Air outlet structure and air conditioner

Abstract

The application relates to an air outlet structure and an air conditioner, and relates to the technical field of air conditioners. The air outlet structure comprises a shell, a first heat exchanger, a second heat exchanger, a first fan and a second fan. The shell comprises a fresh air cavity, a return air cavity and a heat exchange and dehumidification cavity which are separated from each other. The first heat exchanger is arranged in the heat exchange and dehumidification cavity. The second heat exchanger is arranged in the heat exchange and dehumidification cavity and is located downstream of the airflow of the first heat exchanger. The first fan is arranged in the fresh air cavity and is used for conveying fresh air from the fresh air cavity into the heat exchange and dehumidification cavity. The second fan is arranged in the return air cavity and is used for conveying return air from the return air cavity into the heat exchange and dehumidification cavity. The air outlets of the first fan and the second fan are configured to be inclined towards each other, so that the fresh air and the return air are mixed to form mixed air in the heat exchange and dehumidification cavity and upstream of the airflow of the first heat exchanger. The technical scheme disclosed by the application can efficiently dehumidify and simultaneously ensure indoor comfortable temperature.

Description

Technical Field

[0001] This application relates to the field of air conditioning, and more particularly to an air outlet structure and an air conditioner. Background Technology

[0002] During air conditioning operation, the mixed air formed by the mixing of outdoor fresh air and indoor return air will condense if its temperature is lower than its dew point temperature. Existing air conditioners rely on lowering the temperature of the heat exchanger for dehumidification. However, deep dehumidification often results in the outlet air being in a near-saturated state of low temperature and high humidity, which can lead to secondary condensation. Secondary condensation can easily lead to a decrease in the system's heat exchange efficiency, an increase in the risk of component failure, and ultimately affect the long-term stable operation of the air conditioning system. How to efficiently dehumidify the mixed air in high humidity environments while maintaining a comfortable indoor temperature is a key problem that urgently needs to be solved. Utility Model Content

[0003] This application provides an air outlet structure and an air conditioner that can efficiently dehumidify while maintaining a comfortable indoor temperature.

[0004] Firstly, this application provides an air outlet structure, including: The housing includes a phase-separated fresh air chamber, a return air chamber, and a heat exchange and dehumidification chamber; The first heat exchanger is disposed inside the heat exchange and dehumidification chamber; The second heat exchanger is disposed in the heat exchange and dehumidification chamber and is located downstream of the airflow of the first heat exchanger; The first fan is installed inside the fresh air cavity and is used to transport fresh air from the fresh air cavity to the heat exchange and dehumidification cavity; The second fan is disposed in the return air cavity and is used to transport the return air from the return air cavity to the heat exchange and dehumidification cavity; the air outlets of the first fan and the second fan are constructed to be inclined towards each other so that the fresh air and the return air are mixed in the heat exchange and dehumidification cavity and upstream of the airflow of the first heat exchanger to form mixed air.

[0005] In some embodiments, the fresh air cavity and the return air cavity are arranged adjacent to each other and side by side, the heat exchange and dehumidification cavity is arranged adjacent to the return air cavity and the fresh air cavity respectively, the first fan and the second fan are arranged side by side and are symmetrical about a plane perpendicular to the arrangement direction of the fresh air cavity and the return air cavity.

[0006] In some embodiments, the angle between the central axis of the air outlet of the first fan and the central axis of the air outlet of the second fan is 45°-90°.

[0007] In some embodiments, the air outlet structure further includes: A temperature and humidity sensor is installed on the windward side of the first heat exchanger and is used to detect the temperature and humidity of the mixed air. The controller is electrically connected to the first heat exchanger, the second heat exchanger, and the temperature and humidity sensor, respectively. The controller is configured to control the operation of the first heat exchanger and the second heat exchanger based on the detection values ​​of the temperature and humidity sensor.

[0008] In some embodiments, a main partition is provided inside the housing to divide the housing into an air inlet chamber and a heat exchange and dehumidification chamber; a secondary partition is provided inside the air inlet chamber to divide the air inlet chamber into a fresh air chamber and a return air chamber; the fresh air chamber is provided with a fresh air inlet for introducing fresh air, and the return air chamber is provided with a return air inlet for introducing return air; The sub-partition is configured to selectively isolate or connect the fresh air cavity with the return air cavity.

[0009] In some embodiments, the sub-partition includes: The main body is connected to the main partition and the inner wall of the shell, and the main body is provided with through holes; A baffle is rotatably disposed on the main body. The baffle is configured to allow the through hole to be opened by rotation to connect the fresh air chamber and the return air chamber, or to close the through hole to isolate the fresh air chamber and the return air chamber.

[0010] In some embodiments, the baffle includes a first working position, a second working position, and a third working position; in the first working position, the baffle closes the through hole to isolate the fresh air cavity and the return air cavity; in the second working position, the baffle opens the through hole and tilts towards the fresh air cavity so that the return air introduced by the return air inlet can flow to the first fan and the second fan respectively; in the third working position, the baffle opens the through hole and tilts towards the return air cavity so that the fresh air introduced by the fresh air inlet can flow to the first fan and the second fan respectively.

[0011] In some embodiments, the air outlet structure further includes: An air pretreatment module is respectively installed at the fresh air inlet and the return air inlet; An air guide plate is disposed inside the heat exchange and dehumidification chamber and located upstream of the airflow of the first heat exchanger.

[0012] In some embodiments, the air outlet structure further includes a refrigerant circulation assembly, which is connected to the first heat exchanger and the second heat exchanger respectively.

[0013] Secondly, this application provides an air conditioner, including the air outlet structure described above.

[0014] The technical solutions provided in this application have the following advantages compared with the prior art: The air outlet structure provided in this application divides the casing into a fresh air chamber, a return air chamber, and a heat exchange and dehumidification chamber. With the outlets of the first and second fans arranged at opposite angles, the fresh air and return air converge upstream of the first heat exchanger, achieving rapid and thorough mixing. This avoids the problem of airflow stratification or uneven mixing affecting dehumidification and heat exchange efficiency, providing a uniform airflow foundation for subsequent dehumidification and heat exchange. The first and second heat exchangers, arranged sequentially along the airflow direction, allow the mixed air to flow through both stages, achieving graded treatment of dehumidification followed by heat exchange. The first heat exchanger efficiently condenses and removes moisture, while the second heat exchanger heats the low-temperature, dry airflow, preventing secondary condensation and discomfort from low temperatures. Compared to a single heat exchanger structure, this application effectively improves dehumidification while better matching indoor comfort temperature requirements. It avoids the problems of excessive cooling or incomplete dehumidification caused by single heat exchange, resolving the contradiction between dehumidification and comfort in existing air conditioning systems. It delivers air with suitable temperature and humidity, fundamentally eliminating secondary condensation and significantly improving comfort. Attached Figure Description

[0015] The accompanying drawings, which are incorporated in and form part of this specification, illustrate embodiments consistent with the present invention and, together with the description, serve to explain the principles of the present invention.

[0016] To more clearly illustrate the technical solutions in the embodiments of this utility model or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, for those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0017] One or more embodiments are illustrated by way of example with reference numerals in the accompanying drawings. These illustrations do not constitute a limitation on the embodiments. Elements with the same reference numerals in the drawings are denoted as similar elements. Unless otherwise stated, the figures in the drawings are not to be limited by scale.

[0018] Figure 1 This is a schematic diagram of the air outlet structure provided in the embodiment of this application in the first working position; Figure 2 A schematic diagram of the air outlet structure provided in the embodiment of this application in the second working position; Figure 3 This is a schematic diagram of the air outlet structure provided in the embodiment of this application in the third working position.

[0019] Explanation of reference numerals in the attached figures: 10. Shell; 110. Fresh air chamber; 1101. Fresh air inlet; 120. Return air chamber; 1201. Return air inlet; 130. Heat exchange and dehumidification chamber; 1301. Air outlet; 1302. Partition plate; 20. First heat exchanger; 30. Second heat exchanger; 40. First fan; 50. Second fan; 60. Main partition; 70. Secondary partition; 710. Main body; 720. Baffle; 80. Air pretreatment module; 90. Air guide plate. Detailed Implementation

[0020] To make the objectives, technical solutions, and advantages of the embodiments of this application clearer, the technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0021] The following disclosure provides numerous different embodiments or examples for implementing various structures of the present invention. To simplify the disclosure, specific examples of components and arrangements are described below. These are merely examples and are not intended to limit the scope of the invention. Furthermore, reference numerals and / or letters may be repeated in different examples. Such repetition is for simplification and clarity and does not in itself indicate a relationship between the various embodiments and / or arrangements discussed.

