or integral connections; they may refer to direct connections, indirect connections through an intermediate medium, or internal connections between two components. Those skilled in the art will understand the specific meanings of the above terms in this disclosure based on the specific circumstances.

[0041] Most screw refrigeration compressors use oil injection lubrication. The oil lubricates the bearings and seals the rotors during operation. Currently, the oil used to lubricate the compressor's exhaust-side bearings mixes with the refrigerant at the exhaust pressure, resulting in high-pressure oil. Therefore, this oil is routed to the suction chamber to lubricate the suction-side bearings. After lubricating the suction-side bearings, the oil returns to the suction chamber and is discharged as the rotors compress, forming a circulation system.

[0042] However, when the compressor operates under low differential pressure, even though the oil lubricating the exhaust-side bearings reaches the compressor's high exhaust pressure, the pressure differential with the suction-side bearings is insufficient. Furthermore, pressure loss in the oil line connecting the two exhaust-side and suction-side bearings prevents the oil from returning to the suction chamber. Related art screw compressor systems typically address this issue by controlling the operating pressure differential to a minimum and using an external oil pump to increase the pressure differential in the oil line.

[0043] Furthermore, when the screw compressor is operating under light load, oil accumulates at the bottom of the evaporator in the heat exchange loop where the screw compressor is located. Since the pressure in the evaporator is also low, the oil cannot be directly returned to the compressor's suction chamber through the pressure differential, thus preventing the oil from circulating. Related art screw compressor systems typically use an ejector to eject the low-pressure oil from the evaporator back to the compressor's suction chamber.

[0044] In order to solve the technical problems of poor oil return effect and poor reliability of screw compressors in the prior art when operating under low pressure difference conditions or light load, a compressor and heat exchange system are provided that use the rotor to return oil to a low-pressure cavity formed with the rotor cavity, whose pressure is much lower than the evaporation pressure of the evaporator, to ensure the oil return effect.

[0045] The present invention provides a compressor and heat exchange system, in which the rotor pair and the rotor cavity together form a compression flow channel, and as the rotor pair operates, the position of the compression flow channel in the rotor cavity continuously changes. By utilizing this change, the gas in the suction cavity can be sucked in and continuously compressed, ultimately obtaining high-pressure exhaust. The inventors have found that during the process of the position change of the compression flow channel, when the suction section in the compression flow channel that is connected to the suction cavity is about to be disconnected from the inner wall of the rotor cavity, the intake volume of the suction section decreases, but the volume of the compression flow channel is constant. Compared with the decrease in intake volume, the volume is equivalent to a gradual increase, so that the pressure value in the suction section at this time is relatively small, so that a first low-pressure chamber can be formed together with the corresponding part of the inner wall of the rotor cavity. The oil return efficiency of the compressor can be guaranteed by utilizing the pressure difference between the pressure of the first low-pressure chamber and the evaporation pressure of the evaporator or the pressure at the exhaust-side bearing, which effectively solves the problem of the compressor being unable to return oil under low-pressure difference conditions, improves the operating reliability of the compressor, and broadens the operating range of the compressor. At the same time, there is no need to set up a pressurizing structure such as an ejector in the prior art, thereby reducing the cost of the compressor.

[0046] To this end, the present disclosure provides a compressor as shown in Figures 1 to 4. In some embodiments, the compressor includes: a shell 1, in which an intake chamber 11 and a rotor chamber 12 are formed; a rotor pair, in which the rotor pair is arranged in the rotor chamber 12, and the rotor pair and the rotor chamber 12 jointly form at least one compression flow channel; the compression flow channel has an intake section, and the intake section has an intake connection state connected to the intake chamber 11 and an intake disconnection state disconnected from the intake chamber 11; in the process of switching the intake section from the intake connection state to the intake disconnection state, the intake section and the inner wall of the rotor chamber 12 jointly form a first low-pressure chamber 14; a first oil supply channel 15 is provided in the shell 1, and the first oil supply channel 15 is connected to the first low-pressure chamber 14; an intake side bearing 3, configured to support the rotor pair, the intake side bearing 3 is arranged in the shell 1, and the lubricating oil inlet of the intake side bearing 3 is connected to the first low-pressure chamber 14.

