A heat exchange system

Abstract

This application relates to a heat exchange system, including a compressor, a first heat exchanger, and a second heat exchanger. A second flow regulator is provided between the first and second heat exchangers. The first heat exchanger includes a first heat exchange section and a second heat exchange section. A first direction is defined parallel to the height direction of the second heat exchange section. At least a portion of the second heat exchange section is located below the first heat exchange section in the first direction. The heat exchange system includes a bypass branch and has a defrosting mode. In the defrosting mode, one end of the bypass branch is connected to the first outlet of the compressor, and the other end of the bypass branch is connected to one end of the second heat exchange section. The heat exchange system provided by this application enables the high-temperature and high-pressure refrigerant discharged from the first outlet of the compressor to directly enter the second heat exchange channel of the second heat exchange section. When this portion of refrigerant (high-temperature and high-pressure gaseous refrigerant) exchanges heat in the second heat exchange section, it can melt the frost on the surface of the second heat exchange section, thereby improving the heat exchange efficiency of the first heat exchanger.

Description

[0001] This application claims priority to Chinese Patent Application No. 202520343135.1, filed with the State Intellectual Property Office of China on February 28, 2025, entitled "A Heat Exchange System", the entire contents of which are incorporated herein by reference. Technical Field

[0002] This utility model relates to the field of heat exchange technology, and in particular to a heat exchange system used in heat pump air conditioners. Background Technology

[0003] In related technologies, heat exchangers are widely used in heat exchange systems, which include indoor and outdoor heat exchangers. When the heat exchange system operates in heating mode, the outdoor heat exchanger acts as an evaporator in a low-temperature environment. When the surface temperature of the heat exchange tubes is below zero degrees Celsius, water vapor in the air will condense into frost on the surface of the heat exchanger, especially in the area near the bottom of the heat exchanger where the frost layer is thicker, thus affecting the heat exchange performance of the heat exchanger. Therefore, how to balance the heat exchange performance and defrosting performance of the heat exchanger is a problem that technicians need to solve. Utility Model Content

[0004] The purpose of this application is to provide a heat exchange system that can balance the heat exchange performance and defrosting performance of a heat exchanger.

[0005] Therefore, this application proposes a heat exchange system including a compressor, a first heat exchanger, a second heat exchanger, and a flow regulator. The flow regulator is provided between the first heat exchanger and the second heat exchanger. The first heat exchanger includes a first heat exchange section and a second heat exchange section. The first heat exchange section includes a plurality of first heat exchange tubes, and the second heat exchange section includes a plurality of second heat exchange tubes. A first direction is defined as a direction parallel to the thickness direction of either the first or second heat exchange tubes. At least a portion of the second heat exchange section is located below the first heat exchange section in the first direction. The heat exchange system includes a bypass branch and has a defrost mode. In the defrost mode, one end of the bypass branch is connected to a first outlet of the compressor, and the other end of the bypass branch is connected to one end of the second heat exchange section.

[0006] In this application, when the heat exchange system is running in defrost mode, since the first outlet of the compressor is connected to one end of the second heat exchange section, a portion of the high-temperature and high-pressure refrigerant discharged from the compressor can directly enter the second heat exchange section. The heat generated by this portion of refrigerant (high-temperature and high-pressure gaseous refrigerant) can melt the frost on the surface of the second heat exchange section, thereby reducing frost accumulation on the surface of the second heat exchange section, improving the defrosting performance of the heat exchanger, and achieving a balance between the heat exchange performance and defrosting performance of the heat exchanger.

[0007] It should be understood that the above general description and the following detailed description are merely exemplary and do not limit this application. Attached Figure Description

[0008] Figure 1 for Figure 1 This is a connection diagram of the heat exchange system provided in this application in a specific embodiment;

[0009] Figure 2 for Figure 1 A magnified view of part I in the middle;

[0010] Figure 3 This is a connection diagram of the heat exchange system provided in this application in another specific embodiment;

[0011] Figure 4 for Figure 3 A magnified view of a section II;

[0012] Figure 5 This is a connection diagram of the heat exchange system provided in this application in yet another specific embodiment;

[0013] Figure 6 for Figure 5 A magnified view of a portion of IV;

[0014] Figure 7 A schematic diagram of the connection of the first heat exchanger of the heat exchange system provided in this application in a specific embodiment;

[0015] Figure 8 for Figure 7 A cross-sectional view along line AA in one specific embodiment;

[0016] Figure 9 for Figure 8 A magnified view of the middle V section;

[0017] Figure 10 for Figure 8 A partial enlarged view of part VI in one specific embodiment;

[0018] Figure 11 for Figure 8 A partial enlarged view of part VI in another specific embodiment;

[0019] Figure 12 for Figure 8 A partial enlarged view of part IV in yet another specific embodiment;

[0020] Figure 13 for Figure 7 A cross-sectional view along line AA in another specific embodiment;

[0021] Figure 14for Figure 7 A sectional view along line AA in yet another specific embodiment;

[0022] Figure 15 for Figure 7 A sectional view along line AA in yet another specific embodiment;

[0023] Figure 16 for Figure 15 A cross-sectional view of the second heat exchange tube in one specific embodiment;

[0024] Figure 17 for Figure 15 A cross-sectional view of the second heat exchange tube in another specific embodiment;

[0025] Figure 18 for Figure 15 A cross-sectional view of the second heat exchange tube in yet another specific embodiment.

[0026] Explanation of reference numerals in the attached figures:

[0027] 1-Heat exchange system;

[0028] 11-First heat exchanger;

[0029] 12-Second heat exchanger; 121-Third port; 122-Fourth port;

[0030] 131 - First flow regulator; 1311 - Seventh interface; 1312 - Eighth interface;

[0031] 132 - Second flow regulator; 1321 - One interface of the second flow regulator; 1322 - Another interface of the second flow regulator;

[0032] 14-Compressor; 141-First outlet; 142-First inlet;

[0033] 15 - Reversing valve; 151 - First valve port; 152 - Second valve port; 153 - Third valve port; 154 - Fourth valve port;

[0034] 161 - First valve; 1611 - One port of the first valve; 1612 - Another port of the first valve;

[0035] 162 - Second valve; 1621 - Another port of the second valve; 1622 - One port of the second valve;

[0036] 163 - Third valve; 1631 - One port of the third valve; 1632 - Another port of the third valve;

[0037] 164 - Third flow regulator; 1641 - Thirteenth interface; 1642 - Fourteenth interface;

[0038] 165 - Fourth flow regulator; 1651 - Ninth interface; 1652 - Tenth interface;

[0039] 21-First manifold; 211-First cavity; 212-Third cavity;

[0040] 22-Second manifold; 221-Second cavity; 222-Fourth cavity;

[0041] 31-First heat exchange tube; 311-First heat exchange channel; 312-First wall; 313-Second wall;

[0042] 32-Second heat exchange tube; 321-Second heat exchange channel; 322-Separating rib; 323-Third wall; 324-Fourth wall;

[0043] 41-First heat exchange section; 411-First connecting port; 412-Second connecting port;

[0044] 42-Second heat exchange section; 421-Third connecting port; 422-Fourth connecting port;

[0045] 5-Fin; 51-First mounting part; 52-Second mounting part;

[0046] 6-Bypass route;

[0047] 7-First flow path.

[0048] The accompanying drawings, which are incorporated in and form part of this specification, illustrate embodiments consistent with this application and, together with the description, serve to explain the principles of this application. Detailed Implementation

[0049] To better understand the technical solution of this application, the embodiments of this application will be described in detail below with reference to the accompanying drawings.

[0050] The terminology used in the embodiments of this application is for the purpose of describing particular embodiments only and is not intended to be limiting of this application. The singular forms “a,” “the,” and “the” used in the embodiments of this application and the appended claims are also intended to include the plural forms unless the context clearly indicates otherwise.

[0051] When the air conditioning system is in cooling mode, the outdoor unit acts as the condenser, and the indoor unit acts as the evaporator. The working process in cooling mode mainly includes: the compressor compresses and pressurizes the low-temperature, low-pressure gas from the evaporator into a high-temperature, high-pressure refrigerant (consuming electrical energy during compression). The high-temperature, high-pressure refrigerant from the compressor enters the condenser, where it releases heat and liquefies into a medium-temperature, high-pressure refrigerant (releasing heat to the outside during liquefaction). The medium-temperature, high-pressure refrigerant from the condenser enters the throttling device, where it is throttled and depressurized into a low-temperature, low-pressure refrigerant. The low-temperature, low-pressure refrigerant from the throttling device enters the evaporator, where it absorbs heat and vaporizes into a low-temperature, low-pressure gas. During the heat absorption process, it absorbs heat from the room, thus cooling the room. The low-temperature, low-pressure gas in the evaporator then re-enters the compressor to begin the next cooling cycle.

[0052] When the air conditioning system switches from cooling mode to heating mode, the reversing valve switches the direction of refrigerant flow within the system, causing the outdoor unit to act as an evaporator and the indoor unit as a condenser. The heating mode operation mainly includes: the compressor compresses and pressurizes the low-temperature, low-pressure gas from the evaporator into a high-temperature, high-pressure refrigerant (consuming electrical energy during compression). The high-temperature, high-pressure refrigerant from the compressor enters the condenser, where it releases heat and liquefies into a medium-temperature, high-pressure refrigerant. During liquefaction, it releases heat to the room where the condenser is located, thus heating the room. The medium-temperature, high-pressure refrigerant from the condenser enters the throttling device, where it is throttled and depressurized into a low-temperature, low-pressure refrigerant. This low-temperature, low-pressure refrigerant from the throttling device enters the evaporator, where it absorbs heat and vaporizes into a low-temperature, low-pressure gas (absorbing heat from the outdoor environment where the evaporator is located during the heat absorption process). The low-temperature, low-pressure gas in the evaporator then re-enters the compressor to begin the next heating cycle.