[0022] For ease of description, spatial relative terms may be used in the text to describe the relative position or movement of one element or feature relative to another element or feature, as shown in the figure. These relative terms include, for example, "inside," "outside," "middle," "outer," "below," "below," "above," "front," "back," etc. Such spatial relative terms are intended to include different orientations of the device in use or operation, other than those depicted in the figure. For example, if the device in the figure undergoes a positional flip, orientation change, or change of motion, these directional indications will change accordingly. For instance, an element described as "below other elements or features" or "below other elements or features" will subsequently be oriented "above other elements or features" or "above other elements or features." Therefore, the example term "below" can include both upper and lower orientations. The device may be otherwise oriented (rotated 90 degrees or in other directions), and the spatial relative descriptors used in the text will be interpreted accordingly.

[0023] During air conditioning operation, to ensure indoor air circulation and freshness, fresh outdoor air needs to be introduced and mixed with indoor return air to form a mixed airflow. If the temperature is below its dew point temperature, condensation will occur, and the higher the humidity, the greater the condensation. Current air conditioners generally cool and dehumidify the mixed airflow by lowering the heat exchanger temperature. To achieve deep dehumidification, the surface temperature of the heat exchanger must be reduced to a very low level. This can easily lead to excessively low outlet air temperature, making it near-saturated air with low temperature and high humidity. This near-saturated airflow comes into contact with components such as the air supply duct and outlet during transport. These components, acting as cold sources, further cool the thin layer of air they contact. When this thin layer of air is cooled below its dew point temperature, water vapor condenses and forms on the surface of the components, thus creating secondary condensation. Existing air conditioners lack an effective mechanism to deal with this condensation, making it impossible to avoid secondary condensation. This leads to a decrease in system heat exchange efficiency, an increase in the risk of component failure, and ultimately affects the long-term stable operation of the air conditioning system. How to efficiently dehumidify the mixed air while maintaining a comfortable indoor temperature in a high humidity environment is a key problem that urgently needs to be solved.

[0024] Example 1 In response to the above technical problems, such as Figure 1-3As shown, this application embodiment provides an air outlet structure, including a housing 10, a first heat exchanger 20, a second heat exchanger 30, a first fan 40, and a second fan 50; the housing 10 includes a fresh air chamber 110, a return air chamber 120, and a heat exchange and dehumidification chamber 130 separated by phases; the first heat exchanger 20 is disposed in the heat exchange and dehumidification chamber 130; the second heat exchanger 30 is disposed in the heat exchange and dehumidification chamber 130 and located downstream of the airflow of the first heat exchanger 20; the first fan 40 is disposed in the fresh air chamber 50. The first fan 40 and the second fan 50 are located in the heat exchange and dehumidification chamber 130 and are used to transport fresh air from the fresh air chamber 110 to the heat exchange and dehumidification chamber 130. The second fan 50 is located in the return air chamber 120 and is used to transport return air from the return air chamber 120 to the heat exchange and dehumidification chamber 130. The air outlets 1301 of the first fan 40 and the second fan 50 are constructed to be inclined towards each other so that the fresh air and the return air are mixed in the heat exchange and dehumidification chamber 130 and upstream of the airflow of the first heat exchanger 20 to form mixed air.

[0025] As can be seen from the above, by dividing the shell 10 into a fresh air chamber 110, a return air chamber 120 and a heat exchange and dehumidification chamber 130, and coordinating the air outlets 1301 of the first fan 40 and the second fan 50 to be arranged at opposite angles, the fresh air and return air form a counter-current convergence upstream of the airflow of the first heat exchanger 20, which quickly and fully mixes the air, avoiding the problem of airflow stratification or uneven mixing affecting the dehumidification and heat exchange effect, and providing a uniform airflow basis for subsequent dehumidification and heat exchange. By arranging a first heat exchanger 20 and a second heat exchanger 30 sequentially along the airflow direction, the mixed air flows through the two stages of heat exchangers in sequence, achieving a staged treatment of dehumidification followed by heat exchange. The first heat exchanger 20 efficiently condenses and precipitates moisture, while the second heat exchanger 30 heats the low-temperature dry airflow, avoiding secondary condensation and discomfort from low temperatures. Compared to a single heat exchanger structure, this application can effectively improve the dehumidification effect and better match the needs of indoor comfort temperature, avoiding the problems of excessive cooling or incomplete dehumidification caused by single heat exchangers. It solves the contradiction between dehumidification and comfort in existing air conditioning systems, and can deliver air with suitable temperature and humidity, fundamentally eliminating secondary condensation, significantly improving comfort, breaking the functional contradiction of a single heat exchanger, and significantly improving the heat exchange efficiency per unit energy consumption.

[0026] It should be noted that the staged treatment of the mixed air, which involves dehumidification followed by heat exchange, means that the first heat exchanger 20 is used for dehumidification, while the second heat exchanger 30 is used for heat exchange and temperature increase. Specifically, when the first heat exchanger 20 is used for dehumidification, its temperature is kept as low as possible to ensure that when the humid mixed air comes into contact with it, the temperature of the mixed air is cooled below the dew point temperature, causing the moisture in the mixed air to condense and precipitate, thus reducing the humidity of the mixed air and achieving thorough dehumidification. Although the air treated by the first heat exchanger 20 has reduced humidity, its temperature is also low. If it is directly sent into the room or air duct, it itself is a cold source and will immediately cool the surfaces it contacts (such as air outlets), leading to secondary condensation. Therefore, the second heat exchanger 30 reheats the dry, low-temperature mixed air, increasing the supply temperature of the mixed air and avoiding discomfort caused by low-temperature airflow, thus fundamentally eliminating secondary condensation.

[0027] It should also be noted that the air outlets 1301 of the first fan 40 and the second fan 50 can be directly connected to the heat exchange and dehumidification chamber 130.

[0028] Example 2 To address the aforementioned technical issues, such as Figure 1-3 As shown, this application embodiment provides an air outlet structure, including a housing 10, a first heat exchanger 20, a second heat exchanger 30, a first fan 40, and a second fan 50; the housing 10 includes a fresh air chamber 110, a return air chamber 120, and a heat exchange and dehumidification chamber 130 separated by phases; the first heat exchanger 20 is disposed in the heat exchange and dehumidification chamber 130; the second heat exchanger 30 is disposed in the heat exchange and dehumidification chamber 130 and located downstream of the airflow of the first heat exchanger 20; the first fan 40 is disposed in the fresh air chamber 50. The first fan 40 and the second fan 50 are located in the heat exchange and dehumidification chamber 130 and are used to transport fresh air from the fresh air chamber 110 to the heat exchange and dehumidification chamber 130. The second fan 50 is located in the return air chamber 120 and is used to transport return air from the return air chamber 120 to the heat exchange and dehumidification chamber 130. The air outlets 1301 of the first fan 40 and the second fan 50 are constructed to be inclined towards each other so that the fresh air and the return air are mixed in the heat exchange and dehumidification chamber 130 and upstream of the airflow of the first heat exchanger 20 to form mixed air.

[0029] As can be seen from the above, by dividing the shell 10 into a fresh air chamber 110, a return air chamber 120 and a heat exchange and dehumidification chamber 130, and coordinating the air outlets 1301 of the first fan 40 and the second fan 50 to be arranged at opposite angles, the fresh air and return air form a counter-current convergence upstream of the airflow of the first heat exchanger 20, which quickly and fully mixes the air, avoiding the problem of airflow stratification or uneven mixing affecting the dehumidification and heat exchange effect, and providing a uniform airflow basis for subsequent dehumidification and heat exchange. By arranging a first heat exchanger 20 and a second heat exchanger 30 sequentially along the airflow direction, the mixed air flows through the two stages of heat exchangers in sequence, achieving a staged treatment of dehumidification followed by heat exchange. The first heat exchanger 20 efficiently condenses and precipitates moisture, while the second heat exchanger 30 heats the low-temperature dry airflow, avoiding secondary condensation and discomfort from low temperatures. Compared to a single heat exchanger structure, this application can effectively improve the dehumidification effect and better match the needs of indoor comfort temperature, avoiding the problems of excessive cooling or incomplete dehumidification caused by single heat exchangers. It solves the contradiction between dehumidification and comfort in existing air conditioning systems, and can deliver air with suitable temperature and humidity, fundamentally eliminating secondary condensation, significantly improving comfort, breaking the functional contradiction of a single heat exchanger, and significantly improving the heat exchange efficiency per unit energy consumption.

[0030] It should be noted that the staged treatment of the mixed air, which involves dehumidification followed by heat exchange, means that the first heat exchanger 20 is used for dehumidification, while the second heat exchanger 30 is used for heat exchange and temperature increase. Specifically, when the first heat exchanger 20 is used for dehumidification, its temperature is kept as low as possible to ensure that when the humid mixed air comes into contact with it, the temperature of the mixed air is cooled below the dew point temperature, causing the moisture in the mixed air to condense and precipitate, thus reducing the humidity of the mixed air and achieving thorough dehumidification. Although the air treated by the first heat exchanger 20 has reduced humidity, its temperature is also low. If it is directly sent into the room or air duct, it itself is a cold source and will immediately cool the surfaces it contacts (such as air outlets), leading to secondary condensation. Therefore, the second heat exchanger 30 reheats the dry, low-temperature mixed air, increasing the supply temperature of the mixed air and avoiding discomfort caused by low-temperature airflow, thus fundamentally eliminating secondary condensation.

