Rotor compressor and thermal management system

Abstract

The invention relates to the technical field of thermal management, and provides a rotor compressor and a thermal management system.The rotor compressor is provided with at least one bypass pipe for communicating a compression cavity of a rotor pump with an air suction cavity of the rotor pump or a device communicated with the air suction cavity; a first valve is arranged on the bypass pipe, the bypass pipe is blocked by the first valve when the rotor pump works, and the bypass pipe is conducted by the first valve when the rotor pump stops. The pressure difference between the air suction cavity and the compression cavity in the rotor pump is balanced after the compressor is shut down, the gas resistance moment is effectively reduced, and the problem that the starting speed is low due to the fact that the gas resistance moment is larger than the motor moment at the starting moment of the compressor is solved.

Description

Technical Field

[0001] The present invention relates to the field of thermal management technology, and in particular to a rotor compressor and a thermal management system. Background Art

[0002] At present, rotary compressors are widely used in thermal management systems, such as energy storage thermal management, refrigerators, air conditioners, heat pump water heaters, dryers, and cold dryer thermal management systems.

[0003] The compressor is difficult to start under pressure differential conditions, mainly because the pressure difference between the high-pressure side and the low-pressure side inside the compressor pump body is large under pressure differential conditions. This pressure difference provides a torque on the rotor to prevent its rotation. The torque provided by the pressure difference at the moment of starting is greater than the starting torque of the starting motor.

[0004] When the thermal management system is shut down, the refrigerant stops circulating, and a large amount of high-pressure and low-pressure gases remain in the condenser and evaporator of the thermal management system, respectively. This causes a large pressure difference between the high-pressure side and the low-pressure side of the rotary compressor after the system is shut down, making it difficult to start the compressor. The high-pressure side of the compressor refers to the exhaust side of the compressor or the compression chamber of the rotary pump, and the low-pressure side of the compressor refers to the suction side of the compressor or the suction chamber of the rotary pump.

[0005] Moreover, the pressure difference between the high-pressure side and the low-pressure side of the compressor is difficult to quickly reduce to a level that can be overcome by the motor starting torque in a short period of time, especially for single-phase fixed-speed rotor compressors, whose motor torque is relatively small. After the thermal management system is shut down, it often takes a few minutes for the pressure difference between the high-pressure side and the low-pressure side of the compressor to gradually decrease to a balance before it can be restarted.

[0006] Therefore, based on the above technical problems, a rotor compressor and a thermal management system are needed. By improving the rotor compressor, the pressure difference between the high-pressure side and the low-pressure side of the rotor can be quickly balanced after the rotor compression is shut down, so as to shorten the time for the rotor compressor to restart. Summary of the invention

[0007] The object of the present invention is to provide a rotor compressor and a thermal management system. By improving the rotor compressor, the pressure difference between the high-pressure side and the low-pressure side of the rotor compressor can be quickly balanced after the rotor compressor is shut down, so as to shorten the time for restarting the rotor compressor.

[0008] The rotary compressor of the present invention is provided with at least one bypass pipe to connect the compression chamber of the rotary pump with the suction chamber of the rotary pump or a device connected to the suction chamber; a first valve is provided on the bypass pipe, and the first valve blocks the bypass pipe when the rotary pump is working and opens the bypass pipe when the rotary pump is stopped.

[0009] Optionally, the rotary compressor further comprises a shell, an exhaust pipe is arranged on the shell, a second valve is arranged at the exhaust pipe, and the second valve is configured as follows: when the rotary pump is working, the second valve is opened to conduct the exhaust pipe, and when the rotary pump is stopped, the second valve is closed to block the exhaust pipe. The device connected to the suction chamber includes but is not limited to a liquid storage tank, a pipeline connected to the liquid storage tank or the cylinder suction chamber in the air conditioning system, etc. The liquid storage tank includes but is not limited to an air inlet pipe of the liquid storage tank, a shell of the liquid storage tank, or an air outlet pipe of the liquid storage tank.

[0010] Optionally, the device connected to the suction cavity includes a liquid reservoir, and the bypass pipe is connected to the liquid reservoir.

