Compressor and Refrigeration System

Abstract

The present invention discloses a compressor and a refrigeration system. The compressor includes: a housing having an accommodation chamber, a suction port, and a discharge port; a compression mechanism disposed in the accommodation chamber, the compression mechanism having a suction port and a discharge port, the suction port communicating with the suction port, and the discharge port communicating with the accommodation chamber; a driving mechanism drivingly connected to the compression mechanism; a first flow direction control member, one end of the first flow direction control member communicating with the suction port of the compression mechanism, and the other end of the first flow direction control member communicating with the accommodation chamber, the first flow direction control member being switchable between a state of connecting and disconnecting the suction port and the accommodation chamber; a second flow direction control member for controlling the unidirectional flow of air from the suction port, through the compression mechanism to the discharge port; and a wiring portion connected to the driving mechanism and the first flow direction control member respectively. According to the compressor of the present invention, the heat exchange efficiency and the annual energy efficiency are high, the starting impact is small, and the installation is convenient, the integrity is good, and the cost is low.

Description

Technical Field

[0001] The present invention relates to the technical field of compressors, and in particular, to a compressor and a refrigeration system having the compressor. Background Art

[0002] The compressor used in a constant-speed air-conditioning system operates at a constant speed. Thus, when the indoor heat load is less than the refrigerating capacity of the compressor, the compressor must start and stop continuously to maintain approximately constant indoor temperature. The frequent start and stop of the compressor reduces the refrigeration efficiency of the air-conditioning system at part load and the annual energy efficiency decreases.

[0003] Meanwhile, most existing air-conditioning systems use capillary tubes, electronic expansion valves, thermostatic expansion valves, etc. as throttling elements, and these throttling elements do not have the ability to completely shut off when the compressor stops. Therefore, when the compressor just stops running, the refrigerant on the high-pressure side will quickly flow to the low-pressure side through the throttling element, causing the high-temperature refrigerant on the high-pressure side and the low-temperature refrigerant on the low-pressure side to mix quickly, and the high and low pressures of the air-conditioning system quickly reach a completely balanced state.

[0004] However, although the complete balance of the high and low pressures is beneficial to the restart of the compressor (no starting shock will occur), it loses the refrigerating capacity or heating capacity of the air-conditioning system. For example, in the refrigeration mode, when the compressor just stops, the refrigerant in the evaporator is still in a low-temperature and low-pressure state and still has a certain evaporation refrigeration capacity. If the low-temperature and low-pressure refrigerant in the evaporator is balanced with the high-temperature and high-pressure refrigerant in the condenser at this time, it will undoubtedly lose the refrigeration capacity of this part of the refrigerant in the evaporator. The situation in the heating mode is similar, except that it is the heating capacity of the refrigerant in the evaporator that is lost at this time.

[0005] In order to make full use of the remaining cold or heat in the indoor heat exchanger (i.e., the evaporator) when the compressor stops and further improve the annual energy efficiency of the air-conditioning system, the pipeline between the indoor heat exchanger and the outdoor heat exchanger can be blocked when the compressor stops, and at the same time, the indoor-side fan is kept running. In this way, since the pipeline between the indoor heat exchanger and the outdoor heat exchanger is blocked, the refrigerant in the outdoor heat exchanger cannot immediately mix with the refrigerant in the indoor heat exchanger, and the refrigerant in the indoor heat exchanger still has the ability to supply remaining cold (in the refrigeration mode) or supply remaining heat (in the heating mode) for a period of time after the compressor stops. Thus, through the air circulation of the indoor-side fan, cooling or heating can continue to be supplied to the indoor side for a period of time.

[0006] In the air conditioning system in the related art, when the compressor stops operating, the most commonly used method to block the refrigerant between the high-pressure side and the low-pressure side is to connect a liquid line solenoid valve in series between the outdoor heat exchanger and the throttling element in the refrigeration system. For example, in the refrigeration mode, when the compressor is running, the liquid line solenoid valve remains open, and the refrigeration system continues to operate for refrigeration; when the compressor stops running, the liquid line solenoid valve closes accordingly. At this time, the refrigerant flow path is cut off, and the low-temperature refrigerant remaining in the indoor heat exchanger can continue to supply residual cold.

[0007] However, since the liquid line solenoid valve is installed on the main liquid line of the refrigerant, the flow rate through the valve port of the liquid line solenoid valve is large, which requires the valve body of the liquid line solenoid valve to be very large. And a larger liquid line solenoid valve has a higher cost, which greatly increases the cost of the entire air conditioning system. In addition, since this method completely cuts off the pipeline between the indoor and outdoor heat exchangers when the compressor stops running, the high and low pressures cannot be balanced. Therefore, when the compressor restarts, it will inevitably bring a large starting impact to the compressor. Thus, it can only be applied to compressors that are not sensitive to the starting pressure difference (such as scroll compressors with flexible scroll plates), and cannot be used for rotor compressors with a small starting torque and sensitive to the starting pressure difference. In addition, the pressure balance devices adopted by some compressors are inconvenient to install, have poor integrity and high costs. Summary of the Invention

[0008] The present invention aims to solve at least one of the technical problems existing in the prior art. For this purpose, the present invention provides a compressor, which has the advantages of high heat exchange efficiency, high annual energy efficiency, small starting impact, convenient installation, good integrity and low cost.

[0009] The present invention also provides a refrigeration system having the compressor.

[0010] The compressor according to the first aspect embodiment of the present invention includes: a housing having a receiving cavity, a suction port and a discharge port; a compression mechanism disposed in the receiving cavity, the compression mechanism having a suction port and a discharge port, the suction port communicating with the suction port, and the discharge port communicating with the receiving cavity; a driving mechanism drivingly connected to the compression mechanism; a first flow direction control member, one end of the first flow direction control member communicating with the suction port of the compression mechanism, and the other end of the first flow direction control member communicating with the receiving cavity of the compression mechanism, the first flow direction control member being switchable between a state of connecting and disconnecting the suction port and the receiving cavity; a second flow direction control member for controlling the unidirectional flow of air along the suction port, the compression mechanism to the discharge port; and a wiring portion respectively connected to the driving mechanism and the first flow direction control member.

[0011] The compressor according to an embodiment of the present invention can improve the heat exchange efficiency and annual energy efficiency of the refrigeration system, while avoiding the phenomenon of starting with pressure difference, and is easy to install, has good integrity, and low cost.