[0031] It should also be noted that the air outlets 1301 of the first fan 40 and the second fan 50 can be directly connected to the heat exchange and dehumidification chamber 130.

[0032] like Figure 1 As shown, in some embodiments, the fresh air chamber 110 and the return air chamber 120 are arranged side by side adjacent to each other, the heat exchange and dehumidification chamber 130 is arranged adjacent to the return air chamber 120 and the fresh air chamber 110 respectively, and the first fan 40 and the second fan 50 are arranged side by side and are symmetrical about a plane perpendicular to the arrangement direction of the fresh air chamber 110 and the return air chamber 120.

[0033] By arranging the fresh air chamber 110 and the return air chamber 120 side by side and adjacent to the heat exchange and dehumidification chamber 130, the path for fresh air and return air to be delivered to the heat exchange and dehumidification chamber 130 is shortened, reducing the energy consumption of the fan. At the same time, the chamber layout is more compact, reducing the overall volume of the structure. By arranging the first fan 40 and the second fan 50 side by side symmetrically, the fresh air and return air can form an opposing convergence at the inlet of the heat exchange and dehumidification chamber 130, which promotes the rapid and full fusion of the two airflows, avoids local uneven concentration, provides uniform mixed air for the two-stage heat exchanger to process in stages, and ensures the consistency of dehumidification and heat exchange effect. On the other hand, the symmetrical arrangement not only allows the air outlets 1301 of the first fan 40 and the second fan 50 to face the heat exchanger to the maximum extent, but also guides the airflow to flow naturally towards the heat exchanger, reducing airflow backflow and eddies, and shortening the flow path. At the same time, the symmetrical air outlets of the first fan 40 and the second fan 50 ensure relatively stable air pressure in the outlet area, avoiding uneven airflow distribution caused by local air pressure imbalance, ensuring that the mixed air flows evenly across the heat exchanger surface, further improving dehumidification and heat exchange efficiency. Moreover, stable air pressure reduces the energy consumption of the fans. In addition, the side-by-side arrangement of the fans can make full use of the adjacent and side-by-side space of the fresh air cavity 110 and the return air cavity 120, making the outlet structure more compact. At the same time, the symmetrical arrangement of the fans can counteract the vibration generated during the operation of the fans, ensuring the long-term stable operation of the outlet structure.

[0034] It should be noted that, as Figure 1 As shown, the length direction is parallel to the X direction, and the height direction is parallel to the Z direction; the fresh air cavity 110 and the return air cavity 120 are arranged adjacent to each other in the length direction, that is, the arrangement direction of the fresh air cavity 110 and the return air cavity 120 is the length direction; the heat exchange and dehumidification cavity 130 is located on the same side of the fresh air cavity 110 and the return air cavity 120 in the height direction, and is adjacent to the fresh air cavity 110 and the return air cavity 120. The fresh air in the fresh air cavity 110 and the return air in the return air cavity 120 are blown into the same heat exchange and dehumidification cavity 130; thus, the airflow path is clear, short circuits are avoided, and the layout is compact. At the same time, the speed of the first fan 40 and the second fan 50 can be adjusted respectively to control the mixing ratio of fresh air and return air.

[0035] It should also be noted that, such as Figure 1 As shown, the first fan 40 and the second fan 50 are arranged side by side in the length direction, and the first fan 40 and the second fan 50 are symmetrical about the plane P; the central axis of the air outlet 1301 of the first fan 40 is MM', and the central axis of the air outlet 1301 of the second fan 50 is NN'.

[0036] It should also be noted that, such as Figure 1 As shown, the first heat exchanger 20 and the second heat exchanger 30 are arranged at intervals in the height direction.

[0037] like Figure 1As shown, in some embodiments, the angle between the central axis of the air outlet 1301 of the first fan 40 and the central axis of the air outlet 1301 of the second fan 50 is 45°-90°.

[0038] By setting the angle between the central axes of the air outlets 1301 of the first fan 40 and the second fan 50 to 45°-90°, the fresh air and return air can form a suitable symmetry when entering the heat exchange and dehumidification chamber 130. This ensures that the fresh air and return air are fully mixed to form a uniform mixed air, and also guides the mixed air to flow towards the heat exchanger at a suitable angle, reducing energy loss caused by airflow impact. This balances mixing effect and stable operation, thus avoiding the problem of insufficient airflow impact intensity and low mixing efficiency caused by too small an angle, and also avoiding the phenomenon of airflow turbulence and increased fan energy consumption caused by too large an angle.

[0039] It should be noted that, as Figure 1 As shown, the angle between the central axis of the air outlet 1301 of the first fan 40 and the central axis of the air outlet 1301 of the second fan 50 is α, that is, α is 45°-90°.

[0040] It should also be noted that the distance between the first fan 40 and the second fan 50 in the length direction is 300-400mm, and the distance between the outer edge of the first fan 40 and the outer edge of the second fan 50 in the length direction is approximately equal to the length of the first heat exchanger 20, thereby ensuring heat exchange efficiency and compact structure.

[0041] It should also be noted that the distance between the first heat exchanger 20 and the second heat exchanger 30 in the height direction is 50-100mm; the distance between the first heat exchanger 20 and the first fan 40 in the height direction is 150-200mm, and the distance between the first heat exchanger 20 and the first fan 40 in the height direction is equal to the distance between the second heat exchanger 30 and the second fan 50 in the height direction.

[0042] In some embodiments, the air outlet structure further includes a temperature and humidity sensor and a controller; the temperature and humidity sensor is disposed on the windward surface of the first heat exchanger 20 and is used to detect the temperature and humidity of the mixed air; the controller is electrically connected to the first heat exchanger 20, the second heat exchanger 30 and the temperature and humidity sensor respectively, and the controller is configured to control the first heat exchanger 20 and the second heat exchanger 30 to work based on the detection values ​​of the temperature and humidity sensor.

[0043] By placing a temperature and humidity sensor on the windward side of the first heat exchanger 20, the temperature and humidity of the mixed air entering the heat exchange and dehumidification chamber 130 can be detected in real time, providing a reliable basis for the controller's control and avoiding problems such as misjudgment of condensation or control lag caused by lack of real-time detection. When the temperature and humidity sensor detects condensation in the mixed air, on the one hand, the controller controls the first heat exchanger 20 to operate at the maximum refrigerant flow rate to minimize the surface temperature of the first heat exchanger 20 and improve the condensation and dehumidification effect on the mixed air; on the other hand, it controls the first fan 40 and the second fan 50 to reduce their wind speeds to maintain laminar flow in the heat exchange and dehumidification chamber 130, extending the contact path and time between the airflow and the heat exchanger, ensuring that the moisture in the mixed air is fully condensed and precipitated, and improving dehumidification efficiency; at the same time, it controls the second heat exchanger 30 to perform heat exchange treatment, increasing the temperature of the low-temperature dry airflow after dehumidification by the first heat exchanger 20, reducing the temperature difference with the indoor environment or the surface of the air duct, and fundamentally eliminating secondary condensation caused by low-temperature airflow. When the temperature and humidity sensor detects no condensation in the mixed air, the controller controls the first heat exchanger 20 to perform basic dehumidification, while the second heat exchanger 30 is shut down or maintains low-power operation. The first fan 40 and the second fan 50 can be adjusted to appropriate wind speeds according to actual dehumidification needs, avoiding excessive operation of the equipment during non-condensation conditions, reducing overall energy consumption, and balancing dehumidification effect with energy saving and environmental protection. This ensures that the system can maintain stable operation under different humidity scenarios, reduce indoor temperature and humidity fluctuations, and improve comfort.

[0044] It should be noted that the controller controls the operating status of the first heat exchanger 20 and the second heat exchanger 30 based on whether the temperature and humidity sensor detects condensation. The temperature and humidity sensor detects the temperature and humidity of the mixed air. When the temperature and humidity sensor detects that the humidity of the mixed air exceeds the preset humidity threshold, it indicates that condensation has occurred in the mixed air. When the temperature and humidity sensor detects that the humidity of the mixed air does not exceed the preset humidity threshold, it indicates that condensation has not occurred in the mixed air.

[0045] It should also be noted that in high humidity scenarios, i.e., when the humidity in the indoor space increases rapidly and drastically in a short period of time, the first heat exchanger 20 is controlled to operate at maximum refrigerant flow to minimize the surface temperature of the first heat exchanger 20 and improve the condensation and dehumidification effect on the mixed air. On the other hand, the first fan 40 and the second fan 50 are controlled to reduce their wind speeds to maintain laminar flow in the heat exchange and dehumidification chamber 130, extending the contact path and time between the airflow and the heat exchanger, ensuring that the moisture in the mixed air is fully condensed and precipitated, and improving dehumidification efficiency. At the same time, the second heat exchanger 30 is controlled to operate at maximum heat exchange power to increase the temperature of the low-temperature dry airflow after dehumidification by the first heat exchanger 20, reducing the temperature difference with the indoor environment or the surface of the air duct, making the airflow close to the ambient temperature, and fundamentally preventing secondary condensation caused by low-temperature airflow.

