A heat exchanger
By designing a heat exchanger with gas channels and liquid channels in the air conditioner, the flow rate of the liquid heat exchange medium after condensation is ensured, the problem of reduced flow rate during the condensation process is solved and the refrigeration efficiency of the air conditioner is improved.
Patent Information
- Application Number
- CN202421393187.1
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2024-06-18
- Publication Date
- 2025-04-08
- Estimated Expiration
- 2034-06-18
AI Technical Summary
During the condensation process of the tube heat exchanger used in existing air conditioners, the volume of the heat exchange medium decreases, resulting in a decrease in the flow rate, affecting the refrigeration efficiency.
A heat exchanger is designed, and its heat exchange body includes a heat exchange runner, a gas channel and a liquid channel. The gaseous heat exchange medium flows into the heat exchange runner through the gas channel and condenses and flows out through the liquid channel to ensure that the liquid heat exchange medium maintains a suitable flow rate.
By maintaining the appropriate flow rate of the liquid heat exchange medium, the heat transfer coefficient is improved, the heat exchange effect is enhanced, and the cooling efficiency of the air conditioner is improved.
Smart Images
Figure CN222733441U_ABST
Abstract
Description
Technical Field
[0001] The utility model relates to the technical field of heat exchangers, in particular to a heat exchanger. Background Art
[0002] As people's living standards gradually improve, they pay more and more attention to the quality of life. Air conditioners can bring coolness to the room in hot weather and have become an indispensable appliance in people's lives. The working principle of air conditioners is to absorb heat through the evaporation of heat exchange medium, and condense and release heat at the condenser. The heat is released to the outside through the condenser to achieve the purpose of cooling the room.
[0003] At present, the tubular heat exchangers commonly used in the air conditioning industry generally have the same number of inlets and outlets for heat exchange. However, when the heat exchanger is used as a condenser, the heat exchange medium is in a gaseous state when it enters the condenser. After condensation, it first becomes a gas-liquid mixture, and then becomes a liquid and flows out of the heat exchanger. In this process, the volume of the heat exchange medium gradually decreases, resulting in a decrease in the flow rate of the heat exchange medium, affecting the refrigeration efficiency. Utility Model Content
[0004] The utility model aims to provide a heat exchanger which can keep a suitable flow rate of the heat exchange medium, improve the heat transfer coefficient and have a good heat exchange effect.
[0005] To achieve this purpose, the utility model adopts the following technical solutions:
[0006] A heat exchanger, comprising:
[0007] A heat exchange body, the heat exchange body having a heat exchange flow channel and a gas channel and a liquid channel connected to the heat exchange flow channel, a heat exchange medium flows in the heat exchange flow channel, and a flow cross-sectional area of the gas channel is larger than a flow cross-sectional area of the liquid channel;
[0008] The gaseous heat exchange medium flows into the heat exchange channel through the gas channel, and flows out of the heat exchange channel through the liquid channel after condensing into liquid; and / or,
[0009] The liquid heat exchange medium flows into the heat exchange channel through the liquid channel, evaporates into a gaseous state and flows out of the heat exchange channel through the gas channel.
[0010] As an optional solution for the above-mentioned heat exchanger, the gas channel includes a plurality of gas pipes, and the liquid channel includes a plurality of liquid pipes, the plurality of gas pipes and the plurality of liquid pipes are all connected to the heat exchange flow channel, and the sum of the flow cross-sectional areas of the plurality of gas pipes is greater than the sum of the flow cross-sectional areas of the plurality of liquid pipes.
[0011] As an optional solution of the above heat exchanger, the flow cross-sectional area of the gas pipe is equal to the flow cross-sectional area of the liquid pipe, and the number of the gas pipes is greater than the number of the liquid pipes.
[0012] As an optional solution of the above heat exchanger, the height of the gas channel is higher than the height of the liquid channel.
[0013] As an optional scheme for the above-mentioned heat exchanger, the heat exchange channel includes a plurality of sub-channels, each of the sub-channels includes a gas port and a liquid port, all the gas ports of the plurality of sub-channels form the gas channel, all the liquid ports of the plurality of sub-channels form the liquid channel, the flow cross-sectional area of the gas ports of some of the sub-channels is equal to the flow cross-sectional area of the liquid ports, and the flow cross-sectional area of the gas ports of the remaining sub-channels is larger than the flow cross-sectional area of the liquid ports.