[0053] Taking the outdoor heat exchanger of this heat exchange system as an example, it functions as a condenser during the cooling process and as an evaporator during the heating process. When the outdoor heat exchanger is used as an evaporator, the refrigerant temperature inside the heat exchanger may be below zero due to the low outdoor ambient temperature. This results in a low surface temperature for the heat exchanger, posing a risk of water vapor in the outside air condensing and frosting on the surface. Frosting can clog the air ducts of the heat exchanger, leading to a decrease in its performance.

[0054] Normally, heat exchange systems are set to a defrost mode to defrost the heat exchanger used as an evaporator. In this application, the refrigerant flow path in defrost mode is roughly the same as the refrigerant flow path in refrigeration mode, and will not be repeated here.

[0055] This application provides a heat exchange system, such as... Figure 1 and Figure 2 As shown, Figure 1 This is a schematic diagram of the heat exchange system provided in this application in a specific embodiment. Figure 2for Figure 1 A partial enlarged view of part I. The heat exchange system 1 includes a compressor 14, a first heat exchanger 11, a reversing valve 15, a second flow regulator 132, and a second heat exchanger 12. The first heat exchanger 11 includes a first heat exchange section 41 and a second heat exchange section 42. A first direction is defined as a direction parallel to the height direction of the second heat exchange section 42. At least a portion of the second heat exchange section 42 is located below the first heat exchange section 41 in the first direction. The first heat exchange section 41 includes a first heat exchange tube 31, and the second heat exchange section 42 includes a second heat exchange tube 32. The first heat exchange tube 31 has a first heat exchange channel 311, which extends along the length of the first heat exchange tube 31 and penetrates both end faces of the first heat exchange tube 31. It is understood that one end of the first heat exchange section 41 is provided with a second connecting port 412, and the other end of the first heat exchange section 41 is provided with a first connecting port 411. Both the first connecting port 411 and the second connecting port 412 are connected to the first heat exchange channel 311 of the first heat exchange tube 31. The second heat exchange tube 32 has a second heat exchange channel 321, which extends along the length of the second heat exchange tube 32 and penetrates both end faces of the second heat exchange tube 32.

[0056] In some embodiments, one end of the second heat exchange section 42 is provided with a fourth communication port 422, and the other end of the second heat exchange section is provided with a third communication port 421. Both the third communication port 421 and the fourth communication port 422 are connected to the second heat exchange channel 321 of the second heat exchange tube 32.

[0057] The reversing valve 15 includes a first valve port 151, a second valve port 152, a third valve port 153, and a fourth valve port 154. The compressor 14 includes a first outlet 141 and a first inlet 142. The second flow regulator 132 includes one interface 1321 and another interface 1322. The second heat exchanger 12 includes a third interface 121 and a fourth interface 122. In the first heat exchanger 11, the first heat exchange section 41 has a first connecting port 411 and a second connecting port 412 communicating with the first heat exchange channel 311, and the second heat exchange section 42 has a third connecting port 421 and a fourth connecting port 422 communicating with the second heat exchange channel 321.

[0058] like Figure 1As shown, the fourth connection port 422 is connected to one interface 1321 of the second flow regulator, so that the second heat exchange channel 321 of the second heat exchange section 42 is connected to one interface 1321 of the second flow regulator, and the first heat exchange channel 311 of the first heat exchange section 41 is connected to one interface 1321 of the second flow regulator. The other interface 1322 of the second flow regulator is connected to the third interface 121, the fourth interface 122 is connected to the third valve port 153, the third valve port 153 is connected to the fourth valve port 154, the fourth valve port 154 is connected to the first inlet 142, the first outlet 141 is connected to the first valve port 151, the first valve port 151 is connected to the second valve port 152, the second valve port 152 is connected to the second connection port 412, so that the second valve port 152 is connected to the first heat exchange channel 311 of the first heat exchange section 41, and the second valve port 152 is also connected to the fourth connection port 422, so that the second valve port 152 is connected to the second heat exchange channel 321 of the second heat exchange section 42.

[0059] Figure 1 The heat exchange system 1 shown has a defrost mode. In defrost mode, the first heat exchanger 11 acts as a condenser, and the second heat exchanger 12 acts as an evaporator. In defrost mode (refrigerant flow direction as shown...), the heat exchange system 1... Figure 1 and Figure 2During operation (as indicated by the dashed arrow), the high-temperature, high-pressure gaseous refrigerant discharged from the first outlet 141 of the compressor 14 enters the first valve port 151 of the reversing valve 15 and exits from the second valve port 152, which is connected to the first valve port 151. After exiting from the second valve port 152, the high-temperature, high-pressure gaseous refrigerant is divided into a first part of refrigerant and a second part of refrigerant. The first part of the high-temperature, high-pressure refrigerant enters the heat exchange channel of the first heat exchanger 11 through the second connecting port 412. After heat exchange in the first heat exchanger 11, the high-temperature, high-pressure gaseous refrigerant becomes a medium-temperature, high-pressure liquid refrigerant, which is then discharged from the first heat exchanger 11 through the third connecting port 421. The high-temperature, high-pressure gaseous refrigerant, while exchanging heat in the first heat exchanger 11, can melt the frost on the surface of the first heat exchanger 11. The first portion of refrigerant (medium-temperature, high-pressure liquid refrigerant) enters the second flow regulator 132 through one port 1321. After throttling within the second flow regulator 132, the first portion of refrigerant (low-temperature, low-pressure liquid refrigerant) exits the second flow regulator 132 through another port 1322. The first portion of refrigerant (low-temperature, low-pressure liquid refrigerant) enters the second heat exchanger 12 through the third port 121. Within the second heat exchanger 12, the first portion of refrigerant (low-temperature, low-pressure liquid refrigerant) absorbs heat from the air and transforms into low-temperature, low-pressure gaseous refrigerant. The first portion of refrigerant (low-temperature, low-pressure gaseous refrigerant) discharged from the fourth port 122 enters the reversing valve 15 through the third valve port 153. The first portion of refrigerant (low-temperature, low-pressure gaseous refrigerant) exits the reversing valve 15 through the fourth valve port 154, which is connected to the third valve port 153, and enters the compressor 14 through the first inlet 142, completing one cycle.

[0060] Meanwhile, the second portion of refrigerant (high-temperature and high-pressure gaseous refrigerant) discharged from the second valve port 152 of the reversing valve 15 enters the second heat exchange channel 321 of the second heat exchange section 42 through the fourth connecting port 422. After heat exchange in the second heat exchange channel 321, the high-temperature and high-pressure gaseous refrigerant becomes a medium-temperature and high-pressure liquid refrigerant. That is, the second portion of medium-temperature and high-pressure refrigerant is discharged from the first heat exchanger 11 through the third connecting port 421. The second portion of refrigerant (medium-temperature, high-pressure liquid refrigerant) enters the second flow regulator 132 through one port 1321. After throttling within the second flow regulator 132, the second portion of refrigerant (low-temperature, low-pressure liquid refrigerant) exits the second flow regulator 132 through another port 1322. The second portion of refrigerant (low-temperature, low-pressure liquid refrigerant) enters the second heat exchanger 12 through the third port 121. Within the second heat exchanger 12, the second portion of refrigerant (low-temperature, low-pressure liquid refrigerant) absorbs heat from the air and transforms into low-temperature, low-pressure gaseous refrigerant. The second portion of refrigerant (low-temperature, low-pressure gaseous refrigerant) discharged from the fourth port 122 enters the reversing valve 15 through the third valve port 153. The second portion of refrigerant (low-temperature, low-pressure gaseous refrigerant) exits the reversing valve 15 through the fourth valve port 154 and enters the compressor 14 through the first inlet 142, completing one cycle.

[0061] In this embodiment, when the heat exchange system 1 is running in defrost mode, the first outlet 141 of the compressor 14 is connected to the fourth communication port 422 of the second heat exchange section 42 via the first valve port 151 and the second valve port 152 of the reversing valve 15. This allows the high-temperature and high-pressure refrigerant discharged from the first outlet 141 of the compressor 14 to directly enter the second heat exchange channel 321 of the second heat exchange section 42. When the second part of the refrigerant (high-temperature and high-pressure gaseous refrigerant) exchanges heat in the second heat exchange section 42 of the first heat exchanger 11, it can melt the frost on the surface of the second heat exchange section 42. Since the second part of the refrigerant is the refrigerant discharged from the first outlet 141 of the compressor 14, its temperature is high, which can quickly melt the frost on the surface of the second heat exchange section 42 and reduce the risk of frost accumulation on the surface of the second heat exchange section 42 of the first heat exchanger 11 affecting the heat exchange efficiency of the second heat exchange section 42.

[0062] In one specific embodiment, such as Figure 1 and Figure 2 As shown, when the heat exchange system 1 is operating in defrost mode, a first portion of the refrigerant enters the first heat exchange channel 311 of the first heat exchange section 41 through the second connection port 412, exits the first heat exchange section 41 through the first connection port 411, enters the second heat exchange channel 321 of the second heat exchange section 42 through the fourth connection port 422, and exits the second heat exchange section 42 through the third connection port 421. In other words, the first portion of the refrigerant circulates within the first heat exchanger 11, allowing it to remain within the first heat exchanger 11 for a longer period, thus improving defrost efficiency.

[0063] It should be noted that when the first portion of refrigerant circulates within the first heat exchanger 11, that is, when the first portion of refrigerant enters the first heat exchange channel 311 of the first heat exchange section 41 from the second connection port 412, exits the first heat exchange section 41 from the first connection port 411, enters the second heat exchange channel 321 of the second heat exchange section 42 from the fourth connection port 422, and exits the second heat exchange section 42 from the third connection port 421, that is, after the first portion of refrigerant is discharged from the first outlet 141 of the compressor 14, it needs to enter the first heat exchange section 41 first and then the second heat exchange section 42. However, after the second portion of refrigerant is discharged from the first outlet 141 of the compressor 14, it can directly enter the second heat exchange section 42, so that the temperature of the second portion of refrigerant entering the second heat exchange section 42 is higher than the temperature of the first portion of refrigerant. Therefore, due to the presence of this second portion of refrigerant, the defrosting efficiency of the second heat exchange section 42 can be improved.