[0046] In the gradual increase scenario, that is, the indoor humidity rises slowly and steadily, a step-by-step adjustment is adopted. The first heat exchanger 20 gradually increases the refrigerant flow and air speed at set intervals to ensure the dehumidification depth while avoiding airflow stagnation; the second heat exchanger 30 gradually increases the heat exchange power at set intervals to achieve a dynamic balance between heat exchange and energy consumption. In addition, the current humidity and the rate of change of humidity are used to determine whether the scenario is high humidity or gradual transition. Specifically, if the current humidity is greater than the preset humidity threshold and the rate of change of humidity is greater than the preset rate of change threshold, it is a high humidity scenario. If the current humidity is less than the preset humidity threshold and the rate of change of humidity is less than the preset rate of change threshold, and the rate of change of humidity is continuously greater than zero, it is a gradual transition scenario.

[0047] Example 3 To address the aforementioned technical issues, such as Figure 1-3 As shown, this application embodiment provides an air outlet structure, including a housing 10, a first heat exchanger 20, a second heat exchanger 30, a first fan 40, and a second fan 50; the housing 10 includes a fresh air chamber 110, a return air chamber 120, and a heat exchange and dehumidification chamber 130 separated by phases; the first heat exchanger 20 is disposed in the heat exchange and dehumidification chamber 130; the second heat exchanger 30 is disposed in the heat exchange and dehumidification chamber 130 and located downstream of the airflow of the first heat exchanger 20; the first fan 40 is disposed in the fresh air chamber 50. The first fan 40 and the second fan 50 are located in the heat exchange and dehumidification chamber 130 and are used to transport fresh air from the fresh air chamber 110 to the heat exchange and dehumidification chamber 130. The second fan 50 is located in the return air chamber 120 and is used to transport return air from the return air chamber 120 to the heat exchange and dehumidification chamber 130. The air outlets 1301 of the first fan 40 and the second fan 50 are constructed to be inclined towards each other so that the fresh air and the return air are mixed in the heat exchange and dehumidification chamber 130 and upstream of the airflow of the first heat exchanger 20 to form mixed air.

[0048] As can be seen from the above, by dividing the shell 10 into a fresh air chamber 110, a return air chamber 120 and a heat exchange and dehumidification chamber 130, and coordinating the air outlets 1301 of the first fan 40 and the second fan 50 to be arranged at opposite angles, the fresh air and return air form a counter-current convergence upstream of the airflow of the first heat exchanger 20, which quickly and fully mixes the air, avoiding the problem of airflow stratification or uneven mixing affecting the dehumidification and heat exchange effect, and providing a uniform airflow basis for subsequent dehumidification and heat exchange. By arranging a first heat exchanger 20 and a second heat exchanger 30 sequentially along the airflow direction, the mixed air flows through the two stages of heat exchangers in sequence, achieving a staged treatment of dehumidification followed by heat exchange. The first heat exchanger 20 efficiently condenses and precipitates moisture, while the second heat exchanger 30 heats the low-temperature dry airflow, avoiding secondary condensation and discomfort from low temperatures. Compared to a single heat exchanger structure, this application can effectively improve the dehumidification effect and better match the needs of indoor comfort temperature, avoiding the problems of excessive cooling or incomplete dehumidification caused by single heat exchangers. It solves the contradiction between dehumidification and comfort in existing air conditioning systems, and can deliver air with suitable temperature and humidity, fundamentally eliminating secondary condensation, significantly improving comfort, breaking the functional contradiction of a single heat exchanger, and significantly improving the heat exchange efficiency per unit energy consumption.

[0049] It should be noted that the staged treatment of the mixed air, which involves dehumidification followed by heat exchange, means that the first heat exchanger 20 is used for dehumidification, while the second heat exchanger 30 is used for heat exchange and temperature increase. Specifically, when the first heat exchanger 20 is used for dehumidification, its temperature is kept as low as possible to ensure that when the humid mixed air comes into contact with it, the temperature of the mixed air is cooled below the dew point temperature, causing the moisture in the mixed air to condense and precipitate, thus reducing the humidity of the mixed air and achieving thorough dehumidification. Although the air treated by the first heat exchanger 20 has reduced humidity, its temperature is also low. If it is directly sent into the room or air duct, it itself is a cold source and will immediately cool the surfaces it contacts (such as air outlets), leading to secondary condensation. Therefore, the second heat exchanger 30 reheats the dry, low-temperature mixed air, increasing the supply temperature of the mixed air and avoiding discomfort caused by low-temperature airflow, thus fundamentally eliminating secondary condensation.

[0050] It should also be noted that the air outlets 1301 of the first fan 40 and the second fan 50 can be directly connected to the heat exchange and dehumidification chamber 130.

[0051] like Figure 1 As shown, in some embodiments, the fresh air chamber 110 and the return air chamber 120 are arranged side by side adjacent to each other, the heat exchange and dehumidification chamber 130 is arranged adjacent to the return air chamber 120 and the fresh air chamber 110 respectively, and the first fan 40 and the second fan 50 are arranged side by side and are symmetrical about a plane perpendicular to the arrangement direction of the fresh air chamber 110 and the return air chamber 120.

[0052] By arranging the fresh air chamber 110 and the return air chamber 120 side by side and adjacent to the heat exchange and dehumidification chamber 130, the path for fresh air and return air to be delivered to the heat exchange and dehumidification chamber 130 is shortened, reducing the energy consumption of the fan. At the same time, the chamber layout is more compact, reducing the overall volume of the structure. By arranging the first fan 40 and the second fan 50 side by side symmetrically, the fresh air and return air can form an opposing convergence at the inlet of the heat exchange and dehumidification chamber 130, which promotes the rapid and full fusion of the two airflows, avoids local uneven concentration, provides uniform mixed air for the two-stage heat exchanger to process in stages, and ensures the consistency of dehumidification and heat exchange effect. On the other hand, the symmetrical arrangement not only allows the air outlets 1301 of the first fan 40 and the second fan 50 to face the heat exchanger to the maximum extent, but also guides the airflow to flow naturally towards the heat exchanger, reducing airflow backflow and eddies, and shortening the flow path. At the same time, the symmetrical air outlets of the first fan 40 and the second fan 50 ensure relatively stable air pressure in the outlet area, avoiding uneven airflow distribution caused by local air pressure imbalance, ensuring that the mixed air flows evenly across the heat exchanger surface, further improving dehumidification and heat exchange efficiency. Moreover, stable air pressure reduces the energy consumption of the fans. In addition, the side-by-side arrangement of the fans can make full use of the adjacent and side-by-side space of the fresh air cavity 110 and the return air cavity 120, making the outlet structure more compact. At the same time, the symmetrical arrangement of the fans can counteract the vibration generated during the operation of the fans, ensuring the long-term stable operation of the outlet structure.

[0053] It should be noted that, as Figure 1 As shown, the length direction is parallel to the X direction, and the height direction is parallel to the Z direction; the fresh air cavity 110 and the return air cavity 120 are arranged adjacent to each other in the length direction, that is, the arrangement direction of the fresh air cavity 110 and the return air cavity 120 is the length direction; the heat exchange and dehumidification cavity 130 is located on the same side of the fresh air cavity 110 and the return air cavity 120 in the height direction, and is adjacent to the fresh air cavity 110 and the return air cavity 120. The fresh air in the fresh air cavity 110 and the return air in the return air cavity 120 are blown into the same heat exchange and dehumidification cavity 130; thus, the airflow path is clear, short circuits are avoided, and the layout is compact. At the same time, the speed of the first fan 40 and the second fan 50 can be adjusted respectively to control the mixing ratio of fresh air and return air.

[0054] It should also be noted that, such as Figure 1 As shown, the first fan 40 and the second fan 50 are arranged side by side in the length direction, and the first fan 40 and the second fan 50 are symmetrical about the plane P; the central axis of the air outlet 1301 of the first fan 40 is MM', and the central axis of the air outlet 1301 of the second fan 50 is NN'.

[0055] It should also be noted that, such as Figure 1 As shown, the first heat exchanger 20 and the second heat exchanger 30 are arranged at intervals in the height direction.

[0056] like Figure 1As shown, in some embodiments, the angle between the central axis of the air outlet 1301 of the first fan 40 and the central axis of the air outlet 1301 of the second fan 50 is 45°-90°.