[0014] As an optional solution of the above heat exchanger, the height of the gas port of the same sub-channel is higher than the height of the liquid port.
[0015] As an optional solution of the above-mentioned heat exchanger, the heat exchange body includes a plurality of heat exchange tubes, and the plurality of heat exchange tubes are interconnected to form the heat exchange flow channel.
[0016] As an optional solution of the above-mentioned heat exchanger, the heat exchanger further includes an end plate, and the plurality of heat exchange tubes are passed through the end plate and fixedly connected to the end plate.
[0017] As an optional solution of the above heat exchanger, the heat exchanger further includes a tee and a cross-tube, the tee is connected to the two heat exchange tubes and one end of the cross-tube, and the other end of the cross-tube is connected to at least one other heat exchange tube.
[0018] As an optional solution for the above-mentioned heat exchanger, the heat exchange body also includes a plurality of fins arranged at intervals, and the plurality of heat exchange tubes are sequentially passed through the plurality of fins. Along the length direction of the heat exchange tubes, the heat exchange body is divided into a plurality of heat exchange areas. The greater the air flow rate in the heat exchange area, the smaller the spacing between the plurality of fins in the heat exchange area.
[0019] As an optional scheme for the above-mentioned heat exchanger, the heat exchange area includes a high wind area, a medium wind area and a low wind area in which the air flow rate decreases successively, the medium wind area is located on both sides of the high wind area, and the low wind area is located on the side of the medium wind area away from the high wind area.
[0020] As an optional solution of the above heat exchanger, the heat exchange area includes a high wind area, a medium wind area and a low wind area with decreasing air flow rates in sequence, and the fin spacing in the high wind area is 1.2 to 1.6 mm; and / or,
[0021] The fin spacing in the stroke area is 1.7 to 2.1 mm; and / or,
[0022] The fin spacing in the low wind area is 2.2 to 2.6 mm.
[0023] Beneficial effects of the utility model:
[0024] The utility model provides a heat exchanger. In the heat exchanger, the heat exchange body is used to exchange heat with the outside world. When a high-temperature and high-pressure gaseous heat exchange medium flows into the heat exchange flow channel through the gas channel, the heat is released into the external environment along with the heat exchange body, so that the gaseous heat exchange medium is condensed into a liquid state. Since the flow cross-sectional area of the gas channel is larger than the flow cross-sectional area of the liquid channel, although the volume of the heat exchange medium is reduced compared to the gas state, the flow cross-sectional area of the liquid channel is also smaller than the flow cross-sectional area of the gas channel, so that the liquid heat exchange medium can maintain a suitable flow rate, which can improve the heat transfer coefficient, so that the heat exchanger can have a good heat exchange effect. BRIEF DESCRIPTION OF THE DRAWINGS
[0025] Figure 1 This is a front view of the heat exchanger provided by the utility model;
[0026] Figure 2 It is a left side view of the heat exchanger provided by the utility model;
[0027] Figure 3 This is a schematic diagram of the structure of the heat exchange flow channel of the heat exchanger provided by the utility model Figure 1 ;
[0028] Figure 4 This is a schematic diagram of the structure of the heat exchange flow channel of the heat exchanger provided by the utility model Figure 2 ;
[0029] Figure 5 This is a schematic diagram of the structure of the heat exchange flow channel of the heat exchanger provided by the utility model Figure 3 ;
[0030] Figure 6 It is a structural schematic diagram of the heat exchanger provided by the utility model;
[0031] Figure 7 yes Figure 6 A partial enlarged view of point A in the middle.
[0032] In the figure:
[0033] 1. Heat exchange body; 2. End plate; 3. Cross-tube; 4. Tee pipe;
[0034] 11. Heat exchange flow channel; 12. Gas channel; 13. Liquid channel; 14. Heat exchange tube; 15. Fin; 16. U-shaped tube; 17. High wind area; 18. Medium wind area; 19. Low wind area;
[0035] 111, sub-channel; 112, gas port; 113, liquid port; 121, gas pipe; 131, liquid pipe. DETAILED DESCRIPTION
[0036] The embodiments of the present invention are described in detail below, and examples of the embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are intended to be used to explain the present invention, and should not be construed as limiting the present invention.
