Compressor and heat exchange system

Abstract

The present invention provides a compressor and a heat exchange system. The compressor includes a shell; a rotor pair; the compression flow channel has an air intake section, and the air intake section has an air intake connection state connected with the air intake chamber and an air intake disconnection state disconnected from the air intake chamber. The compressor and heat exchange system provided by the present invention use 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 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 up a pressurization structure such as an ejector in the prior art, thereby reducing the cost of the compressor.

Description

Technical Field

[0001] The invention relates to the technical field of compression equipment, in particular to a compressor and a heat exchange system. Background Art

[0002] The screw compressor is a positive displacement refrigeration compressor that utilizes a pair of meshing yin and yang rotors to perform rotational motion in the body cavity, periodically changing the volume between each pair of rotor teeth to complete the suction, compression, and exhaust processes.

[0003] Most screw refrigeration compressors are lubricated by oil injection. The oil plays a role in bearing lubrication and rotor sealing during the operation of the compressor. At present, the oil after lubrication of the exhaust side bearing of the compressor is mixed with the refrigerant of the exhaust pressure, which is a high-pressure oil. Therefore, this part of the oil is connected to the suction chamber to lubricate the suction side bearing. After the lubrication of the suction side bearing is completed, the oil returns to the suction chamber and is discharged with the compression of the rotor pair, thus forming a cycle.

[0004] However, when the pressure difference of the compressor operating condition is small, although the oil that lubricates the exhaust side bearing has the high pressure of the compressor exhaust, the pressure difference with the suction side bearing is not large enough, and the pressure loss in the oil path connecting the two exhaust side bearings and the suction side bearing makes it impossible to return the oil to the suction chamber normally. The screw compressor system in the prior art mainly solves this problem by controlling the minimum operating pressure difference and using an external oil pump to increase the oil path pressure difference.

[0005] Moreover, when the screw compressor is under light load operation, there is oil accumulation at the bottom of the evaporator in the heat exchange cycle where the screw compressor is located. Since the pressure in the evaporator is also low pressure, it cannot be directly returned to the suction chamber of the compressor through the pressure difference, and the oil circuit circulation cannot be completed. The screw compressor system in the prior art usually uses an ejector to eject the low-pressure stored oil in the evaporator back to the suction chamber of the compressor.

[0006] In summary, when the screw compressor is operating with a 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. Summary of the invention

[0007] 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 which utilize a rotor to return oil to a low-pressure cavity formed with a rotor cavity whose pressure is much lower than the evaporation pressure of an evaporator to ensure the oil return effect.

[0008] A compressor, comprising:

[0009] A housing, wherein a suction cavity and a rotor cavity are formed in the housing;

[0010] A rotor pair, wherein 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;

[0011] The compression flow channel has an air suction section, and the air suction section has an air suction connection state connected with the air suction cavity and an air suction disconnection state disconnected from the air suction cavity;

[0012] When the air intake section switches from the air intake connected state to the air intake disconnected state, the air intake section and the inner wall of the rotor cavity together form a first low-pressure cavity;

[0013] A first oil supply passage is provided in the housing, and the first oil supply passage is communicated with the first low-pressure chamber;

[0014] A suction side bearing is used to support the rotor pair, wherein the suction side bearing is arranged in the housing, and a lubricating oil inlet of the suction side bearing is communicated with the first low-pressure chamber.

[0015] The rotor pair comprises a male rotor which is rotatably arranged in the rotor cavity. The male rotor is provided with at least two anode meshing teeth, an anode tooth groove is formed between two adjacent anode meshing teeth, and part of the anode tooth groove forms the air intake section.

[0016] An air intake connection port is formed between the air intake chamber and the rotor chamber. When the air intake section is in the air intake connection state, part of the anode tooth slots are located at the air intake connection port and are connected to the air intake connection port. When the air intake section is in the air intake disconnection state, the anode tooth slots are staggered from the air intake connection port.

