Heat exchanger and air conditioner

Abstract

The utility model relates to the technical field of air conditioning, and discloses a heat exchanger and an air conditioner. The heat exchanger comprises a heat exchange tube set, the first end of the heat exchange tube set is suitable for being communicated with the compressor, the second end of the heat exchange tube set is suitable for being communicated with the throttling device, the heat exchange tube set comprises a plurality of heat exchange channels, and the heat exchange channels are communicated between the first end of the heat exchange tube set and the second end of the heat exchange tube set; each dehumidification valve is arranged between every two adjacent heat exchange channels, and the dehumidification valves can conduct throttling on refrigerants so that the temperature of the refrigerants on the downstream portions of the dehumidification valves can be lower than the temperature of the refrigerants on the upstream portions of the dehumidification valves; the number of the dehumidification valves is multiple, and the multiple dehumidification valves can be arranged in series. And the dehumidification valves in the heat exchange tube group can be throttled for multiple times, so that the number of different temperature intervals of the heat exchanger is further increased, the diversity of dehumidification and temperature adjustment can be improved, and the use experience of a user is improved.

Description

Technical Field

[0001] The present application relates to the technical field of air conditioning, for example, to a heat exchanger and an air conditioner. Background Art

[0002] At present, household air conditioners have been popularized in China. They are used for refrigeration and dehumidification in summer and heating in winter. The dehumidification technology makes the air conditioner operate in the refrigeration mode, and at the same time, the indoor fan maintains a low gear. At this time, the indoor evaporator cools the indoor air to reach the dew point and then condenses water, so as to achieve the purpose of dehumidification.

[0003] In the related art, constant temperature dehumidification is generally used for dehumidification, that is, the process of reheating the air cooled by the evaporator, so that the temperature of the dehumidified air is raised again to ensure the relative stability of the indoor air temperature.

[0004] In the process of implementing the embodiments of the present disclosure, it is found that at least the following problems exist in the related art:

[0005] In different scenarios, the specific dehumidification requirements of users are also different. During the southward return of warm moist air, the temperature is not high but the humidity is very high, and users have a greater demand for heating and dehumidification. During the plum rain season, the temperature is suitable and the humidity is relatively high, and constant temperature dehumidification can meet the requirements. The constant temperature dehumidification function in the related art is relatively single and cannot meet the usage requirements of various user scenarios.

[0006] It should be noted that the information disclosed in the above background art section is only used to enhance the understanding of the background of the present application, and therefore may include information that does not constitute the prior art known to those of ordinary skill in the art. Utility Model Content

[0007] To have a basic understanding of some aspects of the disclosed embodiments, a simple summary is given below. The summary is not a general review, nor is it intended to identify key / important constituent elements or delineate the protection scope of these embodiments, but rather serves as a preface to the following detailed description.

[0008] The embodiments of the present disclosure provide a heat exchanger and an air conditioner to improve the usage diversity of the air conditioner and meet various user scenarios.

[0009] The embodiments of the present disclosure provide a heat exchanger. The heat exchanger includes: a heat exchange tube group, the first end of the heat exchange tube group is adapted to communicate with a compressor, the second end of the heat exchange tube group is adapted to communicate with a throttling device, the heat exchange tube group includes a plurality of heat exchange channels, and the plurality of heat exchange channels communicate between the first end and the second end of the heat exchange tube group; a dehumidification valve is provided between two adjacent heat exchange channels, and the dehumidification valve can throttle the refrigerant so that the temperature of the refrigerant downstream of the dehumidification valve is lower than the temperature of the refrigerant upstream of the dehumidification valve; wherein, the number of the dehumidification valves is multiple, and the multiple dehumidification valves can be arranged in series.

[0010] Optionally, a plurality of dehumidification valves and a plurality of heat exchange channels are alternately arranged at intervals in sequence.

[0011] Optionally, the plurality of dehumidification valves include: a first dehumidification valve, the distance between the first dehumidification valve and the first end of the heat exchange tube group is less than the distance between the first dehumidification valve and the second end of the heat exchange tube group; a second dehumidification valve, the distance between the second dehumidification valve and the first end of the heat exchange tube group is greater than the distance between the second dehumidification valve and the second end of the heat exchange tube group; wherein, the first dehumidification valve and the second dehumidification valve can be connected in series between the first end and the second end of the heat exchange tube group.

[0012] Optionally, when the dehumidification valve includes a capillary tube, the first dehumidification valve includes a first capillary tube, the second dehumidification valve includes a second capillary tube, and the length of the first capillary tube is greater than the length of the second capillary tube.

[0013] Optionally, when the dehumidification valve includes an electronic expansion valve, the first dehumidification valve includes a first electronic expansion valve, the second dehumidification valve includes a second electronic expansion valve, and the opening degree of the first electronic expansion valve is less than the opening degree of the second electronic expansion valve.

[0014] Optionally, when the dehumidification valve includes a capillary tube, the dehumidification valve includes a first bypass pipeline and a first solenoid valve, the first bypass pipeline is connected in parallel with the capillary tube, and the first solenoid valve is arranged on the first bypass pipeline; or, when the dehumidification valve includes an electronic expansion valve, the dehumidification valve includes a second bypass pipeline and a second solenoid valve, the second bypass pipeline is connected in parallel with the electronic expansion valve, and the second solenoid valve is arranged on the second bypass pipeline.

[0015] Optionally, the plurality of heat exchange channels include: a first heat exchange channel, the first end is adapted to be connected to a compressor; a second heat exchange channel, the second end is connected to the second end of the first heat exchange channel; a third heat exchange channel, the first end is connected to the first end of the second heat exchange channel, and the second end of the third heat exchange channel is adapted to be connected to a throttling device; the heat exchange tube group further includes: a second pipeline, the first end is connected to the first end of the second heat exchange channel, and the second end is connected to the first end of the third heat exchange channel; a fourth pipeline, connected between the second end of the first heat exchange channel and the second end of the second heat exchange channel; wherein, the first dehumidification valve is arranged on the fourth pipeline, and the second dehumidification valve is arranged on the second pipeline.

[0016] Optionally, the heat exchange tube group further includes: a first pipeline, the first end of which is adapted to communicate with the compressor, and the second end of which communicates with the first ends of the first heat exchange channel and the second heat exchange channel; a second pipeline, the first end of which communicates with the second end of the first pipeline and the first end of the second heat exchange channel; a diverter, the first end of which communicates with the second ends of the first heat exchange channel and the second heat exchange channel, and the second end of the diverter and the second end of the third heat exchange channel are both adapted to communicate with the throttling device; a third pipeline, adapted to communicate between the second end of the diverter and the throttling device; a flow splitting assembly, including a first valve and a second valve, the first valve is disposed on the first pipeline and is defined to be conductive when flowing from the first end of the second heat exchange channel towards the first end of the first heat exchange channel; the second valve is disposed on the third pipeline and is defined to be conductive when flowing from the throttling device towards the liquid separator; wherein, when the refrigerant flows from the first end of the first heat exchange tube group to the second end of the first heat exchange tube group, both the first valve and the second valve are closed, and the first heat exchange channel, the second heat exchange channel and the third heat exchange channel are connected in series; when the refrigerant flows from the second end of the heat exchange tube group to the first end of the heat exchange tube group, both the first valve and the second valve are conductive, and the first heat exchange channel, the second heat exchange channel and the third heat exchange channel are arranged in parallel.