[0012] In addition, the compressor according to an embodiment of the present invention further has the following additional technical features:

[0013] According to some embodiments of the present invention, the second flow direction control member includes: a first one-way valve, an inlet of the first one-way valve is connected to the accommodation cavity and an outlet is connected to the discharge port.

[0014] According to some embodiments of the present invention, the second flow direction control member includes: a second one-way valve, an inlet of the second one-way valve is connected to the suction port and an outlet is connected to the suction opening.

[0015] Further, the one end of the first flow direction control member is connected to an outlet of the second one-way valve.

[0016] According to some embodiments of the present invention, the driving mechanism starts and stops synchronously with the first flow direction control member.

[0017] According to some embodiments of the present invention, the first flow direction control member is a normally open solenoid valve.

[0018] According to some embodiments of the present invention, when the driving mechanism drives the compression mechanism to operate, two ends of the first flow direction control member are separated, and when the driving mechanism stops, two ends of the first flow direction control member are communicated.

[0019] According to some embodiments of the present invention, when the wiring part energizes the first flow direction control member, the suction opening and the accommodation cavity are separated, and when the wiring part de-energizes the first flow direction control member, the suction opening and the accommodation cavity are communicated.

[0020] According to some embodiments of the present invention, the driving mechanism includes: a stator assembly, the stator assembly is arranged in the accommodation cavity and has a stator winding; a rotor assembly, the rotor assembly is rotatably arranged in the stator assembly; an eccentric rotating shaft, the eccentric rotating shaft is arranged in the accommodation cavity and is respectively in transmission connection with the compression mechanism and the rotor assembly.

[0021] Furthermore, the stator winding includes a main winding and a secondary winding, the terminal portion includes a first terminal, a second terminal and a third terminal, the first flow direction control member has a first terminal and a second terminal, the first terminal is electrically connected to the first terminal and one end of the main winding, the third terminal is electrically connected to one end of the secondary winding, the second terminal is electrically connected to the second terminal, the other end of the main winding and the other end of the secondary winding, and a starting capacitor is connected between the first terminal and the third terminal.

[0022] In some embodiments of the present invention, the compression mechanism includes: a cylinder having an inner cavity connected to the intake port and the exhaust port respectively; and a piston, which is sleeved on the eccentric rotating shaft and rotatable along the inner wall of the cylinder.

[0023] A refrigeration system according to an embodiment of the second aspect of the present invention comprises: a compressor according to an embodiment of the first aspect of the present invention; an indoor heat exchanger, a first end of the indoor heat exchanger being connected to the compressor; an outdoor heat exchanger, a first end of the outdoor heat exchanger being connected to the compressor; and a throttle valve, the throttle valve being connected to the second end of the indoor heat exchanger and the second end of the outdoor heat exchanger, respectively.

[0024] The refrigeration system according to the embodiment of the present invention utilizes the compressor as described above, has high heat exchange efficiency and year-round energy efficiency, can avoid the phenomenon of starting with a pressure difference, and is easy to install, has good integrity, and is low in cost.

[0025] According to some embodiments of the present invention, the refrigeration system also includes: a reversing valve, the reversing valve having a first interface, a second interface, a third interface and a fourth interface and being switchable between a heating state and a cooling state, the exhaust port being connected to the first interface and the suction port being connected to the second interface, wherein one end of the indoor heat exchanger is connected to the third interface, and one end of the outdoor heat exchanger is connected to the fourth interface.

[0026] According to some embodiments of the present invention, the throttle valve is a leak-free thermal expansion valve, wherein the throttle valve is turned on and refrigerant is throttled when the compressor is running; the throttle valve is closed when the compressor stops running to isolate the high-pressure or low-pressure refrigerant in the indoor heat exchanger and the outdoor heat exchanger, respectively, so that the refrigerant in the indoor heat exchanger and the outdoor heat exchanger cannot immediately reach a pressure equilibrium state.

[0027] Furthermore, after the compressor stops running, the fan corresponding to the indoor heat exchanger continues to run for a period of time to fully utilize the residual cold or heat of the refrigerant blocked in the indoor heat exchanger.

[0028] Additional aspects and advantages of the present invention will be given in part in the following description, become apparent in part from the following description, or be learned through the practice of the present invention. Description of the Drawings

[0029] Figure 1 is a schematic structural diagram of a refrigeration system according to an embodiment of the present invention;

[0030] Figure 2 is a schematic structural diagram of a refrigeration system according to an embodiment of the present invention;

[0031] Figure 3 is a schematic structural diagram of a refrigeration system according to an embodiment of the present invention;

[0032] Figure 4 is a schematic wiring diagram of a compressor according to an embodiment of the present invention.

[0033] Reference Numerals:

[0034] Refrigeration system 1,

[0035] Compressor 10, reversing valve 20, first interface 21, second interface 22, third interface 23, fourth interface 24, indoor heat exchanger 30, outdoor heat exchanger 40, throttle valve 50, gas-liquid separator 60, outdoor side fan 70, indoor side fan 80,

[0036] Housing 100, accommodation cavity 101, suction port 102, discharge port 103,

[0037] Cylinder 210, suction port 211, exhaust port 212, piston 220,

[0038] Stator assembly 310, stator winding 301, main winding 311, auxiliary winding 312, rotor assembly 320, eccentric rotating shaft 330,

[0039] First flow control member 410, second flow control member 420, first check valve 421, second check valve 422,

[0040] Wiring part 500, first terminal 501, second terminal 502, third terminal 503, starting capacitor 504. Detailed Description of the Embodiments

[0041] Embodiments of the present invention will be described in detail below. Examples of the embodiments are shown in the drawings, where the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the drawings are exemplary only for explaining the present invention and should not be construed as limiting the present invention.

[0042] The compressor 10 according to an embodiment of the first aspect of the present invention will be described below with reference to the accompanying drawings. For example, the compressor 10 is a rotary compressor.

[0043] As Figures 1-4 shown, the compressor 10 according to an embodiment of the present invention includes: a housing 100, a compression mechanism, a driving mechanism, a first flow direction control member 410, a second flow direction control member 420, and a wiring portion 500.