[0064] In one specific embodiment, such as Figure 2 As shown, the heat exchange system 1 has a bypass branch 6 (such as...) Figure 2 (As shown by the solid red line in the diagram), in defrost mode, one end of the bypass branch 6 of the heat exchange system 1 is connected to the first outlet of the compressor 14, and the other end of the bypass branch 6 is connected to one end of the second heat exchange section 42.

[0065] In some specific embodiments, the bypass branch 6 is provided with a first valve 161, and the heat exchange system 1 includes at least a heating mode and a defrosting mode. In the heating mode, the first valve 161 can disconnect the second heat exchange section 42 from the compressor 14. In the defrosting mode, the first valve 161 can open the bypass branch 6.

[0066] like Figure 1 and Figure 2 As shown, when the heat exchange system 1 is running in heating mode, the first heat exchanger 11 is used as an evaporator and the second heat exchanger 12 is used as a condenser. When the heat exchange system 1 switches from defrosting mode to heating mode or from heating mode to defrosting mode, the reversing valve 15 switches the refrigerant flow direction by changing the connection relationship of each interface.

[0067] Specifically, when heat exchange system 1 is in heating mode (refrigerant flow direction as follows) Figure 1 and Figure 2When operating under the conditions indicated by the solid arrows in the diagram, the high-temperature and high-pressure refrigerant enters the reversing valve 15 from the first outlet 141 of the compressor 14 via the first valve port 151, and exits the reversing valve 15 from the third valve port 153 connected to the first valve port 151. The high-temperature and high-pressure refrigerant then enters the second heat exchanger 12 via the fourth port 122. After heat exchange in the second heat exchanger 12, the high-temperature and high-pressure gaseous refrigerant becomes a medium-temperature and high-pressure liquid refrigerant. The medium-temperature and high-pressure liquid refrigerant exits the second heat exchanger 12 via the third port 121 and enters the second flow regulator 132 via another port 1322. After being throttled in the first flow regulator 131, the medium-temperature and high-pressure liquid refrigerant becomes a low-temperature and low-pressure liquid refrigerant and exits the first flow regulator 131 via one port 1321 of the second flow regulator. The low-temperature, low-pressure liquid refrigerant leaving the first flow regulator 131 enters the second heat exchange section 42 of the first heat exchanger 11 through the third connection port 421. After heat exchange in the second heat exchange channel 321 of the second heat exchange section 42, it leaves the second heat exchange section 42 through the fourth connection port 422 and enters the first heat exchange section 41 of the first heat exchanger 11 through the first connection port 411. After heat exchange in the first heat exchange channel 311 of the first heat exchange section 41, it leaves the first heat exchange section 41 through the second connection port 412. At this time, the low-temperature, low-pressure liquid refrigerant becomes a low-temperature, low-pressure gaseous refrigerant. The low-temperature, low-pressure gaseous refrigerant enters the reversing valve 15 through the second valve port 152 and leaves the reversing valve 15 through the fourth valve port 154 connected to the second valve port 152. The low-temperature, low-pressure gaseous refrigerant returns to the compressor 14 through the first inlet 142, completing one heating cycle. Figure 1 and Figure 2 It can be seen that the refrigerant flows in opposite directions when the heat exchange system 1 is running in heating mode and defrosting mode.

[0068] Therefore, when the heat exchange system 1 is operating in heating mode, the bypass branch 6 is disconnected, thereby preventing the low-temperature, low-pressure gaseous refrigerant leaving the first heat exchange section 41 from re-entering the second heat exchange section 42 via the bypass branch 6. This ensures that the low-temperature, low-pressure gaseous refrigerant leaving the first heat exchange section 41 from the second connection port 412 can return to the first inlet 142 of the compressor 14 via the reversing valve 15, ensuring that the heating mode of the heat exchange system 1 can operate normally. Specifically, when the heat exchange system 1 is operating in heating mode, the bypass branch 6 can be disconnected via the first valve 161.

[0069] When the heat exchange system 1 is operating in defrost mode, the bypass branch 6 is open, allowing the second portion of refrigerant (a part of the high-temperature, high-pressure gaseous refrigerant) discharged from the first outlet 141 of the compressor 14 to be diverted by the reversing valve 15 and directly enter the second heat exchange channel 321 of the second heat exchange section 42 via the bypass branch 6. This second portion of refrigerant then rapidly melts the frost on the surface of the second heat exchange section 42. When the heat exchange system 1 is operating in defrost mode, the bypass branch 6 can be opened via the first valve 161.

[0070] Specifically, such as Figure 1 and Figure 2 As shown, the first valve 161 includes one port 1611 and the other port 1612. When the heat exchange system 1 is operating in heating mode, the first port 1611 and the other port 1612 of the first valve are not connected, thereby disconnecting the bypass branch 6. When the heat exchange system 1 is operating in defrost mode, the first port 1611 and the other port 1612 of the first valve are connected, thereby opening the bypass branch 6. At this time, the first port 1611 of the first valve is connected to the second valve port 152 of the reversing valve 15, and the other port 1612 of the first valve is connected to the fourth connecting port 422 of the second heat exchange section 42.

[0071] In this embodiment, the first flow regulator 131 is used to throttle the refrigerant when the heat exchange system 1 is running in heating mode, and the second flow regulator 132 is used to throttle the refrigerant when the heat exchange system 1 is running in cooling mode and defrost mode.

[0072] The first flow regulator 131 and the second flow regulator 132 are electronic expansion valves or thermal expansion valves.

[0073] In one specific embodiment, please continue to refer to Figure 3 and Figure 4 , Figure 3 This is a schematic diagram of the heat exchange system provided in this application in another specific embodiment. Figure 4 for Figure 3 A magnified view of a section II. (See attached image.) Figure 3 and Figure 4As shown, the heat exchange system 1 may further include a second valve 162, which includes another port 1621 and a second port 1622. In one specific embodiment, when the heat exchange system 1 is operating in heating mode, one port 1622 of the second valve is connected to the first communication port 411 of the first heat exchange section 41, and the other port 1621 of the second valve is connected to the fourth communication port 422 of the second heat exchange section 42. Therefore, when the heat exchange system 1 is operating in heating mode, the first heat exchange section 41 and the second heat exchange section 42 of the first heat exchanger 11 are connected through the second valve 162, allowing the refrigerant in the first heat exchange channel 311 of the first heat exchange section 41 to enter the second heat exchange channel 321 of the second heat exchange section 42, causing the refrigerant to circulate within the first heat exchanger 11 and improving the heat exchange efficiency of the first heat exchanger 11.

[0074] In one specific embodiment, when the heat exchange system 1 is operating in defrost mode, the second valve 162 is disconnected, meaning that the other port 1621 of the second valve is not connected to one port 1622 of the second valve, thus preventing the first heat exchange section 41 of the first heat exchanger 11 from communicating with the second heat exchange section 42. The refrigerant in the first heat exchange channel 311 of the first heat exchange section 41 cannot enter the second heat exchange channel 321 of the second heat exchange section 42 via the second valve 162. However, when the heat exchange system 1 is operating in defrost mode, the high-temperature, high-pressure gaseous refrigerant discharged from the first outlet 141 of the compressor 14 can enter the second heat exchange channel 321 of the second heat exchange section 42 via the bypass branch 6.

[0075] Alternatively, when the heat exchange system 1 is operating in defrost mode, at least one of the first heat exchange section 41 and the second heat exchange section 42 of the first heat exchanger 11 is disconnected from the interface of the second valve 162. That is, when the heat exchange system 1 is operating in defrost mode, the other interface 1621 of the second valve is disconnected from the fourth communication port 422 of the second heat exchange section 42, and / or, one interface 1622 of the second valve is disconnected from the first communication port 411 of the first heat exchange section 41, so that the refrigerant discharged from the first communication port 411 of the first heat exchange section 41 when the heat exchange system 1 is operating in defrost mode cannot enter the second heat exchange channel 321 of the second heat exchange section 42. However, when the heat exchange system 1 is operating in defrost mode, the high-temperature and high-pressure gaseous refrigerant discharged from the first outlet 141 of the compressor 14 can enter the second heat exchange channel 321 of the second heat exchange section 42 via the bypass branch 6.

[0076] Therefore, with Figure 1 and Figure 2 The difference between the embodiments shown is that, Figure 3 and Figure 4In the illustrated embodiment, when the heat exchange system 1 is operating in defrost mode, the first portion of refrigerant discharged from the first heat exchange section 41 does not enter the second heat exchange section 42, while the second portion of refrigerant discharged from the first outlet 141 of the compressor 14 enters the second heat exchange section 42 via the bypass branch 6. That is, when the heat exchange system 1 is operating in defrost mode, the first and second portions of refrigerant do not converge within the first heat exchanger 11, and the first portion of refrigerant does not participate in defrosting the second heat exchange section 42. Defrosting of the second heat exchange section 42 is achieved solely through the second portion of refrigerant. Furthermore, since the second portion of refrigerant is a high-temperature, high-pressure gaseous refrigerant, it can quickly melt the frost on the surface of the second heat exchange section 42.

[0077] In such Figure 3 and Figure 4 In the illustrated embodiment, the heat exchange system 1 may further include a first flow path 7 (such as...). Figure 3 and Figure 4 (As shown by the blue line in the middle), the first flow path 7 is activated when the heat exchange system 1 is running in defrost mode. When the heat exchange system 1 is running in defrost mode, the first flow path 7 connects the first connection port 411 of the first heat exchange section 41 and an interface 1321 of the second flow regulator, so that the first portion of refrigerant discharged from the first connection port 411 of the first heat exchange section 41 enters the interface 1321 of the second flow regulator through the first flow path 7.