[0017] The rotor pair also includes a female rotor, which is provided with at least two cathode meshing teeth, a cathode tooth slot is formed between two adjacent cathode meshing teeth, each of the anode meshing teeth is meshed with one of the cathode tooth slots, and some of the cathode tooth slots form the suction section.

[0018] An air intake connection port is formed between the air intake chamber and the rotor chamber. When the air intake section is in the air intake connection state, part of the cathode tooth slots are located at the air intake connection port and are connected to the air intake connection port. When the air intake section is in the air intake disconnection state, the cathode tooth slots are staggered from the air intake connection port.

[0019] The compressor also includes an exhaust side bearing, one end of the first oil supply passage 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 passage is connected to the lubricating oil supply mechanism, and the other end constitutes the outlet.

[0020] An exhaust cavity is formed in the shell, the compression flow passage has an exhaust section, and the exhaust section has an exhaust connection state connected with the exhaust cavity and an exhaust disconnection state disconnected from the exhaust cavity;

[0021] When the exhaust section switches from the exhaust disconnected state to the exhaust connected state, the exhaust section and the inner wall of the rotor chamber together form a second low-pressure chamber;

[0022] A second oil supply passage is provided in the housing, and the second oil supply passage is communicated with the second low-pressure chamber;

[0023] An exhaust side bearing is used to support the rotor pair, wherein the exhaust side bearing is arranged in the housing, and a lubricating oil inlet of the exhaust side bearing is communicated with the second low-pressure chamber.

[0024] The rotor pair includes a male rotor and a female rotor meshing with each other, the female rotor is provided with at least two cathode meshing teeth, 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, each of the anode meshing teeth meshes with a cathode tooth slot to form a compression flow channel.

[0025] 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 escape from the cathode tooth grooves.

[0026] A compressor, comprising:

[0027] a housing, wherein an exhaust cavity and a rotor cavity are formed in the housing;

[0028] A rotor pair, wherein the rotor pair is disposed in the rotor cavity, and the rotor pair forms at least one compression flow channel in the rotor cavity;

[0029] The compression flow passage has an exhaust section, and the exhaust section has an exhaust connection state in which it is connected to the exhaust chamber and an exhaust disconnection state in which it is disconnected from the exhaust chamber;

[0030] When the exhaust section switches from the exhaust disconnected state to the exhaust connected state, the exhaust section and the inner wall of the rotor chamber together form a second low-pressure chamber;

[0031] A second oil supply passage is provided in the housing, and the second oil supply passage is communicated with the second low-pressure chamber;

[0032] An exhaust side bearing is used to support the rotor pair, wherein the exhaust side bearing is arranged in the housing, and a lubricating oil inlet of the exhaust side bearing is communicated with the second low-pressure chamber.

[0033] The rotor pair includes a male rotor and a female rotor meshing with each other, the female rotor is provided with at least two cathode meshing teeth, 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, each of the anode meshing teeth meshes with a cathode tooth slot to form a compression flow channel.

[0034] 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 escape from the cathode tooth grooves.

[0035] A heat exchange system comprises the above-mentioned compressor.

[0036] The heat exchange system further includes an evaporator, the air suction chamber of the compressor is in communication with the gaseous outlet of the evaporator, and the first liquid supply channel and / or the second liquid supply channel are in communication with the oil return port of the evaporator.

[0037] In the compressor and heat exchange system provided by the present invention, the rotor pair and the rotor cavity jointly 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 to finally obtain high-pressure exhaust. The inventor has found through research that in the process of the position of the compression flow channel changing, 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 amount of the suction section decreases, but the volume of the compression flow channel is constant, which is equivalent to a gradual increase in volume compared to the decrease in intake amount, so that the pressure value in the suction section at this time is small, so that it can form a first low-pressure cavity together with the corresponding part of the inner wall of the rotor cavity, and the pressure difference between the pressure of the first low-pressure cavity 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 pressurizing structure such as an ejector in the prior art, thereby reducing the cost of the compressor. BRIEF DESCRIPTION OF THE DRAWINGS