[0044] Specifically, the housing 100 has an accommodation chamber 101, a suction port 102, and a discharge port 103. The compression mechanism is disposed in the accommodation chamber 101. The compression mechanism has a suction port 211 and an exhaust port 212. The suction port 211 communicates with the suction port 102, and the exhaust port 212 communicates with the accommodation chamber 101. The driving mechanism is disposed in the accommodation chamber 101, and the driving mechanism is in transmission connection with the compression mechanism to drive the compression mechanism to operate.

[0045] One end of the first flow direction control member 410 communicates with the suction port 211 of the compression mechanism, and the other end of the first flow direction control member 410 communicates with the accommodation chamber 101. The first flow direction control member 410 is switchable between a state of connecting and disconnecting the suction port 211 and the accommodation chamber 101. The second flow direction control member 420 is configured to control the unidirectional flow of the air flow (i.e., the refrigerant) along the suction port 102, the compression mechanism to the discharge port 103. The wiring portion 500 is respectively connected to the driving mechanism and the first flow direction control member 410.

[0046] Specifically, when the compressor 10 is operating, the suction port 102 communicates with the suction port 211 and the discharge port 103 communicates with the accommodation chamber 101. At this time, the suction port 211 is disconnected from the accommodation chamber 101. The flow path of the refrigerant in the compressor 10 is: the refrigerant enters from the suction port 102, is then sucked into the compression mechanism via the suction port 211, the refrigerant is compressed in the compression mechanism and the pressure increases, and then is discharged from the exhaust port 212 of the compression mechanism; the refrigerant discharged from the compression mechanism enters the accommodation chamber 101, and finally is discharged from the discharge port 103 of the compressor 10.

[0047] When the compressor 10 stops operating, the throttle valve of the refrigeration system will cut off the high-temperature and high-pressure refrigerant and the low-temperature and low-pressure refrigerant; at the same time, the suction port 211 communicates with the upper space of the accommodation chamber 101. In this way, the pressure of the refrigerant in the accommodation chamber 101 is a low pressure equal to the pressure at the suction port 211. At this time, the remaining cold or waste heat of the refrigerant remaining in the outdoor heat exchanger and the indoor heat exchanger can be utilized to improve the energy utilization efficiency of the heat exchange system and improve the seasonal energy efficiency ratio of the heat exchange system; at the same time, since the suction port 211 communicates with the upper space of the accommodation chamber 101, the exhaust pressure and the suction pressure of the compressor 10 can be fully balanced, avoiding the phenomenon of starting with a pressure difference when the compressor 10 is restarted.

[0048] Thus, the compressor 10 according to the embodiments of the present invention can improve the heat exchange efficiency and the annual energy efficiency. At the same time, the phenomenon of starting with pressure difference can be avoided. Moreover, by arranging the first flow direction control member 410 in the accommodation cavity 101, the connection line between the first flow direction control member 410 and the wiring portion 500 can also be located in the accommodation cavity 101. In this way, compared with the balance structure installed outside the compressor, it is not only convenient for the connection between the first flow direction control member 410 and the wiring portion 500, but also has a compact structure and good integrity, and a lot of connection structures are saved, reducing the cost.

[0049] For this reason, as Figure 1 and Figure 3 shown, the second flow direction control member 420 includes: a first one-way valve 421, the inlet of the first one-way valve 421 is connected to the accommodation cavity 101 and the outlet of the first one-way valve 421 is connected to the discharge port 103. In this way, the first one-way valve 421 controls the one-way conduction of the air flow in the direction from the accommodation cavity 101 to the discharge port 103, so as to reliably cut off the air flow when the compressor 10 stops running, and has a simple structure and low cost.

[0050] Specifically, when the compression mechanism is operating, the first flow direction control member 410 is closed, the suction port 211 is disconnected from the accommodation cavity 101, and the pressure of the refrigerant discharged by the compression mechanism is relatively high. The pressure at the inlet of the first one-way valve 421 is higher than the pressure at the outlet, and the first one-way valve 421 is conducted. In this way, the refrigerant can enter the compression mechanism from the suction port 211, and after being compressed by the compression mechanism, it is discharged from the compressor 10 through the exhaust port 212 and the discharge port 103, realizing the normal operation of the compressor 10.

[0051] When the compressor 10 stops operating, the first flow direction control member 410 is conducted, the suction port 211 is communicated with the accommodation cavity 101, and the pressure of the refrigerant in the accommodation cavity 101 is reduced to be equal to the pressure at the suction port 211. At this time, the pressure at the inlet of the first one-way valve 421 is not higher than the pressure at the outlet, and the first one-way valve 421 is cut off, blocking the flow path between the indoor heat exchanger and the outdoor heat exchanger, so that the remaining cold or heat of the refrigerant remaining in the indoor heat exchanger can be fully utilized.

[0052] According to some embodiments of the present invention, as Figure 2 and Figure 3 shown, the second flow direction control member 420 includes: a second one-way valve 422, the inlet of the second one-way valve 422 is connected to the suction port 102 and the outlet of the second one-way valve 422 is connected to the suction port 211 and the one end of the first flow direction control member 410. In this way, the second one-way valve 422 controls the one-way conduction of the air flow in the direction from the suction port 102 to the suction port 211, so as to reliably cut off the air flow when the compressor 10 stops running, and has a simple structure and low cost.

[0053] Specifically, when the compression mechanism is operating, the refrigerant is sucked into the compression mechanism from the suction port 102, the second one-way valve 422, and the suction opening 211, and is compressed in the compression mechanism, resulting in an increase in pressure. Then, it is discharged from the discharge port 212 into the upper space (i.e., the accommodation chamber 101) within the housing 100, and further discharged from the discharge port 103 out of the compressor 10. When the compressor 10 stops operating, since the refrigerant within the housing 100 is still in a high-pressure state immediately after shutdown, the conduction of the first flow control member 410 causes the pressure at the outlet of the second one-way valve 422 to be greater than the pressure at the inlet, and the second one-way valve 422 is cut off, blocking the flow path between the indoor heat exchanger and the outdoor heat exchanger. Thus, the remaining cold or heat of the refrigerant retained in the indoor heat exchanger can be fully utilized.

[0054] Of course, as Figure 3 shown, a first one-way valve 421 and a second one-way valve 422 can also be provided within the accommodation chamber 101. The first one-way valve 421 controls the one-way flow of the refrigerant from the accommodation chamber 101 to the discharge port 103, and the second one-way valve 422 controls the one-way flow of the refrigerant from the suction port 102 to the suction opening 211, thereby more reliably blocking the flow path between the indoor heat exchanger and the outdoor heat exchanger when the compressor 10 stops operating.