[0078] Specifically, such as Figure 3 and Figure 4 As shown, the first flow path 7 is provided with a third valve 163. In one embodiment, in defrost mode, the third valve 163 can open the first flow path 7. In another embodiment, in heating mode, the third valve 163 can close the first flow path 7. In yet another embodiment, in defrost mode, the third valve 163 can open the first flow path 7, and in heating mode, the third valve 163 can close the first flow path 7.

[0079] like Figure 3 and Figure 4As shown, the third valve 163 has one port 1631 and another port 1632. When the heat exchange system 1 is running in defrost mode, one port 1631 and the other port 1632 of the third valve are connected. One port 1631 is connected to the first connection port 411 of the first heat exchange section 41, and the other port 1632 is connected to one port 1321 of the second flow regulator of the second flow regulator 132. This allows the first portion of refrigerant discharged from the first heat exchange channel 311 of the first heat exchange section 41 to enter the second flow regulator 132 through the first flow path 7. Simultaneously, during this process, the second portion of refrigerant discharged from the first outlet 141 of the compressor 14 undergoes heat exchange in the second heat exchange channel 321 of the second heat exchange section 42 and then enters the second flow regulator 132 through the third connection port 421 of the second heat exchange section 42, causing the first portion of refrigerant and the second portion of refrigerant to merge in the second flow regulator 132.

[0080] In one specific embodiment, when the heat exchange system 1 is running in heating mode, one port 1631 of the third valve is disconnected from the other port 1632 of the third valve, thereby preventing the refrigerant discharged from the second flow regulator 132 from directly entering the first heat exchange section 41 without passing through the second heat exchange section 42, so that the second heat exchange section 42 can participate in heat exchange and improve the heat exchange efficiency of the first heat exchanger 11.

[0081] Alternatively, when the heat exchange system 1 is operating in heating mode, at least one of the first heat exchange channel 311 of the first heat exchange section 41 and the second flow regulator 132 is disconnected from the third valve 163. In one specific embodiment, when the heat exchange system 1 is operating in heating mode, the first heat exchange channel 311 of the first heat exchange section 41 is disconnected from the third valve 163. In another specific embodiment, when the heat exchange system 1 is operating in heating mode, the second flow regulator 132 is disconnected from the third valve 163. In yet another specific embodiment, when the heat exchange system 1 is operating in heating mode, both the first heat exchange channel 311 of the first heat exchange section 41 and the second flow regulator 132 are disconnected from the third valve 163. In the above embodiments, when the heat exchange system 1 is operating in heating mode, the disconnected first flow path 7 can prevent the refrigerant discharged from the second flow regulator 132 from directly entering the first heat exchange section 41 without passing through the second heat exchange section 42, allowing the second heat exchange section 42 to participate in heat exchange and improving the heat exchange efficiency of the first heat exchanger 11.

[0082] In one specific embodiment, please continue to refer to Figure 5 and Figure 6 ,in, Figure 5 This is a schematic diagram of the heat exchange system in yet another specific embodiment. Figure 6 for Figure 5A partially enlarged view of section III. Heat exchange system 1 has a bypass branch 6 (e.g., Figure 5 and Figure 6 (As shown by the red solid line in the diagram), the bypass branch 6 includes a third flow regulator 164. One end of the third flow regulator 164 is connected to the first outlet 141 of the compressor 14, and the other end of the third flow regulator 164 is connected to one end of the second heat exchange section 42. The third flow regulator 164 is a bidirectional flow controller. It can be understood that the third flow regulator 164 has a thirteenth interface 1641 and a fourteenth interface 1642. The thirteenth interface 1641 of the third flow regulator (164) is connected to the first outlet 141 of the compressor 14, and the fourteenth interface 1642 of the third flow regulator 164 is connected to one end of the second heat exchange section 42. This third flow regulator 164 is a bidirectional flow controller.

[0083] In one specific embodiment, when the heat exchange system 1 is operating in defrost mode, it is filled with refrigerant. The second port 152 of the reversing valve 15 is connected to the thirteenth port 1641 of the third flow regulator 164, and the fourteenth port 1642 of the third flow regulator 164 is connected to the second heat exchange channel 321 of the second heat exchange section 42. The refrigerant flows through the third flow regulator 164 to the second heat exchange channel 321 of the second heat exchange section 42. In another specific embodiment, when the heat exchange system 1 is operating in heating mode, it is filled with refrigerant. The first heat exchange channel 311 of the first heat exchange section 41 is connected to the fourteenth port 1642 of the third flow regulator 164, and the thirteenth port 1641 of the third flow regulator 164 is connected to the second port 152 of the reversing valve 15. The refrigerant flows through the second heat exchange channel 321 of the second heat exchange section 42 to the third flow regulator 164.

[0084] like Figure 5 and Figure 6 As shown, when the heat exchange system 1 operates in heating mode, the first heat exchanger 11 functions as an evaporator, and the second heat exchanger 12 functions as a condenser. When the heat exchange system 1 operates in defrost mode, the first heat exchanger 11 functions as a condenser, and the second heat exchanger 12 functions as an evaporator. When the heat exchange system 1 switches from defrost mode to heating mode or vice versa, the reversing valve 15 switches the refrigerant flow direction by changing the connection relationship of each port.

[0085] Specifically, Figure 5 and Figure 6 In the embodiment shown, when the heat exchange system 1 is in defrost mode (refrigerant flow direction as shown) Figure 5 and Figure 6When operating under the conditions indicated by the solid arrows in the diagram, the high-temperature, high-pressure gaseous refrigerant discharged from the first outlet 141 of the compressor 14 enters the first valve port 151 of the reversing valve 15 and exits from the second valve port 152 connected to the first valve port 151. After exiting from the second valve port 152, the high-temperature, high-pressure gaseous refrigerant is divided into a first part of refrigerant and a second part of refrigerant. The high-temperature, high-pressure first part of refrigerant enters the heat exchange channel of the first heat exchanger 11 through the second connecting port 412. After heat exchange in the first heat exchanger 11, the high-temperature, high-pressure gaseous refrigerant becomes a medium-temperature, high-pressure liquid refrigerant, and the medium-temperature, high-pressure first part of refrigerant exits from the first heat exchanger 11 through the third connecting port 421. When the high-temperature, high-pressure gaseous refrigerant exchanges heat in the first heat exchanger 11, it can melt the frost on the surface of the first heat exchanger 11. The first portion of refrigerant (medium-temperature, high-pressure liquid refrigerant) enters the second flow regulator 132 through one port 1321. After throttling within the second flow regulator 132, the first portion of refrigerant (low-temperature, low-pressure liquid refrigerant) exits the second flow regulator 132 through another port 1322. The first portion of refrigerant (low-temperature, low-pressure liquid refrigerant) enters the second heat exchanger 12 through the third port 121. Within the second heat exchanger 12, the first portion of refrigerant (low-temperature, low-pressure liquid refrigerant) absorbs heat from the air and transforms into low-temperature, low-pressure gaseous refrigerant. The first portion of refrigerant (low-temperature, low-pressure gaseous refrigerant) discharged from the fourth port 122 enters the reversing valve 15 through the third valve port 153. The first portion of refrigerant (low-temperature, low-pressure gaseous refrigerant) exits the reversing valve 15 through the fourth valve port 154, which is connected to the third valve port 153, and enters the compressor 14 through the first inlet 142, completing one cycle.

[0086] Simultaneously, the second portion of refrigerant (high-temperature and high-pressure gaseous refrigerant) discharged from the second valve port 152 of the reversing valve 15 enters the thirteenth port 1641 of the third flow regulator 164, and after leaving the third flow regulator 164 through the fourteenth port 1642, it enters the second heat exchange channel 321 of the second heat exchange section 42 through the fourth connecting port 422. After heat exchange in the second heat exchange channel 321, the high-temperature and high-pressure gaseous refrigerant becomes a medium-temperature and high-pressure liquid refrigerant, that is, the second portion of medium-temperature and high-pressure refrigerant is discharged from the third connecting port 421 from the first heat exchanger 11. The second portion of refrigerant (medium-temperature, high-pressure liquid refrigerant) enters the second flow regulator 132 through one port 1321. After throttling within the second flow regulator 132, the second portion of refrigerant (low-temperature, low-pressure liquid refrigerant) exits the second flow regulator 132 through another port 1322. The second portion of refrigerant (low-temperature, low-pressure liquid refrigerant) enters the second heat exchanger 12 through the third port 121. Within the second heat exchanger 12, the second portion of refrigerant (low-temperature, low-pressure liquid refrigerant) absorbs heat from the air and transforms into low-temperature, low-pressure gaseous refrigerant. The second portion of refrigerant (low-temperature, low-pressure gaseous refrigerant) discharged from the fourth port 122 enters the reversing valve 15 through the third valve port 153. The second portion of refrigerant (low-temperature, low-pressure gaseous refrigerant) exits the reversing valve 15 through the fourth valve port 154 and enters the compressor 14 through the first inlet 142, completing one cycle.

[0087] In this embodiment, when the heat exchange system 1 is running in defrost mode, the first outlet 141 of the compressor 14 is connected to the fourth communication port 422 of the second heat exchange section 42 via the reversing valve 15 and the third flow regulator 164. This allows the high-temperature and high-pressure refrigerant discharged from the first outlet 141 of the compressor 14 to enter the second heat exchange channel of the second heat exchange section 42. When the second part of the refrigerant (high-temperature and high-pressure gaseous refrigerant) exchanges heat in the second heat exchange section 42 of the first heat exchanger 11, it can melt the frost on the surface of the second heat exchange section 42. Since the second part of the refrigerant is the refrigerant discharged from the first outlet 141 of the compressor 14, its temperature is high, which can quickly melt the frost on the surface of the second heat exchange section 42 and reduce the risk of frost accumulation on the surface of the second heat exchange section 42 of the first heat exchanger 11 affecting the heat exchange efficiency of the second heat exchange section 42.