[0047] The rotor pair and the rotor cavity 12 together form a compression flow channel, and as the rotor pair operates, the position of the compression flow channel in the rotor cavity 12 changes continuously. By utilizing this change, the gas in the suction cavity 11 can be sucked in and continuously compressed, and finally high-pressure exhaust is obtained. The inventors have found that in the process of the position change of the compression flow channel, when the suction section in the compression flow channel that is connected to the suction cavity 11 is about to be disconnected from the inner wall of the rotor cavity 12, the intake volume of the suction section is reduced, but the volume of the compression flow channel is constant, which is equivalent to the reduction in volume compared with the reduction in intake volume. The volume gradually increases, so that the pressure value in the suction section at this time is relatively small, so that it can form a first low-pressure chamber 14 together with the corresponding part of the inner wall of the rotor chamber 12, and the pressure difference between the pressure of the first low-pressure chamber 14 and the evaporation pressure of the evaporator or the pressure at the exhaust side bearing is used to return oil, which can ensure the oil return efficiency of the compressor, effectively solve the problem that the compressor cannot return oil under low pressure difference conditions, improve the operating reliability of the compressor, and broaden the operating range of the compressor. At the same time, there is no need to set a pressurization structure such as an ejector in the related technology, thereby reducing the cost of the compressor.

[0048] In some embodiments, the rotor pair includes a male rotor 24, which is rotatably disposed in the rotor cavity 12. The male rotor 24 is provided with at least two anode meshing teeth 241, and an anode tooth slot 242 is formed between two adjacent anode meshing teeth 241. Part of the anode tooth slots 242 form an intake section. The part of the anode tooth slots 242 that form the intake section refers to the part that can be directly connected to the intake cavity 11. When the male rotor 24 rotates, the anode tooth slots 242 rotate accordingly, and when connected to the intake cavity 11, part of the gas is sent into the anode tooth slots 242 to achieve the intake process of the compression flow channel. Then, the male rotor 24 continues to rotate, and the connection area between the anode tooth slots 242 and the intake cavity 11 gradually decreases, and eventually completely disconnects from the intake cavity 11. The gas in the anode tooth slots 242 is gradually compressed as the rotor pair rotates, and is eventually discharged from the exhaust section of the rotor pair, completing the gas compression.

[0049] In the related art, the compression flow passage in the compression state is generally studied, while the compression flow passage not in the compression state is ignored. When the inventors of the present disclosure proposed the technical problem that the oil cannot be returned smoothly under low pressure difference or low load, they creatively discovered that when the anode tooth slot 242 completes the suction and is about to rotate to the position sealed with the inner wall of the rotor cavity 12, the communication area between the anode tooth slot 242 and the suction cavity 11 gradually decreases, so that the amount of gas entering the anode tooth slot 242 gradually decreases, while the volume of the anode tooth slot 242 remains unchanged, so that the pressure in this part of the anode tooth slot 242 gradually decreases, and when it is about to rotate to the position sealed with the inner wall of the rotor cavity 12, the communication area between the anode tooth slot 242 and the suction cavity 11 gradually decreases. When the seal with the rotor cavity 12 is completed, the pressure reaches the lowest point. At this time, the part of the anode tooth groove 242 that constitutes the suction section and the rotor cavity 12 together form a first low-pressure cavity 14. The pressure value of the first low-pressure cavity 14 is much lower than the evaporation pressure of the evaporator, so the difference between the evaporation pressure of the first low-pressure cavity 14 and the evaporator can be used to realize the return of oil from the evaporator. The pressure value of the first low-pressure cavity 14 is also much lower than the exhaust pressure of the compressor. Therefore, the pressure difference between the first low-pressure cavity 14 and the exhaust side bearing can smoothly divert the lubricating oil at the exhaust side bearing to the low-pressure side bearing for lubrication, thereby ensuring the reliable oil circulation in the compressor.

[0050] Specifically, an intake communication port is formed between the intake chamber 11 and the rotor chamber 12. When the intake section is in an intake communication state, part of the anode tooth slots 242 are located at the intake communication port and are connected to the intake communication port; when the intake section is in an intake disconnection state, the anode tooth slots 242 are staggered from the intake communication port.