[0017] An embodiment of the present disclosure further provides an air conditioner, which is characterized in that the air conditioner includes a heat exchanger as described in any one of the above embodiments.

[0018] Optionally, the air conditioner further includes an indoor unit, and the indoor unit further includes: a housing that defines a receiving cavity having an air inlet and an air outlet, and the heat exchanger is located in the receiving cavity; a fan, located in the receiving cavity, and the fan can drive the air flow to flow through the first heat exchange channel, the second heat exchange channel and the third heat exchange channel in sequence.

[0019] The heat exchanger and the air conditioner provided by the embodiments of the present disclosure can achieve the following technical effects:

[0020] In the embodiments of the present disclosure, a dehumidification valve is provided between two adjacent heat exchange channels. In this way, the dehumidification valve can throttle the flowing refrigerant so that the temperature of the refrigerant downstream of the dehumidification valve is lower than that of the refrigerant upstream of the dehumidification valve. In this way, the heat exchanger can be divided into multiple different temperature intervals for dehumidification. A plurality of dehumidification valves are provided, and the plurality of dehumidification valves can be connected in series. In this way, the dehumidification valves in the heat exchange tube group can be throttled multiple times, further increasing the number of different temperature intervals of the heat exchanger, improving the diversity of dehumidification and temperature regulation, and improving the user experience.

[0021] The above general description and the following description are only exemplary and explanatory, and are not used to limit the present application. Description of the Drawings

[0022] One or more embodiments are exemplarily illustrated by corresponding drawings. These exemplary illustrations and the drawings do not constitute a limitation on the embodiments. Elements with the same reference numerals in the drawings are shown as similar elements. The drawings do not constitute a scale limitation, and wherein:

[0023] Figure 1 is a schematic structural diagram of a heat exchanger provided by an embodiment of the present disclosure;

[0024] Figure 2 is a schematic diagram of the refrigerant flow when the refrigerant of a heat exchanger provided by an embodiment of the present disclosure flows from the first end of the first heat exchange tube group to the second end of the first heat exchange tube group;

[0025] Figure 3 is a schematic diagram of the refrigerant flow when the refrigerant of a heat exchanger provided by an embodiment of the present disclosure flows from the second end of the first heat exchange tube group to the first end of the first heat exchange tube group;

[0026] Figure 4 is a schematic structural diagram of another heat exchanger provided by an embodiment of the present disclosure;

[0027] Figure 5 is a schematic diagram of the refrigerant flow when the refrigerant of another heat exchanger provided by an embodiment of the present disclosure flows from the first end of the first heat exchange tube group to the second end of the first heat exchange tube group;

[0028] Figure 6 is a schematic diagram of the refrigerant flow when the refrigerant of another heat exchanger provided by an embodiment of the present disclosure flows from the second end of the first heat exchange tube group to the first end of the first heat exchange tube group;

[0029] Figure 7 is a schematic structural diagram of another heat exchanger provided by an embodiment of the present disclosure;

[0030] Figure 8 is a schematic structural diagram of another heat exchanger provided by an embodiment of the present disclosure.

[0031] Reference numerals:

[0032] 10. First heat exchange tube group; 101. First heat exchange channel; 102. Second heat exchange channel; 103. Third heat exchange channel; 104. First pipeline; 105. Second pipeline; 106. Third pipeline; 107. Fourth pipeline; 201. First dehumidification valve; 202. Second dehumidification valve; 203. Third dehumidification valve; 30. Shunt; 301. First valve; 302. Second valve; 40. Second heat exchange tube group; 401. Fourth heat exchange channel; 402. Connecting pipeline; 50. Throttling device; 60. Liquid storage tank; 70. Gas-liquid separator. Detailed implementation manners

[0033] In order to understand the features and technical content of the embodiments of the present disclosure in more detail, the implementation of the embodiments of the present disclosure will be described in detail below with reference to the accompanying drawings. The attached drawings are for reference and illustration only and are not intended to limit the embodiments of the present disclosure. In the following technical description, for the sake of explanation, numerous details are provided to provide a thorough understanding of the disclosed embodiments. However, one or more embodiments may still be implemented without these details. In other cases, well-known structures and devices may be shown in a simplified manner to simplify the drawings.

[0034] In the specification, claims and above-mentioned drawings of the embodiments of the present disclosure, terms such as "first", "second", etc. are used to distinguish similar objects and do not necessarily have to be used to describe a specific order or sequence. It should be understood that the data used in this way can be interchanged under appropriate circumstances so as to describe the embodiments of the present disclosure here. In addition, the terms "comprising" and "having" and any variations thereof are intended to cover non-exclusive inclusion.

[0035] In the embodiments of the present disclosure, the orientation or positional relationship indicated by terms such as "upper", "lower", "inner", "middle", "outer", "front", "rear", etc. is based on the orientation or positional relationship shown in the drawings. These terms are mainly used to better describe the embodiments of the present disclosure and their embodiments, and are not used to limit that the indicated devices, elements or components must have a specific orientation or be constructed and operated in a specific orientation. And, in addition to being able to represent an orientation or positional relationship, some of the above terms may also be used to represent other meanings. For example, the term "upper" may also be used to represent a certain attachment relationship or connection relationship in some cases. For those of ordinary skill in the art, the specific meanings of these terms in the embodiments of the present disclosure can be understood according to specific circumstances.

[0036] In addition, the terms "arranged", "connected", "fixed" should be understood in a broad sense. For example, "connected" can be a fixed connection, a detachable connection, or an integral structure; it can be a mechanical connection or an electrical connection; it can be directly connected, or indirectly connected through an intermediate medium, or there can be internal communication between two devices, elements or components. For those of ordinary skill in the art, the specific meanings of the above terms in the embodiments of the present disclosure can be understood according to specific circumstances.

[0037] Unless otherwise specified, the term "plurality" means two or more.

[0038] The term "and / or" is a description of the associated relationship of an object, indicating that three relationships can exist. For example, A and / or B means: A or B, or, A and B these three relationships.

[0039] It should be noted that, without conflict, the embodiments and features in the embodiments of the present disclosure can be combined with each other.

[0040] For ease of description, the temperature of the refrigerant in the solid arrow in the accompanying drawings is higher than the temperature of the refrigerant in the dashed arrow.

[0041] Combined with Figures 1 to 8 As shown, an embodiment of the present disclosure provides an air conditioner, which includes a refrigerant circulation circuit. The refrigerant circulation circuit includes a compressor, an indoor unit, a throttling device 50, and an outdoor unit connected through refrigerant pipelines. The refrigerant circulation circuit further includes a four-way valve, which can switch the flow direction of the refrigerant in the refrigerant circulation circuit. When the air conditioner is heating, the high-temperature and high-pressure refrigerant flowing out of the compressor flows into the indoor heat exchanger of the indoor unit through the four-way valve. After condensing and dissipating heat in the outdoor heat exchanger, it then flows from the indoor heat exchanger to the throttling device 50 for throttling, and then flows into the outdoor heat exchanger of the outdoor unit. When the air conditioner is cooling, the high-temperature and high-pressure refrigerant flowing out of the compressor flows into the outdoor heat exchanger of the outdoor unit through the four-way valve, and then after flowing out of the outdoor heat exchanger and passing through the throttling device 50 for throttling, it flows into the outdoor heat exchanger of the indoor unit for evaporative cooling.