[0011] Optionally, the rotor pump includes at least a first cylinder, a second cylinder and an isolating member arranged in an axial direction, the isolating member is located between the first cylinder and the second cylinder, the first cylinder, the second cylinder and the middle part of the isolating member are all provided with a channel for the crankshaft to pass through, the isolating member is provided with a pressure relief channel, one end of the pressure relief channel is connected to the compression chamber of the first cylinder and / or the compression chamber of the second cylinder, and the other end of the pressure relief channel is connected to the bypass pipe.

[0012] Optionally, the pressure relief channel is arranged along the radial direction of the isolation element, and one end of the pressure relief channel is connected to the outer wall of the isolation element, and the other end of the pressure relief channel is connected to the inner wall of the channel.

[0013] Optionally, the pressure relief channel is L-shaped, and the isolation member includes at least one L-shaped pressure relief channel, one end of the L-shaped pressure relief channel passes through the outer wall of the isolation member, and the port at the other end is located on the end face of the isolation member in the axial direction.

[0014] Optionally, the pressure relief channel includes a main channel and at least two branch channels connected to the main channel, the main channel is arranged along the radial direction of the isolation member, one end of the main channel is connected to the outer wall of the isolation member, at least one of the branch channels is connected to the end surface of the isolation member facing the first cylinder, and at least one of the branch channels is connected to the end surface of the isolation member facing the second cylinder.

[0015] Optionally, a projection of a port of the pressure relief channel located in the axial direction on the first cylinder or the second cylinder is located within the compression chamber of the first cylinder or the second cylinder.

[0016] Optionally, a central angle α formed between a port of the pressure relief channel in the axial direction and a blade of the rotor pump satisfies 0≤α≤45°.

[0017] The present invention also provides a thermal management system, which includes the rotor compressor described above.

[0018] To summarize, in the present invention, the compression chamber of the rotor pump is connected to the suction chamber on the suction side or a device connected to the suction chamber, which is beneficial to quickly reduce the pressure in the compression chamber when shutting down, balance the pressure difference between the suction chamber and the compression chamber in the rotor pump, effectively reduce the gas resistance torque, and solve the problem of slow starting speed of the compressor due to the gas resistance torque being greater than the motor torque at the moment of starting, so that the pressure difference between the compression chamber and the suction chamber is quickly reduced to a level that can be overcome by the motor starting torque. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] Figure 1 This is a schematic diagram of the structure of a thermal management system according to a first embodiment of the present invention;

[0020] Figure 2 The structure of the rotary compressor of the first embodiment of the present invention is shown in FIG. Figure 1 ;

[0021] Figure 3 The structure of the rotary compressor of the first embodiment of the present invention is shown in FIG. Figure 2 ;

[0022] Figure 4 It is a schematic diagram of the structure of the rotary compressor according to the second embodiment of the present invention.

[0023] The reference numerals are as follows:

[0024] 10-rotor pump; 11-compression chamber; 111-first compression chamber; 112-second compression chamber; 12-intake chamber; 13-exhaust port;

[0025] 101-first cylinder; 102-second cylinder; 103-isolator; 1031-channel; 104-pressure relief channel; 1041-main channel; 1042-branch channel; 105-blade;

[0026] 20-liquid reservoir; 21-bypass pipe;

[0027] 30- first valve;

[0028] 40 - second valve;

[0029] 50-condenser;

[0030] 60-evaporator;

[0031] 70-four-way valve;

[0032] 80-Throttling device. DETAILED DESCRIPTION

[0033] The rotary compressor proposed by the present invention is further described in detail below in conjunction with the accompanying drawings and specific embodiments. The advantages and features of the present invention will become clearer according to the following description. It should be noted that the accompanying drawings are all in a very simplified form and are not in precise proportions, and are only used to conveniently and clearly assist in explaining the purpose of the embodiments of the present invention.