[0057] By setting the angle between the central axes of the air outlets 1301 of the first fan 40 and the second fan 50 to 45°-90°, the fresh air and return air can form a suitable symmetry when entering the heat exchange and dehumidification chamber 130. This ensures that the fresh air and return air are fully mixed to form a uniform mixed air, and also guides the mixed air to flow towards the heat exchanger at a suitable angle, reducing energy loss caused by airflow impact. This balances mixing effect and stable operation, thus avoiding the problem of insufficient airflow impact intensity and low mixing efficiency caused by too small an angle, and also avoiding the phenomenon of airflow turbulence and increased fan energy consumption caused by too large an angle.

[0058] It should be noted that, as Figure 1 As shown, the angle between the central axis of the air outlet 1301 of the first fan 40 and the central axis of the air outlet 1301 of the second fan 50 is α, that is, α is 45°-90°.

[0059] It should also be noted that the distance between the first fan 40 and the second fan 50 in the length direction is 300-400mm, and the distance between the outer edge of the first fan 40 and the outer edge of the second fan 50 in the length direction is approximately equal to the length of the first heat exchanger 20, thereby ensuring heat exchange efficiency and compact structure.

[0060] It should also be noted that the distance between the first heat exchanger 20 and the second heat exchanger 30 in the height direction is 50-100mm; the distance between the first heat exchanger 20 and the first fan 40 in the height direction is 150-200mm, and the distance between the first heat exchanger 20 and the first fan 40 in the height direction is equal to the distance between the second heat exchanger 30 and the second fan 50 in the height direction.

[0061] In some embodiments, the air outlet structure further includes a temperature and humidity sensor and a controller; the temperature and humidity sensor is disposed on the windward surface of the first heat exchanger 20 and is used to detect the temperature and humidity of the mixed air; the controller is electrically connected to the first heat exchanger 20, the second heat exchanger 30 and the temperature and humidity sensor respectively, and the controller is configured to control the first heat exchanger 20 and the second heat exchanger 30 to work based on the detection values ​​of the temperature and humidity sensor.

[0062] By placing a temperature and humidity sensor on the windward side of the first heat exchanger 20, the temperature and humidity of the mixed air entering the heat exchange and dehumidification chamber 130 can be detected in real time, providing a reliable basis for the controller's control and avoiding problems such as misjudgment of condensation or control lag caused by lack of real-time detection. When the temperature and humidity sensor detects condensation in the mixed air, on the one hand, the controller controls the first heat exchanger 20 to operate at the maximum refrigerant flow rate to minimize the surface temperature of the first heat exchanger 20 and improve the condensation and dehumidification effect on the mixed air; on the other hand, it controls the first fan 40 and the second fan 50 to reduce their wind speeds to maintain laminar flow in the heat exchange and dehumidification chamber 130, extending the contact path and time between the airflow and the heat exchanger, ensuring that the moisture in the mixed air is fully condensed and precipitated, and improving dehumidification efficiency; at the same time, it controls the second heat exchanger 30 to perform heat exchange treatment, increasing the temperature of the low-temperature dry airflow after dehumidification by the first heat exchanger 20, reducing the temperature difference with the indoor environment or the surface of the air duct, and fundamentally eliminating secondary condensation caused by low-temperature airflow. When the temperature and humidity sensor detects no condensation in the mixed air, the controller controls the first heat exchanger 20 to perform basic dehumidification, while the second heat exchanger 30 is shut down or maintains low-power operation. The first fan 40 and the second fan 50 can be adjusted to appropriate wind speeds according to actual dehumidification needs, avoiding excessive operation of the equipment during non-condensation conditions, reducing overall energy consumption, and balancing dehumidification effect with energy saving and environmental protection. This ensures that the system can maintain stable operation under different humidity scenarios, reduce indoor temperature and humidity fluctuations, and improve comfort.

[0063] It should be noted that the controller controls the operating status of the first heat exchanger 20 and the second heat exchanger 30 based on whether the temperature and humidity sensor detects condensation. The temperature and humidity sensor detects the temperature and humidity of the mixed air. When the temperature and humidity sensor detects that the humidity of the mixed air exceeds the preset humidity threshold, it indicates that condensation has occurred in the mixed air. When the temperature and humidity sensor detects that the humidity of the mixed air does not exceed the preset humidity threshold, it indicates that condensation has not occurred in the mixed air.

[0064] It should also be noted that in high humidity scenarios, i.e., when the humidity in the indoor space increases rapidly and drastically in a short period of time, the first heat exchanger 20 is controlled to operate at maximum refrigerant flow to minimize the surface temperature of the first heat exchanger 20 and improve the condensation and dehumidification effect on the mixed air. On the other hand, the first fan 40 and the second fan 50 are controlled to reduce their wind speeds to maintain laminar flow in the heat exchange and dehumidification chamber 130, extending the contact path and time between the airflow and the heat exchanger, ensuring that the moisture in the mixed air is fully condensed and precipitated, and improving dehumidification efficiency. At the same time, the second heat exchanger 30 is controlled to operate at maximum heat exchange power to increase the temperature of the low-temperature dry airflow after dehumidification by the first heat exchanger 20, reducing the temperature difference with the indoor environment or the surface of the air duct, making the airflow close to the ambient temperature, and fundamentally preventing secondary condensation caused by low-temperature airflow.

[0065] In the gradual increase scenario, i.e., the indoor humidity rises slowly and steadily, a step-by-step adjustment is adopted. The first heat exchanger 20 gradually increases the refrigerant flow and air velocity at set intervals to ensure the dehumidification depth while avoiding airflow stagnation; the second heat exchanger 30 gradually increases the heat exchange power at set intervals to achieve a dynamic balance between heat exchange and energy consumption. In addition, the current humidity and the rate of change of humidity are used to determine whether the scenario is high humidity or gradual transition. Specifically, if the current humidity is greater than the preset humidity threshold and the rate of change of humidity is greater than the preset rate of change threshold, it is a high humidity scenario. If the current humidity is less than the preset humidity threshold and the rate of change of humidity is less than the preset rate of change threshold, and the rate of change of humidity is continuously greater than zero, it is a gradual transition scenario.

[0066] like Figures 1-3 As shown, in some embodiments, a main partition 60 is provided inside the housing 10 to divide the housing 10 into an air inlet chamber and a heat exchange and dehumidification chamber 130; a secondary partition 70 is provided inside the air inlet chamber to divide the air inlet chamber into a fresh air chamber 110 and a return air chamber 120; the fresh air chamber 110 is provided with a fresh air inlet 1101 for introducing fresh air, and the return air chamber 120 is provided with a return air inlet 1201 for introducing return air; wherein, the secondary partition 70 is configured to selectively isolate or connect the fresh air chamber 110 and the return air chamber 120.

[0067] The main partition 60 divides the housing 10 into an air inlet chamber and a heat exchange and dehumidification chamber 130, ensuring orderly separation of airflow delivery and heat exchange and dehumidification processes, avoiding airflow turbulence, and facilitating subsequent processing. The secondary partition 70 further divides the air inlet chamber into a fresh air chamber 110 and a return air chamber 120. With their respective fresh air inlets 1101 and return air inlets 1201, fresh air and return air can be introduced separately. At the same time, the secondary partition 70 can selectively control the isolation or connection between the fresh air chamber 110 and the return air chamber 120, realizing the switching between independent air intake and mixed air intake. Specifically, when only a single air inlet is inlet, the secondary partition 70 connects the fresh air chamber 110 and the return air chamber 120; when both the return air inlet 1201 and the fresh air inlet 1101 are inlet, the secondary partition 70 isolates the fresh air chamber 110 and the return air chamber 120.

[0068] It should be noted that when fresh air or return air needs to be handled separately, a single air inlet will be selected for air intake.

[0069] It should also be noted that the fresh air inlet 1101 is located on the side of the fresh air cavity 110 away from the heat exchange and dehumidification cavity 130, and the return air inlet 1201 is located on the side of the return air cavity 120 away from the heat exchange and dehumidification cavity 130; the heat exchange and dehumidification cavity 130 is provided with an air outlet 1301, which is located on the side of the heat exchange and dehumidification cavity 130 away from the air inlet, and there can be multiple air outlets 1301; for example, such as Figure 1As shown, the fresh air inlet 1101 is located at the bottom of the fresh air chamber 110, the return air inlet 1201 is located at the bottom of the return air chamber 120, and the air outlet 1301 is located at the top of the heat exchange and dehumidification chamber 130.

[0070] like Figures 1-3 As shown, in some embodiments, the secondary partition 70 includes a main body 710 and a baffle 720; the main body 710 is connected to the main partition 60 and the inner wall of the housing 10 respectively, and a through hole is provided on the main body 710; the baffle 720 is rotatably disposed on the main body 710, and the baffle 720 is configured to be able to open the through hole by rotation to connect the fresh air chamber 110 and the return air chamber 120, or to close the through hole to isolate the fresh air chamber 110 and the return air chamber 120.