[0042] Optionally, the throttling device 50 is an electronic expansion valve or a capillary tube, etc.

[0043] An embodiment of the present disclosure provides a heat exchanger, which includes a heat exchange tube group. The heat exchange tube group includes a plurality of heat exchange channels, and the plurality of heat exchange channels form a heat exchange tube group (for ease of distinction, hereinafter collectively referred to as the first heat exchange tube group 10). The first heat exchange tube group 10 includes a plurality of heat exchange channels. The first end of the first heat exchange tube group 10 is adapted to be connected to the compressor, and the second end of the first heat exchange tube group 10 is adapted to be connected to the throttling device 50. The plurality of heat exchange channels are connected between the first end and the second end of the first heat exchange tube group 10.

[0044] In an embodiment of the present disclosure, the plurality of heat exchange channels are connected between the first end and the second section of the first heat exchange tube group 10. The heat exchange channels include fins and refrigerant pipelines. When the refrigerant flows into the heat exchange channels, heat exchange can be achieved through the fins to realize refrigeration or heating.

[0045] Optionally, the heat exchanger is an indoor heat exchanger or an outdoor heat exchanger.

[0046] Optionally, the heat exchanger further includes a dehumidification valve, which is arranged in the heat exchange channel or between two adjacent heat exchange channels. The dehumidification valve can throttle the refrigerant so that the temperature of the refrigerant downstream of the dehumidification valve is lower than the temperature of the refrigerant upstream of the dehumidification valve.

[0047] In an embodiment of the present disclosure, a dehumidification valve is provided inside the heat exchanger. The dehumidification valve is located between adjacent heat exchange channels or inside the heat exchange channels. The dehumidification valve has a throttling effect. After the refrigerant passes through the throttling of the dehumidification valve, the temperature is further reduced. In this way, the temperature of the refrigerant downstream of the dehumidification valve is lower than that of the refrigerant upstream of the dehumidification valve. Thus, the downstream of the dehumidification valve can be used for dehumidification, and then the heat exchanger has a dehumidification function. The upstream of the dehumidification valve can be a reheating condensation section or a refrigeration section.

[0048] Optionally, when the refrigerant flows from the first end of the first heat exchange tube group 10 to the second end of the first heat exchange tube group 10, a condensation and reheating section is formed between the dehumidification valve and the first end of the heat exchanger, and a dehumidification section is formed between the dehumidification valve and the second end of the heat exchanger; wherein, the area of the condensation and reheating section is greater than the area of the dehumidification section, or the area of the condensation and reheating section is less than the area of the dehumidification section.

[0049] In an embodiment of the present disclosure, when the refrigerant flows from the first end of the first heat exchange tube group 10 to the second end of the first heat exchange tube group 10, the high-temperature and high-pressure refrigerant flowing out of the compressor flows into the first heat exchange tube group 10 through the first end of the first heat exchange tube group 10. After passing through the throttling of the dehumidification valve, the temperature is reduced. In this way, the heat exchange channel between the dehumidification valve and the first end of the first heat exchange tube group 10 forms a condensation and reheating section, and the heat exchange channel between the dehumidification valve and the second end of the first heat exchange tube group 10 forms a dehumidification section. In this way, the air flow of the indoor unit first flows through the condensation and reheating section to be heated, and then flows through the dehumidification section to be cooled and dehumidified. When the indoor temperature needs to be moderately heated but the humidity is high, the air flow flows through the condensation and reheating section to be heated and then flows through the dehumidification section, so that dehumidification can be achieved and the temperature can be kept constant. The air flow of the indoor unit can also first flow through the dehumidification section to be dehumidified, and then flow through the condensation and reheating section to be heated, so as to achieve constant-temperature dehumidification. Among them, the area of the condensation and reheating section is greater than the area of the dehumidification section, so the heating range is larger, which is suitable for environments with lower humidity. The area of the condensation and reheating section can also be less than the area of the dehumidification section, which is suitable for environments with higher humidity. In this way, the heat exchanger at different positions of the dehumidification valve can be selected according to different use environments, and then different dehumidification effects can be achieved.

[0050] Optionally, the ratio range of the area of the condensation and reheating section to the area of the heat exchanger is 1 / 3 - 3 / 4.

[0051] In the embodiments of the present disclosure, when the ratio of the area of the condensation and reheating section to the area of the heat exchanger is less than 1 / 3, the area of the condensation and reheating section is too small, which may cause incomplete condensation of the refrigerant. When passing through the dehumidification valve, it is in a two-phase state, and the two-phase cold impact on the valve core results in very loud noise, large throttling energy loss, and it will also affect the normal operation of the refrigerant circuit. When the ratio of the area of the condensation and reheating section to the area of the heat exchanger is greater than 3 / 4, the area of the dehumidification section is too small, and the dehumidification effect is not obvious. The ratio range of the area of the condensation and reheating section to the area of the heat exchanger is 1 / 3 - 3 / 4, which can ensure sufficient condensation of the refrigerant, and the refrigerant completely becomes liquid, even in a subcooled state, which is beneficial to dehumidification and has low noise.

[0052] Optionally, the ratio range of the area of the condensation and reheating section to the area of the heat exchanger is 1 / 3 - 2 / 3.

[0053] In the embodiments of the present disclosure, when the ratio of the area of the condensation and reheating section to the area of the heat exchanger is further reduced within the range of 1 / 3 - 2 / 3, it can ensure the flow uniformity of the refrigerant in the heat exchanger, and maximize the efficiency of ensuring the sufficient condensation of the refrigerant and the dehumidification effect of the dehumidification section.

[0054] Exemplarily, the ratio of the area of the condensation and reheating section to the area of the heat exchanger is 1 / 3, 1 / 2, 2 / 3, or 3 / 4, etc.

[0055] Optionally, as Figures 1 to 3 shown, the number of dehumidification valves is multiple, and the multiple dehumidification valves can be arranged in series.

[0056] In the embodiments of the present disclosure, multiple dehumidification valves are provided and can be arranged in series. In this way, the dehumidification valves in the first heat exchange tube group 10 can be throttled multiple times, further increasing the number of different temperature intervals of the heat exchanger, and improving the diversity and width of dehumidification and temperature adjustment, thus enhancing the user experience.

[0057] Optionally, the multiple dehumidification valves and the multiple heat exchange channels are alternately arranged at intervals.

[0058] In the embodiments of the present disclosure, when there are multiple dehumidification valves, the dehumidification valves and the heat exchange channels can be alternately arranged at intervals. In this way, different heat exchange channels can form different temperatures, further increasing the temperature intervals and temperature ranges.

[0059] Optionally, the multiple dehumidification valves include a first dehumidification valve and a second dehumidification valve. The distance between the first dehumidification valve and the first end of the heat exchange tube group is less than the distance between the first dehumidification valve and the second end of the heat exchange tube group; the distance between the second dehumidification valve and the first end of the heat exchange tube group is greater than the distance between the second dehumidification valve and the second end of the heat exchange tube group; wherein, the first dehumidification valve and the second dehumidification valve can be connected in series between the first end and the second end of the heat exchange tube group.