[0038] Figure 1 A schematic diagram of the structure of a compressor provided by an embodiment of the present invention;

[0039] Figure 2 Another structural schematic diagram of a compressor provided by an embodiment of the present invention;

[0040] Figure 3 for Figure 2 A local schematic diagram of the A;

[0041] Figure 4 A schematic diagram of a compressor provided by an embodiment of the present invention;

[0042] In the figure:

[0043] 1. Shell; 11. Intake chamber; 12. Rotor chamber; 14. First low-pressure chamber; 15. First oil supply channel; 3. Intake side bearing; 24. Yang rotor; 241. Anode meshing teeth; 242. Anode tooth grooves; 25. Yin 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

[0044] In order to make the purpose, technical solution and advantages of the present invention more clearly understood, the present invention is further described in detail below in conjunction with the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present invention and are not used to limit the present invention.

[0045] In order to enable those skilled in the art to better understand the scheme of the present invention, the technical scheme in the embodiments of the present invention will be clearly and completely described below in conjunction with the drawings in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work should fall within the scope of protection of the present invention.

[0046] It should be noted that the terms "first", "second", etc. in the specification and claims of the present invention and the above-mentioned drawings are used to distinguish similar objects, and are not necessarily used to describe a specific order or sequence. It should be understood that the terms used in this way can be interchanged where appropriate, so as to describe the embodiments of the present invention 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 device that includes a series of steps or units is not necessarily limited to those steps or units that are clearly listed, but may include other steps or units that are not clearly listed or inherent to these processes, methods, products or devices.

[0047] It should be noted that in the description of the present invention, the terms "upper", "lower", "left", "right", "inner", "outer" and the like indicating directions or positional relationships are based on the directions or positional relationships shown in the drawings, which are only for the convenience of description, and do not indicate or imply that the device or element must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as limiting the present invention. In addition, the terms "first" and "second" are only used for descriptive purposes and cannot be understood as indicating or implying relative importance.

[0048] In addition, it should be noted that in the description of the present invention, unless otherwise clearly specified and limited, the terms "installation", "setting", and "connection" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a direct connection, an indirect connection through an intermediate medium, or the internal connection of two components. For those skilled in the art, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0049] Most screw refrigeration compressors are lubricated by oil spraying. The oil plays a role in bearing lubrication and rotor sealing during the operation of the compressor. At present, the oil after lubrication of the exhaust side bearing of the compressor is mixed with the refrigerant of the exhaust pressure, which is a high-pressure oil. Therefore, this part of the oil is connected to the suction chamber to lubricate the suction side bearing. After the suction side bearing is lubricated, the oil returns to the suction chamber and is discharged with the compression of the rotor pair, thus forming a cycle. However, when the pressure difference of the compressor operating conditions is small, although the oil that has lubricated the exhaust side bearing has the high exhaust pressure of the compressor, the pressure difference with the suction side bearing is not large enough, and the pressure loss in the oil circuit connecting the two exhaust side bearings and the suction side bearing makes it impossible to return the oil to the suction chamber normally. When encountering such problems, the screw compressor system in the prior art mainly solves them by controlling the minimum operating pressure difference conditions and using an external oil pump to increase the oil circuit pressure difference. Moreover, when the screw compressor is under light load operation, there is oil accumulation at the bottom of the evaporator in the heat exchange cycle where the screw compressor is located. Since the pressure in the evaporator is also low pressure, it cannot be directly returned to the suction chamber of the compressor through the pressure difference, and the oil circuit circulation cannot be completed. The screw compressor system in the prior art usually uses an ejector to eject the low-pressure stored oil in the evaporator back to the suction chamber of the compressor. To this end, the present application provides a method such as Figures 1 to 4The compressor shown comprises: a shell 1, in which an intake cavity 11 and a rotor cavity 12 are formed; a rotor pair 2, in which the rotor pair is arranged in the rotor cavity 12, and the rotor pair and the rotor cavity 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 with the intake cavity 11 and an intake disconnection state disconnected from the intake cavity 11; when the intake section switches from the intake connection state to the intake disconnection state, the intake section and the inner wall of the rotor cavity 12 jointly form a first low-pressure cavity 14; a first oil supply channel 15 is arranged in the shell 1, and the first oil supply channel 15 is connected to the first low-pressure cavity 14; an intake side bearing 3 for supporting 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 cavity 14. 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 a high-pressure exhaust is obtained. The inventor has found through research that in the process of the position change of the compression flow channel, when the suction section in the compression flow channel 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 volume reduction compared with the reduction in intake volume. The volume gradually increases, so that the pressure value in the suction section is relatively small at this time, 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 the 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 prior art, thereby reducing the cost of the compressor.