[0055] According to some embodiments of the present invention, as Figures 1-4 shown, the drive mechanism starts and stops synchronously with the first flow control member 410. That is, when the compressor 10 is operating, the drive mechanism is energized and running, and the first flow control member 410 is energized; when the compressor 10 stops operating, the drive mechanism is de-energized and stops running, and the first flow control member 410 is de-energized, making the wiring and control more convenient.

[0056] According to some embodiments of the present invention, as Figures 1-4 shown, the first flow control member 410 is a normally open solenoid valve. That is, when the first flow control member 410 is de-energized, both ends of the first flow control member 410 are conductive, and when the first flow control member 410 is energized, both ends of the first flow control member 410 are disconnected. For example, the first flow control member 410 has a coil electrically connected to the wiring portion 500. When the wiring portion 500 energizes the coil, the first flow control member 410 switches to the cut-off state, and when the wiring portion 500 de-energizes the coil, the first flow control member 410 switches to the connected state.

[0057] According to some embodiments of the present invention, as Figures 1-4 shown, when the drive mechanism drives the compression mechanism to operate, both ends of the first flow control member 410 are separated, and when the drive mechanism stops, both ends of the first flow control member 410 are connected. In this way, when the compressor 10 is operating, the compression mechanism is operating and the suction opening 211 and the accommodation chamber 101 are disconnected; when the compressor 10 stops operating, the compression mechanism stops operating and the suction opening 211 and the accommodation chamber 101 are connected, thereby achieving the balance of high and low pressures.

[0058] According to some embodiments of the present invention, Figures 1-4 As shown, when the wiring part 500 is powered on to the first flow direction control component 410, the air inlet 211 and the accommodating chamber 101 are blocked, and when the wiring part 500 is powered off to the first flow direction control component 410, the air inlet 211 and the accommodating chamber 101 are connected, so that the first flow direction control component 410 and the driving mechanism can be started and stopped synchronously.

[0059] According to some embodiments of the present invention, Figures 1-3 As shown, the driving mechanism includes: a stator assembly 310, a rotor assembly 320 and an eccentric shaft 330. The stator assembly 310 is arranged in the accommodating chamber 101, and the stator assembly 310 has a stator winding 301. The rotor assembly 320 is rotatably arranged in the stator assembly 310. The eccentric shaft 330 is arranged in the accommodating chamber 101, and the eccentric shaft 330 is respectively connected to the compression mechanism and the rotor assembly 320. Therefore, when the connection part 500 is powered on, the compression mechanism operates; when the connection part 500 is powered off, the compression mechanism stops operating.

[0060] Furthermore, the stator winding 301 includes a main winding 311 and a secondary winding 312, the terminal portion 500 includes a first terminal 501, a second terminal 502 and a third terminal 503, the coil has a first terminal and a second terminal, the first terminal 501 is electrically connected to the first terminal and one end of the main winding 311, the third terminal 503 is electrically connected to one end of the secondary winding 312, the second terminal 502 is electrically connected to the second terminal, the other end of the main winding 311 and the other end of the secondary winding 312, and a starting capacitor 504 is connected between the first terminal 501 and the third terminal 503.

[0061] In this way, when the wiring part 500 applies alternating current between the first terminal 501 and the second terminal 502, the compressor 10 runs and the first flow direction control component 410 cuts off the air intake port 211 and the accommodating chamber 101; when the wiring part 500 disconnects the alternating current between the first terminal 501 and the second terminal 502, the compressor 10 stops running and the first flow direction control component 410 connects the air intake port 211 and the accommodating chamber 101.

[0062] In some embodiments of the present invention, Figures 1-3 As shown, the compression mechanism includes a cylinder 210 and a piston 220. The piston 220 is sleeved on the eccentric shaft 330, and the piston 220 can rotate along the inner wall of the cylinder 210. In this way, the refrigerant is compressed.

[0063] like Figures 1-4As shown in the figure, the refrigeration system 1 according to the embodiment of the second aspect of the present invention includes: the compressor 10, the reversing valve 20, the indoor heat exchanger 30, the outdoor heat exchanger 40, and the throttle valve 50 according to the embodiment of the first aspect of the present invention. For example, the refrigeration system 1 can be an air-conditioning system.

[0064] Specifically, the reversing valve 20 has a first interface 21, a second interface 22, a third interface 23, and a fourth interface 24. The discharge port 103 is connected to the first interface 21, and the suction port 102 is connected to the second interface 22; one end of the indoor heat exchanger 30 is connected to the third interface 23; one end of the outdoor heat exchanger 40 is connected to the fourth interface 24.

[0065] Among them, the reversing valve 20 is switchable between a heating state and a cooling state. When the reversing valve 20 is in the heating state, the first interface 21 is communicated with the third interface 23, and the second interface 22 is communicated with the fourth interface 24. When the reversing valve 20 is in the cooling state, the first interface 21 is communicated with the fourth interface 24, and the second interface 22 is communicated with the third interface 23.

[0066] The throttle valve 50 is respectively connected to the other ends of the indoor heat exchanger 30 and the outdoor heat exchanger 40. The throttle valve 50 can be a leak-free thermostatic expansion valve. The leak-free thermostatic expansion valve is conducted when the compressor 10 is running and the high and low pressure difference is large. The refrigerant on the high-pressure side can pass through the valve holes inside the leak-free thermostatic expansion valve. At this time, the leak-free thermostatic expansion valve plays a role in throttling the refrigerant.

[0067] The leak-free thermostatic expansion valve is cut off when the compressor 10 stops running and the high and low pressure difference is small. The refrigerant on the high-pressure side cannot pass through the valve holes inside the leak-free thermostatic expansion valve. At this time, the leak-free thermostatic expansion valve plays a blocking role, that is, the high-pressure and high-temperature refrigerant and the low-pressure and low-temperature refrigerant are respectively blocked in the outdoor heat exchanger 40 and the indoor heat exchanger 30. The refrigerant in the indoor heat exchanger and the outdoor heat exchanger cannot immediately reach the pressure and temperature equilibrium state, thereby improving the heat exchange efficiency and the annual energy efficiency. Moreover, the pressure balance component can balance the high and low pressures when the system is shut down.