[0060] In the embodiments of the present disclosure, the first dehumidification valve is close to the first end of the heat exchange tube group, and the second dehumidification valve is close to the second end of the first heat exchange tube group, so that the front and rear parts of the heat exchanger can be throttled respectively to improve the uniformity of the refrigerant temperature distribution.

[0061] Optionally, when there are multiple dehumidification valves, the condensation reheating section refers to the part between the dehumidification valve closest to the compressor and the first end of the first heat exchange tube group, and the dehumidification section refers to the part between the dehumidification valve closest to the compressor and the second end of the first heat exchange tube group.

[0062] Optionally, the first heat exchange tube group 10 further includes a flow splitting assembly. The flow splitting assembly is located inside the first heat exchange tube group 10. When the refrigerant flows from the first end of the first heat exchange tube group 10 to the second end of the first heat exchange tube group 10, multiple heat exchange channels are arranged in series. When the refrigerant flows from the second end of the first heat exchange tube group 10 to the first end of the first heat exchange tube group 10, multiple heat exchange channels are arranged in parallel.

[0063] In the embodiments of the present disclosure, the flow splitting assembly makes the refrigerant flow paths different when the heat exchanger switches between refrigeration and heating. In this way, when the refrigerant flows from the second end of the first heat exchange tube group 10 to the first end of the first heat exchange tube group 10, the refrigerant flows through more branches, which can effectively reduce the frictional pressure drop of the refrigerant and improve the heat exchange efficiency. When the refrigerant flows from the first end of the first heat exchange tube group 10 to the second end of the first heat exchange tube group 10, the flow path of the refrigerant becomes longer, the flow branches become shorter, the flow speed increases, and the cycle is improved, increasing the heat transfer coefficient on the inner side of the tube and improving the heat exchange efficiency.

[0064] In addition, through the flow splitting assembly and the dehumidification valve, while the heat exchanger has a dehumidification function, the heat exchange efficiency can be improved, thereby improving the energy efficiency of the air conditioner.

[0065] Optionally, the number of multiple heat exchange channels can be three, four, five or six, and can be set according to the size of the heat exchanger.

[0066] Optionally, the multiple heat exchange channels include a first heat exchange channel 101, a second heat exchange channel 102 and a third heat exchange channel 103. When the refrigerant flows from the first end of the first heat exchange tube group 10 to the second end of the first heat exchange tube group 10, along the flow direction of the refrigerant, the first heat exchange channel 101, the second heat exchange channel 102 and the third heat exchange channel 103 are connected in series in sequence; when the refrigerant flows from the second end of the first heat exchange tube group 10 to the first end of the first heat exchange tube group 10, the first heat exchange channel 101, the second heat exchange channel 102 and the third heat exchange channel 103 are connected in parallel between the first end and the second end of the first heat exchange tube group 10.

[0067] In the embodiments of the present disclosure, the three heat exchange channels of the heat exchanger can achieve variable flow distribution during refrigeration and heating. When the refrigerant flows from the first end of the first heat exchange tube group 10 to the second end of the first heat exchange tube group 10, the high-temperature and high-pressure refrigerant at the first end of the first heat exchange tube group 10 sequentially flows through the first heat exchange channel 101, the second heat exchange channel 102, and the third heat exchange channel 103 connected in series and then flows out from the second end of the first heat exchange tube group 10. In this way, the flow rate can be increased, the circulation can be improved, the heat transfer coefficient inside the tube can be increased, and the heat transfer efficiency can be improved. When the refrigerant flows from the second end of the first heat exchange tube group 10 to the first end, the low-temperature refrigerant flowing into the second end of the first heat exchange tube group 10 flows to the three heat exchange channels respectively, and the three heat exchange channels are arranged in parallel. In this way, the flow branches can be increased, the frictional pressure drop of the refrigerant can be effectively reduced, and the heat transfer efficiency can be improved.

[0068] Optionally, when the first heat exchange channel 101, the second heat exchange channel 102, and the third heat exchange channel 103 are connected in series in sequence, the first dehumidification valve 201 is located between the first heat exchange channel 101 and the second heat exchange channel 102, and the second dehumidification valve 202 is located between the second heat exchange channel 102 and the third heat exchange channel 103.

[0069] In the embodiments of the present disclosure, when the first dehumidification valve 201 is located between the first heat exchange channel 101 and the second heat exchange channel 102, when the refrigerant flows from the first end of the first heat exchange tube group 10 to the second end of the first heat exchange tube group 10, the first heat exchange channel 101 is the condensation and reheating section, and the second heat exchange channel 102 and the third heat exchange channel 103 are the dehumidification sections. In this case, the refrigerant enters the heat exchanger to condense and heat the air at the same time. After the refrigerant passes through the throttling of the first dehumidification valve 201, the temperature and pressure decrease, and it evaporates and absorbs heat while cooling and dehumidifying the air. In this way, the dehumidification area is relatively large, and it can be applied to places with high humidity.

[0070] Optionally, when the dehumidification valve is arranged on the fourth pipeline 107, the heat exchanger further includes an electric heater, and the electric heater corresponds to the first heat exchange channel 101 and is used for supplementary heating.

[0071] In the embodiments of the present disclosure, the heat exchanger is a variable flow distribution dehumidification heat exchanger, and the condensation and reheating area is relatively small. When the heat is insufficient, the electric heater can be turned on for supplementary heating. At the same time, because the relative humidity is lower than 95% after the pre-mixing of hot and cold air, the amount of water droplets is greatly reduced. When the electric heater is turned on at this time, it can avoid the noise caused by the direct contact between the water droplets and the electric heating and the flash evaporation.

[0072] When the second dehumidifying valve 202 is located between the second heat exchange channel 102 and the third heat exchange channel 103, when the refrigerant flows from the first end of the first heat exchange tube group 10 to the second end of the first heat exchange tube group 10, the first heat exchange channel 101 and the second heat exchange channel 102 are the condensation and reheating sections, and the third heat exchange channel 103 is the dehumidifying section. In this way, the dehumidifying area is smaller and the condensation and reheating area is larger, so that the refrigerant condenses more fully, the loss after throttling by the second dehumidifying valve 202 is smaller, and the temperature after throttling by the second dehumidifying valve 202 can be lower, realizing efficient dehumidification.

[0073] Optionally, the areas of the first heat exchange channel 101, the second heat exchange channel 102, and the third heat exchange channel 103 are the same, which can improve the flow distribution uniformity of the refrigerant. And the dehumidifying valve is located between the first heat exchange channel 101 and the second heat exchange channel 102, so that the ratio of the area of the condensation and reheating section to the area of the dehumidifying section is 1 / 2. When the dehumidifying valve is located between the second heat exchange channel 102 and the third heat exchange channel 103, the ratio of the area of the condensation and reheating section to the area of the dehumidifying section is 2.