[0088] The third flow regulator 164 is used to regulate the flow rate of the refrigerant flowing through it, specifically the flow rates of the first and second portions of refrigerant. When the number of first heat exchange tubes 31 in the first heat exchange section 41 is greater than the number of second heat exchange tubes 32 in the second heat exchange section 42, the refrigerant demand of the second heat exchange section 42 is less than the refrigerant demand of the first heat exchange section 41. In this case, the third flow regulator 164 ensures that the flow rate of the second portion of refrigerant entering the second heat exchange section 42 is less than the flow rate of the first portion of refrigerant entering the first heat exchange section 41.

[0089] In yet another specific embodiment, please refer to... Figure 5 and Figure 6 , Figure 5 This is a schematic diagram of the heat exchange system provided in this application in yet another specific embodiment. Figure 6 for Figure 5 A magnified view of a portion of IV. (See image below.) Figure 5 and Figure 6 As shown, the heat exchange system 1 may further include a first flow path 7 ( Figure 5 and Figure 6 (As shown by the blue line in the middle), the first flow path 7 connects the first communication port 411 of the first heat exchange section 41 and the seventh interface 1311 of the first flow regulator 131. At the same time, in this embodiment, the third communication port 421 of the second heat exchange section 42 is also connected to the seventh interface 1311 of the first flow regulator 131.

[0090] When the heat exchange system 1 is operating in defrost mode, the first portion of refrigerant discharged from the second valve port 152 of the reversing valve 15 enters the first heat exchange section 41 through the second connecting port 412. After heat exchange in the first heat exchange channel 311 of the first heat exchange section 41, it leaves the first heat exchange section 41 through the first connecting port 411 and flows through the first flow path 7 to the seventh port 1311 of the first flow regulator 131. At the same time, the second portion of refrigerant discharged from the second valve port 152 of the reversing valve 15 enters the second heat exchange channel 321 of the second heat exchange section 42 through the third flow regulator 164. After heat exchange in the second heat exchange channel 321, the first portion of refrigerant leaves the second heat exchange section 42 through the third connecting port 421 and flows to the seventh port 1311 of the first flow regulator 131.

[0091] In some embodiments, when the heat exchange system 1 is operating in defrost mode, the first portion of refrigerant and the second portion of refrigerant converge in the second heat exchange channel 321 of the second heat exchange section 42, while Figure 5 and Figure 6 In the embodiment shown, when the heat exchange system 1 is operating in defrost mode, the first portion of refrigerant and the second portion of refrigerant converge outside the first heat exchanger 11 and before the first flow regulator 131.

[0092] Figure 5 and Figure 6 In the embodiment shown, the heat exchange system 1 is in heating mode ( Figure 5 and Figure 6 When operating under the conditions indicated by the solid arrows in the diagram, the high-temperature and high-pressure refrigerant enters the reversing valve 15 from the first outlet 141 of the compressor 14 via the first valve port 151, and exits the reversing valve 15 from the third valve port 153 connected to the first valve port 151. The high-temperature and high-pressure refrigerant then enters the second heat exchanger 12 via the fourth port 122. After heat exchange in the second heat exchanger 12, the high-temperature and high-pressure gaseous refrigerant becomes a medium-temperature and high-pressure liquid refrigerant. The medium-temperature and high-pressure liquid refrigerant exits the second heat exchanger 12 via the third port 121 and enters the first flow regulator 131. After being throttled in the first flow regulator 131, the medium-temperature and high-pressure liquid refrigerant becomes a low-temperature and low-pressure liquid refrigerant and exits the first flow regulator 131 from the seventh port 1311. The low-temperature, low-pressure liquid refrigerant leaving the first flow regulator 131 is divided into a fifth refrigerant portion and a sixth refrigerant portion. The fifth refrigerant portion enters the second heat exchange section 42 of the first heat exchanger 11 through the third connection port 421. After heat exchange in the second heat exchange channel 321 of the second heat exchange section 42, it becomes a low-temperature, low-pressure gaseous refrigerant and exits the second heat exchange section 42 through the fourth connection port 422. The fifth refrigerant portion leaving the second heat exchange section 42 then enters the third flow regulator 164 through the fourteenth interface 1642, and exits the third flow regulator 164 through the thirteenth interface 1641. The sixth refrigerant portion flows through the first flow path 7 and enters the first heat exchange section 41 through the first connection port 411. After heat exchange in the first heat exchange channel 311 of the first heat exchange section 41, it exits the first heat exchange section 41 through the second connection port 412. The fifth portion of refrigerant leaving the third flow regulator 164 and the sixth portion of refrigerant leaving the first heat exchange section 41 merge and enter the reversing valve 15 through the second valve port 152. The refrigerant then exits the reversing valve 15 through the fourth valve port 154, which is connected to the second valve port 152. The merged refrigerant then returns to the compressor 14 through the first inlet 142, completing one heating cycle. Figure 5 and Figure 6 It can be seen that the refrigerant flows in opposite directions when the heat exchange system 1 is running in heating mode and defrosting mode.

[0093] Therefore, in this embodiment, after the first flow path 7 is set, when the heat exchange system 1 is running in the heating mode, the refrigerant after being throttled by the first flow regulator 131 can enter the first heat exchange section 41 and the second heat exchange section 42 of the first heat exchanger 11 respectively, so that the heat exchange area of ​​the first heat exchanger 11 is larger and the heat exchange efficiency of the heat exchange system 1 in the heating mode is improved.

[0094] In such Figure 5 and Figure 6In the illustrated embodiment, the heat exchange system 1 may further include a fourth flow regulator 165, which has a ninth interface 1651 and a tenth interface 1652. The ninth interface 1651 is connected to the third communication port 421 of the second heat exchange section 42, and the tenth interface 1652 is connected to the seventh interface 1311 of the first flow regulator 131. In one specific embodiment, when the heat exchange system 1 is operating in defrost mode, the refrigerant flowing out of the fourth flow regulator 165 can flow to the second heat exchange channel 321 of the second heat exchange section 42. In another specific embodiment, when the heat exchange system 1 is operating in heating mode, the refrigerant flowing out of the second heat exchange channel 321 of the second heat exchange section 42 flows to the fourth flow regulator 165. In yet another specific embodiment, when the heat exchange system 1 is operating in defrost mode, the refrigerant flowing out of the fourth flow regulator 165 can flow to the second heat exchange channel 321 of the second heat exchange section 42. When the heat exchange system 1 is running in heating mode, the refrigerant flowing out of the second heat exchange channel 321 of the second heat exchange section 42 flows to the fourth flow regulator 165.

[0095] When the heat exchange system 1 is operating in heating mode, the fourth flow regulator 165 is used to regulate the flow rates of the fifth and sixth portions of refrigerant. When the number of first heat exchange tubes 31 in the first heat exchange section 41 is greater than the number of second heat exchange tubes 32 in the second heat exchange tubes 42, the required refrigerant charge in the first heat exchange channel 311 of the first heat exchange section 41 is greater than the required refrigerant charge in the second heat exchange channel 321 of the second heat exchange section 42. When the heat exchange system 1 is operating in heating mode, under the regulation of the fourth flow regulator 165, the flow rate of the fifth portion of refrigerant is made less than the flow rate of the sixth portion of refrigerant. This results in less refrigerant entering the second heat exchange channel 321 of the second heat exchange section 42 through the third connecting port 421 than entering the first heat exchange channel 311 of the first heat exchange section 41 through the first flow path 7. This ensures that the refrigerant flow rate is matched with the volume of the first heat exchange section 41 and the second heat exchange section 42, guaranteeing the heat exchange efficiency of the first heat exchanger 11 in heating mode.

[0096] The fourth flow regulator 164 can be a regulating valve or a pipeline, and the flow cross-sectional area of ​​the pipeline is smaller than the flow cross-sectional area of ​​the bypass branch 6.

[0097] In the above embodiments, as Figure 6As shown, when the heat exchange system 1 is running in defrost mode, a first portion of the refrigerant enters the first heat exchange section 41 through the second connection port 412, and a second portion of the refrigerant enters the second heat exchange section 42 through the fourth connection port 422. Since the second connection port 412 and the fourth connection port 422 are located at the two ends of the first heat exchanger 11 along the length direction of the first heat exchange tube 31 and the second heat exchange tube 32, the flow direction of the refrigerant in the first heat exchange tube 31 is opposite to the flow direction in the second heat exchange tube 32. The heat exchange performance of the heat exchanger gradually decreases from the refrigerant inlet side to the outlet side. That is, for the first heat exchange section 41, the heat exchange performance at the end near the second connecting port 412 is stronger than that at the end near the first connecting port 411. For the second heat exchange section 42, the heat exchange performance at the end near the third connecting port 421 is weaker than that at the end near the fourth connecting port 422. For the first heat exchanger 11 as a whole, the heat exchange performance of the first heat exchanger 11 is more uniform at both ends along the length direction of the first heat exchange tube 31 and the second heat exchange tube 32, thereby improving the defrosting efficiency of the first heat exchanger 11.

[0098] The above describes an embodiment of heat exchange system 1. The structure of the first heat exchanger 11 in heat exchange system 1 is described in detail below.

[0099] Please refer to Figure 7 and Figure 8 ,in, Figure 7 This is a schematic diagram of the structure of the first heat exchanger of the heat exchange system provided in this application in one specific embodiment. Figure 8 for Figure 7 A sectional view along line AA. For example... Figure 7 and Figure 8 As shown, the first heat exchanger 11 includes multiple fins 5, which are arranged along the length Y direction of the first heat exchange tube 31. Each fin 5 has multiple first mounting portions 51 and multiple second mounting portions 52, both arranged along the length X direction of the fin 5. The first mounting portions 51 are used to mount the first heat exchange tube 31, and the second mounting portions 52 are used to mount the second heat exchange tube 32. The first heat exchange tube 31 passes through the multiple first mounting portions 51, and the second heat exchange tube 32 passes through the multiple second mounting portions 52. In heating mode, the length Y direction of both the first heat exchange tube 31 and the second heat exchange tube 32 is perpendicular to the height X direction of the first heat exchanger 11.