[0068] According to the refrigeration system 1 of the embodiment of the present invention, by using the compressor 10 as described above, the heat exchange efficiency and the annual energy efficiency are high, the phenomenon of starting with pressure difference can be avoided, and the installation is convenient, the integrity is good, and the cost is low.

[0069] Next, the refrigeration system 1 according to the specific embodiment of the present invention will be described in detail with reference to the accompanying drawings.

[0070] In Figure 1 In the shown embodiment, the refrigeration system 1 includes a compressor 10, a reversing valve 20, an indoor heat exchanger 30, an outdoor heat exchanger 40, a throttle valve 50, a gas-liquid separator 60, an outdoor-side fan 70, and an indoor-side fan 80.

[0071] Among them, the compressor 10 is a high back-pressure compressor. That is, when the compressor 10 is in the working state, the space (i.e., the accommodation chamber 101) inside the housing 100 outside the cylinder 210 is filled with high-pressure gas. That is to say, the background pressure of the compressor 10 is in a high-pressure state. The inlet of the gas-liquid separator 60 is connected to the second interface 22, and the outlet of the gas-liquid separator 60 is connected to the suction port 102.

[0072] In this embodiment, the outlet of the first one-way valve 421 is communicated with the discharge port 103 and the inlet is communicated with the accommodation chamber 101. One end of the first flow direction control member 410 is respectively communicated with the suction port 211 and the suction port 102, and the other end of the first flow direction control member 410 is communicated with the accommodation chamber 101.

[0073] Among them, the first flow direction control member 410 is a normally open solenoid valve. When alternating current is applied between the first wiring terminal and the second wiring terminal (the first terminal 501 and the second terminal 502) of the coil, the compressor 10 operates and the first flow direction control member 410 is in a cut-off state; when the alternating current is disconnected between the first wiring terminal and the second wiring terminal, the compressor 10 stops operating and the first flow direction control member 410 is in a connected state.

[0074] The working characteristic of the compressor 10 in this embodiment is that when the pressure inside the housing 100 is higher than the pressure at the discharge port 103, the refrigerant can flow out of the housing 100 through the discharge port 103, but cannot flow back from the discharge port 103 into the housing 100; when the pressure inside the housing 100 is lower than the pressure at the discharge port 103, the refrigerant cannot flow from inside the housing 100 to the outside of the compressor 10, nor can it flow from the outside of the compressor 10 into the housing 100. That is, the refrigerant in this embodiment can only flow out of the accommodation chamber 101 unidirectionally through the discharge port 103.

[0075] As Figure 1 shown in the embodiment, it is possible to realize the normal operation of the compressor 10 and the utilization of the remaining cold (or waste heat) when the compressor 10 stops, thereby improving the seasonal energy efficiency of the air-conditioning system.

[0076] When the compressor 10 is operating normally, the first flow direction control member 410 is in a cut-off state. At this time, the flow path of the refrigerant inside the compressor 10 is: the refrigerant enters the compressor 10 from the suction port 102, is sucked into the cylinder 210 through the suction port 211, the pressure of the refrigerant increases after being compressed in the cylinder 210, and is discharged from the exhaust port 212 of the cylinder 210; then, the refrigerant discharged from the cylinder 210 reaches the upper space inside the housing 100 through the gap between the stator assembly 310 and the housing 100. Since the exhaust pressure is relatively high at this time, the first one-way valve 421 is conducted, so the refrigerant can be discharged from the compressor 10 through the first one-way valve 421 and the discharge port 103.

[0077] Specifically, when the refrigeration system 1 is in the refrigeration cycle mode (the reversing valve 20 is switched to the refrigeration state), the circulation path of the refrigerant discharged from the compressor 10 outside the compressor 10 is: discharge port 103 → first interface 21 → fourth interface 24 → outdoor heat exchanger 40 → throttle valve 50 → indoor heat exchanger 30 → third interface 23 → second interface 22 → gas-liquid separator 60 → suction port 102, thus forming a complete refrigeration cycle. In the refrigeration cycle mode, the refrigerant in the outdoor heat exchanger 40 is in a high-pressure condensation state, the refrigerant in the indoor heat exchanger 30 is in a low-pressure evaporation state, and there is a large pressure difference on both sides of the throttle valve 50. Therefore, the leak-free thermostatic expansion valve is in a conducting and normal throttling state.

[0078] When the refrigeration system 1 is in the heating cycle mode (the reversing valve 20 is switched to the heating state), the circulation path of the refrigerant outside the compressor 10 is: discharge port 103 → first interface 21 → third interface 23 → indoor heat exchanger 30 → throttle valve 50 → outdoor heat exchanger 40 → fourth interface 24 → second interface 22 → gas-liquid separator 60 → suction port 102. In the heating cycle mode, the refrigerant in the indoor heat exchanger 30 is in a high-pressure condensation state, the refrigerant in the outdoor heat exchanger 40 is in a low-pressure evaporation state, and there is a large pressure difference on both sides of the throttle valve 50. Therefore, the leak-free thermostatic expansion valve is in a conducting and normal throttling state.

[0079] As Figure 1 shown, when the compressor 10 has just stopped running, the coil of the first flow control member 410 is de-energized, the first flow control member 410 is conducting, the pressure inside the housing 100 is the low pressure equal to the pressure at the suction port 102 and the second interface 22, and the first check valve 421 is closed; at the same time, since the valve port of the leak-free thermostatic expansion valve is closed when the compressor 10 stops, the high-temperature and high-pressure refrigerant and the low-temperature and low-pressure refrigerant are separated on both sides of the leak-free thermostatic expansion valve so that they cannot mix with each other.

[0080] In this way, the remaining cold or heat of the refrigerant still remaining in the outdoor heat exchanger 40 and the indoor heat exchanger 30 after the compressor 10 stops can be fully utilized to improve the energy utilization efficiency and seasonal energy efficiency ratio of the refrigeration system 1, and the discharge pressure and suction pressure of the compressor 10 can be fully balanced to avoid the compressor 10 starting with a pressure difference.

[0081] The following is an explanation for the two cases of refrigeration and heating respectively:

[0082] When the refrigeration system 1 is in the refrigeration cycle mode and the compressor 10 has just stopped, since the compressor 10 no longer continuously compresses and does work on the refrigerant, the pressure difference between the outdoor heat exchanger 40 and the indoor heat exchanger 30 will decrease. When the pressure difference decreases to the cut-off pressure of the leak-free thermostatic expansion valve, the leak-free thermostatic expansion valve will be cut off.

