Rotor compressor and heat exchange system

Abstract

The invention relates to the technical field of heat management, and provides a rotor compressor and a heat exchange system.The rotor compressor is provided with at least one bypass pipe, and one end of the bypass pipe is connected to the cylinder wall of an air cylinder of a rotor pump and communicates with a compression cavity of the rotor pump; the other end is communicated 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 too large 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 heat exchange system. Background Art

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

[0007] The object of the present invention is to provide a rotor compressor and a heat exchange 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, one end of which is connected to the cylinder wall of the rotary pump cylinder and communicated with the compression chamber of the rotary pump, and the other end is communicated with the suction chamber of the rotary pump or a device communicated with 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 also includes a shell, an exhaust pipe is provided on the shell, and a second valve is provided at the exhaust pipe, and 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.

[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 one cylinder, a channel for the crankshaft to pass through is arranged in the middle of the cylinder, a pressure relief channel is opened on the cylinder, one end of the pressure relief channel is connected to the compression chamber of the cylinder, and the other end of the pressure relief channel is connected to the bypass pipe.

[0012] Optionally, one end of the pressure relief channel is connected to the outer peripheral wall of the cylinder and connected to the bypass pipe, and the other end is connected to the inner wall of the channel and connected to the compression chamber.

[0013] Optionally, the pressure relief channel extends in the radial direction of the cylinder.

[0014] Optionally, one end of the pressure relief channel communicating with the compression chamber is located in an upper middle portion of the cylinder along its axial direction.

[0015] Optionally, a central angle α formed between one end of the pressure relief channel communicating with the compression chamber and the blades of the rotor pump satisfies 0≤α≤45°.

[0016] Optionally, along the circumference of the cylinder, the exhaust port of the cylinder is located between one end of the pressure relief channel connected to the compression chamber and the blades of the rotor pump, and a central angle formed between one end of the pressure relief channel connected to the compression chamber and the exhaust port of the cylinder is β, satisfying 0≤β≤30°.

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

[0018] In summary, 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 through a bypass pipe, which is conducive to quickly reducing the pressure in the compression chamber when shutting down, balancing the pressure difference between the suction chamber and the compression chamber in the rotor pump, effectively reducing the gas resistance torque, and solving the problem of slow starting speed due to excessive gas resistance torque at the moment of compressor startup, 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. In addition, the bypass pipe is directly connected to the cylinder wall of the rotor pump, which can be more directly connected to the compression chamber of the rotor pump, which is conducive to the rapid balance of the air pressure in the compression chamber. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] Figure 1 This is a schematic structural diagram of a heat exchange system according to a first embodiment of the present invention;

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

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

[0022] The reference numerals are as follows:

[0023] 10-rotor pump; 11-compression chamber; 12-intake chamber; 13-exhaust port;

[0024] 101-cylinder; 102-pressure relief channel; 103-channel; 104-blade;

[0025] 20-liquid reservoir; 21-bypass pipe;

[0026] 30- first valve;

[0027] 40 - second valve;

[0028] 50-condenser;

[0029] 60-evaporator;

[0030] 70-four-way valve;

[0031] 80-Throttling device. DETAILED DESCRIPTION

[0032] 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.

[0033] 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.

[0034] At present, rotary compressors are widely used in heat exchange systems, such as in energy storage thermal management, refrigerators, air conditioners, heat pump water heaters, dryers, and cold and dryer heat exchange systems.

[0035] 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.

[0036] When the heat exchange 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 heat exchange 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.

[0037] 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 heat exchange 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.

[0038] Therefore, based on the above technical problems, a rotor compressor and a heat exchange system are needed. By improving the rotor compressor, the pressure difference between the high-pressure side and the low-pressure side can be quickly balanced after the rotor compression is shut down, so as to shorten the restart time of the rotor compressor.

[0039] Embodiment 1:

[0040] Please refer to Figure 1 and Figure 2 As shown, a heat exchange system is provided, wherein the heat exchange system comprises a rotary compressor;

[0041] The rotary compressor includes: a rotary pump 10, a liquid reservoir 20, a first valve 30 and a second valve 40;

[0042] The heat exchange system further includes a condenser 50 , an evaporator 60 , a four-way valve 70 and a throttling element 80 .

[0043] The exhaust port 13 of the rotor pump 10 is connected to its compression chamber 11, the exhaust pipe of the compressor is externally connected to the first port of the 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 intake pipe of the liquid reservoir 20, and the flow direction and flow rate of the refrigerant are controlled by the four-way valve 70.

[0044] 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.

[0045] Please continue to refer to Figure 1 and Figure 2 As shown, the compression chamber 11 of the rotor pump 10 is communicated with the inner cavity of the liquid reservoir 20 through the bypass pipe 21, and the inner cavity of the liquid reservoir 20 is also communicated with the suction chamber 12 of the rotor pump 10;

[0046] 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.