[0034] As used in the present invention, the singular forms "one", "an" and "the" include plural objects, the term "or" is usually used to include the meaning of "and / or", the term "several" is usually used to include the meaning of "at least one", and the terms "at least two" or "multiple" are usually used to include the meaning of "two or more". In addition, the terms "first", "second" and "third" are only used for descriptive purposes and cannot be understood as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Therefore, the features defined as "first", "second" and "third" can explicitly or implicitly include one or at least two of the features. In addition, as used in the present invention, "installed", "connected", "connected", and one element "set" on another element should be understood in a broad sense, usually only indicating that there is a connection, coupling, matching or transmission relationship between the two elements, and the connection, coupling, matching or transmission between the two elements can be direct or indirect through an intermediate element, and cannot be understood as indicating or implying the spatial position relationship between the two elements, that is, one element can be in any orientation such as inside, outside, above, below or on one side of another element, unless the content clearly indicates otherwise. For those skilled in the art, the specific meanings of the above terms in the present invention can be understood according to specific circumstances. In addition, directional terms such as above, below, up, down, upward, downward, left, right, etc. are used with respect to the exemplary embodiments as they are shown in the figures, with the upward or upper direction toward the top of the corresponding figure, and the downward or lower direction toward the bottom of the corresponding figure.

[0035] At present, rotary compressors are widely used in thermal management systems, such as energy storage thermal management, refrigerators, air conditioners, heat pump water heaters, dryers, and cold dryer thermal management systems.

[0036] The compressor is difficult to start under pressure differential conditions, mainly because the pressure difference between the high-pressure side and the low-pressure side inside the compressor pump body is large under pressure differential conditions. This pressure difference provides a torque on the rotor to prevent its rotation. The torque provided by the pressure difference at the moment of starting is greater than the starting torque of the motor.

[0037] When the thermal management system is shut down, the refrigerant stops circulating, and the high-pressure gas in the condenser pipeline will continue to flow back into the compressor. The volume of the evaporator and condenser is much larger than the volume of the compressor housing and the liquid reservoir. When the system is shut down, a large amount of high-pressure and low-pressure gas remains in the condenser and evaporator in the thermal management system, respectively, which makes the pressure difference between the high-pressure side and the low-pressure side of the rotary compressor large after the system is shut down, making it difficult to start the compressor. The high-pressure side of the compressor refers to the exhaust side of the compressor or the compression chamber of the rotary pump, and the low-pressure side of the compressor refers to the suction side of the compressor or the suction chamber of the rotary pump.

[0038] Moreover, the pressure difference between the high-pressure side and the low-pressure side of the compressor is difficult to quickly reduce to a level that can be overcome by the motor starting torque in a short period of time, especially for single-phase fixed-speed rotor compressors, whose motor torque is relatively small. After the thermal management system is shut down, it often takes a few minutes for the pressure difference between the high-pressure side and the low-pressure side of the compressor to gradually decrease to a balance before it can be restarted.

[0039] Therefore, based on the above technical problems, a rotor compressor and a thermal management system are needed. By improving the rotor compressor, the pressure difference between the high-pressure side and the low-pressure side of the rotor can be quickly balanced after the rotor compression is shut down, so as to shorten the restart time of the rotor compressor.

[0040] Embodiment 1:

[0041] Please refer to Figure 1 and Figure 2 As shown, a thermal management system includes a rotor compressor;

[0042] The rotary compressor includes: a rotary pump 10, a liquid reservoir 20, a first valve 30 and a second valve 40;

[0043] The thermal management system further includes a condenser 50 , an evaporator 60 , a four-way valve 70 and a throttle 80 .

[0044] The exhaust port 13 of the rotor pump 10 is connected to its compression chamber 11, the compressor exhaust pipe is externally connected to one port of a four-way valve 70, the second port of the four-way valve 70 is connected to the liquid inlet of the condenser 50, the liquid outlet of the condenser 50 is connected to the inlet of the evaporator 60 through the throttling device 80, the outlet of the evaporator 60 is connected to the third port of the four-way valve 70, and the fourth port of the four-way valve 70 is connected to the liquid reservoir 20, and the flow direction and flow rate of the refrigerant are controlled by the four-way valve 70.

[0045] The liquid storage device 20 is usually a liquid storage tank, the throttling device 80 is usually an expansion valve, and the condenser 50, the evaporator 60, the four-way valve 70 and the throttling device 80 are all existing equipment and will not be described in detail here.

