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 pipe set and a heat exchange pipe, wherein the heat exchange pipe set comprises a plurality of communicated heat exchange channels; the dehumidification valve is arranged between the two adjacent heat exchange channels and is used for throttling the refrigerant, so that the temperature of the refrigerant at the downstream of the dehumidification valve is lower than that of the refrigerant at the upstream of the dehumidification valve; and the liquid storage tank is arranged at the upstream of the dehumidification valve. The liquid storage tank is located on the upstream of the dehumidification valve, so that the liquid storage tank can store the liquid refrigerant on the upstream of the dehumidification valve, the proportion of the liquid refrigerant in the heat exchanger is reduced, the proportion of the two-phase refrigerant is increased, and the efficiency of the heat exchanger 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, used for refrigeration and dehumidification in summer and heating in winter. The dehumidification technology is to make the air conditioner operate in the refrigeration mode, and at the same time, the indoor fan is maintained at a lower 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 increased 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 the air conditioner in the related art, the heat exchanger is divided into a condensation section and a dehumidification section during dehumidification, which will reduce the heat exchange area and affect the heat exchange efficiency of the entire air conditioner.

[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] In order 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 subsequent detailed description.

[0008] The embodiments of the present disclosure provide a heat exchanger and an air conditioner to ensure the heat exchange efficiency of the heat exchanger and the air conditioner while realizing dehumidification.

[0009] The embodiments of the present disclosure provide a heat exchanger, which includes: a heat exchange tube group including a plurality of interconnected heat exchange channels; a dehumidification valve disposed between two adjacent heat exchange channels for throttling the 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; and a liquid storage tank disposed upstream of the dehumidification valve.

[0010] Optionally, the first end of the heat exchange tube group is adapted to communicate with a compressor, and the second end of the heat exchange tube group is adapted to communicate with a throttling device. When the refrigerant flows from the first end of the heat exchange tube group to the second end of the heat exchange tube group, the dehumidification valve is located between at least two heat exchange channels, and the liquid storage tank is located on the side of the dehumidification valve facing the first end of the heat exchange tube group.

[0011] Optionally, when the refrigerant flows from the first end of the heat exchange tube group to the second end of the heat exchange tube group, a condensation reheating section is formed between the dehumidification valve and the first end of the heat exchange tube group, and a dehumidification section is formed between the dehumidification valve and the second end of the heat exchange tube group; wherein, the liquid storage tank is located between the outlet of the condensation reheating section and the inlet of the dehumidification valve.

[0012] Optionally, the area of the condensation reheating section is larger than the area of the dehumidification section, or the area of the condensation reheating section is smaller than the area of the dehumidification section.

[0013] Optionally, the heat exchanger further includes: a gas-liquid separator disposed on the side of the dehumidification valve facing the second end of the heat exchange tube group, the gaseous outlet of the gas-liquid separator is adapted to communicate with the throttling device, and the liquid outlet of the gas-liquid separator communicates with the heat exchange tube group.

[0014] Optionally, the number of dehumidification valves is one or more. When there are multiple dehumidification valves and the refrigerant flows from the first end of the heat exchange tube group to the second end of the heat exchange tube group, the multiple dehumidification valves are arranged in an alternating and spaced manner with multiple heat exchange channels arranged in series.

[0015] Optionally, when there are multiple dehumidification valves, the number of liquid storage tanks is the same as the number of dehumidification valves and they correspond one by one.

[0016] Optionally, the multiple heat exchange channels include a first heat exchange channel, a second heat exchange channel, and a third heat exchange channel. When the refrigerant flows from the first end of the heat exchange tube group to the second end of the heat exchange tube group, the first heat exchange channel, the second heat exchange channel, and the third heat exchange channel are connected in series in sequence; the heat exchange tube group further includes: a second pipeline, the first end of which communicates with the first end of the second heat exchange channel, and the second end of which communicates with the first end of the third heat exchange channel; a fourth pipeline, which is connected between the second end of the first heat exchange channel and the second end of the second heat exchange channel; the dehumidification valve is disposed on the second pipeline and / or the fourth pipeline.

[0017] 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, and the second end of which communicates with the first end of the third heat exchange channel; a diverter, the first end of the diverter communicates with the fourth pipeline 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 communicate with the throttling device; a third pipeline, which is adapted to be connected 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 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 separator; 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.

[0018] An embodiment of the present disclosure further provides an air conditioner, which includes the heat exchanger described in any one of the above embodiments.