[0037] In the description of the present invention, it should be noted that the terms "center", "up", "down", "left", "right", "vertical", "horizontal", "inside", "outside" and the like indicate positions or positional relationships based on the positions or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present invention. In addition, the terms "first" and "second" are used for descriptive purposes only and cannot be understood as indicating or implying relative importance. Among them, the terms "first position" and "second position" are two different positions.
[0038] Unless otherwise clearly specified and limited, the terms "installed", "connected", "connected", and "fixed" should be understood in a broad sense, for example, it can be a fixed connection or a detachable connection; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, it can be the internal connection of two elements or the interaction relationship between two elements. For ordinary technicians in this field, the specific meanings of the above terms in this utility model can be understood according to specific circumstances.
[0039] Unless otherwise clearly specified and limited, a first feature being "above" or "below" a second feature may include the first feature being in direct contact with the second feature, or may include the first feature being in contact with the second feature through another feature between them instead of being in direct contact. Moreover, a first feature being "above", "above" and "above" a second feature includes the first feature being directly above and obliquely above the second feature, or simply indicates that the first feature is higher in level than the second feature. A first feature being "below", "below" and "below" a second feature includes the first feature being directly below and obliquely below the second feature, or simply indicates that the first feature is lower in level than the second feature.
[0040] The technical solution of the utility model is further explained below with reference to the accompanying drawings and through specific implementation methods.
[0041] As people's living standards gradually improve, they pay more and more attention to the quality of life. Air conditioners can bring coolness to the room in hot weather and have become an indispensable appliance in people's lives. The working principle of air conditioners is to absorb heat through the evaporation of heat exchange medium, and condense and release heat at the condenser. The heat is released to the outside through the condenser to achieve the purpose of cooling the room.
[0042] At present, the tubular heat exchangers commonly used in the air conditioning industry generally have the same number of inlets and outlets for heat exchange channels. In order to improve the heat exchange efficiency, it is necessary to increase the flow rate of the heat exchange medium in the heat exchange channel. However, when the heat exchanger is used as a condenser, the heat exchange medium is in a gaseous state when entering the condenser. After condensation, it first becomes a gas-liquid mixture, and then becomes a liquid and flows out of the heat exchanger. In this process, the volume of the heat exchange medium decreases, while the flow cross-sectional area of the heat exchange channel does not change, resulting in a decrease in the flow rate of the heat exchange medium, affecting the refrigeration efficiency.
[0043] To solve the above problems, this embodiment provides a heat exchanger, such as Figure 1 and Figure 2 As shown, the heat exchanger includes a heat exchange body 1, which has a heat exchange flow channel 11 and a gas channel 12 and a liquid channel 13 connected to the heat exchange flow channel 11. A heat exchange medium flows in the heat exchange flow channel 11, and the flow cross-sectional area of the gas channel 12 is larger than the flow cross-sectional area of the liquid channel 13. The gaseous heat exchange medium flows into the heat exchange flow channel 11 through the gas channel 12, and flows out of the heat exchange flow channel 11 through the liquid channel 13 after condensing into liquid.
[0044] In the heat exchanger, the heat exchange body 1 is used to exchange heat with the outside world. When the high-temperature and high-pressure gaseous heat exchange medium flows into the heat exchange flow channel 11 through the gas channel 12, the heat is released to the outside environment along with the heat exchange body 1, causing the gaseous heat exchange medium to condense into a liquid state. Since the flow cross-sectional area of the gas channel 12 is larger than the flow cross-sectional area of the liquid channel 13, although the volume of the heat exchange medium is reduced compared to the gas state, the flow cross-sectional area of the liquid channel 13 is also smaller than the flow cross-sectional area of the gas channel 12, so that the liquid heat exchange medium can maintain a suitable flow rate, which can improve the heat transfer coefficient and enable the heat exchanger to have a good heat exchange effect.