[0050] Specifically, the rotor pair includes a male rotor 24, which is rotatably disposed in the rotor cavity 12. At least two anode meshing teeth 241 are disposed on the male rotor 24, and an anode tooth slot 242 is formed between two adjacent anode meshing teeth 241. Part of the anode tooth slot 242 forms the suction section. The part of the anode tooth slot 242 that forms the suction section refers to the part that can be directly connected to the suction cavity 11. When the male rotor 24 rotates, the anode tooth slot 242 rotates accordingly, and when connected to the suction cavity 11, part of the gas is sent into the anode tooth slot 242 to realize the suction process of the compression flow channel. Then the male rotor 24 continues to rotate, and the connection area between the anode tooth slot 242 and the suction cavity 11 gradually decreases, and finally completely disconnects from the suction cavity 11. The gas in the anode tooth slot 242 is gradually compressed as the rotor pair rotates, and finally discharged from the exhaust section of the rotor pair to complete the gas compression.

[0051] In the prior 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 inventor of the present application proposed the technical problem that the oil cannot be smoothly returned under low pressure difference or low load conditions, he creatively discovered that when the anode tooth slot 242 completes the intake and is about to rotate to the position sealed with the inner wall of the rotor cavity 12, the communicating area between the anode tooth slot 242 and the intake 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 of this part of the anode tooth slot 242 gradually decreases, and when it is about to complete the intake, the anode tooth slot 242 is rotated to the position sealed with the inner wall of the rotor cavity 12. When the rotor cavity 12 is sealed, the pressure reaches the lowest point. At this time, part of the anode tooth grooves 242 constituting the suction section and the rotor cavity 12 together enclose the 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 oil return 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 guide the lubricating oil at the exhaust side bearing to the low-pressure side bearing for lubrication, ensuring reliable oil circulation in the compressor. Specifically, an air suction connection port is formed between the air suction cavity 11 and the rotor cavity 12. When the air suction section is in the air suction connection state, part of the anode tooth grooves 242 are located at the air suction connection port and are connected to the air suction connection port; when the air suction section is in the air suction disconnection state, the anode tooth grooves 242 are staggered from the air suction connection port.

[0052] 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, and the intake section is connected with the intake cavity 11 through the spacing, and with the rotation of the positive rotor 24, 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 of the 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.

[0053] Similarly, the rotor pair also includes a female rotor 25, on which at least two cathode meshing teeth 251 are provided, and a cathode tooth slot 252 is formed between two adjacent cathode meshing teeth 251, and each of the anode meshing teeth 241 is meshed with one of the cathode tooth slots 252, and part of the cathode tooth slots 252 form the suction section. The part of the cathode tooth slots 252 that forms the suction section refers to the part that can be directly connected to the suction chamber 11. When the female rotor 25 rotates, the cathode tooth slots 252 rotate accordingly, and when connected to the suction chamber 11, part of the gas is sent into the cathode tooth slots 252 to realize the suction process of the compression flow channel, and then the female rotor 25 continues to rotate, and the connection area between the cathode tooth slots 252 and the suction chamber 11 gradually decreases, and finally completely disconnects from the suction chamber 11, and the gas in the cathode tooth slots 252 is gradually compressed as the rotor pair rotates, and finally discharged from the exhaust section of the rotor pair, completing the gas compression. The process of compressing the gas in the compression channel is that the anode meshing teeth 241 extend into the corresponding cathode tooth grooves 252 for meshing, thereby forcing the gas to flow along the axial direction of the rotor pair, and in this process, as the pitch of the positive rotor 24 and the negative rotor 25 changes, the volume of the compression channel where the gas is located gradually decreases, thereby achieving compression of the gas and achieving the purpose of increasing the gas pressure.