[0071] The main body 710 is connected to the main partition 60 and the inner wall of the shell 10 respectively to form a stable partition foundation. The through hole opened on the main body 710 provides a channel for the connection between the fresh air cavity 110 and the return air cavity 120. The baffle 720 is rotatably set on the main body 710. The through hole can be quickly opened or closed by rotating the baffle 720. The operation is convenient and simple and can meet the needs of different air intake conditions in a timely manner. When only a single air inlet is inlet, the baffle 720 rotates to open the through hole, connecting the fresh air chamber 110 and the return air chamber 120. At the same time, both the first fan 40 and the second fan 50 are controlled to work. On the one hand, the combined operation of the two fans avoids the efficiency limitations of a single fan and improves the processing efficiency of a single airflow. On the other hand, the two fans can operate in a low-frequency mode while ensuring the required air volume, which can effectively reduce the operating noise of the equipment compared to the high-frequency operation of a single fan. When the return air inlet 1201 and the fresh air inlet 1101 are inlet together, the baffle 720 rotates to close the through hole, isolating the fresh air chamber 110 and the return air chamber 120, ensuring that the fresh air and return air are mixed before entering the heat exchange and dehumidification chamber 130.

[0072] It should be noted that a drive component can be connected to the baffle 720 to drive the baffle 720 to rotate. The drive component can be, but is not limited to, a motor. The motor's shaft is connected to the baffle 720 to drive the baffle 720 to rotate, thereby realizing the opening and closing of the through hole.

[0073] like Figures 1-3 As shown, in some embodiments, the baffle 720 includes a first working position, a second working position, and a third working position; in the first working position, the baffle 720 closes the through hole to isolate the fresh air cavity 110 and the return air cavity 120; in the second working position, the baffle 720 opens the through hole and tilts towards the fresh air cavity 110 so that the return air introduced by the return air inlet 1201 can flow to the first fan 40 and the second fan 50 respectively; in the third working position, the baffle 720 opens the through hole and tilts towards the return air cavity 120 so that the fresh air introduced by the fresh air inlet 1101 can flow to the first fan 40 and the second fan 50 respectively.

[0074] In the first working position, the baffle 720 closes the through hole, isolating the fresh air cavity 110 and the return air cavity 120 to avoid cross-interference between fresh and return air. This is compatible with the operating condition where both the fresh air inlet 1101 and the return air inlet 1201 are inlet, ensuring that the fresh and return air mix before entering the heat exchange and dehumidification cavity 130, thus guaranteeing the heat exchange and dehumidification effect. In the second working position, the baffle 720 opens the through hole and tilts towards the fresh air cavity 110, forming a directional airflow structure. This guides the return air introduced by the return air inlet 1201 to be diverted to the first fan 40 and the second fan 50, avoiding concentrated load on a single fan. The first fan 40 and the second fan 50 can operate synchronously at low frequency, reducing noise and energy consumption while ensuring airflow, and improving the efficiency and stability of individual return air treatment. In the third working position, the baffle 720 opens its through-hole and tilts towards the return air cavity 120, forming a directional airflow structure to guide the fresh air introduced by the fresh air inlet 1101 to be diverted to the first fan 40 and the second fan 50, avoiding concentrated load on a single fan. At the same time, the first fan 40 and the second fan 50 can operate synchronously at low frequency, reducing noise and energy consumption while ensuring airflow, and improving the efficiency and stability of individual fresh air treatment. In addition, the baffle 720 achieves directional airflow guidance through its tilt angle, reducing eddies and resistance in the cavity, thus balancing operating efficiency and adaptability to operating conditions.

[0075] It should be noted that the baffle 720 includes, but is not limited to, the first working position, the second working position, and the third working position, as well as other working positions. It can be understood that when there is only a single air inlet, the baffle 720 can be rotated to be parallel to the length direction, which can also satisfy the requirement of diverting the airflow to the first fan 40 and the second fan 50.

[0076] Example 4 In response to the above technical problems, such as Figure 1-3 As shown, this application embodiment provides an air outlet structure, including a housing 10, a first heat exchanger 20, a second heat exchanger 30, a first fan 40, and a second fan 50; the housing 10 includes a fresh air chamber 110, a return air chamber 120, and a heat exchange and dehumidification chamber 130 separated by phases; the first heat exchanger 20 is disposed in the heat exchange and dehumidification chamber 130; the second heat exchanger 30 is disposed in the heat exchange and dehumidification chamber 130 and located downstream of the airflow of the first heat exchanger 20; the first fan 40 is disposed in the fresh air chamber 50. The first fan 40 and the second fan 50 are located in the heat exchange and dehumidification chamber 130 and are used to transport fresh air from the fresh air chamber 110 to the heat exchange and dehumidification chamber 130. The second fan 50 is located in the return air chamber 120 and is used to transport return air from the return air chamber 120 to the heat exchange and dehumidification chamber 130. The air outlets 1301 of the first fan 40 and the second fan 50 are constructed to be inclined towards each other so that the fresh air and the return air are mixed in the heat exchange and dehumidification chamber 130 and upstream of the airflow of the first heat exchanger 20 to form mixed air.

[0077] As can be seen from the above, by dividing the shell 10 into a fresh air chamber 110, a return air chamber 120 and a heat exchange and dehumidification chamber 130, and coordinating the air outlets 1301 of the first fan 40 and the second fan 50 to be arranged at opposite angles, the fresh air and return air form a counter-current convergence upstream of the airflow of the first heat exchanger 20, which quickly and fully mixes the air, avoiding the problem of airflow stratification or uneven mixing affecting the dehumidification and heat exchange effect, and providing a uniform airflow basis for subsequent dehumidification and heat exchange. By arranging a first heat exchanger 20 and a second heat exchanger 30 sequentially along the airflow direction, the mixed air flows through the two stages of heat exchangers in sequence, achieving a staged treatment of dehumidification followed by heat exchange. The first heat exchanger 20 efficiently condenses and precipitates moisture, while the second heat exchanger 30 heats the low-temperature dry airflow, avoiding secondary condensation and discomfort from low temperatures. Compared to a single heat exchanger structure, this application can effectively improve the dehumidification effect and better match the needs of indoor comfort temperature, avoiding the problems of excessive cooling or incomplete dehumidification caused by single heat exchangers. It solves the contradiction between dehumidification and comfort in existing air conditioning systems, and can deliver air with suitable temperature and humidity, fundamentally eliminating secondary condensation, significantly improving comfort, breaking the functional contradiction of a single heat exchanger, and significantly improving the heat exchange efficiency per unit energy consumption.

[0078] It should be noted that the staged treatment of the mixed air, which involves dehumidification followed by heat exchange, means that the first heat exchanger 20 is used for dehumidification, while the second heat exchanger 30 is used for heat exchange and temperature increase. Specifically, when the first heat exchanger 20 is used for dehumidification, its temperature is kept as low as possible to ensure that when the humid mixed air comes into contact with it, the temperature of the mixed air is cooled below the dew point temperature, causing the moisture in the mixed air to condense and precipitate, thus reducing the humidity of the mixed air and achieving thorough dehumidification. Although the air treated by the first heat exchanger 20 has reduced humidity, its temperature is also low. If it is directly sent into the room or air duct, it itself is a cold source and will immediately cool the surfaces it contacts (such as air outlets), leading to secondary condensation. Therefore, the second heat exchanger 30 reheats the dry, low-temperature mixed air, increasing the supply temperature of the mixed air and avoiding discomfort caused by low-temperature airflow, thus fundamentally eliminating secondary condensation.

[0079] It should also be noted that the air outlets 1301 of the first fan 40 and the second fan 50 can be directly connected to the heat exchange and dehumidification chamber 130.

[0080] like Figure 1 As shown, in some embodiments, the fresh air chamber 110 and the return air chamber 120 are arranged side by side adjacent to each other, the heat exchange and dehumidification chamber 130 is arranged adjacent to the return air chamber 120 and the fresh air chamber 110 respectively, and the first fan 40 and the second fan 50 are arranged side by side and are symmetrical about a plane perpendicular to the arrangement direction of the fresh air chamber 110 and the return air chamber 120.

[0081] By arranging the fresh air chamber 110 and the return air chamber 120 side by side and adjacent to the heat exchange and dehumidification chamber 130, the path for fresh air and return air to be delivered to the heat exchange and dehumidification chamber 130 is shortened, reducing the energy consumption of the fan. At the same time, the chamber layout is more compact, reducing the overall volume of the structure. By arranging the first fan 40 and the second fan 50 side by side symmetrically, the fresh air and return air can form an opposing convergence at the inlet of the heat exchange and dehumidification chamber 130, which promotes the rapid and full fusion of the two airflows, avoids local uneven concentration, provides uniform mixed air for the two-stage heat exchanger to process in stages, and ensures the consistency of dehumidification and heat exchange effect. On the other hand, the symmetrical arrangement not only allows the air outlets 1301 of the first fan 40 and the second fan 50 to face the heat exchanger to the maximum extent, but also guides the airflow to flow naturally towards the heat exchanger, reducing airflow backflow and eddies, and shortening the flow path. At the same time, the symmetrical air outlets of the first fan 40 and the second fan 50 ensure relatively stable air pressure in the outlet area, avoiding uneven airflow distribution caused by local air pressure imbalance, ensuring that the mixed air flows evenly across the heat exchanger surface, further improving dehumidification and heat exchange efficiency. Moreover, stable air pressure reduces the energy consumption of the fans. In addition, the side-by-side arrangement of the fans can make full use of the adjacent and side-by-side space of the fresh air cavity 110 and the return air cavity 120, making the outlet structure more compact. At the same time, the symmetrical arrangement of the fans can counteract the vibration generated during the operation of the fans, ensuring the long-term stable operation of the outlet structure.