[0051] Among them, in the two anode meshing teeth 241 constituting the anode tooth groove 242: when the intake section is in the intake connection state, at least one anode meshing tooth 241 is exposed at the intake connection port and has a spacing with the edge of the intake connection port. The intake section is connected with the intake cavity 11 through the spacing, and as the positive rotor 24 rotates, the spacing gradually decreases until the spacing becomes 0, at which time the intake end switches to the intake disconnection state; that is, when the intake section is in the intake disconnection state, both anode meshing teeth 241 rotate to a position that seals with the inner wall of the rotor cavity 12, thereby disconnecting the anode tooth groove 242 from the intake connection port, and preparing for sealing for the next step of compressing the gas in the compression flow channel.

[0052] In some embodiments, the rotor pair also includes a negative rotor 25, which is provided with at least two cathode meshing teeth 251, and a cathode tooth groove 252 is formed between two adjacent cathode meshing teeth 251. Each anode meshing tooth 241 is engaged with a cathode tooth groove 252, and some cathode tooth grooves 252 form an intake section.

[0053] The cathode slots 252 forming the intake section are those that can directly communicate with the intake chamber 11. As the female rotor 25 rotates, the cathode slots 252 rotate accordingly. When communicating with the intake chamber 11, some gas is delivered into the cathode slots 252, completing the intake process of the compression channel. The female rotor 25 then continues to rotate, gradually reducing the area of ​​communication between the cathode slots 252 and the intake chamber 11, and ultimately completely disconnecting from the intake chamber 11. The gas within the cathode slots 252 is gradually compressed as the rotor pair rotates, and ultimately discharged from the exhaust section of the rotor pair, completing the gas compression. The compression channel compresses the gas by causing the anode meshing teeth 241 to engage with the corresponding cathode slots 252, forcing the gas to flow along the axis of the rotor pair. During this process, as the pitch of the male and female rotors 24 and 25 changes, the volume of the compression channel in which the gas resides gradually decreases, thereby compressing the gas and increasing the gas pressure.

[0054] When the inventors of the present disclosure proposed the technical problem of the inability to smoothly return oil under low pressure difference or low load conditions, they also creatively discovered that when the cathode tooth slot 252 completes suction and is about to rotate to a position sealed with the inner wall of the rotor cavity 12, the communication area between the cathode tooth slot 252 and the suction cavity 11 gradually decreases, causing the amount of gas entering the cathode tooth slot 252 to gradually decrease, while the volume of the cathode tooth slot 252 remains unchanged, causing the pressure in this part of the cathode tooth slot 252 to gradually decrease. When the cathode tooth slot 252 is about to be sealed with the rotor cavity 12, the pressure reaches the lowest point. At this time, part of the cathode tooth grooves 252 that constitute the suction section and the rotor cavity 12 together form a first low-pressure cavity 14. The pressure value of the first low-pressure cavity 14 is much lower than the evaporation pressure of the evaporator, so that the difference between the evaporation pressure of the first low-pressure cavity 14 and the evaporator can be used to realize the return of oil from the evaporator. The pressure value of the first low-pressure cavity 14 is also much lower than the exhaust pressure of the compressor. Therefore, the pressure difference between the first low-pressure cavity 14 and the exhaust side bearing can smoothly divert the lubricating oil at the exhaust side bearing to the low-pressure side bearing for lubrication, thereby ensuring reliable oil circulation in the compressor.

[0055] Specifically, an intake communication port is formed between the intake chamber 11 and the rotor chamber 12. When the intake section is in an intake communication state, part of the cathode tooth slots 252 are located at the intake communication port and are connected to the intake communication port; when the intake section is in an intake disconnection state, the cathode tooth slots 252 are staggered with the intake communication port.

[0056] Among them, in the two cathode meshing teeth 251 constituting the cathode tooth slot 252: when the intake section is in the intake connection state, at least one cathode meshing tooth 251 is exposed at the intake connection port and has a spacing with the edge of the intake connection port. The intake section is connected with the intake cavity 11 through the spacing, and as the negative rotor 25 rotates, the spacing gradually decreases until the spacing becomes 0, at which time the intake end switches to the intake disconnection state; that is, when the intake section is in the intake disconnection state, both cathode meshing teeth 251 rotate to a position that seals with the inner wall of the rotor cavity 12, thereby disconnecting the cathode tooth slot 252 from the intake connection port, preparing for sealing for the next step of compressing the gas in the compression flow channel.