[0083] Since the first flow control member 410 is turned on, the high-pressure refrigerant in the housing 100 will pass through the first flow control member 410, the gas-liquid separator 60, the second interface 22, and the third interface 23, and then release pressure to the indoor heat exchanger 30 on the low-pressure side. Finally, the pressure in the housing 100, the pressure at the suction port 211, and the pressure of the refrigerant in the indoor heat exchanger 30 tend to be equal, that is, they are all in a low-pressure state.

[0084] The low-pressure state in the housing 100 effectively reduces the exhaust resistance of the cylinder 210, avoiding phenomena such as excessive starting current, difficult starting, impact, and vibration when the compressor 10 starts again, which is beneficial to extending the service life of the compressor 10.

[0085] At the same time, since the pressure in the housing 100 is in a low-pressure state during shutdown, while the refrigerant in the outdoor heat exchanger 40 is still in a high-pressure state, the first one-way valve 421 will be closed, and the high-pressure refrigerant in the outdoor heat exchanger 40 cannot flow back into the housing 100 through the first one-way valve 421. Thus, the high-temperature refrigerant with a still relatively high temperature is blocked in the outdoor heat exchanger 40, and the refrigerant with a still relatively low temperature is blocked in the indoor heat exchanger 30. The high-temperature refrigerant and the low-temperature refrigerant cannot mix with each other, and thus the heating capacity of the high-temperature refrigerant and the heat absorption capacity of the low-temperature refrigerant are respectively retained when the compressor 10 is shut down.

[0086] At this time, if the indoor fan 80 is still running, the cold quantity in the indoor heat exchanger 30 can be taken away to continue cooling the indoor air. In this way, the remaining cold in the indoor heat exchanger 30 is fully utilized, which can effectively improve the seasonal energy efficiency ratio of the refrigeration system 1 and make the refrigeration system 1 more energy-efficient.

[0087] When the refrigeration system 1 is in the heating cycle mode and the compressor 10 has just stopped, since the compressor 10 no longer continuously compresses and does work on the refrigerant, the pressure difference between the outdoor heat exchanger 40 and the indoor heat exchanger 30 will decrease. When the pressure difference drops to the cut-off pressure of the leak-free thermostatic expansion valve, the leak-free thermostatic expansion valve will be closed. Since the first flow control member 410 is turned on, the high-pressure refrigerant in the housing 100 will pass through the first flow control member 410, the gas-liquid separator 60, the second interface 22, and the fourth interface 24, and then release pressure to the outdoor heat exchanger 40 on the low-pressure side. Finally, the pressure in the housing 100, the pressure at the suction port 211, and the pressure of the refrigerant in the outdoor heat exchanger 40 tend to be equal, that is, they are all in a low-pressure state.

[0088] The low-pressure state in the housing 100 effectively reduces the exhaust resistance of the cylinder 210, avoiding phenomena such as excessive starting current, difficult starting, impact, and vibration when the compressor 10 starts again, which is beneficial to extending the service life of the compressor 10.

[0089] Meanwhile, since the inside of the housing 100 is in a low-pressure state when the compressor stops, while the refrigerant in the indoor heat exchanger 30 is still in a high-pressure state, the high-pressure refrigerant in the indoor heat exchanger 30 cannot flow back into the housing 100 through the first check valve 421. Thus, the refrigerant with a still relatively high temperature is blocked in the indoor heat exchanger 30, and the refrigerant with a still relatively low temperature is blocked in the outdoor heat exchanger 40. The high-temperature refrigerant and the low-temperature refrigerant cannot mix with each other, and thus the heating capacity of the high-temperature refrigerant and the heat absorption capacity of the low-temperature refrigerant are respectively retained when the compressor 10 stops.

[0090] At this time, if the indoor fan 80 is still running, the heat in the indoor heat exchanger 30 can be taken away to continue heating the indoor air. In this way, the waste heat in the indoor heat exchanger 30 is fully utilized, and the heating season energy efficiency ratio of the refrigeration system 1 can be effectively improved, making the refrigeration system 1 more energy-efficient.

[0091] Figure 2 The difference between the illustrated embodiment and Figure 1 the illustrated embodiment is that Figure 2 the inlet of the second check valve 422 shown is communicated with the suction port 102, and the one end of the first flow control member 410 is respectively communicated with the outlet of the second check valve 422 and the suction port 211.

[0092] In Figure 2 the illustrated embodiment, when the compressor 10 is running, the first flow control member 410 is in a cut-off state. At this time, the flow path of the refrigerant in the compressor 10 is: the refrigerant is sucked into the cylinder 210 from the suction port 102, the second check valve 422, and the suction port 211. After being compressed in the cylinder 210, the pressure of the refrigerant increases and it is discharged from the exhaust port 212 of the cylinder 210; the refrigerant discharged from the cylinder 210 reaches the upper space inside the housing 100 through the gap between the stator assembly 310 and the housing 100, and then is discharged from the compressor 10 via the discharge port 103.

[0093] When the refrigeration system 1 is in the refrigeration cycle mode, the circulation path of the refrigerant outside the compressor 10 is: discharge port 103 → first interface 21 → fourth interface 24 → outdoor heat exchanger 40 → throttle valve 50 → indoor heat exchanger 30 → third interface 23 → second interface 22 → gas-liquid separator 60 → suction port 102, thus forming a complete refrigeration cycle. In the refrigeration cycle mode, the refrigerant in the outdoor heat exchanger 40 is in a high-pressure condensation state, the refrigerant in the indoor heat exchanger 30 is in a low-pressure evaporation state, and there is a large pressure difference on both sides of the throttle valve 50. Therefore, the non-leaking thermostatic expansion valve is in a conducting and normal throttling state.

[0094] When the refrigeration system 1 is in the heating cycle mode, the refrigerant circulation path outside the compressor 10 is: discharge port 103 → first interface 21 → third interface 23 → indoor heat exchanger 30 → throttle valve 50 → outdoor heat exchanger 40 → fourth interface 24 → second interface 22 → gas-liquid separator 60 → suction port 102. In the heating cycle mode, the refrigerant in the indoor heat exchanger 30 is in a high-pressure condensation state, the refrigerant in the outdoor heat exchanger 40 is in a low-pressure evaporation state, and there is a large pressure difference on both sides of the throttle valve 50. Therefore, the non-leakage thermostatic expansion valve is in a conducting and normal throttling state.