[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 heat exchanger of the embodiment of the present disclosure, the temperature of the refrigerant will decrease after throttling by the dehumidifying valve. The dehumidifying valve can divide the heat exchanger into different temperature zones, so that when the air flow passes through the heat exchange channel with a lower temperature, dehumidification can be carried out. In this way, when the refrigerant upstream of the dehumidifying valve is at a high temperature, the area of the heat exchanger for condensation is reduced, and the liquid storage tank is located upstream of the dehumidifying valve, so that the liquid storage tank can store the excess liquid refrigerant upstream of the dehumidifying valve, avoiding the accumulation of a large amount of liquid refrigerant upstream of the dehumidifying valve and ensuring the stable operation of the dehumidifying valve. Moreover, when the air conditioner operates at a low frequency, the liquid storage tank stores the excess liquid refrigerant, which can also reduce the proportion of the liquid refrigerant in the heat exchanger and increase the proportion of the two-phase refrigerant, thereby improving the efficiency of the heat exchanger.

[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 the 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 proportional limitation, and among them:

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

[0024] Figure 2 It is a schematic diagram of the refrigerant flow 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 provided by an embodiment of the present disclosure;

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

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

[0027] Figure 5 It is a schematic diagram of the refrigerant flow 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 provided by another embodiment of the present disclosure;

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

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

[0030] Figure 8 It is a schematic diagram of the refrigerant flow 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 provided by another embodiment of the present disclosure;

[0031] Figure 9 It is a schematic diagram of the refrigerant flow when the refrigerant flows from the second end of the first heat exchange tube group to the first end of the first heat exchange tube group provided by another embodiment of the present disclosure;

[0032] Figure 10 It is a schematic structural diagram of another heat exchanger provided by an embodiment of the present disclosure;

[0033] Figure 11 It is a schematic diagram of the refrigerant flow 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 provided by another embodiment of the present disclosure;

[0034] Figure 12 It is a schematic diagram of the refrigerant flow when the refrigerant flows from the second end of the first heat exchange tube group to the first end of the first heat exchange tube group provided by another embodiment of the present disclosure;

[0035] Figure 13 It is a schematic structural diagram of another heat exchanger provided by an embodiment of the present disclosure;

[0036] Figure 14 It is a schematic structural diagram of another heat exchanger provided by an embodiment of the present disclosure;

[0037] Figure 15 It is a schematic structural diagram of another heat exchanger provided by an embodiment of the present disclosure;

[0038] Figure 16 It is a schematic structural diagram of another heat exchanger provided by an embodiment of the present disclosure.

[0039] Reference numerals:

[0040] 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; 20. Dehumidification valve; 201. First dehumidification valve; 202. Second dehumidification valve; 203. Third dehumidification valve; 30. Diverter; 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

[0041] In order to be able 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 only for reference and explanation, and are not used to limit the embodiments of the present disclosure. In the following technical description, for the convenience of explanation, a sufficient understanding of the disclosed embodiments is provided through multiple details. However, one or more embodiments can still be implemented without these details. In other cases, well-known structures and devices can be shown in a simplified manner to simplify the drawings.

[0042] The terms "first", "second", etc. in the description and claims of the embodiments of the present disclosure and the above-mentioned drawings are used to distinguish similar objects, and do not have to be used to describe a specific order or sequence. It should be understood that such data 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.

[0043] 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. Moreover, in addition to being able to represent the 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.

[0044] In addition, the terms "arrangement", "connection", "fixation" should be understood in a broad sense. For example, "connection" 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 is an internal connection 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.

[0045] Unless otherwise specified, the term "plurality" means two or more.

[0046] 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.

[0047] It should be noted that, without conflict, the embodiments in the embodiments of the present disclosure and the features in the embodiments can be combined with each other.

[0048] For the convenience of description, the temperature of the refrigerant in the solid arrow in the drawings is higher than the temperature of the refrigerant in the dashed arrow.

[0049] Combined Figures 1 to 16 As shown, the embodiments of the present disclosure provide 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 refrigerant flow direction 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 heat exchanger of the indoor unit through the four-way valve, condenses and dissipates heat in the outdoor heat exchanger, and then flows from the 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 flows out of the outdoor heat exchanger and is throttled by the throttling device 50, and then flows into the heat exchanger of the indoor unit for evaporation and refrigeration.

[0050] Optionally, the throttling device 50 is an electronic expansion valve or a capillary tube, etc.

[0051] 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. The plurality of heat exchange channels form the heat exchange tube group (hereinafter collectively referred to as the first heat exchange tube group 10 for convenience of distinction). 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 a 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.

[0052] In the embodiment of the present disclosure, the plurality of heat exchange channels are connected between the first end and the second end 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 performed through the fins to achieve refrigeration or heating.

[0053] Optionally, the heat exchanger further includes a dehumidification valve 20. The dehumidification valve 20 is arranged in the heat exchange channel or between any two heat exchange channels. The dehumidification valve 20 can throttle the refrigerant so that the temperature of the refrigerant downstream of the dehumidification valve 20 is lower than the temperature of the refrigerant upstream of the dehumidification valve 20.