[0082] It should be noted that, as Figure 1 As shown, the length direction is parallel to the X direction, and the height direction is parallel to the Z direction; the fresh air cavity 110 and the return air cavity 120 are arranged adjacent to each other in the length direction, that is, the arrangement direction of the fresh air cavity 110 and the return air cavity 120 is the length direction; the heat exchange and dehumidification cavity 130 is located on the same side of the fresh air cavity 110 and the return air cavity 120 in the height direction, and is adjacent to the fresh air cavity 110 and the return air cavity 120. The fresh air in the fresh air cavity 110 and the return air in the return air cavity 120 are blown into the same heat exchange and dehumidification cavity 130; thus, the airflow path is clear, short circuits are avoided, and the layout is compact. At the same time, the speed of the first fan 40 and the second fan 50 can be adjusted respectively to control the mixing ratio of fresh air and return air.

[0083] It should also be noted that, such as Figure 1 As shown, the first fan 40 and the second fan 50 are arranged side by side in the length direction, and the first fan 40 and the second fan 50 are symmetrical about the plane P; the central axis of the air outlet 1301 of the first fan 40 is MM', and the central axis of the air outlet 1301 of the second fan 50 is NN'.

[0084] It should also be noted that, such as Figure 1 As shown, the first heat exchanger 20 and the second heat exchanger 30 are arranged at intervals in the height direction.

[0085] like Figure 1As shown, in some embodiments, the angle between the central axis of the air outlet 1301 of the first fan 40 and the central axis of the air outlet 1301 of the second fan 50 is 45°-90°.

[0086] By setting the angle between the central axes of the air outlets 1301 of the first fan 40 and the second fan 50 to 45°-90°, the fresh air and return air can form a suitable symmetry when entering the heat exchange and dehumidification chamber 130. This ensures that the fresh air and return air are fully mixed to form a uniform mixed air, and also guides the mixed air to flow towards the heat exchanger at a suitable angle, reducing energy loss caused by airflow impact. This balances mixing effect and stable operation, thus avoiding the problem of insufficient airflow impact intensity and low mixing efficiency caused by too small an angle, and also avoiding the phenomenon of airflow turbulence and increased fan energy consumption caused by too large an angle.

[0087] It should be noted that, as Figure 1 As shown, the angle between the central axis of the air outlet 1301 of the first fan 40 and the central axis of the air outlet 1301 of the second fan 50 is α, that is, α is 45°-90°.

[0088] It should also be noted that the distance between the first fan 40 and the second fan 50 in the length direction is 300-400mm, and the distance between the outer edge of the first fan 40 and the outer edge of the second fan 50 in the length direction is approximately equal to the length of the first heat exchanger 20, thereby ensuring heat exchange efficiency and compact structure.

[0089] It should also be noted that the distance between the first heat exchanger 20 and the second heat exchanger 30 in the height direction is 50-100mm; the distance between the first heat exchanger 20 and the first fan 40 in the height direction is 150-200mm, and the distance between the first heat exchanger 20 and the first fan 40 in the height direction is equal to the distance between the second heat exchanger 30 and the second fan 50 in the height direction.

[0090] In some embodiments, the air outlet structure further includes a temperature and humidity sensor and a controller; the temperature and humidity sensor is disposed on the windward surface of the first heat exchanger 20 and is used to detect the temperature and humidity of the mixed air; the controller is electrically connected to the first heat exchanger 20, the second heat exchanger 30 and the temperature and humidity sensor respectively, and the controller is configured to control the first heat exchanger 20 and the second heat exchanger 30 to work based on the detection values ​​of the temperature and humidity sensor.

[0091] By placing a temperature and humidity sensor on the windward side of the first heat exchanger 20, the temperature and humidity of the mixed air entering the heat exchange and dehumidification chamber 130 can be detected in real time, providing a reliable basis for the controller's control and avoiding problems such as misjudgment of condensation or control lag caused by lack of real-time detection. When the temperature and humidity sensor detects condensation in the mixed air, on the one hand, the controller controls the first heat exchanger 20 to operate at the maximum refrigerant flow rate to minimize the surface temperature of the first heat exchanger 20 and improve the condensation and dehumidification effect on the mixed air; on the other hand, it controls the first fan 40 and the second fan 50 to reduce their wind speeds to maintain laminar flow in the heat exchange and dehumidification chamber 130, extending the contact path and time between the airflow and the heat exchanger, ensuring that the moisture in the mixed air is fully condensed and precipitated, and improving dehumidification efficiency; at the same time, it controls the second heat exchanger 30 to perform heat exchange treatment, increasing the temperature of the low-temperature dry airflow after dehumidification by the first heat exchanger 20, reducing the temperature difference with the indoor environment or the surface of the air duct, and fundamentally eliminating secondary condensation caused by low-temperature airflow. When the temperature and humidity sensor detects no condensation in the mixed air, the controller controls the first heat exchanger 20 to perform basic dehumidification, while the second heat exchanger 30 is shut down or maintains low-power operation. The first fan 40 and the second fan 50 can be adjusted to appropriate wind speeds according to actual dehumidification needs, avoiding excessive operation of the equipment during non-condensation conditions, reducing overall energy consumption, and balancing dehumidification effect with energy saving and environmental protection. This ensures that the system can maintain stable operation under different humidity scenarios, reduce indoor temperature and humidity fluctuations, and improve comfort.

[0092] It should be noted that the controller controls the operating status of the first heat exchanger 20 and the second heat exchanger 30 based on whether the temperature and humidity sensor detects condensation. The temperature and humidity sensor detects the temperature and humidity of the mixed air. When the temperature and humidity sensor detects that the humidity of the mixed air exceeds the preset humidity threshold, it indicates that condensation has occurred in the mixed air. When the temperature and humidity sensor detects that the humidity of the mixed air does not exceed the preset humidity threshold, it indicates that condensation has not occurred in the mixed air.

[0093] It should also be noted that in high humidity scenarios, i.e., when the humidity in the indoor space increases rapidly and drastically in a short period of time, the first heat exchanger 20 is controlled to operate at maximum refrigerant flow to minimize the surface temperature of the first heat exchanger 20 and improve the condensation and dehumidification effect on the mixed air. On the other hand, the first fan 40 and the second fan 50 are controlled to reduce their wind speeds to maintain laminar flow in the heat exchange and dehumidification chamber 130, extending the contact path and time between the airflow and the heat exchanger, ensuring that the moisture in the mixed air is fully condensed and precipitated, and improving dehumidification efficiency. At the same time, the second heat exchanger 30 is controlled to operate at maximum heat exchange power to increase the temperature of the low-temperature dry airflow after dehumidification by the first heat exchanger 20, reducing the temperature difference with the indoor environment or the surface of the air duct, making the airflow close to the ambient temperature, and fundamentally preventing secondary condensation caused by low-temperature airflow.

[0094] In the gradual increase scenario, that is, the indoor humidity rises slowly and steadily, a step-by-step adjustment is adopted. The first heat exchanger 20 gradually increases the refrigerant flow and air speed at set intervals to ensure the dehumidification depth while avoiding airflow stagnation; the second heat exchanger 30 gradually increases the heat exchange power at set intervals to achieve a dynamic balance between heat exchange and energy consumption. In addition, the current humidity and the rate of change of humidity are used to determine whether the scenario is high humidity or gradual transition. Specifically, if the current humidity is greater than the preset humidity threshold and the rate of change of humidity is greater than the preset rate of change threshold, it is a high humidity scenario. If the current humidity is less than the preset humidity threshold and the rate of change of humidity is less than the preset rate of change threshold, and the rate of change of humidity is continuously greater than zero, it is a gradual transition scenario.

[0095] like Figures 1-3 As shown, in some embodiments, a main partition 60 is provided inside the housing 10 to divide the housing 10 into an air inlet chamber and a heat exchange and dehumidification chamber 130; a secondary partition 70 is provided inside the air inlet chamber to divide the air inlet chamber into a fresh air chamber 110 and a return air chamber 120; the fresh air chamber 110 is provided with a fresh air inlet 1101 for introducing fresh air, and the return air chamber 120 is provided with a return air inlet 1201 for introducing return air; wherein, the secondary partition 70 is configured to selectively isolate or connect the fresh air chamber 110 and the return air chamber 120.