[0095] As Figure 2 shown, when the compressor 10 just stops running, the coil of the first flow control member 410 is de-energized and the first flow control member 410 is conducting. Since the inside of the housing 100 is at high pressure just after shutdown, the outlet of the second one-way valve 422 is at high pressure due to the conduction of the first flow control member 410, and the second one-way valve 422 is closed; at the same time, since the valve port of the non-leakage thermostatic expansion valve is closed when the compressor 10 stops, the high-temperature and high-pressure refrigerant and the low-temperature and low-pressure refrigerant are separated on both sides of the non-leakage thermostatic expansion valve so that they cannot mix with each other.

[0096] In this way, the remaining cold or heat of the refrigerant still remaining in the outdoor heat exchanger 40 and the indoor heat exchanger 30 after the compressor 10 stops can be fully utilized to improve the energy utilization efficiency and seasonal energy efficiency ratio of the refrigeration system 1, and the discharge pressure and suction pressure of the compressor 10 can be fully balanced to avoid the compressor 10 starting with a pressure difference.

[0097] The following will be described separately for the two cases of refrigeration and heating:

[0098] When the refrigeration system 1 is in the refrigeration cycle mode and the compressor 10 just stops, since the compressor 10 no longer continuously compresses and does work on the refrigerant, the pressure difference between the outdoor heat exchanger 40 and the indoor heat exchanger 30 will decrease. When the pressure difference drops to the cut-off pressure of the non-leakage thermostatic expansion valve, the non-leakage thermostatic expansion valve will cut off.

[0099] Since the first flow control member 410 is conducting, the pressure at the suction port 211 will be balanced with the pressure inside the housing 100, that is, the pressure at the suction port 211 of the cylinder 210 will be equal to the pressure at the discharge port 212, making the starting torque of the compressor 10 small and avoiding phenomena such as excessive starting current, difficult starting, impact, and vibration when the compressor 10 starts again with a pressure difference, which is beneficial to extending the life of the compressor 10.

[0100] At the same time, since the shell 100 is in a high-pressure state when shut down, while the indoor heat exchanger 30 is still in a low-pressure state, the second one-way valve 422 is in a closed state, and the low-pressure refrigerant in the indoor heat exchanger 30 cannot flow back into the shell 100 through the second one-way valve 422, thereby blocking the refrigerant with a still relatively low temperature in the indoor heat exchanger 30, and blocking the high-temperature refrigerant with a still relatively high temperature in the outdoor heat exchanger 40. The high-temperature refrigerant and the low-temperature refrigerant cannot mix with each other, thereby retaining the heating capacity of the high-temperature refrigerant and the heat absorption capacity of the low-temperature refrigerant when the compressor 10 is shut down.

[0101] At this time, if the indoor fan 80 is still running, the cold in the indoor heat exchanger 30 can be taken away to continue cooling the indoor air. This makes full use of the residual cold in the indoor heat exchanger 30, which can effectively improve the cooling season energy efficiency ratio of the refrigeration system 1 and make the refrigeration system 1 more energy-efficient.

[0102] When the refrigeration system 1 is in the heating cycle mode and the compressor 10 has just stopped, the pressure difference between the outdoor heat exchanger 40 and the indoor heat exchanger 30 will decrease because the compressor 10 no longer continues to compress the refrigerant. When the pressure difference drops to the cut-off pressure of the non-leakage thermal expansion valve, the non-leakage thermal expansion valve will be cut off. Since the first flow direction control element 410 is turned on, the pressure at the air inlet 211 will reach equilibrium with the pressure in the shell 100, that is, the pressure at the air inlet 211 of the cylinder 210 will be equal to the pressure at the exhaust port 212, which can effectively reduce the starting torque of the compressor 10 and avoid the compressor 10 starting with pressure difference, such as excessive starting current, difficulty in starting, impact, vibration, etc. when the compressor 10 is started again.

[0103] At the same time, since the shell 100 is in a high-pressure state when shut down, while the outdoor heat exchanger 40 is still in a low-pressure state, the low-pressure refrigerant in the outdoor heat exchanger 40 cannot flow back into the shell 100 through the second one-way valve 422, thereby blocking the refrigerant with a still low temperature in the outdoor heat exchanger 40, and blocking the refrigerant with a still high temperature in the indoor heat exchanger 30. The high-temperature refrigerant and the low-temperature refrigerant cannot mix with each other, and thus when the compressor 10 is shut down, the heating capacity of the high-temperature refrigerant and the heat absorption capacity of the low-temperature refrigerant are respectively retained.

[0104] At this time, if the indoor fan 80 is still running, it can take away the heat in the indoor heat exchanger 30 and continue to heat the indoor air. This makes full use of the waste heat in the indoor heat exchanger 30, which can effectively improve the energy efficiency ratio of the refrigeration system 1 in the heating season and make the refrigeration system 1 more energy-efficient.

[0105] Figure 3 The embodiment shown is in Figure 2Based on the shown embodiment, a first one-way valve 421 is added. The outlet of the first one-way valve 421 communicates with the discharge port 103 and the inlet communicates with the accommodation chamber 101. The normal operation process and the shutdown protection process of the compressor 10 in this embodiment can be referred to Figures 1-2 the embodiment of, and will not be elaborated here.

[0106] In short, for the refrigeration system 1 according to the embodiment of the present invention, by using the combined on-off state of the one-way valve and the solenoid valve, the high and low pressure differences in the indoor heat exchanger 30 and the outdoor heat exchanger 40 are maintained when the compressor 10 shuts down, so that the remaining cold or heat in the indoor heat exchanger 30 can be fully utilized after the compressor 10 shuts down; at the same time, the pressure inside the compressor 10 is quickly balanced to ensure that the compressor 10 can start smoothly when it is started again, ensuring the starting safety of the compressor 10.

[0107] In addition, since both the one-way valve and the solenoid valve are arranged in the accommodation chamber 101, the installation process can be greatly simplified, the pipeline connection is convenient, the structure is very compact, and the costs of the one-way valve and the solenoid valve are both low. Therefore, for the compressor 10 according to the embodiment of the present invention, while improving the energy efficiency of the refrigeration system 1, the assembly of the refrigeration system 1 can be facilitated, the integrity of the refrigeration system 1 can be improved, and the cost of the refrigeration system 1 can be reduced.