[0054] In the embodiment of the present disclosure, the dehumidification valve 20 is arranged inside the heat exchanger. The dehumidification valve 20 is located between adjacent heat exchange channels or arranged inside the heat exchange channel. The dehumidification valve 20 has a throttling effect. In this way, the temperature of the refrigerant is further reduced after being throttled by the dehumidification valve 20, so that the temperature of the refrigerant downstream of the dehumidification valve 20 is lower than the temperature of the refrigerant upstream of the dehumidification valve 20. In this way, the downstream of the dehumidification valve 20 can be used for dehumidification, and thus the heat exchanger has a dehumidification function. The upstream of the dehumidification valve 20 can be a reheating condensation section or a refrigeration section.

[0055] Optionally, as Figures 1 to 6 shown, there is one dehumidification valve 20. 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 reheating section is formed between the dehumidification valve 20 and the first end of the heat exchanger, and a dehumidification section is formed between the dehumidification valve 20 and the second end of the heat exchanger; wherein, the area of the condensation reheating section is greater than the area of the dehumidification section, or the area of the condensation reheating section is less than the area of the dehumidification section.

[0056] 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 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 throttling by the dehumidifying valve 20, the temperature decreases. In this way, the heat exchange channel between the dehumidifying valve 20 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 dehumidifying valve 20 and the second end of the first heat exchange tube group 10 forms a dehumidifying 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 dehumidifying section to be cooled and dehumidified. In this way, when the indoor temperature needs to be moderately heated but the humidity is relatively high, the air flow flows through the condensation and reheating section to be heated and then flows through the dehumidifying section, so that dehumidification can be achieved and a constant temperature can be maintained. The air flow of the indoor unit can also first flow through the dehumidifying section to be dehumidified, and then flow through the condensation and reheating section to be heated, so as to realize constant temperature dehumidification. Among them, the area of the condensation and reheating section is larger than the area of the dehumidifying section, so that the heating range is larger and it is suitable for an environment with lower humidity. The area of the condensation and reheating section can also be smaller than the area of the dehumidifying section, which is suitable for an environment with higher humidity. In this way, heat exchangers at different positions of the dehumidifying valve 20 can be selected according to different use environments, so as to achieve different dehumidification effects.

[0057] 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.

[0058] 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 will cause incomplete condensation of the refrigerant. When passing through the dehumidifying valve 20, it is in a two-phase state. The two-phase cold impacts the valve core, resulting in very loud noise, large throttling energy loss, and affecting 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 dehumidifying 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 is completely changed into a liquid state, or even a subcooled state, which is beneficial to dehumidification and has low noise.

[0059] 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.

[0060] 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, the flow uniformity of the refrigerant in the heat exchanger can be ensured, and the condensation sufficiency of the refrigerant and the dehumidification effect of the dehumidifying section can be ensured with the highest efficiency.

[0061] For example, 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.

[0062] Optionally, as Figures 7 to 10As shown, the number of dehumidifying valves 20 is multiple, and the multiple dehumidifying valves 20 can be arranged in series.

[0063] In the embodiment of the present disclosure, multiple dehumidifying valves 20 are provided, and the multiple dehumidifying valves 20 can be arranged in series. In this way, the dehumidifying valves 20 in the first heat exchange tube group 10 can be throttled multiple times, further increasing the number of different temperature ranges of the heat exchanger, improving the diversity and width of dehumidification and temperature adjustment, and enhancing the user experience.

[0064] Optionally, the dehumidifying valves 20 and the heat exchange channels are alternately arranged at intervals.

[0065] In the embodiment of the present disclosure, when there are multiple dehumidifying valves 20, the dehumidifying valves 20 and the heat exchange channels can be alternately arranged at intervals, so that different heat exchange channels can form different temperatures, further increasing the temperature range and temperature span.

[0066] Optionally, the first heat exchange tube group 10 further includes a flow splitting component. The flow splitting component 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, the 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, the multiple heat exchange channels are arranged in parallel.

[0067] In the embodiment of the present disclosure, the flow splitting component enables the refrigerant to have different flow paths 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 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.

[0068] In addition, through the flow splitting component and the dehumidifying valves 20, while enabling the heat exchanger to have a dehumidifying function, the heat exchange efficiency can be improved, thereby improving the energy efficiency of the air conditioner.

[0069] Optionally, the number of the multiple heat exchange channels can be three, four, five or six, which can be set according to the size of the heat exchanger.

[0070] 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. 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.