[0100] like Figure 7 As shown, the first heat exchanger 11 also includes a first manifold 21 and a second manifold 22, with the first heat exchange tube 31 connecting the first manifold 21 and the second manifold 22, and the second heat exchange tube 32 connecting the second manifold 22. Wherein, as... Figure 7As shown, the first heat exchanger 11 has a first heat exchange section 41 and a second heat exchange section 42. In the height direction of the first heat exchanger 11, the second heat exchange section 42 is located below the first heat exchange section 41. The first heat exchange section 41 includes a plurality of first heat exchange tubes 31, a first cavity 211, and a second cavity 221. The first heat exchange tubes 31 have a first heat exchange channel 311 for refrigerant flow, which connects the first cavity 211 and the second cavity 221. Similarly, the second heat exchange section 42 includes a plurality of second heat exchange tubes 32, a third cavity 212, and a fourth cavity 222. The second heat exchange tubes 32 have a second heat exchange channel 321 for refrigerant flow, which connects the third cavity 212 and the fourth cavity 222. The inner cavity of the first manifold 21 is the first cavity 211 and the third cavity 212, and the inner cavity of the second manifold 22 is the second cavity 221 and the fourth cavity 222.

[0101] Normally, the first cavity 211 and the third cavity 212 are isolated from each other, and the second cavity 221 and the fourth cavity 222 are isolated from each other. A first partition can be installed inside the first manifold 21, thereby dividing the inner cavity of the first manifold 21 into the first cavity 211 and the third cavity 212. A second partition can be installed inside the second manifold 22, thereby dividing the inner cavity of the second manifold 22 into the second cavity 221 and the fourth cavity 222.

[0102] In this embodiment, the pressure of the refrigerant entering the second heat exchange tube of the second heat exchange section is increased to raise the temperature of the second heat exchange section, thereby reducing frost formation in the second heat exchange section.

[0103] Specifically, the sum of the flow cross-sectional areas of the plurality of first heat exchange tubes 31 in the first heat exchange section 41 is S1, and the sum of the flow cross-sectional areas of the plurality of second heat exchange tubes 32 in the second heat exchange section 42 is S2, where S1 > S2. The flow resistance of the refrigerant flowing in the second heat exchange tubes 32 of the second heat exchange section 42 is greater than the flow resistance of the refrigerant flowing in the first heat exchange tubes 31 of the first heat exchange section 41. When the first heat exchanger 11 is operating in low-temperature heating mode and the pressure at the outlet of the first heat exchanger 11 (the outlet connected to the first cavity 211) is constant, the pressure of the second heat exchange section 42 located at the inlet end of the first heat exchanger 11 increases. That is, the pressure of the second heat exchange section 42 located upstream is greater than the pressure of the first heat exchange section 41 located downstream. As a result, the temperature of the second heat exchange section 42 is higher than the temperature of the first heat exchange section 41. That is, the temperature of the outer wall of the second heat exchange tubes 32 of the second heat exchange section 42 is higher, the risk of frosting is lower, and the heat exchange efficiency is improved.

[0104] Meanwhile, compared to the traditional first heat exchanger 11, when the sum of the flow cross-sectional areas of the second heat exchange tubes 32 of the second heat exchange section 42 of the first heat exchanger 11 in this embodiment is smaller, the overall internal volume of the first heat exchanger 11 can also be reduced, making the internal volumes of the first heat exchanger 11 (outdoor heat exchanger) and the second heat exchanger 12 (indoor heat exchanger) in the heat exchange system 1 closer. This makes the refrigerant charge of the first heat exchanger 11 and the second heat exchanger 12 closer in both cooling and heating modes, resulting in higher performance of the heat exchange system 1 in both cooling and heating modes.

[0105] In one specific embodiment, such as Figure 7 and Figure 8 As shown, two or more first heat exchange tubes 31 are arranged along the length direction X of the first manifold 21, and two or more second heat exchange tubes 32 are arranged along the length direction X of the first manifold 21. The flow cross-sectional area of ​​the first heat exchange tubes 31 is larger than the flow cross-sectional area of ​​the second heat exchange tubes 32. That is, the flow cross-sectional area of ​​the second heat exchange tubes 32 in the second heat exchange section 42 is smaller than the flow cross-sectional area of ​​the first heat exchange tubes 31 in the first heat exchange section 41, thereby facilitating the realization of S1 > S2.

[0106] It should be noted that the flow cross-sectional area of ​​a heat exchanger tube refers to the cross-sectional area of ​​the refrigerant flowing through the heat exchanger tube. When the heat exchanger tube includes one channel, the flow cross-sectional area refers to the cross-sectional area of ​​that channel. When the heat exchanger tube includes multiple channels, the flow cross-sectional area refers to the sum of the cross-sectional areas of the multiple channels.

[0107] In one specific embodiment, the flow cross-sectional area of ​​the first heat exchange tube 31 is A1, and the flow cross-sectional area of ​​the second heat exchange tube 32 is A2. The flow cross-sectional areas A1 of the first heat exchange tube 31 and A2 of the second heat exchange tube 32 satisfy the following relationship: 1 < A1 / A2 ≤ 8. For example, A1 / A2 can be 1.1, 2, 3, 4, 5, 6, 7, 8, etc.

[0108] When A1 / A2 is too small, the flow cross-sectional area A1 of the first heat exchange tube 31 is close to the flow cross-sectional area A2 of the second heat exchange tube 32. This makes it difficult to effectively increase the pressure of the refrigerant flowing in the second heat exchange section 42, thus failing to effectively increase the temperature of the second heat exchange section 42 and resulting in a higher risk of frost formation in the second heat exchange section 42. When A1 / A2 is too large, the flow cross-sectional area A2 of the second heat exchange tube 32 is too small, which not only increases the manufacturing difficulty of the second heat exchange tube 32 but also results in a small flow rate of the refrigerant flowing in the second heat exchange section 42, reducing the heat exchange efficiency of the first heat exchanger 11. Therefore, in this embodiment, when 1 < A1 / A2 ≤ 8, the pressure of the refrigerant flowing in the second heat exchange section 42 can be effectively increased, thereby effectively increasing the temperature of the second heat exchange section 42 and reducing the risk of frost formation. At the same time, it can also avoid the small flow rate of the refrigerant flowing in the second heat exchange section 42 affecting the heat exchange efficiency of the first heat exchanger 11, resulting in a lower risk of frost formation in the first heat exchanger 11 and a higher heat exchange efficiency.

[0109] The following describes in detail the specific structure for achieving a flow cross-sectional area of ​​the first heat exchange tube 31 that is larger than that of the second heat exchange tube 32.

[0110] In one specific embodiment, please refer to Figure 9-13 , Figure 9 for Figure 8 A magnified view of a portion of the V-shaped section. Figure 10 for Figure 8 A magnified view of section VI. (See attached image.) Figure 9 As shown, the first heat exchange tube 31 includes a first wall 312 and a second wall 313 in the thickness direction of the first heat exchange tube 31. (As...) Figure 10 As shown, the second heat exchange tube 32 includes a third wall 323 and a fourth wall 324 in the thickness direction of the second heat exchange tube 32.

[0111] In one specific embodiment, combined with Figure 9 and Figure 10 It is known that the wall thickness of the third wall 323 is greater than at least one of the first wall 312 and the second wall 313, that is, the thickness of the third wall 323 is greater than the thickness of the first wall 312, or the thickness of the third wall 323 is greater than the thickness of the second wall 313, or the thickness of the third wall 323 is greater than the thickness of the first wall 312, and the thickness of the third wall 323 is greater than the thickness of the second wall 313. Therefore, when the external dimensions of the first heat exchange tube 31 and the second heat exchange tube 32 along the thickness direction are the same, the flow cross-sectional area of ​​the second heat exchange channel 321 of the second heat exchange tube 32 is smaller than the flow cross-sectional area of ​​the first heat exchange channel 311 of the first heat exchange tube 31.

[0112] In another specific embodiment, combined with Figure 9 and Figure 10It is known that the wall thickness of the fourth wall 324 is greater than at least one of the first wall 312 and the second wall 313, that is, the thickness of the fourth wall 324 is greater than the thickness of the first wall 312, or the thickness of the fourth wall 324 is greater than the thickness of the second wall 313, or the thickness of the fourth wall 324 is greater than the thickness of the first wall 312, and the thickness of the fourth wall 324 is greater than the thickness of the second wall 313. Therefore, when the external dimensions of the first heat exchange tube 31 and the second heat exchange tube 32 along the thickness direction are the same, the flow cross-sectional area of ​​the second heat exchange channel 321 of the second heat exchange tube 32 is smaller than the flow cross-sectional area of ​​the first heat exchange channel 311 of the first heat exchange tube 31.

[0113] In yet another specific embodiment, combined with Figure 9 and Figure 10 It can be seen that the thickness of the third wall 323 is greater than at least one of the first wall 312 and the second wall 313, and the thickness of the fourth wall 324 is greater than at least one of the first wall 312 and the second wall 313. For example, Figure 4 and Figure 5 In the embodiment shown, the thickness of the third wall 323 is greater than the thickness of the first wall 312 and greater than the thickness of the second wall 313, and the thickness of the fourth wall 324 is greater than the thickness of the first wall 312 and greater than the thickness of the second wall 313. Thus, when the outer dimensions of the first heat exchange tube 31 and the second heat exchange tube 32 in the thickness direction are the same, the flow cross-sectional area of ​​the second heat exchange channel 321 of the second heat exchange tube 32 is smaller than the flow cross-sectional area of ​​the first heat exchange channel 311 of the first heat exchange tube 31.

[0114] In addition, in the embodiments described above, when the thicknesses of the first wall 312, the second wall 313, the third wall 323, and the fourth wall 324 meet the conditions described above, the wall of the second heat exchange tube 32 is thicker, thereby increasing the strength of the second heat exchange tube 32 and reducing the risk of breakage of the second heat exchange tube 32.