[0045] It is understandable that if the flow cross-sectional area of the gas channel 12 is too large and the flow cross-sectional area of the liquid channel 13 is too small, the flow rate of the liquid heat exchange medium will be too fast, which will increase the pressure drop of the heat exchange medium, thereby increasing the exhaust pressure of the compressor and increasing energy consumption. Therefore, the flow cross-sectional area of the gas channel 12 and the flow cross-sectional area of the liquid channel 13 need to be designed according to the actual situation, and the specific heat exchange medium circulation volume is calculated. Then, according to the relative position of the phase change of the heat exchange medium in the heat exchange flow channel 11, the appropriate ratio of the flow cross-sectional area of the gas channel 12 to the flow cross-sectional area of the liquid channel 13 is selected, so as to ensure a certain refrigerant flow rate without excessive pressure drop, thereby improving the heat exchange coefficient and saving energy consumption.
[0046] It is worth noting that in some embodiments, when the flow direction of the heat exchange medium of the heat exchanger is opposite, the liquid heat exchange medium flows into the heat exchange channel 11 through the liquid channel 13, evaporates into a gaseous state and then flows out of the heat exchange channel 11 through the gas channel 12. Then, the temperature of the heat exchange body 1 is relatively low and needs to absorb heat from the external environment. At this time, the heat exchanger is an evaporator.
[0047] It is understandable that in a conventional evaporator, the gas-liquid mixed state of the heat exchange medium eventually turns into a gaseous state. In this process, the volume of the heat exchange medium increases, while the flow cross-sectional area of the heat exchange flow channel 11 does not change, resulting in an increase in the flow rate of the heat exchange medium, which increases the pressure drop of the heat exchange medium, thereby increasing the output pressure of the compressor and increasing energy consumption. When the heat exchanger in this embodiment is used, since the flow cross-sectional area of the gas channel 12 is larger than the flow cross-sectional area of the liquid channel 13, the gaseous heat exchange medium can maintain a suitable flow rate, avoiding excessive increase in the pressure drop of the heat exchange medium, preventing the power of the compressor from increasing, and saving energy consumption.
[0048] In this embodiment, the heat exchanger is described by taking a condenser as an example, so at this time the gas channel 12 is the inlet and the liquid channel 13 is the outlet.
[0049] like Figure 1 As shown, the heat exchange body 1 includes a plurality of heat exchange tubes 14, which are connected to form a heat exchange flow channel 11. Specifically, the plurality of heat exchange tubes 14 are arranged in parallel and at intervals, and the ends of the heat exchange tubes 14 are connected through a U-shaped tube 16, wherein the plurality of heat exchange tubes 14 can be connected in series, in parallel, or connected into two non-connected passages. The plurality of heat exchange tubes 14 are connected in sequence through the U-shaped tube 16 to form an N-shaped heat exchange flow channel 11, which prolongs the flow path of the heat exchange medium and improves the heat exchange effect.
[0050] like Figure 3As shown, the heat exchange channel 11 includes a sub-channel 111, which has two gas ports 112 and one liquid port 113. The two gas ports 112 form a gas channel 12, and the one liquid port 113 forms a liquid channel 13. The gaseous heat exchange medium enters the sub-channel 111 from the two gas ports 112 and flows out from the liquid port 113 after being condensed into liquid.
[0051] In some embodiments, the heat exchange channel 11 may also include multiple sub-channels 111, each sub-channel 111 includes a gas port 112 and a liquid port 113, all the gas ports 112 of the multiple sub-channels 111 form a gas channel 12, all the liquid ports 113 of the multiple sub-channels 111 form a liquid channel 13, the flow cross-sectional area of the gas ports 112 of some sub-channels 111 is equal to the flow cross-sectional area of the liquid port 113, and the flow cross-sectional area of the gas ports 112 of the remaining sub-channels 111 is greater than the flow cross-sectional area of the liquid port 113.
[0052] like Figure 4 As shown, the heat exchange channel 11 includes two sub-channels 111, one of which includes two gas ports 112 and one liquid port 113, and the other sub-channel 111 includes one gas port 112 and one liquid port 113. It is worth noting that the sub-channel 111 with one gas port 112 and one liquid port 113 is shorter, so the volume change of the heat exchange medium in the sub-channel 111 is relatively small, thereby reducing the influence of the flow cross-sectional area at the liquid port 113 on the flow rate.