[0054] When the inventor of the present application proposed the technical problem that oil cannot be returned smoothly under low pressure difference or low load conditions, he also creatively discovered that when the cathode tooth slot 252 completes the air intake and is about to rotate to the position of sealing with the inner wall of the rotor chamber 12, the connecting area between the cathode tooth slot 252 and the air intake chamber 11 gradually decreases, so that the amount of gas entering the cathode tooth slot 252 gradually decreases, while the volume of the cathode tooth slot 252 remains unchanged, so that the pressure in this part of the cathode tooth slot 252 gradually decreases. When the airtightness with the rotor chamber 12 is about to be completed, the pressure reaches the lowest point. When the air intake section is in the state of being connected to the rotor cavity 12, part of the cathode tooth grooves 252 and the rotor cavity 12 together enclose the 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 oil return 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 guide 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. Specifically, an air intake connection port is formed between the air intake cavity 11 and the rotor cavity 12. When the air intake section is in the air intake connection state, part of the cathode tooth grooves 252 are located at the air intake connection port and are connected to the air intake connection port; when the air intake section is in the air intake disconnection state, the cathode tooth grooves 252 are staggered from the air intake connection port.

[0055] Among them, in the two cathode meshing teeth 251 constituting the cathode tooth groove 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, and the intake section is connected with the intake cavity 11 through the spacing, and as the female 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, the two cathode meshing teeth 251 are rotated to a position that seals with the inner wall of the rotor cavity 12, thereby disconnecting the cathode tooth groove 252 from the intake connection port, and preparing for sealing for the next step of compressing the gas in the compression flow channel.

[0056] The compressor also includes an exhaust side bearing 4, one end of the first oil supply channel 15 is connected to the lubricating oil outlet of the exhaust side bearing 4, and the other end constitutes the outlet. Since the gas is compressed by the compression flow channel, the pressure at the exhaust side bearing 4 is much 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 channel 15 by utilizing the pressure difference between the pressure at the exhaust side bearing 4 and the pressure of the first low-pressure chamber 14, and finally sent to the suction side bearing 3 for lubrication, and then refluxed to the suction chamber 11 through the suction side bearing 3, realizing the oil circuit circulation in the compressor.

[0057] Alternatively, one end of the first oil supply passage 15 is connected to the lubricating oil supply mechanism, and the other end constitutes the 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 the oil return of the compressor.

[0058] 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 with 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 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. As the rotor pair operates, the position of the compression flow channel in the rotor chamber 12 is constantly changing. By utilizing this change, the gas in the suction chamber 11 can be sucked in and continuously compressed, and finally high-pressure exhaust is obtained. The inventor has found through research that in the process of the compression flow channel being connected to the exhaust chamber 13, the gas in the compression flow channel will be completely squeezed out, thereby achieving exhaust of the compression flow channel. When the exhaust section of the compression flow channel used to communicate with the exhaust chamber 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 chamber 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 pressure of 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 prior art that an ejector is required to eject the stored oil in the evaporator, 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.