[0071] In the embodiments of the present disclosure, the three heat exchange channels of the heat exchanger can achieve variable flow splitting during refrigeration and heating. When the refrigerant of the first heat exchange tube group 10 flows from the first end of the first heat exchange tube group to the second end of the first heat exchange tube group, the high-temperature and high-pressure refrigerant at the first end of the first heat exchange tube group 10 flows through the first heat exchange channel 101, the second heat exchange channel 102, and the third heat exchange channel 103 connected in series in sequence and then flows out from the second end of the first heat exchange tube group 10. In this way, the flow speed can be increased, the circulation can be improved, the heat transfer coefficient on the inner side of the tube can be increased, and the heat transfer efficiency can be improved. When the refrigerant of the first heat exchange tube group 10 flows from the second end of the first heat exchange tube group to the first end of the first heat exchange tube group, 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. The three heat exchange channels are arranged in parallel, which can increase the flow branches, effectively reduce the frictional pressure drop of the refrigerant, and improve the heat transfer efficiency.

[0072] Optionally, there is one dehumidification valve 20, and 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, as Figures 1 to 3 shown, the dehumidification valve 20 is located between the first heat exchange channel 101 and the second heat exchange channel 102, or, as Figures 4 to 6 shown, the dehumidification valve 20 is located between the second heat exchange channel 102 and the third heat exchange channel 103.

[0073] In the embodiments of the present disclosure, when the dehumidification valve 20 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 to the second end of the first heat exchange tube group, 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 dehumidification valve 20, 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.

[0074] Optionally, when the dehumidification valve 20 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.

[0075] In the embodiments of the present disclosure, the heat exchanger is a variable shunt dehumidifying heat exchanger with a relatively small condensation and reheating area. When the heat is insufficient, an electric heater can be turned on for supplementary heating. At the same time, since the relative humidity is lower than 95% after the pre-mixing of hot and cold air, the amount of water droplets is greatly reduced. Turning on the electric heater at this time can avoid the noise caused by the flashing of water droplets directly contacting the electric heating.

[0076] When the dehumidification valve 20 is located between the second heat exchange channel 102 and the third heat exchange channel 103, when the refrigerant in the first heat exchange tube group 10 flows from the first end of the first heat exchange tube group to the second end of the first heat exchange tube group, 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 dehumidification section. In this way, the dehumidification area is relatively small, and the reheating and condensation area is relatively large, so that the refrigerant condenses more fully, the loss after throttling by the dehumidification valve 20 is smaller, and the temperature after throttling by the dehumidification valve 20 can be lower, achieving efficient dehumidification.

[0077] 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 shunt uniformity of the refrigerant. And the dehumidification valve 20 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 dehumidification section is 1 / 2. When the dehumidification valve 20 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 dehumidification section is 2.

[0078] 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 shunt device 30. The first end of the first pipeline 104 is adapted to be connected to a 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 shunt device 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 shunt device 30 and the second end of the third heat exchange channel 103 are both adapted to be connected to a throttling device 50; the third pipeline 106 is adapted to be connected between the second end of the shunt device 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 shunt device 30.

[0079] The flow splitting component includes a first valve 301 and a second valve 302. The first valve 301 is arranged 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 arranged 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 heat exchange tube group to the first end of the heat exchange tube group, 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.

[0080] 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, 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.

[0081] 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.

[0082] Optionally, the first valve 301 can be a solenoid valve, a Tesla valve, a ball valve or a check valve, etc.

[0083] Optionally, the second valve 302 can be a solenoid valve, a Tesla valve, a ball valve or a check valve, etc.

[0084] Optionally, the dehumidification valve 20 is arranged in the second pipeline 105 or the fourth pipeline 107.

[0085] In the embodiments of the present disclosure, the dehumidification valve 20 is provided in the second pipeline 105. When the refrigerant of the first heat exchange tube group 10 flows from the first end of the first heat exchange tube group to the second end of the first heat exchange tube group, 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 dehumidification section. When the refrigerant of the first heat exchange tube group 10 flows from the second end of the first heat exchange tube group to the first end of the first heat exchange tube group, the dehumidification valve 20 can throttle the refrigerant flowing from the third heat exchange channel 103 to the first end of the first heat exchange tube group, further reducing the temperature of the refrigerant. When the dehumidification valve 20 is located in the fourth pipeline 107 and the refrigerant of the first heat exchange tube group 10 flows from the first end of the first heat exchange tube group to the second end of the first heat exchange tube group, 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. When the refrigerant of the first heat exchange tube group 10 flows from the second end of the first heat exchange tube group to the first end of the first heat exchange tube group, the dehumidification valve 20 can throttle the refrigerant flowing into the first heat exchange channel 101 to reduce the temperature of the first heat exchange channel 101, so that the heat exchange channels of the first heat exchange tube group 10 have different temperatures, thereby realizing various dehumidification functions.

[0086] Optionally, the dehumidification valve 20 includes a capillary tube or an electronic expansion valve.

[0087] In the embodiments of the present disclosure, the dehumidification valve 20 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 mixture state and reducing the temperature of the refrigerant.

[0088] Optionally, when the dehumidification valve 20 includes a capillary tube, the dehumidification valve 20 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 provided in the first bypass pipeline.