[0115] In this embodiment, the first heat exchange tube 31 and the second heat exchange tube 32 can be flat tubes or round tubes. This application does not limit the type of heat exchange tubes. When the first heat exchange tube 31 and the second heat exchange tube 32 are flat tubes, the first heat exchange channel 311 and the second heat exchange channel 321 can be circular, square or other shapes. This application does not limit the specific shape of the first heat exchange channel 311 and the second heat exchange channel 321.

[0116] In another specific embodiment, such as Figure 9As shown, the first heat exchange tube 31 has multiple first heat exchange channels 311, which are spaced apart along the width direction of the first heat exchange tube 31. Therefore, the flow cross-sectional area A1 of the first heat exchange tube 31 is the sum of the cross-sectional areas of the multiple first heat exchange channels 311. On a cross-section perpendicular to the length direction of the first heat exchange tube 31, the shortest distance between two adjacent first heat exchange channels 311 along the width direction of the first heat exchange tube 31 is W1. Figure 10 As shown, the second heat exchange tube 32 has multiple second heat exchange channels 321, which are spaced apart along the width direction of the second heat exchange tube 32. Therefore, the flow cross-sectional area A2 of the second heat exchange tube 32 is the sum of the cross-sectional areas of the multiple second heat exchange channels 321. On a cross-section perpendicular to the length direction of the second heat exchange tube 32, the shortest distance between two adjacent second through holes along the width direction of the second heat exchange tube 32 is W2.

[0117] Combination Figure 9 and Figure 10 It can be seen that W1 can represent the wall thickness of the first heat exchange channel 311 in the width direction of the first heat exchange tube 31, and W2 can represent the wall thickness of the second heat exchange channel 321 in the width direction of the second heat exchange tube 32. When W2≥W1, when the external dimensions of the first heat exchange tube 31 and the second heat exchange tube 32 are the same along the width direction of the first heat exchange tube 31 and the second heat exchange tube 32, the flow cross-sectional area of ​​the second heat exchange channel 321 of the second heat exchange tube 32 is smaller than the flow cross-sectional area of ​​the first heat exchange channel 311 of the first heat exchange tube 31. Therefore, the flow cross-sectional area A2 of the second heat exchange tube 32 (the sum of the flow cross-sectional areas of multiple second heat exchange channels 321) is smaller than the flow cross-sectional area A1 of the first heat exchange tube 31 (the sum of the flow cross-sectional areas of multiple first heat exchange channels 311).

[0118] In addition, when the wall thickness W2 of the second heat exchange channel 321 in the width direction of the second heat exchange tube 32 is greater than the wall thickness W1 of the first heat exchange channel 311 in the width direction of the first heat exchange tube 31, the strength of the second heat exchange tube 32 is higher, reducing the risk of the second heat exchange tube 32 breaking.

[0119] In this embodiment, the first heat exchange tube 31 and the second heat exchange tube 32 can be as follows: Figure 10 The flat tube shown can also be as follows: Figure 11 The application does not limit the type of heat exchange tube shown in the circular tube. When the first heat exchange tube 31 and the second heat exchange tube 32 are flat tubes, the first heat exchange channel 311 and the second heat exchange channel 321 can be circular, square or other shapes. The application does not limit the specific shape of the first heat exchange channel 311 and the second heat exchange channel 321.

[0120] In yet another specific embodiment, such as Figure 9 As shown, the length of the first heat exchange tube 31 is L1, as... Figure 12 As shown, the length of the second heat exchange tube 32 is L2, which is less than L1. That is, the length L2 of the second heat exchange tube 32 of the second heat exchange section 42 is less than the length L1 of the first heat exchange tube 31 of the first heat exchange section 41. This makes the space for the refrigerant to flow in the second heat exchange tube 32 smaller than the space for the refrigerant to flow in the first heat exchange tube 31. This also makes the flow cross-sectional area A2 of the second heat exchange tube 32 (the sum of the flow cross-sectional areas of the multiple second heat exchange channels 321) smaller than the flow cross-sectional area A1 of the first heat exchange tube 31 (the sum of the flow cross-sectional areas of the multiple first heat exchange channels 311).

[0121] In other words, in this embodiment, the sum of the flow cross-sectional areas of the second heat exchange section 42 is reduced by selecting a second heat exchange tube 32 with a shorter length in the second heat exchange section 42.

[0122] like Figure 8 In the illustrated embodiment, the first mounting portion 51 can be a groove structure disposed on the fins 5. When assembling the first heat exchanger 11, the first heat exchange tube 31 can be inserted into the first mounting portion 51 through the opening of the first mounting portion 51. The second mounting portion 52 can be a groove structure. When assembling the first heat exchanger 11, the second heat exchange tube 32 can be inserted into the second mounting portion 52 through the opening of the second mounting portion 52.

[0123] like Figure 9 As shown, the first mounting portion 51 has a first wall portion in the width direction of the fin 5, and this first wall portion is the bottom wall of the groove structure of the first mounting portion 51. Figure 12 As shown, the second mounting portion 52 has a second wall portion in the width direction of the fin 5, and this second wall portion is the bottom wall of the groove structure of the second mounting portion 52. Figure 9 As shown, the first heat exchange tube 31 is attached to the first wall portion, as... Figure 12 As shown, there is a gap t between the second heat exchange tube 32 and the second wall portion, so that the dimension of the second heat exchange tube 32 in the width direction is smaller than the dimension of the first heat exchange tube 31 in the width direction, and thus the flow cross-sectional area A2 of the second heat exchange tube 32 is smaller than the flow cross-sectional area A1 of the first heat exchange tube 31.

[0124] Alternatively, in another embodiment, there may be a first gap between the first heat exchange tube 31 and the first wall portion, and a second gap between the second heat exchange tube 32 and the second wall portion, with the first gap being smaller than the second gap. This results in the second heat exchange tube 32 having a smaller dimension in the width direction than the first heat exchange tube 31 having a smaller cross-sectional area A2 in the width direction than the first heat exchange tube 31. Consequently, the flow cross-sectional area A2 of the second heat exchange tube 32 is smaller than the flow cross-sectional area A1 of the first heat exchange tube 31.

[0125] In this embodiment, when the first heat exchange tube 31 and the second heat exchange tube 32 are flat tubes, the first heat exchange channel 311 and the second heat exchange channel 321 can be circular, square or other shapes. This application does not limit the specific shape of the first heat exchange channel 311 and the second heat exchange channel 321.

[0126] like Figure 13 As shown, both the first mounting part 51 and the second mounting part 52 can be holes. When assembling the first heat exchanger 11, the first heat exchange tube 31 can be inserted into the first mounting part 51 and the second heat exchange tube 32 can be inserted into the second mounting part 52.

[0127] like Figure 13 In the illustrated embodiment, the diameters of the first mounting portion 51 and the second mounting portion 52 can be the same, and the outer diameter of the first heat exchange tube 31 is smaller than the outer diameter of the second heat exchange tube 32. This results in a larger gap between the second heat exchange tube 32 and the wall of the second mounting portion 52 than the gap between the first heat exchange tube 31 and the wall of the first mounting portion 51, and consequently, a smaller flow cross-sectional area for the second heat exchange tube 32 than for the first heat exchange tube 31. In this embodiment, when the dimensions of the first mounting portion 51 and the second mounting portion 52 are the same, the processing difficulty of the fins can be reduced.

[0128] like Figure 14 In the illustrated embodiment, the diameters of the first mounting portion 51 and the second mounting portion 52 may also be different. The diameter of the first mounting portion 51 is larger than the diameter of the second mounting portion 52, and the outer diameter of the first heat exchange tube 31 is smaller than the outer diameter of the second heat exchange tube 32. This allows the first mounting portion 51 to be adapted to the first heat exchange tube 31, and the second mounting portion 52 to be adapted to the second heat exchange tube 32. The reliability of the first heat exchange tube 31 installed on the first mounting portion 51 is high, and the reliability of the second heat exchange tube 32 installed on the second mounting portion 52 is also high, reducing the risk of the first heat exchange tube 31 and the second heat exchange tube 32 shaking.

[0129] In another specific embodiment, the equivalent diameter of the first heat exchange tube 31 is D1, and the equivalent diameter of the second heat exchange tube 32 is D2. Those skilled in the art will understand that the diameter of a circular tube with the same hydraulic radius is the equivalent diameter of a non-circular tube. When both the first heat exchange tube 31 and the second heat exchange tube 32 are circular tubes, D1 is the diameter of the first heat exchange tube 31, and D2 is the diameter of the second heat exchange tube 32. When both the first heat exchange tube 31 and the second heat exchange tube 32 are flat tubes, D1 is the diameter of the circular tube, where the hydraulic radius of the flat tube is the same as the diameter of the circular tube.

[0130] The equivalent diameter D1 of the first heat exchange tube 31 and the equivalent diameter D2 of the second heat exchange tube 32 satisfy the following relationship: D1≥D2, so that the flow cross-sectional area A2 of the second heat exchange tube 32 is smaller than the flow cross-sectional area A1 of the first heat exchange tube 31.

[0131] In one specific embodiment, such as Figure 15 As shown, the first heat exchange tube 31 and the second heat exchange tube 32 have the same external dimensions, making the first mounting part 51 and the second mounting part 52 of the fin body the same size, which is convenient for manufacturing.

[0132] like Figure 15 As shown, the first heat exchange tube 31 includes a first heat exchange channel 311, as... Figure 16-18 As shown, the interior of the second heat exchange tube 32 has a partition rib 322, which divides the inner cavity of the second heat exchange tube 32 into multiple second heat exchange channels 321. Since the outer dimensions of the first heat exchange tube 31 and the second heat exchange tube 32 are the same, the partition rib 322 inside the second heat exchange tube 32 occupies the space of the inner cavity of the second heat exchange tube 32, making the flow cross-sectional area A2 of the second heat exchange tube 32 for refrigerant flow smaller than the flow cross-sectional area A1 (inner cavity of the first heat exchange tube 31).