[0053] like Figure 5 As shown, the heat exchange channel 11 includes two sub-channels 111, and the two sub-channels 111 each include two gas ports 112 and one liquid port 113. The gaseous heat exchange medium enters one sub-channel 111 from the two gas ports 112, enters the other sub-channel 111 from the other two gas ports 112, and flows out through their respective liquid ports 113, and the two sub-channels 111 do not affect each other.
[0054] like Figure 1 and Figure 6 As shown, the heat exchanger further includes an end plate 2, and a plurality of heat exchange tubes 14 are passed through the end plate 2 and fixedly connected to the end plate 2. The end plate 2 is used to fix the plurality of heat exchange tubes 14 to ensure that the plurality of heat exchange tubes 14 remain stable with each other, reduce the vibration of the heat exchange tubes 14 when the gas flows through the heat exchange tubes 14, and reduce noise. Moreover, the end plate 2 can also serve as a fixed structure of the heat exchanger to ensure the stability of the heat exchanger in the air conditioner.
[0055] Furthermore, the heat exchanger further includes a tee pipe 4 and a cross pipe 3, wherein the tee pipe 4 is connected to two heat exchange pipes 14 and one end of the cross pipe 3, and the other end of the cross pipe 3 is connected to at least one other heat exchange pipe 14. The tee pipe 4 and the cross pipe 3 can connect the heat exchange pipes 14 corresponding to the two gas ports 112 with another heat exchange pipe 14, so that the heat exchange medium in the gas-liquid mixed state merges, for example, the gaseous heat exchange medium entering the two gas ports 112 merges and condenses into a liquid state, and then flows out from a liquid port 113.
[0056] In this embodiment, the gas channel 12 includes a plurality of gas pipes 121, and the liquid channel 13 includes a plurality of liquid pipes 131. The plurality of gas pipes 121 and the plurality of liquid pipes 131 are both connected to the heat exchange channel 11, and the sum of the flow cross-sectional areas of the plurality of gas pipes 121 is greater than the sum of the flow cross-sectional areas of the plurality of liquid pipes 131.
[0057] The heat exchange medium enters the heat exchange channel 11 through multiple gas pipes 121 and flows out through multiple liquid pipes 131 after condensation. Therefore, it is only necessary to ensure that the sum of the flow cross-sectional areas of the multiple gas pipes 121 is greater than the sum of the flow cross-sectional areas of the multiple liquid pipes 131 to ensure that the liquid heat exchange medium can maintain a suitable flow rate, improve the heat transfer coefficient, and enable the heat exchanger to have a good heat exchange effect.
[0058] It is worth noting that, for the sub-channel 111 , the gas pipe 121 is connected to the gas port 112 , and the liquid pipe 131 is connected to the liquid port 113 .
[0059] To achieve the above purpose, the flow cross-sectional area of the gas pipe 121 is equal to the flow cross-sectional area of the liquid pipe 131, and the number of the gas pipes 121 is greater than the number of the liquid pipes 131. Since the specifications of the heat exchange tubes 14 are the same, generally speaking, the gas pipes 121 and the liquid pipes 131 need to be adapted to the heat exchange tubes 14, and the flow cross-sectional areas of the two are also the same, which is convenient for assembly.
[0060] In some embodiments, a gas pipe 121 with a larger flow cross-sectional area may also be used, and accordingly, the end of the heat exchange tube 14 connected to the gas pipe 121 also needs to have a larger flow cross-sectional area, otherwise the flow rate of the gaseous heat exchange medium will increase when entering the heat exchange tube 14, which will in turn increase the flow rate difference between the gaseous heat exchange medium and the liquid heat exchange medium in the heat exchange flow channel 11. A gas pipe 121 with a large area may also be used, and a larger number of gas pipes 121 may be provided to achieve the above purpose.
[0061] In this embodiment, the height of the gas channel 12 is higher than the height of the liquid channel 13. It can be understood that the density of the gaseous heat exchange medium is small, and the density of the liquid heat exchange medium is large. When the heat exchange medium is condensed, it will flow downward under the action of gravity. The height of the gas channel 12 is higher than the height of the liquid channel 13, which conforms to the natural flow direction of the cooling medium, facilitates the flow of the cooling medium, and reduces the load of the compressor.