[0089] In the embodiments of the present disclosure, the dehumidification valve 20 includes a first bypass pipeline and a capillary tube connected in parallel. In this way, when the dehumidification valve 20 has the functions of throttling and non-throttling, the function of the dehumidification valve 20 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 20 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 20 can be fully opened without throttling, so that the temperature and pressure of the flowing refrigerant do not change.

[0090] Optionally, when the dehumidification valve 20 includes an electronic expansion valve, the dehumidification valve 20 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 provided in the second bypass pipeline.

[0091] In the disclosed embodiment, the dehumidification valve 20 includes a second bypass line and an electronic expansion valve arranged in parallel, so that when the dehumidification valve 20 has the functions of throttling and non-throttling, the function of the dehumidification valve 20 can be switched. When the second solenoid valve is closed, the second bypass line is closed, and the refrigerant flows through the electronic expansion valve for throttling, thereby realizing the throttling function of the dehumidification valve 20. When the second solenoid valve is opened, the second bypass line is connected, and the refrigerant flows from the second bypass line without passing through the electronic expansion valve, thereby enabling the dehumidification valve 20 to be fully opened without throttling, so that the temperature and pressure of the refrigerant flowing through do not change.

[0092] Alternatively, if Figures 7 to 9 As 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, and when there are multiple dehumidification valves 20, the multiple dehumidification valves 20 include a first dehumidification valve 201 and a second dehumidification valve 202, the first dehumidification valve 201 is arranged in 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 in the second pipeline 105, and the second dehumidification valve 202 can throttle the refrigerant in the second pipeline 105.

[0093] In the embodiment of the present disclosure, the first heat exchange tube group 10 is provided with two dehumidification valves 20. Figure 8 As shown, when the refrigerant of the first heat exchange tube group 10 flows from the first end of the first heat exchange tube group to the second end of the first heat exchange tube group, the two dehumidification valves 20 are arranged in series, so that the refrigerant flowing out of the first heat exchange channel 101 flows into the second heat exchange channel 102 after throttling and cooling through the first dehumidification valve 201, and the refrigerant flowing out of the second heat exchange channel 102 can be throttled and cooled again through the second dehumidification valve 202, and then flows into the third heat exchange channel 103, so that 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 dehumidification valve 201 and the second dehumidification valve 202 can also be completely un-throttled or one throttled and the other fully opened without throttling, which can further increase the range width of the temperature and humidity regulation of the heat exchanger and improve the diversity of use.

[0094] Likewise, if Figure 9 As shown, when the refrigerant in the first heat exchange tube group 10 flows from the second end of the first heat exchange tube group to the first end of the first heat exchange tube group, the first heat exchange channel 101, the second heat exchange channel 102 and the third heat exchange channel 103 are arranged in parallel, and the first dehumidification valve 201 can throttle and cool the refrigerant flowing into the first heat exchange channel 101 when the throttling is turned on, so that the temperature of the first heat exchange channel 101 is lower than the temperature of the second heat exchange channel 102 and the third heat exchange channel 103, and deep dehumidification can be performed. The first dehumidification valve 201 and the second dehumidification valve 202 can also be fully opened without throttling, so that refrigeration and dehumidification can be achieved.

[0095] Optionally, when the dehumidification valve 20 includes a capillary tube, the first dehumidification valve 201 includes a first capillary tube, the second dehumidification 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.

[0096] In an embodiment of the present disclosure, when the refrigerant of the first heat exchange tube group 10 flows from the first end of the first heat exchange tube group to the second end of the first heat exchange tube group, 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. Therefore, the length of the first capillary tube of the first dehumidification valve 201 is greater than the length of the second capillary tube, which can improve the throttling effect of the first dehumidification valve 201.

[0097] Optionally, when the dehumidification valve 20 includes an electronic expansion valve, the first dehumidification valve 201 includes a first electronic expansion valve, the second dehumidification 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.

[0098] In an embodiment of the present disclosure, 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, 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. Therefore, the opening degree of the first electronic expansion valve of the first dehumidification valve 201 is smaller than the opening degree of the second electronic expansion valve, which can improve the throttling effect of the first dehumidification valve 201.

[0099] Optionally, as Figures 13 to 16 shown, the heat exchanger further includes a liquid storage tank 60, and the liquid storage tank 60 is provided upstream of the dehumidification valve 20.

[0100] In an embodiment of the present disclosure, the liquid storage tank 60 is located upstream of the dehumidification valve 20. In this way, when the medium flows from the first end of the first heat exchange tube group to the second end of the first heat exchange tube group and the dehumidification valve is opened, the heat exchanger is in the reheating and dehumidification mode. The liquid storage tank 60 can store the excess liquid refrigerant upstream of the dehumidification valve 20, 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 20, provide a stable liquid refrigerant flow for the dehumidification valve 20, and reduce the amount of refrigerant that the dehumidification valve 20 needs to process.