[0074] Optionally, the first heat exchange tube group 10 further includes a first pipeline 104, a second pipeline 105, a third pipeline 106, a fourth pipeline 107, and a flow divider 30. The first end of the first pipeline 104 is adapted to be connected to the compressor, and the second end of the first pipeline 104 is connected to the first end of the first heat exchange channel 101 and the first end of the second heat exchange channel 102. The first end of the second pipeline 105 is connected to the second end of the first pipeline 104 and the first end of the second heat exchange channel 102, and the second end of the second pipeline 105 is connected to the first end of the third heat exchange channel 103; the first end of the flow divider 30 is connected to the second end of the first heat exchange channel 101 and the second end of the second heat exchange channel 102, and the second end of the flow divider 30 and the second end of the third heat exchange channel 103 are both adapted to be connected to the throttling device 50; the third pipeline 106 is adapted to be connected between the second end of the flow divider 30 and the throttling device 50. The fourth pipeline 107 is connected between the second end of the first heat exchange channel and the first end of the flow divider 30.

[0075] The flow splitting assembly includes a first valve 301 and a second valve 302. The first valve 301 is disposed in the first pipeline 104 and is defined to be conductive when flowing from the first end of the second heat exchange channel 102 towards the first end of the first heat exchange channel 101; the second valve 302 is disposed in the third pipeline 106 and is defined to be conductive when flowing from the throttling device 50 towards the liquid distributor. Wherein, when the refrigerant flows from the first end of the first heat exchange tube group 10 to the second end of the first heat exchange tube group 10, both the first valve 301 and the second valve 302 are closed, so that the first heat exchange channel 101, the second heat exchange channel 102 and the third heat exchange channel 103 are connected in series; when the refrigerant flows from the second end of the first heat exchange tube group 10 to the first end of the first heat exchange tube group 10, both the first valve 301 and the second valve 302 are conductive, so that the first heat exchange channel 101, the second heat exchange channel 102 and the third heat exchange channel 103 are arranged in parallel.

[0076] In the embodiment of the present disclosure, when the refrigerant flows from the first end of the first heat exchange tube group 10 to the second end of the first heat exchange tube group 10, the first valve 301 and the second valve 302 are closed. In this way, the first pipeline 104 and the third pipeline 106 are not conductive. In this way, the high-temperature and high-pressure refrigerant flowing out of the compressor flows into the first heat exchange channel 101 and then into the fourth pipeline 107, and then flows from the fourth pipeline 107 into the second heat exchange channel 102, and then flows from the second heat exchange channel 102 into the second pipeline 105, and then flows along the second pipeline 105 into the third heat exchange channel 103, and then flows from the third heat exchange channel 103 to the second end of the first heat exchange tube group 10 and flows out of the heat exchanger from the second end of the first heat exchange tube group 10.

[0077] When the refrigerant flows from the second end of the first heat exchange tube group 10 to the first end of the first heat exchange tube group 10, both the first valve 301 and the second valve 302 are conductive. In this way, both the first pipeline 104 and the third pipeline 106 are conductive. In this way, the refrigerant throttled by the throttling device 50 flows in from the second end of the first heat exchange tube group 10, and then flows to the third heat exchange channel 103 and the flow splitter 30 respectively, and flows to the first heat exchange channel 101 and the second heat exchange channel 102 respectively through the flow splitter 30, and then the refrigerant in the three heat exchange channels flows out and converges at the first end of the first heat exchange tube group 10 and flows out of the heat exchanger.

[0078] Optionally, the first valve 301 can be a solenoid valve, a Tesla valve, a ball valve or a check valve, etc.

[0079] Optionally, the second valve 302 can be a solenoid valve, a Tesla valve, a ball valve or a check valve, etc.

[0080] Optionally, the dehumidification valve includes a capillary tube or an electronic expansion valve.

[0081] In the embodiments of the present disclosure, the dehumidification valve can be a capillary tube or an electronic expansion valve, which can throttle the refrigerant. The high-temperature and high-pressure liquid refrigerant passes through the capillary tube or the electronic expansion valve, and the pressure suddenly drops. Due to the pressure reduction, part of the refrigerant will evaporate, forming a gas-liquid mixed state and reducing the temperature of the refrigerant.

[0082] Optionally, when the dehumidification valve includes a capillary tube, the dehumidification valve includes a first bypass pipeline and a first solenoid valve. The first bypass pipeline is connected in parallel with the capillary tube, and the first solenoid valve is arranged on the first bypass pipeline.

[0083] In the embodiments of the present disclosure, the dehumidification valve includes a first bypass pipeline and a capillary tube connected in parallel. In this way, when the dehumidification valve has the functions of throttling and non-throttling, the function of the dehumidification valve can be switched. When the first solenoid valve is closed, the first bypass pipeline is closed, and the refrigerant flows through the capillary tube for throttling, so that the throttling function of the dehumidification valve can be realized. When the first solenoid valve is opened, the first bypass pipeline is conducted, and the refrigerant flows through the first bypass pipeline without passing through the capillary tube, so that the dehumidification valve can be fully opened without throttling, so that the temperature and pressure of the flowing refrigerant do not change.

[0084] Optionally, when the dehumidification valve includes an electronic expansion valve, the dehumidification valve includes a second bypass pipeline and a second solenoid valve. The second bypass pipeline is connected in parallel with the electronic expansion valve, and the second solenoid valve is arranged on the second bypass pipeline.

[0085] In the embodiments of the present disclosure, the dehumidification valve includes a second bypass pipeline and an electronic expansion valve connected in parallel. In this way, when the dehumidification valve has the functions of throttling and non-throttling, the function of the dehumidification valve can be switched. When the second solenoid valve is closed, the second bypass pipeline is closed, and the refrigerant flows through the electronic expansion valve for throttling, so that the throttling function of the dehumidification valve can be realized. When the second solenoid valve is opened, the second bypass pipeline is conducted, and the refrigerant flows through the second bypass pipeline without passing through the electronic expansion valve, so that the dehumidification valve can be fully opened without throttling, so that the temperature and pressure of the flowing refrigerant do not change.

[0086] Optionally, as Figures 1 to 3 shown, the first heat exchange tube group 10 includes a first heat exchange channel 101, a second heat exchange channel 102 and a third heat exchange channel 103. When there are multiple dehumidification valves, the multiple dehumidification valves include a first dehumidification valve 201 and a second dehumidification valve 202. The first dehumidification valve 201 is arranged on the fourth pipeline 107, and the first dehumidification valve 201 can throttle the refrigerant in the third pipeline 106; the second dehumidification valve 202 is arranged on the second pipeline 105, and the second dehumidification valve 202 can throttle the refrigerant in the second pipeline 105.

[0087] In the embodiments of the present disclosure, two dehumidification valves are provided in the first heat exchange tube group 10. In this way, as Figure 2As shown, when the refrigerant flows from the first end of the first heat exchange tube group 10 to the second end of the first heat exchange tube group 10, the two dehumidifying valves are arranged in series. In this way, the refrigerant flowing out of the first heat exchange channel 101 is throttled and cooled by the first dehumidifying valve 201 and then flows into the second heat exchange channel 102. The refrigerant flowing out of the second heat exchange channel 102 can be throttled and cooled again by the second dehumidifying valve 202 and then flows into the third heat exchange channel 103. In this way, the temperatures of the first heat exchange channel 101, the second heat exchange channel 102, and the third heat exchange channel 103 are all different, and more diverse temperature and humidity regulation can be achieved. It can be understood that the first dehumidifying valve 201 and the second dehumidifying valve 202 can also be all unthrottled or one is throttled and the other is fully open without throttling, which can further increase the width of the temperature and humidity regulation range of the heat exchanger and improve the diversity of use.