[0047] It is conceivable that the bypass pipe 21 may also be directly connected between the compression chamber 11 and the suction chamber 12 of the rotor pump 10 .

[0048] In this embodiment, the liquid reservoir 20 is used as a device in communication with the air inlet cavity. It is conceivable that other devices in communication with the air inlet cavity may also be in communication with the bypass pipe 21. Specifically, the device in communication with the air inlet cavity may be different based on the actual heat exchange system. For example, the device in communication with the air inlet cavity may be a pipeline or other heat exchange equipment.

[0049] Please combine Figure 2 As shown, the rotor pump 10 is provided with blades 104 and a rotor (not shown in the figure), wherein 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 blades 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.

[0050] The suction side of the rotor pump of the present invention includes the suction chamber 12 of the rotor pump or the inner chamber of the liquid reservoir 20. One end of the bypass pipe 21 is connected to the cylinder wall of the rotor pump 10 and communicates with the compression chamber 11 of the rotor pump 10. The bypass pipe 21 is directly connected to the cylinder wall of the cylinder, so that it can be more directly connected to the compression chamber 11. 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 chamber 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, or 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.

[0051] 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 148s. 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 52s, and the shutdown and startup time is significantly shortened.

[0052] 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 compressor. The exhaust pipe is fixed on the outer shell of the rotary compressor and is connected to the inner cavity of the outer shell of the rotary 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.

[0053] 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.

[0054] 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 23 seconds.

[0055] Please continue to refer to Figure 1 As shown, an air inlet pipe is provided at the top position of the liquid reservoir 20. The air inlet pipe is connected to the fourth port of the four-way valve 70 as the inlet of the liquid reservoir 20. The refrigerant in the liquid reservoir 20 is usually in a gas-liquid mixed state, and the liquid refrigerant gathers at the bottom of the inner cavity of the liquid reservoir 20. The compression chamber 11 is connected to the air inlet pipe at the top of the liquid reservoir 20 through the bypass pipe 21, which is beneficial to ensure 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 beneficial to ensure 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.

[0056] The existing liquid reservoir 20 is generally provided with a gas-liquid separation device, so that the gas in the liquid reservoir 20 enters the suction chamber 12 of the rotor pump 10 through the gas outlet pipe of the liquid reservoir 20. Therefore, at this time, the bypass pipe 21 can also be connected to the gas outlet pipe at the bottom of the liquid reservoir 20, which can also ensure that the compression chamber 11 contacts the gaseous refrigerant in the inner cavity of the liquid reservoir 20 through the bypass pipe 21.

[0057] Please refer to Figure 2 and Figure 3 As shown, the rotor pump 10 includes a cylinder 101, a channel 103 for the crankshaft to pass through is arranged in the middle of the cylinder 10, and the channel 103 is also used to install the rotor (not shown in the figure), and the rotor is driven to rotate by the crankshaft. A pressure relief channel 102 is opened on the cylinder 10, one end of the pressure relief channel 102 is connected to the compression chamber of the cylinder 10, and the other end of the pressure relief channel 102 is connected to the bypass pipe 21.

[0058] In this embodiment, only one cylinder 101 is provided, so a single cylinder is formed. A rotor is adaptively provided in the cylinder, so the rotor pump 10 is a single rotor, forming a single rotor compressor. The cylinder wall of the cylinder 101 refers to the side wall of the component on which the rotor is installed. For a single rotor compressor, cylinder heads are provided at the upper and lower ends of the cylinder, and the side walls of the cylinder head do not belong to the cylinder wall of the cylinder 101. A single rotor compressor has only one cylinder, so it has only one compression chamber, so the method of directly connecting the bypass pipe 21 to the cylinder wall of the cylinder is more suitable for a single rotor compressor.

[0059] It is conceivable that the rotary compressor may also include a plurality of cylinders and additional spacers are provided between adjacent cylinders, a rotor is provided in each cylinder, and a multi-rotor compressor is formed, and each cylinder has a compression chamber and an intake chamber. The structure of the multi-rotor compressor is prior art and will not be described in detail here. In the case of a multi-rotor compressor, the bypass pipe 21 may be provided with a plurality of branches, the number of which matches the number of cylinders, and each branch is respectively connected to the cylinder wall of each cylinder and is respectively connected to the compression chamber in each cylinder. It should be noted here that the multi-rotor compressor includes a plurality of cylinders, spacers isolated between adjacent cylinders, and a cylinder head. The cylinder wall specifically refers to the side wall of the component on which the rotor is installed, and the spacers and the side walls of the cylinder head do not belong to the cylinder wall of the cylinder.

[0060] In this embodiment, a pressure relief channel 102 is provided in the cylinder 101, and the pressure relief channel 102 is arranged along the radial direction of the cylinder 101. One end of the pressure relief channel 102 is connected to the outer peripheral wall of the cylinder 101 and connected to the bypass pipe 102, and the other end is connected to the inner wall of the channel 103 and connected to the compression chamber.