[0133] In another specific embodiment, the first heat exchange tube 31 includes a plurality of first heat exchange channels 311, and the second heat exchange tube 32 includes a plurality of second heat exchange channels 321. The inner cavity of the first heat exchange tube 31 may be provided with partition ribs 322, which divide the inner cavity of the first heat exchange tube 31 into a plurality of first heat exchange channels 311. The sum of the cross-sectional areas of the plurality of first heat exchange channels 311 is the flow cross-sectional area A1 of the first heat exchange tube 31. The inner cavity of the second heat exchange tube 32 may be provided with partition ribs 322, which divide the inner cavity of the second heat exchange tube 32 into a plurality of second heat exchange channels 321. The sum of the cross-sectional areas of the plurality of second heat exchange channels 321 is the flow cross-sectional area A2 of the second heat exchange tube 32. The cross-sectional area of ​​one of the multiple second heat exchange channels 321 is smaller than the cross-sectional area of ​​one of the multiple first heat exchange channels 311, so that the sum of the cross-sectional areas of the multiple second heat exchange channels 321 is less than the sum of the cross-sectional areas of the multiple first heat exchange channels 311, thereby making the flow cross-sectional area A2 of the second heat exchange tube 32 smaller than the flow cross-sectional area A1 of the first heat exchange tube 31.

[0134] In addition, in this embodiment, the partition ribs 322 in the inner cavities of the first heat exchange tube 31 and the second heat exchange tube 32 can not only separate multiple channels, but also improve the overall structural strength of the first heat exchange tube 31 and the second heat exchange tube 32, and reduce the risk of breakage of the first heat exchange tube 31 and the second heat exchange tube 32.

[0135] It should be noted that in the embodiments of this application, the structure, quantity and distribution of the partition ribs 322 can be arbitrarily set according to actual needs, and this application does not impose any limitations.

[0136] In the above embodiments, the wall thickness of the first heat exchange tube 31 is T1, and the wall thickness of the second heat exchange tube 32 is T2. When the outer dimensions of the first heat exchange tube 31 and the outer dimensions of the second heat exchange tube 32 are the same, T2≥T1.

[0137] In other embodiments, in addition to making the flow cross-sectional area A2 of the second heat exchange tube 32 smaller than the flow cross-sectional area A1 of the first heat exchange tube 31, the sum of the flow cross-sectional areas S2 of the plurality of second heat exchange tubes 32 in the second heat exchange section 42 can be made smaller than the sum of the flow cross-sectional areas S1 of the plurality of first heat exchange tubes 31 in the first heat exchange section 41 by adjusting the number of the first heat exchange tubes 31 and the second heat exchange tubes 32.

[0138] Specifically, the number of first heat exchange tubes 31 is N1, and the number of second heat exchange tubes 32 is N2. The first heat exchanger 11 satisfies the following relationship: 0.04≤N2 / (N1+N2)≤0.08. In the first heat exchanger 11, the number of second heat exchange tubes 32 N2 is less than the number of first heat exchange tubes 31 N1. N2 / (N1+N2) represents the proportion of the number of second heat exchange tubes 32 N2 in the total number of heat exchange tubes N1+N2 in the first heat exchanger 11. This proportion can be 0.04, 0.05, 0.06, 0.07, 0.08, etc.

[0139] If N2 / (N1+N2) is too small, it means that there are too few second heat exchange tubes 32 in the first heat exchanger 11, and the volume of the second heat exchange section 42 in the first heat exchanger 11 is too small, which cannot cover the areas of the first heat exchanger 11 that are prone to frost, resulting in a still high risk of frost formation in the first heat exchanger 11. If N2 / (N1+N2) is too large, it means that there are too few first heat exchange tubes 31 in the first heat exchanger 11, and the volume of the first heat exchange section 41 in the first heat exchanger 11 is too small, while the volume of the second heat exchange section 42 is too large. Since the sum of the flow cross-sectional areas S2 of the second heat exchange tubes 32 in the second heat exchange section 42 is less than the sum of the flow cross-sectional areas S1 of the first heat exchange tubes 31 in the first heat exchange section 41, the excessive volume of the second heat exchange section 42 results in a smaller overall flow cross-sectional area of ​​the first heat exchanger 11, which can accommodate less refrigerant and affects the heat exchange efficiency of the first heat exchanger 11. Therefore, in this embodiment, when 0.04≤N2 / (N1+N2)≤0.08, the number of first heat exchange tubes 31 N1 and the number of second heat exchange tubes 32 N2 are moderate, which can reduce the risk of frost formation at the bottom of the first heat exchanger 11 while ensuring that the first heat exchanger 11 has a high heat exchange efficiency.

[0140] It should be noted that in this embodiment, the flow cross-sectional area A1 of the first heat exchange tube 31 and the flow cross-sectional area A2 of the second heat exchange tube 32 can be the same or different, that is, A1 = A2, or A1 > A2. Specifically, A1 > A2 can be achieved through the methods described in the above embodiments, which will not be repeated here.

[0141] The above description is only a specific implementation of the embodiments of this application, but the protection scope of the technical solution of this application is not limited thereto. Any changes or substitutions within the technical scope disclosed in the embodiments of this application should be covered within the protection scope of the embodiments of this application.

Claims

1. A heat exchange system, characterized by, The heat exchange system includes a compressor (14), a first heat exchanger (11), a second heat exchanger (12), and a second flow regulator (132). The second flow regulator (132) is provided between the first heat exchanger (11) and the second heat exchanger (12). The first heat exchanger (11) includes a first heat exchange section (41) and a second heat exchange section (42). A first direction is defined parallel to the height direction of the second heat exchange section (42). At least a portion of the second heat exchange section (42) is located below the first heat exchange section (41) in the first direction. The heat exchange system (1) also includes a bypass branch (6). The heat exchange system (1) has a defrost mode. In the defrost mode, one end of the bypass branch (6) is connected to the first outlet (141) of the compressor, and the other end of the bypass branch (6) is connected to one end of the second heat exchange section (42).

2. The heat exchange system according to claim 1, wherein The bypass branch includes a first valve (161). In the defrost mode, one port (1611) of the first valve (161) is connected to the first outlet (141) of the compressor (14), and the other port (1612) of the first valve (161) is connected to one end of the second heat exchange section (42). Part of the refrigerant flowing out of the compressor (14) flows to the second heat exchange section (42) through the first valve (161).

3. The heat exchange system according to claim 2, wherein One end of the first heat exchange section (41) is connected to the first outlet (141) of the compressor (14). The refrigerant flowing through the first heat exchange section (41) and the refrigerant flowing through the bypass branch (6) merge and flow to the second heat exchange section (42); or, the refrigerant flowing through the first heat exchange section (41) flows to the second flow regulator (132).

4. The heat exchange system according to claim 2 or 3, characterized in that, The heat exchange system (1) includes a second valve (162) having two ports. The heat exchange system (1) also includes a heating mode. In the heating mode, one port (1622) of the second valve (162) is connected to the first heat exchange section (41), and the other port (1621) of the second valve (162) is connected to the second heat exchange section (42). In the defrosting mode, at least one of the first heat exchange section (41) and the second heat exchange section (42) is disconnected from the second valve (162).

5. The heat exchange system of claim 4, wherein, The heat exchange system (1) further includes a third valve (163), which has two ports. In the defrost mode, one port (1631) of the third valve (163) is connected to the other end of the first heat exchange unit (41), and the other port (1632) of the third valve (163) is connected to one port (1321) of the second flow regulator (132); and / or, in the heating mode, the first heat exchange unit (41) is disconnected from the third valve (163).

6. The heat exchange system according to claim 5, wherein The second valve (162) is a check valve; and / or, the third valve (163) is a check valve.

7. The heat exchange system of claim 1, wherein, The bypass branch includes a third flow regulator (164), which has a thirteenth interface (1641) and a fourteenth interface (1642). The thirteenth interface (1641) of the third flow regulator (164) is connected to the first outlet (141) of the compressor (14), and the fourteenth interface (1642) of the third flow regulator (164) is connected to one end of the second heat exchange section (42). The third flow regulator (164) is a bidirectional flow controller.

8. The heat exchange system according to claim 1 or 2 or 3 or 7, characterized in that, The first heat exchanger (11) includes a plurality of fins (5), the first heat exchange section (41) includes a plurality of first heat exchange tubes (31), and the second heat exchange section (42) includes a plurality of second heat exchange tubes (32). The plurality of fins (5) are arranged in the length direction of the first heat exchange tubes (31). The fins (5) have a plurality of first mounting portions (51) and a plurality of second mounting portions (52). The first mounting portions (51) and the second mounting portions (52) are both arranged in the length direction of the fins (5). The first heat exchange tubes (31) pass through the plurality of first mounting portions (51), and the second heat exchange tubes (32) pass through the plurality of second mounting portions (52). The sum of the flow cross-sectional areas of the plurality of first heat exchange tubes (31) in the first heat exchange section (41) is S1, and the sum of the flow cross-sectional areas of the plurality of second heat exchange tubes (32) in the second heat exchange section (42) is S2, where S1 > S2.

9. The heat exchange system of claim 8, wherein, The flow cross-sectional area of ​​the first heat exchange tube (31) is A1, and the flow cross-sectional area of ​​the second heat exchange tube (32) is A2. The first heat exchange tube (31) and the second heat exchange tube (32) satisfy the following relationship: 1 < A1 / A2 ≤ 8.

10. The heat exchange system of claim 9, wherein, The number of the first heat exchange tubes (31) is N1, and the number of the second heat exchange tubes (32) is N2. The first heat exchange tubes (31) and the second heat exchange tubes (32) satisfy the following relationship: 0.04≤N2 / (N1+N2)≤0.

08.

11. The heat exchange system according to claim 1 or 2 or 3 or 7, characterized in that, The first heat exchange section (41) includes a plurality of first heat exchange tubes (31), and the second heat exchange section (42) includes a plurality of second heat exchange tubes (32). The refrigerant flow direction in at least one of the first heat exchange tubes (31) is opposite to the refrigerant flow direction in the second heat exchange tubes (32).

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