[0108] Other components and operations of the refrigeration system 1 according to the embodiment of the present invention are known to those of ordinary skill in the art and will not be described in detail here.

[0109] In the description of the present invention, it should be understood that the orientation or positional relationship indicated by the terms "center", "upper", "lower", "top", "bottom", "inner", "outer", "circumferential", etc. is based on the orientation or positional relationship shown in the drawings, and is only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be construed as a limitation to the present invention.

[0110] In addition, the terms "first", "second", "third", "fourth" are only used for descriptive purposes and cannot be understood as indicating or implying relative importance or implicitly specifying the quantity of the indicated technical features. Thus, the features defined with "first", "second", "third", "fourth" may explicitly or implicitly include one or more of such features. In the description of the present invention, unless otherwise stated, the meaning of "plurality" is two or more.

[0111] In the description of the present invention, it should be noted that, unless otherwise clearly defined and limited, the terms "installed", "connected", and "coupled" should be understood in a broad sense. For example, it may be a fixed connection, a detachable connection, or an integral connection; it may be a mechanical connection or an electrical connection; it may be directly connected or indirectly connected through an intermediate medium, or it may be the communication inside two components. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0112] In the description of this specification, the description with reference to the terms "one embodiment", "some embodiments", "specific embodiments", "examples" or "some examples", etc. means that the specific features, structures, materials or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic expressions of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described can be combined in a suitable manner in any one or more embodiments or examples.

[0113] Although the embodiments of the present invention have been shown and described, those of ordinary skill in the art can understand that various changes, modifications, substitutions and variations can be made to these embodiments without departing from the principles and spirit of the present invention. The scope of the present invention is defined by the claims and their equivalents.

Claims

1. A compressor, characterized in that, it comprises: a housing having a receiving cavity, a suction port and a discharge port; a compression mechanism disposed in the receiving cavity, the compression mechanism having a suction port and a discharge port, the suction port communicating with the suction port, and the discharge port communicating with the receiving cavity; a driving mechanism drivingly connected to the compression mechanism; a first flow direction control member, one end of the first flow direction control member communicating with the suction port of the compression mechanism, and the other end of the first flow direction control member communicating with the receiving cavity of the compression mechanism, the first flow direction control member being switchable between a state of connecting and disconnecting the suction port and the receiving cavity; a second flow direction control member for controlling the unidirectional flow of air from the suction port, through the compression mechanism to the discharge port; a wiring portion connected to the driving mechanism and the first flow direction control member respectively.

2. The compressor according to claim 1, characterized in that, the second flow direction control member comprises: a first check valve, an inlet of the first check valve being connected to the receiving cavity and an outlet thereof being connected to the discharge port.

3. The compressor according to claim 1 or 2, characterized in that, the second flow direction control member comprises: a second check valve, an inlet of the second check valve being connected to the suction port and an outlet thereof being connected to the suction port.

4. The compressor according to claim 3, characterized in that, the one end of the first flow direction control member is connected to the outlet of the second check valve.

5. The compressor according to claim 1, characterized in that, the driving mechanism starts and stops synchronously with the first flow direction control member.

6. The compressor according to claim 1, characterized in that, the first flow direction control member is a normally open solenoid valve.

7. The compressor according to claim 1, characterized in that, when the driving mechanism drives the compression mechanism to operate, two ends of the first flow direction control member are separated, and when the driving mechanism stops, two ends of the first flow direction control member are connected.

8. The compressor according to claim 1, characterized in that, when the wiring portion energizes the first flow direction control member, the suction port and the receiving cavity are disconnected, and when the wiring portion de-energizes the first flow direction control member, the suction port and the receiving cavity are connected.

9. The compressor according to any one of claims 1-2, 5-8, characterized in that, the driving mechanism comprises: a stator assembly disposed in the receiving cavity and having a stator winding; a rotor assembly rotatably disposed in the stator assembly; an eccentric rotating shaft disposed in the receiving cavity and drivingly connected to the compression mechanism and the rotor assembly respectively.

10. The compressor according to claim 9, characterized in that, The stator winding includes a main winding and a secondary winding, the terminal portion includes a first terminal, a second terminal and a third terminal, the first flow direction control component has a first terminal and a second terminal, the first terminal is electrically connected to the first terminal and one end of the main winding, the third terminal is electrically connected to one end of the secondary winding, the second terminal is electrically connected to the second terminal, the other end of the main winding and the other end of the secondary winding, and a starting capacitor is connected between the first terminal and the third terminal.

11. The compressor according to claim 9, It is characterized in that The compression mechanism comprises: a cylinder having an inner cavity communicating with the air intake port and the air exhaust port; A piston is sleeved on the eccentric rotating shaft and is rotatable along the inner wall of the cylinder.

12. A refrigeration system, It is characterized in that include: The compressor according to any one of claims 1 to 11; an indoor heat exchanger, wherein a first end of the indoor heat exchanger is connected to the compressor; an outdoor heat exchanger, wherein a first end of the outdoor heat exchanger is connected to the compressor; A throttle valve is connected to the second end of the indoor heat exchanger and the second end of the outdoor heat exchanger respectively.

13. The refrigeration system according to claim 12, It is characterized in that The refrigeration system further comprises: a reversing valve, the reversing valve having a first interface, a second interface, a third interface and a fourth interface and being switchable between a heating state and a cooling state, the discharge port being connected to the first interface and the suction port being connected to the second interface, Among them, one end of the indoor heat exchanger is connected to the third interface, and one end of the outdoor heat exchanger is connected to the fourth interface.

14. The refrigeration system according to claim 12, It is characterized in that The throttle valve is a leak-free thermal expansion valve. Wherein, when the compressor is running, the throttle valve is turned on and refrigerant throttling is performed; When the compressor stops running, the throttle valve is closed to isolate the high-pressure or low-pressure refrigerant in the indoor heat exchanger and the outdoor heat exchanger respectively, so that the refrigerant in the indoor heat exchanger and the outdoor heat exchanger cannot immediately reach a pressure equilibrium state.

15. The refrigeration system according to claim 14, It is characterized in that After the compressor stops running, the fan corresponding to the indoor heat exchanger continues to run for a period of time to fully utilize the residual cold or heat of the refrigerant blocked in the indoor heat exchanger.

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