[0046] Please continue to refer to Figure 1As shown, the compression chamber 11 of the rotor pump 10 is communicated with the inner cavity of the liquid reservoir 20, and the inner cavity of the liquid reservoir 20 is also communicated with the suction chamber 12 of the rotor pump 10;

[0047] The first valve 30 is arranged on the bypass pipe 21 connecting the compression chamber 11 and the inner cavity of the liquid reservoir 20, and is used to control the opening and closing of the passage. The first valve 30 is configured as follows: when the rotor pump 10 is working, the first valve 30 is closed, and the passage connecting the compression chamber 11 and the inner cavity of the liquid reservoir 20 is interrupted, thereby ensuring that the refrigerant does not flow between the compression chamber 11 and the suction chamber 12, thereby reducing the mutual interference between the two; when the rotor pump 10 is stopped, the first valve 30 is opened, and the passage connecting the compression chamber 11 and the inner cavity of the liquid reservoir 20 is connected, thereby ensuring that the refrigerant between the liquid reservoir 20 and the compression chamber 11 flows through the passage, thereby indirectly connecting the compression chamber 11 and the suction chamber 12, thereby facilitating the rapid balance of the pressure difference between the two. The first valve 30 is preferably a solenoid valve, which is connected to the controller so that the solenoid valve and the rotor pump 10 form an electrical locking relationship, that is, when the rotor pump 10 is shut down, the solenoid valve opens; when the speed of the rotor pump 10 reaches the reference value set in the control, the solenoid valve closes.

[0048] Please combine Figure 2 As shown, the rotor pump 10 is provided with blades 105 and a rotor (not shown in the figure), the outer circle of the rotor is always in contact with the end of the blade, and the inner cavity of the rotor pump 10 is divided into a compression chamber 11 and a suction chamber 12 by the blade and the rotor. As the rotor rotates, the volume of the compression chamber 11 and the suction chamber 12 changes to achieve the purpose of inhaling and discharging the refrigerant, wherein the compression chamber 11 is the high-pressure side of the rotor pump 10, and the suction chamber 12 is the low-pressure side of the rotor pump 10; the operating principle of the rotor pump 10 is the prior art and will not be repeated here.

[0049] The suction side of the rotor pump of the present invention includes the suction chamber 12 of the rotor pump or the inner cavity of the liquid reservoir 20. One end of the bypass pipe 21 is connected to the compression chamber 11 of the rotor pump, and the other end of the bypass pipe 21 is connected to the suction chamber 12 of the rotor pump, or the other end of the bypass pipe 21 is indirectly connected to the suction chamber 12 of the rotor pump by connecting to the inner cavity of the liquid reservoir 20. Further, the other end of the bypass pipe 21 can be connected to the air inlet pipe of the liquid reservoir 20, can be connected to the outer shell of the liquid reservoir 20, or can be connected to the air outlet pipe of the liquid reservoir 20. In this embodiment, the compression chamber 11 is connected to the air inlet pipe of the liquid reservoir 20 through the bypass pipe 21, which is convenient for processing. Moreover, the compression chamber 11 is connected to the liquid reservoir 20. On the one hand, the liquid reservoir 20 is connected to the compression chamber 11 as a low-pressure area, which is conducive to quickly reducing the pressure in the compression chamber 11, so that the pressure difference between the compression chamber 11 and the suction chamber 12 is quickly reduced to a level that can be overcome by the starting torque of the motor; on the other hand, the liquid reservoir 20 is connected to the compression chamber 11 and the suction chamber 12 at the same time. When the rotor pump 10 is shut down, the liquid reservoir 20 also serves as a buffer structure, so that the pressures in the compression chamber 11 and the suction chamber 12 are simultaneously balanced toward the pressure center point in the liquid reservoir 20, which not only ensures the rapid balance of the air pressure in the compression chamber 11 and the suction chamber 12 to shorten the restart time of the rotor compressor, but also ensures that the air pressure in the compression chamber 11 and the suction chamber 12 will not change suddenly and affect the performance of the rotor pump 10.

[0050] Taking an existing rotor compressor as an example, after it is shut down, the pressure difference between the compression chamber 11 and the suction chamber 12 is 2.5MPa. Under normal circumstances, the time interval for the system to shut down and restart is about 129s. When the compression chamber 11 is connected to the inner cavity of the liquid reservoir 20, the time interval for the system to shut down and restart is about 45s, and the shutdown and startup time is significantly shortened.