[0062] It can be understood that if the heat exchange channel 11 includes a plurality of sub-channels 111 , the height of the gas port 112 of the same sub-channel 111 is higher than the height of the liquid port 113 .
[0063] In order to improve the heat dissipation efficiency of the condenser, most air conditioners are also equipped with a fan. When the fan is started, it can accelerate the flow rate of the gas through the heat exchanger, thereby quickly taking away the heat from the condenser.
[0064] like Figure 1 and Figure 6 As shown, the heat exchange body 1 further includes a plurality of fins 15 arranged at intervals, and a plurality of heat exchange tubes 14 are sequentially passed through the plurality of fins 15. At the junction of the fins 15 and the heat exchange tubes 14, the heat of the heat exchange tubes 14 can be transferred to the fins 15, and the structure of the fins 15 greatly increases the heat exchange area. When the gas flows through the gaps between adjacent fins 15, it can fully exchange heat with the fins 15 to ensure the heat exchange efficiency.
[0065] However, when the fan is started, the flow speed of the gas along the length of the heat exchange tube 14 is not exactly the same, and is limited by the internal structure of the air conditioner, the flow speed varies greatly. This results in insufficient heat exchange in areas with fast flow rates, and insufficient heat exchange in areas with slow flow rates due to the small amount of heat carried by the gas, thereby affecting the overall heat dissipation efficiency of the condenser.
[0066] like Figure 1 , Figure 6 and Figure 7 As shown, in order to solve the above problem, the heat exchange body 1 is divided into a plurality of heat exchange areas along the length direction of the heat exchange tube 14. The greater the air velocity in the heat exchange area, the smaller the spacing between the plurality of fins 15 in the heat exchange area. Reducing the spacing between the fins 15 in the area with a large air velocity is equivalent to increasing the heat exchange area in the area, thereby achieving sufficient heat exchange, while increasing the spacing between the fins 15 in the area with a small air velocity, although reducing the heat exchange area, can also meet the heat dissipation requirements, so that the condenser as a whole is in a relatively uniform heat dissipation state, improving the comprehensive heat exchange efficiency and reducing energy consumption.
[0067] like Figure 1 , Figure 6 and Figure 7As shown, the heat exchange body 1 can be divided into three heat exchange areas according to the flow rate, namely, the high wind area 17, the medium wind area 18 and the low wind area 19, and the fin spacing is also divided into three schemes, wherein the fin spacing of the high wind area 17 is 1.2-1.6mm, and the fins 15 are densely spaced; the fin spacing of the medium wind area 18 is 1.7-2.1mm, which is a regular fin spacing; the fin spacing of the low wind area 19 is 2.2-2.6mm, and the fin spacing is sparse.
[0068] Specifically, the fin spacing in the high wind area 17 can be 1.2mm, 1.3mm, 1.4mm, 1.5mm or 1.6mm, the fin spacing in the medium wind area 18 can be 1.7mm, 1.8mm, 1.9mm, 2.0mm or 2.1mm, and the fin spacing in the low wind area 19 can be 2.2mm, 2.3mm, 2.4mm, 2.5mm or 2.6mm.
[0069] In this embodiment, the middle position of the heat exchange body 1 is a low wind area 19, and the low wind area 19 is followed by the medium wind area 18 and the high wind area 17, that is, the medium wind area 18 is located on both sides of the high wind area 17, and the low wind area 19 is located on the side of the medium wind area 18 away from the high wind area 17. In some embodiments, the flow rate of the gas does not change continuously, and may be the lowest in the middle, the highest outward, and the lowest outward, or the lowest in the middle, the highest outward, and the second highest outward.
[0070] The above contents are only preferred embodiments of the present invention. For ordinary technicians in this field, according to the concept of the present invention, there will be changes in the specific implementation methods and application scopes. The contents of this specification should not be understood as limiting the present invention.