[0061] In this embodiment, the pressure relief channel 102 can be processed by fine hole processing. Further, a section of the channel near the outer wall of the cylinder 101 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 pressure relief channel 102 can also be set as a cylindrical shape with equal diameter or other shapes.

[0062] It is conceivable that more pressure relief channels 102 may be provided, and each pressure relief channel 102 may be flexibly allocated and provided on the outer peripheral wall of the cylinder 101 .

[0063] It is conceivable that the pressure relief channel 102 may also be set at other angles. For example, the axial direction of the pressure relief channel 102 may be set at an angle with the radial direction of the cylinder 101 to meet usage requirements.

[0064] Please refer to Figure 2 and Figure 3As shown, in this embodiment, the pressure relief channel 102 is located at the exhaust side of the rotor pump 10, and the central angle formed between the end of the pressure relief channel 102 communicating with the compression chamber 11 and the blade 104 of the rotor pump is α, satisfying 0≤α≤45°.

[0065] Please refer to Figure 2 and Figure 3 As shown, in this embodiment, along the circumference of the cylinder, the exhaust port 13 of the cylinder is located between the end of the pressure relief channel 102 communicating with the compression chamber 11 and the blade 104 of the rotor pump, and the central angle formed between the end of the pressure relief channel 102 communicating with the compression chamber 11 and the exhaust port 13 of the cylinder 101 is β, which satisfies 0≤β≤30°. Further, the end of the pressure relief channel 102 communicating with the compression chamber 11 and the exhaust port 13 are preferably arranged at intervals, so that in the process of the compression chamber 11 being compressed and exhausted through the exhaust port 13, the influence of the pressure relief channel 102 on the airflow is reduced.

[0066] It can be imagined that in order to eliminate the influence of the pressure relief channel 102 on the exhaust, the first valve 30 can be integrated on the cylinder body 101. The first valve 30 is used to directly control the opening and closing of the pressure relief channel 102. Therefore, when the first valve 30 closes the pressure relief channel 102, the airflow will not be compressed into the pressure relief channel 102 during the exhaust process, so as to eliminate the influence of the pressure relief channel 102 on the exhaust.

[0067] By limiting the central angle between the pressure relief channel 102 and the blade 104, and limiting the pressure relief channel 102 and the exhaust port 13, it is helpful to ensure that the refrigerant in the high-pressure compression chamber is effectively depressurized when the machine is shut down.

[0068] Please continue to refer to Figure 3 As shown, the end of the pressure relief channel 102 communicating with the compression chamber 11 is located in the upper middle part of the cylinder 101 along its axial direction. Figure 1 As shown, in the actual installation of the rotary compressor, the axial direction of the cylinder 101 of the rotary pump 10 extends vertically, so the up and down direction is the axial direction of the cylinder 101. The upper middle position of the cylinder 101 along its axial direction is relatively far away from the bottom of the cylinder 101. The end of the pressure relief channel 102 connected to the compression chamber 11 is far away from the bottom of the cylinder 101, so in the compression and exhaust process, the phenomenon that the lubricating fluid in the cylinder 101 is compressed into the pressure relief channel 102 can be improved.

[0069] 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.

[0070] 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, one end of which is connected to the cylinder wall of the rotor pump's cylinder and communicated with the compression chamber of the rotor pump, and the other end is communicated with the suction chamber of the rotor pump or a device communicated with the suction chamber; a first valve is provided on the bypass pipe, 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 includes at least one cylinder, a passage for the crankshaft to pass through is arranged in the middle of the cylinder, a pressure relief passage is opened on the cylinder, one end of the pressure relief passage is connected to the compression chamber of the cylinder, and the other end of the pressure relief passage is connected to the bypass pipe.

5. The rotary compressor according to claim 4, characterized in that: One end of the pressure relief passage is communicated with the outer peripheral wall of the cylinder and connected to the bypass pipe, and the other end is communicated with the inner wall of the passage and communicated with the compression chamber.

6. The rotary compressor according to claim 4 or 5, characterized in that: The pressure relief passage extends in a radial direction of the cylinder.

7. The rotary compressor according to claim 4, characterized in that: One end of the pressure relief channel communicating with the compression chamber is located at an upper middle portion of the cylinder along the axial direction thereof.

8. The rotary compressor according to claim 4, characterized in that: A central angle α is formed between one end of the pressure relief channel communicating with the compression chamber and the blades of the rotor pump, satisfying 0≤α≤45°.

9. The rotary compressor according to claim 4 or 8, characterized in that: Along the circumference of the cylinder, the exhaust port of the cylinder is located between one end of the pressure relief channel connected to the compression chamber and the blades of the rotor pump, and the central angle formed between one end of the pressure relief channel connected to the compression chamber and the exhaust port of the cylinder is β, satisfying 0≤β≤30°.

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

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