[0057] In some embodiments, the compressor further includes an exhaust-side bearing 4. One end of a first oil supply passage 15 is connected to the lubricating oil outlet of the exhaust-side bearing 4, and the other end forms an outlet. Because the gas is compressed by the compression flow passage, the pressure at the exhaust-side bearing 4 is significantly greater than the pressure value of the first low-pressure chamber 14. At this time, the lubricating oil at the exhaust-side bearing 4 is transported to the first low-pressure chamber 14 through the first oil supply passage 15 by utilizing the pressure difference between the pressure at the exhaust-side bearing 4 and the pressure in the first low-pressure chamber 14. The lubricating oil is ultimately delivered to the suction-side bearing 3 for lubrication, and then flows back into the suction chamber 11 through the suction-side bearing 3, thus achieving oil circulation within the compressor.

[0058] Alternatively, one end of the first oil supply channel 15 is connected to the lubricating oil supply mechanism, and the other end constitutes an outlet. The lubricating oil of the lubricating oil supply mechanism is introduced into the first low-pressure chamber 14 by utilizing the pressure difference between the pressure of the first low-pressure chamber 14 and the lubricating oil supply mechanism, and then supplied to the suction side bearing 3 for lubrication, thereby realizing oil return of the compressor.

[0059] As shown in Figure 4 , one end of the upper first oil supply passage 15 communicates with the exhaust chamber 13, and the other end forms an outlet for directing lubricating oil to the intake-side bearing 3. One end of the lower first oil supply passage 15 is connected to the lubricating oil supply mechanism, and the other end forms an outlet for directing lubricating oil to the intake-side bearing 3. One end of the second oil supply passage 17 is connected to the lubricating oil supply mechanism, and the other end forms an outlet for directing lubricating oil to the exhaust-side bearing 4.

[0060] In some embodiments, an exhaust chamber 13 is formed in the shell 1, and the compression flow channel has an exhaust section, and the exhaust section has an exhaust connection state connected to the exhaust chamber 13 and an exhaust disconnection state disconnected from the exhaust chamber 13; in the process of the exhaust section switching from the exhaust disconnection state to the exhaust connection state, the exhaust section and the inner wall of the rotor chamber 12 jointly form a second low-pressure chamber 16; a second oil supply channel 17 is provided in the shell 1, and the second oil supply channel 17 is connected to the second low-pressure chamber 16; the exhaust side bearing 4 for supporting the rotor pair is provided in the shell 1, and the exhaust side bearing 4 is provided in the shell 1, and the lubricating oil inlet of the exhaust side bearing 4 is connected to the second low-pressure chamber 16.

[0061] As the rotor pair operates, the position of the compression flow channel in the rotor cavity 12 is constantly changing. By utilizing this change, the gas in the suction cavity 11 can be sucked in and continuously compressed, and finally high-pressure exhaust is obtained. The inventor has found that in the process of the compression flow channel being connected to the exhaust cavity 13, the gas in the compression flow channel will be completely squeezed out, thereby realizing the exhaust of the compression flow channel. When the exhaust section of the compression flow channel used to communicate with the exhaust cavity 13 completes the exhaust, there is no gas in the exhaust section. However, as the rotor pair rotates, the volume of the exhaust section gradually increases, causing the pressure in the exhaust section to gradually decrease, and even forming a vacuum state. Therefore, at this time, the exhaust section and the inner wall of the rotor cavity 12 jointly surround The pressure of the second low-pressure chamber 16 is much lower than the evaporation pressure of the evaporator. When the pressure difference between the second low-pressure chamber 16 and the evaporation pressure of the evaporator is large, the stored oil in the evaporator can be smoothly drained into the second low-pressure chamber 16 and supplied to the exhaust side bearing 4 for lubrication, which overcomes the problem of the need to set an ejector to eject the stored oil in the evaporator in the prior art, improves the reliability of the compressor when running at low load, ensures the oil return efficiency of the compressor, and effectively solves the problem that the compressor cannot return oil under low pressure difference conditions, improves the operating reliability of the compressor, and broadens the operating range of the compressor. At the same time, there is no need to set a pressurization structure such as an ejector in the prior art, thereby reducing the cost of the compressor.

[0062] In some embodiments, the rotor pair includes a male rotor 24 and a female rotor 25 that mesh with each other. The female rotor 25 is provided with at least two cathode meshing teeth 251, and a cathode tooth groove 252 is formed between two adjacent cathode meshing teeth 251. The male rotor 24 is provided with at least two anode meshing teeth 241, and each anode meshing tooth 241 is meshed with a cathode tooth groove 252 to form a compression flow channel.