Claims
1. A heat exchanger, characterized in that: include: A heat exchange body (1), the heat exchange body (1) comprising a heat exchange channel (11) and a gas channel (12) and a liquid channel (13) connected to the heat exchange channel (11), a heat exchange medium flowing in the heat exchange channel (11), and a flow cross-sectional area of the gas channel (12) being greater than a flow cross-sectional area of the liquid channel (13); The gaseous heat exchange medium flows into the heat exchange channel (11) through the gas channel (12), condenses into a liquid state, and then flows out of the heat exchange channel (11) through the liquid channel (13); or, The liquid heat exchange medium flows into the heat exchange channel (11) through the liquid channel (13), evaporates into a gaseous state, and then flows out of the heat exchange channel (11) through the gas channel (12).
2. The heat exchanger according to claim 1, characterized in that: The gas channel (12) includes a plurality of gas pipes (121), and the liquid channel (13) includes a plurality of liquid pipes (131). The plurality of gas pipes (121) and the plurality of liquid pipes (131) are both connected to the heat exchange flow channel (11), and the sum of the flow cross-sectional areas of the plurality of gas pipes (121) is greater than the sum of the flow cross-sectional areas of the plurality of liquid pipes (131).
3. The heat exchanger according to claim 2, characterized in that: The flow cross-sectional area of the gas tube (121) is equal to the flow cross-sectional area of the liquid tube (131), and the number of the gas tubes (121) is greater than the number of the liquid tubes (131).
4. The heat exchanger according to claim 1, characterized in that: The height of the gas channel (12) is higher than the height of the liquid channel (13).
5. The heat exchanger according to claim 1, characterized in that: The heat exchange flow channel (11) comprises a plurality of sub-flow channels (111), each of the sub-flow channels (111) comprises a gas port (112) and a liquid port (113), all of the gas ports (112) of the plurality of sub-flow channels (111) form the gas channel (12), and all of the liquid ports (113) of the plurality of sub-flow channels (111) form the liquid channel (13), the flow cross-sectional area of the gas ports (112) of some of the sub-flow channels (111) is equal to the flow cross-sectional area of the liquid ports (113), and the flow cross-sectional area of the gas ports (112) of the remaining sub-flow channels (111) is greater than the flow cross-sectional area of the liquid ports (113).
6. The heat exchanger according to claim 5, characterized in that The height of the gas port (112) of the same sub-channel (111) is higher than the height of the liquid port (113).
7. The heat exchanger according to any one of claims 1 to 6, characterized in that: The heat exchange body (1) comprises a plurality of heat exchange tubes (14), and the plurality of heat exchange tubes (14) are connected to form the heat exchange flow channel (11).
8. The heat exchanger according to claim 7, characterized in that The heat exchanger further comprises an end plate (2), and a plurality of heat exchange tubes (14) are passed through the end plate (2) and fixedly connected to the end plate (2).
9. The heat exchanger according to claim 8, characterized in that The heat exchanger further comprises a tee pipe (4) and a cross pipe (3); the tee pipe (4) is connected to the two heat exchange pipes (14) and one end of the cross pipe (3); the other end of the cross pipe (3) is connected to at least one other heat exchange pipe (14).
10. The heat exchanger according to claim 7, characterized in that The heat exchange body (1) further comprises a plurality of fins (15) arranged at intervals, and the plurality of heat exchange tubes (14) are sequentially passed through the plurality of fins (15). Along the length direction of the heat exchange tubes (14), the heat exchange body (1) is divided into a plurality of heat exchange areas. The greater the air flow rate in the heat exchange area, the smaller the spacing between the plurality of fins (15) in the heat exchange area.
11. The heat exchanger according to claim 10, characterized in that The heat exchange area comprises a high wind area (17), a medium wind area (18) and a low wind area (19) in which the air flow rates decrease successively, the medium wind area (18) being located on both sides of the high wind area (17), and the low wind area (19) being located on a side of the medium wind area (18) away from the high wind area (17).
12. The heat exchanger according to claim 10, characterized in that The heat exchange area comprises a high wind area (17), a medium wind area (18) and a low wind area (19) in which the air flow rate decreases successively, and the fin spacing of the high wind area (17) is 1.2 to 1.6 mm; and / or, The fin spacing of the stroke area (18) is 1.7 to 2.1 mm; and / or, The fin spacing in the low wind area (19) is 2.2-2.6 mm.