[0088] Similarly, as Figure 3 shown, when the refrigerant flows from the second end of the first heat exchange tube group 10 to the first end, the first heat exchange channel 101, the second heat exchange channel 102, and the third heat exchange channel 103 are arranged in parallel. When the first dehumidifying valve 201 is opened and throttled, it can throttle and cool the refrigerant flowing into the first heat exchange channel 101. In this way, the temperature of the first heat exchange channel 101 is lower than the temperatures of the second heat exchange channel 102 and the third heat exchange channel 103, and deep dehumidification can be carried out. The first dehumidifying valve 201 and the second dehumidifying valve 202 can also be fully open without throttling, so that refrigeration and dehumidification can be achieved.

[0089] Optionally, when the dehumidifying valve includes a capillary tube, the first dehumidifying valve 201 includes a first capillary tube, the second dehumidifying valve 202 includes a second capillary tube, and the length of the first capillary tube is greater than the length of the second capillary tube.

[0090] In the embodiment of the present disclosure, when the refrigerant flows from the first end of the first heat exchange tube group 10 to the second end of the first heat exchange tube group 10, the first dehumidifying valve 201 is close to the first end of the first heat exchange tube group 10, and the second dehumidifying valve 202 is located downstream of the first dehumidifying valve 201. Therefore, the temperature of the refrigerant flowing into the first dehumidifying valve 201 is relatively high. Therefore, the length of the first capillary tube of the first dehumidifying valve 201 is greater than the length of the second capillary tube, which can improve the throttling effect of the first dehumidifying valve 201.

[0091] Optionally, when the dehumidifying valve includes an electronic expansion valve, the first dehumidifying valve 201 includes a first electronic expansion valve, the second dehumidifying valve 202 includes a second electronic expansion valve, and the opening degree of the first electronic expansion valve is smaller than the opening degree of the second electronic expansion valve.

[0092] In the embodiments of the present disclosure, when the refrigerant flows from the first end of the first heat exchange tube group 10 to the second end of the first heat exchange tube group 10, the first dehumidification valve 201 is close to the first end of the first heat exchange tube group 10, and the second dehumidification valve 202 is located downstream of the first dehumidification valve 201. Therefore, the temperature of the refrigerant flowing into the first dehumidification valve 201 is relatively high. As a result, the opening degree of the first electronic expansion valve of the first dehumidification valve 201 is smaller than that of the second electronic expansion valve, which can improve the throttling effect of the first dehumidification valve 201.

[0093] Optionally, as Figures 7 to 8 shown, the heat exchanger further includes a liquid storage tank 60, and the liquid storage tank 60 is provided upstream of the dehumidification valve.

[0094] In the embodiments of the present disclosure, the liquid storage tank 60 is located upstream of the dehumidification valve. In this way, when the refrigerant flows from the first end of the first heat exchange tube group 10 to the second end of the first heat exchange tube group 10, the liquid storage tank 60 can store the liquid refrigerant upstream of the dehumidification valve, reduce the proportion of the liquid refrigerant in the heat exchanger, increase the proportion of the two-phase refrigerant, and improve the efficiency of the heat exchanger. Moreover, the liquid storage tank 60 can reduce the burden on the dehumidification valve, provide a stable liquid refrigerant flow for the dehumidification valve, and reduce the amount of refrigerant that the dehumidification valve needs to process.

[0095] Optionally, when the refrigerant flows from the first end of the first heat exchange tube group 10 to the second end of the first heat exchange tube group 10, at least two heat exchange channels are arranged in series. The refrigerant flows from the first end of the first heat exchange tube group 10 to the second end of the first heat exchange tube group 10. The dehumidification valve is located between at least two heat exchange channels, and the liquid storage tank 60 is located on the side of the dehumidification valve facing the first end of the first heat exchange tube group 10.

[0096] In the embodiments of the present disclosure, the liquid storage tank 60 is located on the side of the dehumidification valve facing the first end of the first heat exchange tube group 10. In this way, when the refrigerant flows from the first end of the first heat exchange tube group 10 to the second end of the first heat exchange tube group 10, after the high-temperature and high-pressure refrigerant condenses and dissipates heat in the heat exchange channel upstream of the dehumidification valve, the liquid refrigerant can flow into the liquid storage tank 60, and then flow from the liquid storage tank 60 to the dehumidification valve. The liquid storage tank 60 can store the excess liquid refrigerant.

[0097] Optionally, the liquid storage tank 60 is located between the outlet of the condensation and reheating section and the dehumidification valve, which can ensure that the liquid refrigerant flowing into the liquid storage tank 60 is the liquid refrigerant that has condensed and dissipated heat in the condensation and reheating section, and ensure the condensation effect.

[0098] Optionally, the heat exchanger further includes a gas-liquid separator 70. The gas-liquid separator 70 is provided on the side of the dehumidification valve facing the second end of the first heat exchange tube group 10. The gas outlet of the gas-liquid separator 70 is adapted to communicate with the throttling device 50, and the liquid outlet of the gas-liquid separator 70 communicates with the first heat exchange tube group 10.

[0099] In the embodiments of the present disclosure, a gas-liquid separator 70 is added downstream of the dehumidification valve, that is, after the dehumidification valve. When the refrigerant flows from the first end of the first heat exchange tube group 10 to the second end of the first heat exchange tube group 10, the gaseous refrigerant is sent to the outlet at the second end of the heat exchanger, and the liquid refrigerant enters the heat exchange channel, avoiding excessive gaseous refrigerant occupying the heat exchanger, reducing the dryness of the refrigerant entering the heat exchanger, improving the heat exchange efficiency, and enhancing the dehumidification effect.

[0100] Optionally, when there are multiple dehumidification valves, the number of liquid storage tanks 60 is the same as and corresponds one-to-one to the number of dehumidification valves.

[0101] In the embodiments of the present disclosure, each dehumidification valve is correspondingly provided with a liquid storage tank 60, which can ensure the stable throttling of each dehumidification valve and increase the proportion of two-phase refrigerant in the branch where each dehumidification valve is located, improving the heat exchange efficiency.

[0102] In some alternative embodiments, as Figures 4 to 6 shown, multiple heat exchange channels further form a second heat exchange tube group 40. The first heat exchange tube group 10 is connected to the second heat exchange tube group 40. A flow splitting component is arranged in the first heat exchange tube group 10. When the refrigerant flows from the first end of the first heat exchange tube group 10 to the second end of the first heat exchange tube group 10, the multiple heat exchange channels of the first heat exchange tube group 10 are arranged in series. When the refrigerant flows from the second end of the first heat exchange tube group 10 to the first end, the multiple heat exchange channels of the first heat exchange tube group 10 are arranged in parallel. Among them, the dehumidification valve (collectively referred to as the third dehumidification valve 203 hereinafter for the convenience of distinction) is arranged in the second heat exchange tube group 40, or the third dehumidification valve 203 is arranged between the first heat exchange tube group 10 and the second heat exchange tube group 40, and is used to throttle the refrigerant so that the temperature of the refrigerant downstream of the third dehumidification valve 203 is lower than the temperature of the refrigerant upstream of the third dehumidification valve 203.