[0063] The gas is forced to flow in the compression channel by the meshing of the anode meshing teeth 241 and the cathode meshing teeth 252. As the pitch of the anode meshing teeth 241 and the cathode meshing teeth 251 gradually decreases, the volume of the compression channel gradually decreases, thereby compressing the gas. When the compression channel is exhausted, the compressed gas is in the exhaust section. When the exhaust section is connected to the exhaust chamber 13, the compressed gas enters the exhaust chamber 13 for exhaust. As the compressed gas enters the exhaust chamber 13, the gas in the exhaust section gradually decreases, and the anode meshing teeth 241 gradually exhaust the gas in the compression channel, so that the volume of the compression channel in the exhaust section is reduced. It is basically zero, and as the rotor section rotates, the anode meshing teeth 241 gradually leave the compression flow channel, that is, in the process of the exhaust section switching from the exhaust disconnected state to the exhaust connected state, the anode meshing teeth 241 constituting the exhaust section gradually disengage from the cathode tooth groove 252, and the internal volume of the exhaust section gradually increases. At this time, there is no gas replenished in the exhaust section, so that the pressure in the exhaust section at this time is lower and lower, and even a vacuum state can be formed. Therefore, the position of the exhaust section at this time and the inner wall of the corresponding rotor cavity 12 together form a second low-pressure cavity 16, and the low pressure of the second low-pressure cavity 16 and the evaporation pressure of the evaporator are used to form a pressure difference, thereby ensuring the smooth oil return of the compressor.

[0064] Other embodiments of the present disclosure provide a compressor as shown in Figures 2 to 4, including: a shell 1, in which an exhaust chamber 13 and a rotor chamber 12 are formed; a rotor pair, which is arranged in the rotor chamber 12, and the rotor pair forms at least one compression flow channel in the rotor chamber 12; the compression flow channel has an exhaust section, and the exhaust section has an exhaust connection state connected to the exhaust chamber 13 and an exhaust disconnection state disconnected from the exhaust chamber 13; when the exhaust section switches from the exhaust disconnection state to the exhaust connection state, the exhaust section and the inner wall of the rotor chamber 12 jointly form a second low-pressure chamber 16; a second oil supply channel 17 is provided in the shell 1, and the second oil supply channel 17 is connected to the second low-pressure chamber 16; an exhaust side bearing 4 for supporting the rotor pair, the exhaust side bearing 4 is arranged in the shell 1, and the lubricating oil inlet of the exhaust side bearing 4 is connected to the second low-pressure chamber 16.

[0065] As the rotor pair operates, the position of the compression flow channel in the rotor cavity 12 is constantly changing. By utilizing this change, the gas in the suction cavity 11 can be sucked in and continuously compressed, and finally high-pressure exhaust is obtained. The inventor has found that in the process of the compression flow channel being connected to the exhaust cavity 13, the gas in the compression flow channel will be completely squeezed out, thereby realizing the exhaust of the compression flow channel. When the exhaust section of the compression flow channel used to communicate with the exhaust cavity 13 completes the exhaust, there is no gas in the exhaust section. However, as the rotor pair rotates, the volume of the exhaust section gradually increases, causing the pressure in the exhaust section to gradually decrease, and even forming a vacuum state. Therefore, at this time, the exhaust section and the inner wall of the rotor cavity 12 jointly surround The pressure of the second low-pressure chamber 16 is much lower than the evaporation pressure of the evaporator. When the pressure difference between the second low-pressure chamber 16 and the evaporation pressure of the evaporator is large, the stored oil in the evaporator can be smoothly drained into the second low-pressure chamber 16 and supplied to the exhaust side bearing 4 for lubrication, which overcomes the problem of the need to set an ejector to eject the stored oil in the evaporator in the prior art, improves the reliability of the compressor when running at low load, ensures the oil return efficiency of the compressor, and effectively solves the problem that the compressor cannot return oil under low pressure difference conditions, improves the operating reliability of the compressor, and broadens the operating range of the compressor. At the same time, there is no need to set a pressurization structure such as an ejector in the prior art, thereby reducing the cost of the compressor.