[0051] Please continue to refer to Figure 1 As shown, the rotary compressor also includes a second valve 40, which is arranged at the exhaust pipe of the rotary pump 10. The exhaust pipe is fixed on the outer shell of the compressor and is connected to the inner cavity of the outer shell of the compressor. The compression chamber 11 discharges the high-pressure refrigerant into the inner cavity of the outer shell of the compressor through the exhaust port 13. The second valve is configured as follows: when the rotary pump 10 is working, the second valve 40 is opened, and when the rotary pump 10 is stopped, the second valve 40 is closed.

[0052] Preferably, the second valve 40 is a solenoid valve or a one-way valve for one-way flow from the inside of the rotary compressor 10 to the outside. When the rotary pump 10 is working, the second valve 40 is opened, and the refrigerant in the compression chamber 11 flows normally through the exhaust pipe. When the rotary pump 10 is shut down, the second valve 40 is closed, and the high-pressure return refrigerant from the condenser is cut off from entering the compressor housing, that is, after the rotary pump 10 is shut down, the compressor housing will not be replenished with high-pressure refrigerant, avoiding the increase of high-pressure refrigerant and delaying the pressure difference balance. The compression chamber 11 is connected to the liquid reservoir 20, which is conducive to further shortening the time required for the pressure difference between the compression chamber 11 and the suction chamber 12 to be reduced to a level that can be overcome by the motor starting torque.

[0053] Still taking the above-mentioned existing rotary compressor as an example, the compression chamber 11 is connected with the inner cavity of the liquid reservoir 20, and after adding the second valve 40, the time interval between system shutdown and restart is further shortened to about 19 seconds.

[0054] Please continue to refer to Figure 1 As shown, the top position of the liquid reservoir 20 is connected to the fourth port of the four-way valve 70 as its liquid inlet. The refrigerant in the liquid reservoir 20 is usually in a gas-liquid mixed state, and its liquid refrigerant gathers at the bottom of the inner cavity of the liquid reservoir 20. The compression chamber 11 is connected to the top position of the liquid reservoir 20 through the bypass pipe 21, which is conducive to ensuring that the compression chamber 11 contacts the gaseous refrigerant in the inner cavity of the liquid reservoir 20 through the bypass pipe 21. The gaseous refrigerant flows faster in the bypass pipe 21 than the liquid refrigerant and has less resistance. When the first valve 30 is opened, it is conducive to ensuring that the high-pressure refrigerant in the compression chamber 11 is quickly exchanged with the gaseous low-pressure refrigerant in the liquid reservoir 20 to achieve the purpose of quickly reducing the pressure difference.

[0055] Please refer to Figure 2 and Figure 3 As shown, the rotor pump 10 at least includes a first cylinder 101, a second cylinder 102 and a spacer 103 arranged in an axial direction, and the first cylinder 101, the second cylinder 102 and the spacer 103 are all provided with a channel 1031 for the crankshaft to pass through. The spacer 103 is located between the first cylinder 101 and the second cylinder 102, and the inner diameter of the spacer 103 is smaller than the inner diameters of the first cylinder 101 and the second cylinder 102. The inner diameters of the first cylinder 101 and the second cylinder 102 are not limited, and the two can be the same or different. Rotors are installed in the first cylinder 101 and the second cylinder 102, respectively, and the first cylinder 101 and the second cylinder 102 have a compression chamber and an intake chamber, respectively. As shown Figure 3 As shown, the first compression chamber 111 is the compression chamber of the first cylinder 101 , and the second compression chamber 112 is the compression chamber of the second cylinder 102 .

[0056] In this embodiment, only the first cylinder 101 and the second cylinder 102 are provided, so a double cylinder is formed, and a rotor is adaptively provided in each cylinder, so the rotor pump 10 is a double rotor, forming a double rotor compressor. Of course, in other alternative embodiments, the number of cylinders and the number of spacers can be adaptively increased to form a multi-rotor compressor. The structure of the multi-rotor compressor is prior art and will not be described in detail here.