[0103] In an embodiment of the present disclosure, the first heat exchange tube group 10 is provided with a flow splitting assembly. In this way, when the first heat exchange tube group 10 switches between refrigeration and heating, not only can the refrigerant flow direction be switched, but also the refrigerant flow path will be different. When the refrigerant flows from the second end of the first heat exchange tube group 10 to the first end, the refrigerant flows through more branches, which can effectively reduce the frictional pressure drop of the refrigerant and improve the heat exchange efficiency. When the refrigerant flows from the first end of the first heat exchange tube group 10 to the second end of the first heat exchange tube group 10, the flow path of the refrigerant becomes longer, the flowing branch becomes shorter, the flow velocity increases, and the circulation is improved, increasing the heat transfer coefficient on the inner side of the tube and improving the heat exchange efficiency. The first heat exchange tube group 10 realizes multi-branch evaporation and few-branch condensation through the flow splitting assembly, which can improve the energy efficiency of the air conditioner. In addition, a third dehumidification valve 203 is provided in the second heat exchange tube group 40 or between the first heat exchange tube group 10 and the second heat exchange tube group 40. In this way, the first heat exchange tube group 10 and the second heat exchange tube group 40 can form different temperature ranges through the third dehumidification valve 203, and thus dehumidification can be realized. In this way, while the air conditioner dehumidifies, it can also take into account the energy efficiency of the air conditioner when switching between refrigeration and heating.

[0104] Optionally, when the third dehumidification valve 203 is opened for throttling, the first dehumidification valve 201 and the second dehumidification valve 202 can be fully opened without throttling or partially opened for throttling.

[0105] Optionally, the heat exchange tube group further includes a connecting pipeline 402, and the connecting pipeline 402 is connected between the second end of the first heat exchange tube group 10 and the first end of the second heat exchange tube group 40, wherein the third dehumidification valve 203 is provided in the connecting pipeline 402.

[0106] In an embodiment of the present disclosure, the third dehumidification valve 203 is provided in the connecting pipeline 402. The third dehumidification valve 203 can throttle the refrigerant flowing from the first heat exchange tube group 10 to the second heat exchange tube group 40, and can also throttle the refrigerant flowing from the second heat exchange tube group 40 to the first heat exchange tube group 10.

[0107] Optionally, the first end of the first heat exchange tube group 10 is adapted to be connected to a compressor, the first end of the second heat exchange tube group 40 is connected to the second end of the first heat exchange tube group 10, and the second end of the second heat exchange tube group 40 is adapted to be connected to an outdoor unit.

[0108] In the embodiments of the present disclosure, when the refrigerant flows from the first end of the first heat exchange tube group 10 to the second end of the first heat exchange tube group 10, the high-temperature refrigerant flows from the first heat exchange tube group 10 into the second heat exchange tube group 40. Specifically, the high-temperature refrigerant flows through a plurality of serially connected heat exchange channels of the first heat exchange tube group 10 in sequence. The first dehumidification valve 201 and the second dehumidification valve 202 are fully opened without throttling, and then it can flow into the second heat exchange tube group 40 after being throttled and cooled by the third dehumidification valve 203, and then flow from the second heat exchange tube group 40 to the outdoor unit. In this way, the temperature of the first heat exchange tube group 10 is higher than that of the second heat exchange tube group 40, and the air flow can flow through the first heat exchange tube group 10 first and then through the second heat exchange tube group 40, or flow through the second heat exchange tube group 40 first and then through the first heat exchange tube group 10. In this way, not only can reheating and dehumidification be achieved, but also the refrigerant flow in the first heat exchange tube group 10 is not affected, ensuring the condensation effect and the normal operation of the air conditioner. When the refrigerant flows from the first end of the first heat exchange tube group 10 to the second end of the first heat exchange tube group 10, at least one of the first dehumidification valve and the second dehumidification valve can also be opened for throttling. In this way, the high-temperature refrigerant flows out of the indoor heat exchanger after multiple throttlings, so that multiple different temperature ranges can be formed in the first heat exchange tube group, and the temperature of the second heat exchange tube group is also lower than that of the first heat exchange tube group, thereby enabling deep dehumidification while heating.

[0109] When the refrigerant flows from the second heat exchange tube group 40 to the first heat exchange tube group 10, the refrigerant flowing out of the second heat exchange tube group 40 is throttled by the third dehumidification valve 203 and then flows into the first heat exchange tube group 10. The first dehumidification valve and the second dehumidification valve are fully opened without throttling. In this way, the temperature of the second heat exchange tube group 40 is higher than that of the first heat exchange tube group 10. In this way, the first heat exchange tube group 10 is the refrigeration and dehumidification section, and the second heat exchange tube group 40 is the heating section, and refrigeration, dehumidification and reheating can be achieved. It can be understood that at least one of the first dehumidification valve and the second dehumidification valve can also be opened for throttling, so that deep refrigeration and then reheating can be achieved. It can be understood that the third dehumidification valve is a throttling device of the air conditioning system.

[0110] Optionally, the ratio range of the area of the second heat exchange tube group 40 to the area of the first heat exchange tube group 10 is 1 / 2 - 3, or the ratio range of the area of the second heat exchange tube group 40 to the area of the first heat exchange tube group 10 is 1 / 2 - 2.

[0111] In the embodiments of the present disclosure, when the ratio of the area of the first heat exchange tube group 10 to the area of the heat exchanger is less than 1 / 3, the area of the first heat exchange tube group 10 is too small, which will cause incomplete condensation of the refrigerant. When passing through the third dehumidification valve 203, it is in a two-phase state. The two-phase cold shock valve core has very loud noise, large throttling energy loss, and will affect the normal operation of the refrigerant circuit. When the ratio of the area of the first heat exchange tube group 10 to the area of the heat exchanger is greater than 3 / 4, the area of the second heat exchange tube group 40 is too small, and the dehumidification effect is not obvious. When the ratio of the area of the first heat exchange tube group 10 to the area of the heat exchanger ranges from 1 / 3 to 3 / 4, it can ensure sufficient condensation of the refrigerant, and the refrigerant is completely changed into a liquid state, or even a subcooled state, which is beneficial to dehumidification and has low noise.

[0112] Optionally, the ratio of the area of the first heat exchange tube group 10 to the area of the heat exchanger ranges from 1 / 3 to 2 / 3.

[0113] In the embodiments of the present disclosure, when the ratio of the area of the first heat exchange tube group 10 to the area of the heat exchanger is further reduced within the range of 1 / 3 to 2 / 3, it can ensure the flow uniformity of the refrigerant in the heat exchanger and maximize the condensation sufficiency of the refrigerant and the dehumidification effect of the second heat exchange tube group 40.

[0114] For example, the ratio of the area of the first heat exchange tube group 10 to the area of the heat exchanger is 1 / 3, 1 / 2, 2 / 3, or 3 / 4, etc.

[0115] Optionally, there is an included angle between adjacent heat exchange channels, and the heat exchanger is matched with the internal structure of the indoor unit. This makes the structure of the heat exchanger more compact and convenient to be installed in the indoor unit.

[0116] The embodiments of the present disclosure further provide an air conditioner, which includes an indoor unit and the heat exchanger as described in any one of the above.

[0117] The air conditioner according to the embodiments of the present disclosure includes the heat exchanger according to any one of the above embodiments, and thus has the beneficial effects of the heat exchanger described in any one of the above, which will not be elaborated here.