[0066] In some embodiments, the rotor pair includes a male rotor 24 and a female rotor 25 that mesh with each other. The female rotor 25 is provided with at least two cathode meshing teeth 251, and a cathode tooth groove 252 is formed between two adjacent cathode meshing teeth 251. The male rotor 24 is provided with at least two anode meshing teeth 241, and each anode meshing tooth 241 is meshed with a cathode tooth groove 252 to form a compression flow channel.

[0067] The gas is forced to flow in the compression channel by the meshing of the anode meshing teeth 241 and the cathode meshing teeth 252. As the pitch of the anode meshing teeth 241 and the cathode meshing teeth 251 gradually decreases, the volume of the compression channel gradually decreases, thereby compressing the gas. When the compression channel is exhausted, the compressed gas is in the exhaust section. When the exhaust section is connected to the exhaust chamber 13, the compressed gas enters the exhaust chamber 13 for exhaust. As the compressed gas enters the exhaust chamber 13, the gas in the exhaust section gradually decreases, and the anode meshing teeth 241 gradually exhaust the gas in the compression channel, so that the volume of the compression channel in the exhaust section is reduced. It is basically zero, and as the rotor section rotates, the anode meshing teeth 241 gradually leave the compression flow channel, that is, in the process of the exhaust section switching from the exhaust disconnected state to the exhaust connected state, the anode meshing teeth 241 constituting the exhaust section gradually disengage from the cathode tooth groove 252, and the internal volume of the exhaust section gradually increases. At this time, there is no gas replenished in the exhaust section, so that the pressure in the exhaust section at this time is lower and lower, and even a vacuum state can be formed. Therefore, the position of the exhaust section at this time and the inner wall of the corresponding rotor cavity 12 together form a second low-pressure cavity 16, and the low pressure of the second low-pressure cavity 16 and the evaporation pressure of the evaporator are used to form a pressure difference, thereby ensuring the smooth oil return of the compressor.

[0068] Secondly, an embodiment of the present disclosure provides a heat exchange system, including the above-mentioned compressor.

[0069] In some embodiments, the heat exchange system further includes an evaporator, the suction chamber 11 of the compressor is connected to the gaseous outlet of the evaporator, and the first oil supply channel and / or the second oil supply channel are connected to the oil return port of the evaporator.

[0070] The above embodiments merely illustrate several implementations of the present disclosure, and while their descriptions are relatively specific and detailed, they should not be construed as limiting the scope of the present invention. It should be noted that a person skilled in the art would be able to make numerous variations and improvements without departing from the scope of the present disclosure, all of which fall within the scope of protection of the present disclosure. Therefore, the scope of protection of the present invention shall be determined by the appended claims.

Claims

1. A compressor, comprising: A housing (1), wherein an air intake chamber (11), a rotor chamber (12) and a first oil supply passage (15) are formed in the housing (1); A rotor pair, the rotor pair being arranged in the rotor cavity (12), and the rotor pair and the rotor cavity (12) jointly forming at least one compression flow channel; the compression flow channel having an air intake section, the air intake section having an air intake connection state connected with the air intake cavity (11) and an air intake disconnection state disconnected from the air intake cavity (11); the air intake section being configured to, in a process of switching from the air intake connection state to the air intake disconnection state, jointly enclose a first low-pressure cavity (14) with an inner wall of the rotor cavity (12), the first low-pressure cavity (14) being connected with the first oil supply channel (15); and The suction side bearing (3) is configured to support the rotor pair. The suction side bearing (3) is arranged in the housing (1), and the lubricating oil inlet of the suction side bearing (3) is connected to the first low-pressure chamber (14).

2. The compressor according to claim 1, wherein the rotor pair includes a male rotor (24), the male rotor (24) is rotatably disposed in the rotor cavity (12), at least two anode meshing teeth (241) are disposed on the male rotor (24), an anode tooth groove (242) is formed between two adjacent anode meshing teeth (241), and part of the anode tooth groove (242) forms the suction section.

3. The compressor according to claim 2, wherein an intake communication port is formed between the intake chamber (11) and the rotor chamber (12), and when the intake section is in the intake communication state, part of the anode tooth slots (242) are located at the intake communication port and are connected to the intake communication port; when the intake section is in the intake disconnection state, the anode tooth slots (242) are staggered with the intake communication port.

4. A compressor according to claim 2 or 3, wherein the rotor pair further comprises a female rotor (25), at least two cathode meshing teeth (251) are arranged on the female rotor (25), a cathode tooth groove (252) is formed between two adjacent cathode meshing teeth (251), each of the anode meshing teeth (241) is meshed with one of the cathode tooth grooves (252), and part of the cathode tooth grooves (252) form the suction section.