[0057] In this embodiment, at least one pressure relief channel 104 is provided on the isolation member 103, and the pressure relief channel 104 is L-shaped, with one end of the L-shaped pressure relief channel 104 connected to the outer wall of the isolation member 103, and the other end connected to the end face of the isolation member 103 in the axial direction. Specifically, when one pressure relief channel 104 is provided, one end of the L-shaped pressure relief channel 104 is located on the end face of the isolation member 103 facing the first compression chamber 111 or the second compression chamber 112. When two pressure relief channels 104 are provided, the ports of the two pressure relief channels 104 can be connected to the first compression chamber 111 and the second compression chamber 112, respectively. The pressure relief channel 104 is connected to the inner cavity of the liquid reservoir 20 through the bypass pipe 21. If there are two or more pressure relief channels 104, a corresponding number of bypass pipes 21 can be added to connect the various pressure relief channels 104, or a connecting pipe can be added to the port of each pressure relief channel 104 located on the outer wall of the isolation member 103, and multiple connecting pipes are connected to one bypass pipe 21. When the compression chamber of each cylinder is provided with a pressure relief channel connected to the liquid reservoir 20, it is beneficial to balance the pressure difference between the compression chamber and the suction chamber of the two cylinders respectively, and at the same time reduce the pressure difference caused by the asynchronous pressure change between the two chambers, so as to ensure that the rotor pump 10 is uniformly stressed as a whole.

[0058] Furthermore, the two L-shaped pressure relief channels 104 may also be connected and share the L-shaped radial channel, that is, a cross-shaped pressure relief channel. Figure 2 and Figure 3 As shown, in this embodiment, the pressure relief channel 104 includes a main channel 1041 and two branch channels 1042 connected to the main channel 1041, the main channel 1041 is arranged along the radial direction of the isolation member 103, one end of the main channel 1041 is connected to the outer wall of the isolation member 103, an opening of the branch channel 1042 is located on the end surface of the isolation member 103 facing the first cylinder 101, and is connected to the compression chamber of the first cylinder 101, and an opening of the branch channel 1042 is located on the end surface of the isolation member 103 facing the second cylinder 102, and is connected to the compression chamber of the second cylinder 102.

[0059] In this embodiment, the pressure relief channel can be processed by fine hole processing. Further, a section of the channel near the outer wall of the isolation member 103 can be set as a wide hole, combined with the internal fine holes to form a stepped channel. Of course, in other alternative embodiments, the main channel can also be set as a cylindrical shape with equal diameter or other shapes.

[0060] The branch channel 1042 is perpendicular to the main channel 1041 , and extends along the axial direction of the rotor pump 10 to ensure smooth communication with the first cylinder 101 and the second cylinder 102 , and is also conducive to processing and forming.

[0061] It is conceivable that more branch channels 1042 can be provided, and the number of branch channels 1042 connected to the first cylinder 101 and the second cylinder 102 can be flexibly allocated. In this embodiment, the number of branch channels 1042 connected to the first cylinder 101 and the second cylinder 102 is preferably the same.

[0062] It is conceivable that the branch channel 1042 and the main channel 1041 may also be set at other angles to make the overall channel smoother to reduce fluid resistance.

[0063] Please refer to Figure 2 and Figure 3 As shown, in this embodiment, the pressure relief channel 104 is located on the exhaust side of the rotor pump 10, and the projection of the axial port of the pressure relief channel 104 on the first cylinder 101 or the second cylinder 102 is located in the compression chamber of the first cylinder 101 or the second cylinder 102. More specifically, the central angle α between the opening of the end face of the pressure relief channel 104 facing the axial direction of the isolation member 103 and the blade 105 of the rotor pump 10 is 0° to 45°. By limiting the central angle between the opening at one end of the pressure relief channel 104 and the blade 105, it is beneficial to ensure that the refrigerant in the high-pressure compression chamber is effectively depressurized when the machine is shut down.

[0064] Embodiment 2:

[0065] The difference between this embodiment and the first embodiment lies in the difference of the pressure relief passage 104;

[0066] Please refer to Figure 4 As shown, the pressure relief channel 104 is in communication with the channel 1031 of the isolation member 103 .

[0067] The pressure relief channel 104 is disposed along the radial direction of the isolation member 103 , and one end of the pressure relief channel 104 is connected to the outer wall of the isolation member 103 , and the other end of the pressure relief channel 104 is connected to the inner wall of the channel 1031 .