[0101] 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 connected in series, the dehumidification valve 20 is located between at least two heat exchange channels, and the liquid storage tank 60 is located on the side of the dehumidification valve 20 facing the first end of the first heat exchange tube group 10.

[0102] In the embodiments of the present disclosure, the liquid storage tank 60 is located on one side of the first end of the dehumidification valve 20 facing the first heat exchange tube group 10. In this way, when the refrigerant in the first heat exchange tube group 10 flows from the first end of the first heat exchange tube group to the second end, the dehumidification valve is opened to operate the reheating dehumidification mode. After the high-temperature and high-pressure refrigerant condenses and dissipates heat in the heat exchange channel upstream of the dehumidification valve 20, the liquid refrigerant can flow into the liquid storage tank 60, and then flow from the liquid storage tank 60 to the dehumidification valve 20. The liquid storage tank 60 can store the excess liquid refrigerant to ensure the stable operation of the dehumidification valve.

[0103] Optionally, the liquid storage tank 60 is located between the outlet of the condensation and reheating section and the dehumidification valve 20, so as to 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.

[0104] Optionally, the heat exchanger further includes a gas-liquid separator 70. The gas-liquid separator 70 is arranged on one side of the second end of the dehumidification valve 20 facing 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.

[0105] In the embodiments of the present disclosure, a gas-liquid separator 70 is added downstream of the dehumidification valve 20, that is, behind the dehumidification valve 20. In this way, when the reheating dehumidification mode is operated, the gaseous refrigerant is sent to the outlet of the second end of the heat exchanger, and the liquid refrigerant enters the heat exchange channel, avoiding the excess 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.

[0106] Optionally, when there are multiple dehumidification valves 20, the number of liquid storage tanks 60 is the same as and corresponds to the number of dehumidification valves 20 one by one.

[0107] In the embodiments of the present disclosure, each dehumidification valve 20 is correspondingly provided with a liquid storage tank 60, so as to ensure the stable throttling of each dehumidification valve 20, and increase the proportion of two-phase refrigerant in the branch where each dehumidification valve 20 is located, improving the heat exchange efficiency.

[0108] In some alternative embodiments, such as Figures 10 to 12As shown, a plurality of heat exchange channels further form a second heat exchange tube group 40. The flow splitting assembly is disposed within the first heat exchange tube group 10. When the refrigerant in the first heat exchange tube group 10 flows from the first end of the first heat exchange tube group to the second end, the plurality of heat exchange channels in the first heat exchange tube group 10 are arranged in series. When the refrigerant in the first heat exchange tube group 10 flows from the second end of the first heat exchange tube group to the first end, the plurality of heat exchange channels in the first heat exchange tube group 10 are arranged in parallel. Among them, a dehumidifying valve 20 (hereinafter collectively referred to as the third dehumidifying valve 203 for convenience of distinction) is disposed within the second heat exchange tube group 40, or the third dehumidifying valve 203 is disposed 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 dehumidifying valve 203 is lower than the temperature of the refrigerant upstream of the third dehumidifying valve 203.

[0109] In the 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 flow path of the refrigerant will be different. When the first heat exchange tube group 10 is in refrigeration, the refrigerant flows from the second end of the first heat exchange tube group to the first end, and 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 first heat exchange tube group 10 is in heating, the refrigerant flows from the first end of the first heat exchange tube group to the second end. In this way, the flow path of the refrigerant becomes longer, the flowing branches become shorter, the flowing speed is accelerated, and the circulation is increased, the heat transfer coefficient on the inner side of the tube is increased, and the heat exchange efficiency is improved. The first heat exchange tube group 10 realizes multiple evaporation branches and fewer condensation branches through the flow splitting assembly, which can improve the energy efficiency of the air conditioner. In addition, a third dehumidifying valve 203 is disposed within 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, different temperature ranges can be formed between the first heat exchange tube group 10 and the second heat exchange tube group 40 through the third dehumidifying valve 203, and thus dehumidification can be realized. In this way, while the air conditioner is dehumidifying, it can also take into account the energy efficiency of the air conditioner when switching between refrigeration and heating.

[0110] 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. Among them, the third dehumidifying valve 203 is disposed on the connecting pipeline 402.

[0111] In the embodiment of the present disclosure, the third dehumidifying valve 203 is disposed on the connecting pipeline 402, and the third dehumidifying 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.

[0112] Optionally, the number of the third dehumidification valves is plural, and the plural third dehumidification valves are arranged in parallel in the communication pipeline. In this way, one or more of the third dehumidification valves can be selectively opened for throttling to adjust the throttling effect, achieve different temperatures, and further adjust the refrigeration and dehumidification effects.

[0113] Optionally, the first end of the first heat exchange tube group 10 is adapted to communicate with the compressor, the first end of the second heat exchange tube group 40 communicates with 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 communicate with the outdoor unit.