5. The compressor according to claim 4, wherein an intake connection port is formed between the intake chamber (11) and the rotor chamber (12), and when the intake section is in the intake connection state, part of the cathode tooth slots (252) are located at the intake connection port and are connected to the intake connection port; when the intake section is in the intake disconnection state, the cathode tooth slots (252) are staggered with the intake connection port.

6. A compressor according to any one of claims 1 to 5, wherein the compressor further comprises an exhaust side bearing (4), one end of the first oil supply passage (15) is connected to the lubricating oil outlet of the exhaust side bearing (4), and the other end constitutes the outlet; or, one end of the first oil supply passage (15) is connected to the lubricating oil supply mechanism, and the other end constitutes the outlet.

7. The compressor according to any one of claims 1 to 6, wherein an exhaust chamber (13) is formed in the housing (1), the compression flow passage has an exhaust section, the exhaust section has an exhaust connection state connected with the exhaust chamber (13) and an exhaust disconnection state disconnected from the exhaust chamber (13); the exhaust section is configured to enclose a second low-pressure chamber (16) together with the inner wall of the rotor chamber (12) during a process of switching from the exhaust disconnection state to the exhaust connection state; in, A second oil supply passage (17) is provided in the housing (1), and the second oil supply passage (17) is communicated with the second low-pressure chamber (16); The compressor further comprises an exhaust side bearing (4) for supporting the rotor pair, wherein the exhaust side bearing (4) is arranged in the housing (1), and a lubricating oil inlet of the exhaust side bearing (4) is connected to the second low-pressure chamber (16).

8. The compressor according to claim 7, wherein the rotor pair comprises a male rotor (24) and a female rotor (25) meshing with each other, the female rotor (25) is provided with at least two cathode meshing teeth (251), a cathode tooth groove (252) is formed between two adjacent cathode meshing teeth (251), and the male rotor (24) is provided with at least two anode meshing teeth (241), each of the anode meshing teeth (241) is meshed with a cathode tooth groove (252) to form a compression flow channel.

9. The compressor according to claim 8, wherein during the process of the exhaust section switching from the exhaust disconnected state to the exhaust connected state, part of the anode meshing teeth (241) constituting the exhaust section gradually disengages from the cathode tooth grooves (252).

10. A compressor, comprising: A housing (1), wherein an exhaust chamber (13), a rotor chamber (12) and a second oil supply passage (17) are formed in the housing (1); A rotor pair, the rotor pair being arranged in the rotor cavity (12), and the rotor pair forming at least one compression flow channel in the rotor cavity (12); the compression flow channel having an exhaust section, the exhaust section having an exhaust connection state in communication with the exhaust cavity (13) and an exhaust disconnection state in communication with the exhaust cavity (13); the exhaust section being configured to, in a process of switching from the exhaust disconnection state to the exhaust connection state, enclose together with the inner wall of the rotor cavity (12) a second low-pressure cavity (16), the second low-pressure cavity (16) being in communication with the second oil supply channel (17); and An exhaust side bearing (4) is configured to support the rotor pair. The exhaust side bearing (4) is disposed in the housing (1), and a lubricating oil inlet of the exhaust side bearing (4) is connected to the second low-pressure chamber (16).

11. A compressor according to claim 10, wherein the rotor pair comprises a male rotor (24) and a female rotor (25) meshing with each other, the female rotor (25) is provided with at least two cathode meshing teeth (251), a cathode tooth groove (252) is formed between two adjacent cathode meshing teeth (251), and the male rotor (24) is provided with at least two anode meshing teeth (241), each of the anode meshing teeth (241) is meshed with a cathode tooth groove (252) to form a compression flow channel.

12. The compressor according to claim 11, wherein during the process of the exhaust section switching from the exhaust disconnected state to the exhaust connected state, part of the anode meshing teeth (241) constituting the exhaust section gradually disengages from the cathode tooth grooves (252).

13. A heat exchange system, comprising the compressor according to any one of claims 1 to 12.

14. The heat exchange system according to claim 13, further comprising an evaporator, the suction chamber (11) of the compressor is connected to the gaseous outlet of the evaporator, and the first oil supply channel and the second oil supply channel are connected to the oil return port of the evaporator.

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