[0059] Specifically, 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, and 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. The meshing of the anode meshing teeth 241 and the cathode tooth grooves 252 is used to force the gas to flow in the compression flow channel, and as the pitch of the anode meshing teeth 241 and the cathode meshing teeth 251 gradually decreases, the volume of the compression flow channel gradually decreases, thereby achieving compression of the gas. When the compression flow 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 flow channel, so that the volume of the compression flow channel in the exhaust section is substantially zero. As the rotor segment rotates, the anode meshing teeth 241 gradually leave the compression flow channel, that is, in the process of the exhaust segment switching from the exhaust disconnected state to the exhaust connected state, the anode meshing teeth 241 constituting the exhaust segment gradually disengage from the cathode tooth grooves 252, and the exhaust segment content volume gradually increases. At this time, no gas is replenished in the exhaust segment, so that the pressure in the exhaust segment at this time becomes lower and lower, and even a vacuum state can be formed. Therefore, the position of the exhaust segment 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 form a pressure difference, thereby ensuring the smooth oil return of the compressor.

[0060] Another technical solution of the present application provides a Figures 2 to 4The compressor shown comprises: a shell 1, in which an exhaust chamber 13 and a rotor chamber 12 are formed; a rotor pair, in which the rotor pair is arranged in the rotor chamber 12, and in which the rotor pair forms at least one compression flow channel; 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 arranged 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. As the rotor pair operates, the position of the compression flow channel in the rotor chamber 12 is constantly changing. By utilizing this change, the gas in the suction chamber 11 can be sucked in and continuously compressed, and finally high-pressure exhaust is obtained. The inventor has found through research that in the process of the compression flow channel being connected to the exhaust chamber 13, the gas in the compression flow channel will be completely squeezed out, thereby achieving exhaust of the compression flow channel. When the exhaust section of the compression flow channel used to communicate with the exhaust chamber 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 chamber 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 pressure of 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 prior art that an ejector is required to eject the stored oil in the evaporator, 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.

[0061] 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. The meshing of the anode meshing teeth 241 and the cathode tooth grooves 252 is used to force the gas to flow in the compression flow channel, and as the pitch of the anode meshing teeth 241 and the cathode meshing teeth 251 gradually decreases, the volume of the compression flow channel gradually decreases, thereby achieving compression of the gas. When the compression flow 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 flow channel, so that the volume of the compression flow channel in the exhaust section is substantially zero. As the rotor segment rotates, the anode meshing teeth 241 gradually leave the compression flow channel, that is, in the process of the exhaust segment switching from the exhaust disconnected state to the exhaust connected state, the anode meshing teeth 241 constituting the exhaust segment gradually disengage from the cathode tooth grooves 252, and the exhaust segment content volume gradually increases. At this time, no gas is replenished in the exhaust segment, so that the pressure in the exhaust segment at this time becomes lower and lower, and even a vacuum state can be formed. Therefore, the position of the exhaust segment 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 form a pressure difference, thereby ensuring the smooth oil return of the compressor.

[0062] A heat exchange system comprises the above-mentioned compressor.

[0063] The heat exchange system further includes an evaporator, the air suction chamber 11 of the compressor is in communication with the gaseous outlet of the evaporator, and the first liquid supply channel and / or the second liquid supply channel are in communication with the oil return port of the evaporator.

[0064] The above-mentioned embodiments only express several implementation methods of the present invention, and the description thereof is relatively specific and detailed, but it cannot be understood as limiting the scope of the patent of the present invention. It should be pointed out that, for ordinary technicians in this field, several variations and improvements can be made without departing from the concept of the present invention, which all belong to the protection scope of the present invention. Therefore, the protection scope of the patent of the present invention shall be subject to the attached claims.

Claims

1. A compressor, characterized in that: include: A housing (1), wherein an air suction chamber (11) and a rotor chamber (12) 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) together forming at least one compression flow channel; The compression flow channel has an air suction section, the air suction section having an air suction connection state in which it is connected to the air suction chamber (11) and an air suction disconnection state in which it is disconnected from the air suction chamber (11); When the air intake section switches from the air intake connected state to the air intake disconnected state, the air intake section and the inner wall of the rotor cavity (12) together form a first low-pressure cavity (14); A first oil supply passage (15) is provided in the housing (1), and the first oil supply passage (15) is communicated with the first low-pressure chamber (14); An air intake side bearing (3) for supporting the rotor pair, the air intake side bearing (3) being arranged in the housing (1), and a lubricating oil inlet of the air intake side bearing (3) being in communication with the first low-pressure chamber (14).