[0114] In the embodiment of the present disclosure, when the refrigerant of the first heat exchange tube group 10 flows from the first end of the first heat exchange tube group to the second end of the first heat exchange tube group, the high-temperature refrigerant flows into the second heat exchange tube group 40 from the first heat exchange tube group 10. Specifically, the high-temperature refrigerant sequentially flows through a plurality of series-connected heat exchange channels of the first heat exchange tube group 10, and then can flow into the second heat exchange tube group 40 after throttling and cooling through the dehumidification valve 20, and then flows 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 dehumidification be achieved, but also the refrigerant flow in the first heat exchange tube group 10 will not be affected, ensuring the condensation effect and the normal operation of the air conditioner.

[0115] 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 dehumidification valve 20 and then flows into the first heat exchange tube group 10. In this way, the temperature of the second heat exchange tube group 40 is greater than that of the first heat exchange tube group 10. In this way, the first heat exchange tube group 10 is a refrigeration and dehumidification section, and the second heat exchange tube group 40 is a heating section, and refrigeration, dehumidification and reheating can be achieved.

[0116] 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.

[0117] In the embodiment 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, and the two-phase state cold impacts the valve core, resulting in very loud noise, large throttling energy loss, and affecting 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. The ratio range of the area of the first heat exchange tube group 10 to the area of the heat exchanger is 1 / 3 - 3 / 4, which can ensure sufficient condensation of the refrigerant, the refrigerant is completely changed into a liquid state, or even a subcooled state, which is beneficial to dehumidification and has low noise.

[0118] 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.

[0119] In the embodiments of the present disclosure, 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, which can ensure the uniform flow 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.

[0120] Exemplarily, 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, 3 / 4, etc.

[0121] Optionally, when the heat exchanger includes a third dehumidification valve, the heat exchanger may further include a first dehumidification valve and / or a second dehumidification valve.

[0122] Optionally, when the heat exchanger includes a first dehumidification valve and a third dehumidification valve, when the refrigerant flows from the first end of the heat exchange tube group to the second end of the heat exchange tube group, the first dehumidification valve can be fully opened without throttling or can be opened with throttling. When the first dehumidification valve is fully opened without throttling and the third dehumidification valve is throttled, the section between the third dehumidification valve and the first end of the heat exchanger is the condensation reheating section, and the section between the third dehumidification valve and the second end of the heat exchanger is the dehumidification section. When both the first dehumidification valve and the third dehumidification valve are opened with throttling, three different temperatures are formed along the refrigerant flow direction of the heat exchanger. In this way, when the air flow flows from the first heat exchange tube group to the second heat exchange tube group, it can be reheated first and then undergo two-stage refrigeration dehumidification to achieve deep reheating dehumidification. When the refrigerant flows from the second end of the heat exchange tube group to the first end of the heat exchange tube group, the first dehumidification valve is fully opened without throttling, the third dehumidification valve is a throttling device, the refrigerant flowing out of the outdoor unit flows into the fourth heat exchange section for condensation and heat dissipation, and then flows into the third dehumidification valve for throttling and then into the first heat exchange tube group. In this way, when the air flow flows from the first heat exchange tube group to the second heat exchange tube group, it can achieve refrigeration dehumidification and reheating. When both the first dehumidification valve and the third dehumidification valve are throttled, the first heat exchange tube group has two different temperatures, and deep refrigeration dehumidification and then reheating can be achieved.

[0123] It can be understood that when the heat exchanger includes a second dehumidification valve and a third dehumidification valve, its working principle is the same as that of the heat exchanger including a first dehumidification valve and a third dehumidification valve, and will not be elaborated here.

[0124] Optionally, the heat exchanger includes a first dehumidification valve, a second dehumidification valve, and a third dehumidification valve. The first dehumidification valve 201 and the second dehumidification valve 202 are fully open without throttling. 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 into 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. The air flow can first flow through the first heat exchange tube group 10 and then through the second heat exchange tube group 40, or first flow through the second heat exchange tube group 40 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 will not be affected, ensuring the condensation effect and the normal operation of the air conditioner. When the refrigerant in the first heat exchange tube group 10 flows from the first end of the first heat exchange tube group to the second end of the first heat exchange tube group, 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 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.

[0125] The refrigerant flows from the second heat exchange tube group 40 to the first heat exchange tube group 10. After the refrigerant flowing out of the second heat exchange tube group 40 is throttled by the third dehumidification valve 203, it then flows into the first heat exchange tube group 10, and the first dehumidification valve and the second dehumidification valve are fully open 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, capable of achieving refrigeration, dehumidification, and reheating. 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 reheating can be achieved after deep refrigeration.

[0126] Optionally, one heat exchange channel includes one or more heat exchange sections. When there are multiple heat exchange channels, the multiple heat exchange channels are arranged in parallel or in series. This can ensure the performance requirements of the heat exchanger in different working modes.