[0118] Optionally, the heat exchanger is an indoor heat exchanger. The indoor unit includes an indoor heat exchanger, a housing, and a fan. The housing defines a receiving cavity with an air inlet and an air outlet. The indoor heat exchanger is located in the receiving cavity; the fan is located in the receiving cavity, and the fan can drive the air flow to flow through the first heat exchange channel 101, the second heat exchange channel 102, and the third heat exchange channel 103 in sequence.

[0119] In the embodiments of the present disclosure, the fan can drive the air flow to flow through the first heat exchange channel 101, the second heat exchange channel 102, and the third heat exchange channel 103 in sequence, so that the air flow flowing through the heat exchanger can adjust the temperature while dehumidifying to meet different temperature adjustment requirements. In this way, when the refrigerant flows from the first end of the heat exchanger to the second end, the heat exchanger can form reheating and dehumidification. When the refrigerant flows from the second end of the heat exchanger to the first end, the heat exchanger can form refrigeration or deep dehumidification.

[0120] Optionally, when the indoor heat exchanger includes a fourth heat exchange channel 104, the fan can drive the air flow to flow through the first heat exchange channel 101, the second heat exchange channel 102, the third heat exchange channel 103, and the fourth heat exchange channel 104 in sequence. In this way, when the refrigerant flows from the first end of the heat exchanger to the second end, the heat exchanger can form reheating and dehumidification. When the refrigerant flows from the second end of the heat exchanger to the first end, the heat exchanger can form refrigeration, dehumidification, and reheating.

[0121] Optionally, the outdoor unit includes an outdoor heat exchanger, and the outdoor heat exchanger is a variable flow splitting heat exchanger.

[0122] The above description and the drawings fully illustrate the embodiments of the present disclosure so that those skilled in the art can practice them. Other embodiments may include structural and other changes. The embodiments represent only possible variations. Unless explicitly required, the individual components and functions are optional, and the order of operations can vary. Some parts and features of some embodiments can be included in or replaced by those of other embodiments. The embodiments of the present disclosure are not limited to the structures already described and shown in the drawings, and various modifications and changes can be made without departing from its scope. The scope of the present disclosure is limited only by the appended claims.

Claims

1. A heat exchanger, characterized in that, Comprising: A heat exchange tube group, the first end of the heat exchange tube group is adapted to communicate with a compressor, the second end of the heat exchange tube group is adapted to communicate with a throttling device, the heat exchange tube group includes a plurality of heat exchange channels, and the plurality of heat exchange channels communicate between the first end and the second end of the heat exchange tube group; A dehumidification valve, disposed between two adjacent heat exchange channels, the dehumidification valve can throttle the refrigerant, so that the temperature of the refrigerant downstream of the dehumidification valve is lower than the temperature of the refrigerant upstream of the dehumidification valve; Wherein, the number of dehumidification valves is multiple, and the multiple dehumidification valves can be arranged in series.

2. The heat exchanger according to claim 1, wherein The multiple dehumidification valves and the multiple heat exchange channels are alternately arranged at intervals in sequence.

3. The heat exchanger according to claim 1, characterized in that, The multiple dehumidification valves include: A first dehumidification valve, the distance between the first dehumidification valve and the first end of the heat exchange tube group is less than the distance between the first dehumidification valve and the second end of the heat exchange tube group; A second dehumidification valve, the distance between the second dehumidification valve and the first end of the heat exchange tube group is greater than the distance between the second dehumidification valve and the second end of the heat exchange tube group; Wherein, the first dehumidification valve and the second dehumidification valve can be connected in series between the first end and the second end of the heat exchange tube group.

4. The heat exchanger according to claim 3, wherein When the dehumidification valve includes a capillary tube, the first dehumidification valve includes a first capillary tube, the second dehumidification valve includes a second capillary tube, and the length of the first capillary tube is greater than the length of the second capillary tube.

5. The heat exchanger according to claim 3, wherein When the dehumidification valve includes an electronic expansion valve, the first dehumidification valve includes a first electronic expansion valve, the second dehumidification valve includes a second electronic expansion valve, and the opening degree of the first electronic expansion valve is less than the opening degree of the second electronic expansion valve.

6. The heat exchanger according to claim 3, wherein When the dehumidification valve includes a capillary tube, the dehumidification valve includes a first bypass pipeline and a first solenoid valve, the first bypass pipeline is connected in parallel with the capillary tube, and the first solenoid valve is disposed on the first bypass pipeline; or When the dehumidification valve includes an electronic expansion valve, the dehumidification valve includes a second bypass pipeline and a second solenoid valve, the second bypass pipeline is connected in parallel with the electronic expansion valve, and the second solenoid valve is disposed on the second bypass pipeline.

7. The heat exchanger according to any one of claims 3 to 6, characterized in that, The multiple heat exchange channels include: A first heat exchange channel, the first end is adapted to communicate with a compressor; A second heat exchange channel, the second end is connected to the second end of the first heat exchange channel; A third heat exchange channel, the first end is connected to the first end of the second heat exchange channel, and the second end of the third heat exchange channel is adapted to communicate with a throttling device; The heat exchange tube group further includes: A second pipeline, the first end is connected to the first end of the second heat exchange channel, and the second end is connected to the first end of the third heat exchange channel; A fourth pipeline, communicating between the second end of the first heat exchange channel and the second end of the second heat exchange channel; Wherein, the first dehumidification valve is disposed on the fourth pipeline, and the second dehumidification valve is disposed on the second pipeline.

8. The heat exchanger according to claim 7, wherein, The heat exchange tube group further includes: A first pipeline, the first end is adapted to communicate with a compressor, the second end is connected to the first end of the first heat exchange channel and the first end of the second heat exchange channel, and the first end of the second pipeline is connected to the second end of the first pipeline and the first end of the second heat exchange channel; A diverter, the first end of the diverter is communicated with the second end of the first heat exchange channel and the second end of the second heat exchange channel, and the second end of the diverter and the second end of the third heat exchange channel are both adapted to be communicated with a throttling device; A third pipeline, adapted to be communicated between the second end of the diverter and the throttling device; A diversion assembly, including a first valve and a second valve. The first valve is arranged in the first pipeline, and the first valve is defined to be conductive when flowing from the first end of the second heat exchange channel towards the first end of the first heat exchange channel; the second valve is arranged in the third pipeline, and the second valve is defined to be conductive when flowing from the throttling device towards the liquid distributor; Wherein, when the refrigerant flows from the first end of the heat exchange tube group to the second end of the heat exchange tube group, both the first valve and the second valve are closed, and the first heat exchange channel, the second heat exchange channel and the third heat exchange channel are connected in series; when the refrigerant flows from the second end of the heat exchange tube group to the first end of the heat exchange tube group, both the first valve and the second valve are conductive, and the first heat exchange channel, the second heat exchange channel and the third heat exchange channel are arranged in parallel.

9. An air conditioner, characterized in that, It includes a heat exchanger according to any one of claims 1 to 8.

10. The air conditioner according to claim 9, characterized in that, It further includes an indoor unit, and the indoor unit further includes: A housing, defining a receiving cavity with an air inlet and an air outlet, and the heat exchanger is located in the receiving cavity; A fan, located in the receiving cavity, and the fan can drive the air flow to flow through the first heat exchange channel, the second heat exchange channel and the third heat exchange channel in sequence.

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