[0068] The rotor pump 10 is a multi-rotor pump, and there is a small gap between the rotor and the adjacent isolating member 103 along the axial direction. Therefore, in fact, the channel 1031 is connected to the inner cavity of the first cylinder 101 and the inner cavity of the second cylinder 102 through the small gap, so the pressure relief channel 104 can be directly opened radially to communicate with the channel 1031. Therefore, from a macroscopic point of view, the pressure relief channel 104 is connected to the inner cavity of the rotor pump 10.

[0069] It is conceivable that the pressure relief channel 104 can also be connected only to the compression chamber of the first cylinder 101 or the compression chamber of the second cylinder 102, or the pressure relief channel 104 can choose to be directly connected to two or all of the compression chamber of the first cylinder 101, the compression chamber of the second cylinder 102 and the channel 1031.

[0070] The various embodiments in this specification are described in a progressive manner, and each embodiment focuses on the differences from other embodiments. The same or similar parts between the various embodiments can be referenced to each other.

[0071] The above description is only a description of the preferred embodiments of the present invention, and is not intended to limit the scope of the present invention. Any changes or modifications made by a person skilled in the art in the field of the present invention based on the above disclosure shall fall within the scope of protection of the claims.

Claims

1. A rotary compressor, characterized in that: At least one bypass pipe is provided to connect the compression chamber of the rotor pump with the suction chamber of the rotor pump or a device connected to the suction chamber; a first valve is provided on the bypass pipe, and the first valve blocks the bypass pipe when the rotor pump is working and opens the bypass pipe when the rotor pump is stopped.

2. The rotary compressor according to claim 1, characterized in that: The rotary compressor also includes a shell, an exhaust pipe is provided on the shell, and a second valve is provided at the exhaust pipe. The second valve is configured as follows: when the rotary pump is working, the second valve opens to connect the exhaust pipe, and when the rotary pump is stopped, the second valve closes to block the exhaust pipe.

3. The rotary compressor according to claim 1, characterized in that: The device connected to the air suction cavity includes a liquid reservoir, and the bypass pipe is connected to the liquid reservoir.

4. The rotary compressor according to claim 1, characterized in that: The rotor pump at least includes a first cylinder, a second cylinder and an isolating member arranged in an axial direction, the isolating member is located between the first cylinder and the second cylinder, the first cylinder, the second cylinder and the middle of the isolating member are all provided with a channel for the crankshaft to pass through, the isolating member is provided with a pressure relief channel, one end of the pressure relief channel is connected to the compression chamber of the first cylinder and / or the compression chamber of the second cylinder, and the other end of the pressure relief channel is connected to the bypass pipe.

5. The rotary compressor according to claim 4, characterized in that: The pressure relief channel is arranged along the radial direction of the isolation element, one end of the pressure relief channel is connected to the outer wall of the isolation element, and the other end of the pressure relief channel is connected to the inner wall of the channel.

6. The rotary compressor according to claim 4, characterized in that: The pressure relief channel is L-shaped, and the isolation member includes at least one L-shaped pressure relief channel, one end of the L-shaped pressure relief channel is connected to the outer wall of the isolation member, and the other end is connected to the end surface of the isolation member in the axial direction.

7. The rotary compressor according to claim 6, characterized in that: The pressure relief channel includes a main channel and at least two branch channels connected to the main channel, the main channel is arranged along the radial direction of the isolation member, one end of the main channel is connected to the outer wall of the isolation member, at least one of the branch channels is connected to the end surface of the isolation member facing the first cylinder, and at least one of the branch channels is connected to the end surface of the isolation member facing the second cylinder.

8. The rotary compressor according to claim 6 or 7, characterized in that: A projection of a port of the pressure relief passage in the axial direction on the first cylinder or the second cylinder is located on a compression chamber side of the first cylinder or the second cylinder.

9. The rotary compressor according to claim 6 or 7, characterized in that: A central angle formed between a port of the pressure relief channel in the axial direction and the blades of the rotor pump is α, which satisfies 0≤α≤45°.

10. A thermal management system, characterized in that: The thermal management system comprises a rotary compressor as claimed in any one of claims 1 to 9.

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