2. The compressor according to claim 1, characterized in that: The rotor pair comprises a male rotor (24), the male rotor (24) being rotatably disposed in the rotor cavity (12), the male rotor (24) being provided with at least two anode meshing teeth (241), an anode tooth groove (242) being formed between two adjacent anode meshing teeth (241), and a portion of the anode tooth grooves (242) forming the air intake section.

3. The compressor according to claim 2, characterized in that: An air intake communication port is formed between the air intake cavity (11) and the rotor cavity (12); when the air intake section is in the air intake communication state, part of the anode tooth slots (242) are located at the air intake communication port and are connected to the air intake communication port; when the air intake section is in the air intake disconnection state, the anode tooth slots (242) are staggered from the air intake communication port.

4. The compressor according to claim 2, characterized in that: The rotor pair further comprises a negative rotor (25), the negative rotor (25) being provided with at least two cathode meshing teeth (251), a cathode tooth groove (252) being formed between two adjacent cathode meshing teeth (251), each of the anode meshing teeth (241) being meshed with one of the cathode tooth grooves (252), and a portion of the cathode tooth grooves (252) forming the air intake section.

5. The compressor according to claim 4, characterized in that: An air intake communication port is formed between the air intake cavity (11) and the rotor cavity (12); when the air intake section is in the air intake communication state, part of the cathode tooth slots (252) are located at the air intake communication port and are connected to the air intake communication port; when the air intake section is in the air intake disconnection state, the cathode tooth slots (252) are staggered from the air intake communication port.

6. The compressor according to any one of claims 1 to 5, characterized in that: The compressor further comprises an exhaust side bearing (4), one end of the first oil supply passage (15) being connected to the lubricating oil outlet of the exhaust side bearing (4), and the other end constituting the outlet; or one end of the first oil supply passage (15) being connected to the lubricating oil supply mechanism, and the other end constituting the outlet.

7. The compressor according to claim 1, characterized in that: 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 in which it is connected to the exhaust chamber (13) and an exhaust disconnection state in which it is disconnected from the exhaust chamber (13); When the exhaust section switches from the exhaust disconnected state to the exhaust connected state, the exhaust section and the inner wall of the rotor chamber (12) together form a second low-pressure chamber (16); 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); An exhaust side bearing (4) for supporting the rotor pair, the exhaust side bearing (4) being arranged in the housing (1), and a lubricating oil inlet of the exhaust side bearing (4) being in communication with the second low-pressure chamber (16).

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

9. The compressor according to claim 8, characterized in that: 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, characterized in that: include: A housing (1), wherein an exhaust cavity (13) and a rotor cavity (12) 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 passage has an exhaust section, the exhaust section having an exhaust connection state in which it is connected to the exhaust chamber (13) and an exhaust disconnection state in which it is disconnected from the exhaust chamber (13); When the exhaust section switches from the exhaust disconnected state to the exhaust connected state, the exhaust section and the inner wall of the rotor chamber (12) together form a second low-pressure chamber (16); 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); An exhaust side bearing (4) for supporting the rotor pair, the exhaust side bearing (4) being arranged in the housing (1), and a lubricating oil inlet of the exhaust side bearing (4) being in communication with the second low-pressure chamber (16).

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

12. The compressor according to claim 11, characterized in that: 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, characterized in that: A compressor comprising the compressor according to any one of claims 1 to 12.

14. The heat exchange system according to claim 13, characterized in that: The heat exchange system further comprises an evaporator, and the suction chamber (11) of the compressor is in communication with the gaseous outlet of the evaporator.

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