[0127] Exemplarily, the first heat exchange channel includes multiple heat exchange sections arranged in parallel, which makes the distribution of the refrigerant flowing into the first heat exchange channel more uniform, improving the uniformity and heat exchange effect of the heat exchanger.

[0128] 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 facilitates installation in the indoor unit.

[0129] The embodiments of the present disclosure also provide an air conditioner, which includes an indoor unit and the heat exchanger as described in any one of the above.

[0130] The air conditioner according to the embodiment 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 according to any one of the above, which will not be elaborated herein.

[0131] 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 having an air inlet and an air outlet, and the 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.

[0132] In the embodiment 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 to the second end of the heat exchanger, the heat exchanger can form reheating and dehumidification. When the refrigerant flows from the second end to the first end of the heat exchanger, the heat exchanger can form refrigeration or deep dehumidification.

[0133] Optionally, when the 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 to the second end of the heat exchanger, the heat exchanger can form reheating and dehumidification. When the refrigerant flows from the second end to the first end of the heat exchanger, the heat exchanger can form refrigeration, dehumidification, and reheating.

[0134] Optionally, the outdoor unit includes an outdoor heat exchanger, and the outdoor heat exchanger is a variable flow splitting heat exchanger.

[0135] 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 only represent 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 parts and features of other embodiments. The embodiments of the present disclosure are not limited to the structures described above 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 only limited by the appended claims.

Claims

1. A heat exchanger, characterized in that, Comprising: A heat exchange tube group, including a plurality of interconnected heat exchange channels; A dehumidification valve, disposed between two adjacent heat exchange channels, for throttling 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; A liquid storage tank, disposed upstream of the dehumidification valve.

2. The heat exchanger according to claim 1, wherein The first end of the heat exchange tube group is adapted to communicate with a compressor, and the second end of the heat exchange tube group is adapted to communicate with a throttling device. When the refrigerant flows from the first end of the heat exchange tube group to the second end of the heat exchange tube group, the dehumidification valve is located between at least two heat exchange channels, and the liquid storage tank is located on the side of the dehumidification valve facing the first end of the heat exchange tube group.

3. The heat exchanger according to claim 2, 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, a condensation reheating section is formed between the dehumidification valve and the first end of the heat exchange tube group, and a dehumidification section is formed between the dehumidification valve and the second end of the heat exchange tube group; wherein, the liquid storage tank is located between the outlet of the condensation reheating section and the inlet of the dehumidification valve.

4. The heat exchanger according to claim 3, wherein The area of the condensation reheating section is greater than the area of the dehumidification section, or the area of the condensation reheating section is less than the area of the dehumidification section.

5. The heat exchanger according to claim 2, characterized in that, Further comprising: A gas-liquid separator, disposed on the side of the dehumidification valve facing the second end of the heat exchange tube group. The gas outlet of the gas-liquid separator is adapted to communicate with a throttling device, and the liquid outlet of the gas-liquid separator communicates with the heat exchange tube group.

6. The heat exchanger according to claim 2, wherein The number of dehumidification valves is one or more. When there are multiple dehumidification valves, and the refrigerant flows from the first end of the heat exchange tube group to the second end of the heat exchange tube group, the multiple dehumidification valves are arranged in an alternating and spaced manner with multiple series-connected heat exchange channels.

7. The heat exchanger according to claim 6, wherein When there are multiple dehumidification valves, the number of liquid storage tanks is the same as and corresponds one-to-one with the number of dehumidification valves.

8. The heat exchanger according to any one of claims 1 to 7, wherein The multiple heat exchange channels include a first heat exchange channel, a second heat exchange channel, and a third heat exchange channel. When the refrigerant flows from the first end of the heat exchange tube group to the second end of the heat exchange tube group, the first heat exchange channel, the second heat exchange channel, and the third heat exchange channel are connected in series in sequence; The heat exchange tube group further includes: A second pipeline, with the first end communicating with the first end of the second heat exchange channel and the second end communicating with 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; The dehumidification valve is disposed on the second pipeline and / or the fourth pipeline.

9. The heat exchanger according to claim 8, characterized in that, The heat exchange tube group further includes: A first pipeline, with the first end adapted to communicate with a compressor and the second end communicating with the first end of the first heat exchange channel and the first end of the second heat exchange channel; A second pipeline, with the first end communicating with the second end of the first pipeline and the first end of the second heat exchange channel and the second end communicating with the first end of the third heat exchange channel; A diverter, with the first end of the diverter communicating with the fourth pipeline 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 both being adapted to communicate with a throttling device; A third pipeline, adapted to be connected between the second end of the diverter and the throttling device; The flow splitting component includes a first valve and a second valve. The first valve is arranged in a 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 arranged in a third pipeline and 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.

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

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