[0096] The main partition 60 divides the housing 10 into an air inlet chamber and a heat exchange and dehumidification chamber 130, ensuring orderly separation of airflow delivery and heat exchange and dehumidification processes, avoiding airflow turbulence, and facilitating subsequent processing. The secondary partition 70 further divides the air inlet chamber into a fresh air chamber 110 and a return air chamber 120. With their respective fresh air inlets 1101 and return air inlets 1201, fresh air and return air can be introduced separately. At the same time, the secondary partition 70 can selectively control the isolation or connection between the fresh air chamber 110 and the return air chamber 120, realizing the switching between independent air intake and mixed air intake. Specifically, when only a single air inlet is inlet, the secondary partition 70 connects the fresh air chamber 110 and the return air chamber 120; when both the return air inlet 1201 and the fresh air inlet 1101 are inlet, the secondary partition 70 isolates the fresh air chamber 110 and the return air chamber 120.

[0097] It should be noted that when fresh air or return air needs to be handled separately, a single air inlet will be selected for air intake.

[0098] It should also be noted that the fresh air inlet 1101 is located on the side of the fresh air cavity 110 away from the heat exchange and dehumidification cavity 130, and the return air inlet 1201 is located on the side of the return air cavity 120 away from the heat exchange and dehumidification cavity 130; the heat exchange and dehumidification cavity 130 is provided with an air outlet 1301, which is located on the side of the heat exchange and dehumidification cavity 130 away from the air inlet, and there can be multiple air outlets 1301; for example, such as Figure 1As shown, the fresh air inlet 1101 is located at the bottom of the fresh air chamber 110, the return air inlet 1201 is located at the bottom of the return air chamber 120, and the air outlet 1301 is located at the top of the heat exchange and dehumidification chamber 130.

[0099] like Figures 1-3 As shown, in some embodiments, the secondary partition 70 includes a main body 710 and a baffle 720; the main body 710 is connected to the main partition 60 and the inner wall of the housing 10 respectively, and a through hole is provided on the main body 710; the baffle 720 is rotatably disposed on the main body 710, and the baffle 720 is configured to be able to open the through hole by rotation to connect the fresh air chamber 110 and the return air chamber 120, or to close the through hole to isolate the fresh air chamber 110 and the return air chamber 120.

[0100] The main body 710 is connected to the main partition 60 and the inner wall of the shell 10 respectively to form a stable partition foundation. The through hole opened on the main body 710 provides a channel for the connection between the fresh air cavity 110 and the return air cavity 120. The baffle 720 is rotatably set on the main body 710. The through hole can be quickly opened or closed by rotating the baffle 720. The operation is convenient and simple and can meet the needs of different air intake conditions in a timely manner. When only a single air inlet is inlet, the baffle 720 rotates to open the through hole, connecting the fresh air chamber 110 and the return air chamber 120. At the same time, both the first fan 40 and the second fan 50 are controlled to work. On the one hand, the combined operation of the two fans avoids the efficiency limitations of a single fan and improves the processing efficiency of a single airflow. On the other hand, the two fans can operate in a low-frequency mode while ensuring the required air volume, which can effectively reduce the operating noise of the equipment compared to the high-frequency operation of a single fan. When the return air inlet 1201 and the fresh air inlet 1101 are inlet together, the baffle 720 rotates to close the through hole, isolating the fresh air chamber 110 and the return air chamber 120, ensuring that the fresh air and return air are mixed before entering the heat exchange and dehumidification chamber 130.

[0101] It should be noted that a drive component can be connected to the baffle 720 to drive the baffle 720 to rotate. The drive component can be, but is not limited to, a motor. The motor's shaft is connected to the baffle 720 to drive the baffle 720 to rotate, thereby realizing the opening and closing of the through hole.

[0102] like Figures 1-3 As shown, in some embodiments, the baffle 720 includes a first working position, a second working position, and a third working position; in the first working position, the baffle 720 closes the through hole to isolate the fresh air cavity 110 and the return air cavity 120; in the second working position, the baffle 720 opens the through hole and tilts towards the fresh air cavity 110 so that the return air introduced by the return air inlet 1201 can flow to the first fan 40 and the second fan 50 respectively; in the third working position, the baffle 720 opens the through hole and tilts towards the return air cavity 120 so that the fresh air introduced by the fresh air inlet 1101 can flow to the first fan 40 and the second fan 50 respectively.

[0103] In the first working position, the baffle 720 closes the through hole, isolating the fresh air cavity 110 and the return air cavity 120 to avoid cross-interference between fresh and return air. This is compatible with the operating condition where both the fresh air inlet 1101 and the return air inlet 1201 are inlet, ensuring that the fresh and return air mix before entering the heat exchange and dehumidification cavity 130, thus guaranteeing the heat exchange and dehumidification effect. In the second working position, the baffle 720 opens the through hole and tilts towards the fresh air cavity 110, forming a directional airflow structure. This guides the return air introduced by the return air inlet 1201 to be diverted to the first fan 40 and the second fan 50, avoiding concentrated load on a single fan. The first fan 40 and the second fan 50 can operate synchronously at low frequency, reducing noise and energy consumption while ensuring airflow, and improving the efficiency and stability of individual return air treatment. In the third working position, the baffle 720 opens its through-hole and tilts towards the return air cavity 120, forming a directional airflow structure to guide the fresh air introduced by the fresh air inlet 1101 to be diverted to the first fan 40 and the second fan 50, avoiding concentrated load on a single fan. At the same time, the first fan 40 and the second fan 50 can operate synchronously at low frequency, reducing noise and energy consumption while ensuring airflow, and improving the efficiency and stability of individual fresh air treatment. In addition, the baffle 720 achieves directional airflow guidance through its tilt angle, reducing eddies and resistance in the cavity, thus balancing operating efficiency and adaptability to operating conditions.

[0104] It should be noted that the baffle 720 includes, but is not limited to, the first working position, the second working position, and the third working position, as well as other working positions. It can be understood that when there is only a single air inlet, the baffle 720 can be rotated to be parallel to the length direction, which can also satisfy the requirement of diverting the airflow to the first fan 40 and the second fan 50.

[0105] like Figures 1-3 As shown, in some embodiments, the air outlet structure also includes an air pretreatment module 80 and an air guide plate 90; the air pretreatment module 80 is respectively disposed at the fresh air inlet 1101 and the return air inlet 1201; the air guide plate 90 is disposed in the heat exchange and dehumidification chamber 130 and is located upstream of the airflow of the first heat exchanger 20.

[0106] The air pretreatment module 80 can pre-treat the fresh and return air entering the chamber, which not only prevents impurities from adhering to and clogging the heat exchanger fins, extending the service life of the components, but also reduces the risk of pollution during airflow treatment and improves the cleanliness of the air supplied to the room. The air guide plate 90, located within the heat exchange and dehumidification chamber 130 and above the airflow of the first heat exchanger 20, can guide and divert the airflow entering the chamber, breaking up the turbulent airflow and guiding the airflow to flow evenly and smoothly into the first heat exchanger 20. This avoids the problem of low dehumidification and heat exchange efficiency caused by uneven local airflow, ensuring that the heat exchanger can fully dehumidify and exchange heat; at the same time, it can also avoid the noise problem caused by excessively concentrated airflow at high speeds.

[0107] It should be noted that the air pretreatment module 80 includes a dehumidification module, a sterilization module, and a dust removal module. The dehumidification module includes moisture-absorbing materials such as molecular sieves, the sterilization module includes, but is not limited to, ultraviolet lamps, and the dust removal module includes, but is not limited to, filters.

[0108] It should also be noted that the air guide plate 90 includes a support frame and multiple air guide blades rotatably disposed within the support frame. The multiple air guide blades are arranged in parallel and spaced apart to form a grid shape. By adjusting the tilt angle of the air guide blades, the airflow can be guided and diffused to the entire surface of the heat exchanger, so that each part of the heat exchanger can be evenly covered by the airflow, avoiding uneven airflow that could lead to localized overcooling or incomplete dehumidification of the heat exchanger.

[0109] In some embodiments, the air outlet structure further includes a refrigerant circulation assembly, which is connected to the first heat exchanger 20 and the second heat exchanger 30 respectively.

[0110] The refrigerant is circulated between the first heat exchanger 20 and the second heat exchanger 30 through the refrigerant circulation component, so as to achieve a reasonable distribution of cooling and heating, and take into account both dehumidification and temperature control requirements.

[0111] It should be noted that the refrigerant circulation component can be electrically connected to the controller and, in conjunction with the temperature and humidity sensor, dynamically adjust the refrigerant flow rate, flexibly adjust the working intensity of the first heat exchanger 20 and the second heat exchanger 30, and adapt to different operating conditions.

[0112] It should also be noted that the refrigerant circulation assembly can be a three-pipe indoor unit system. The refrigerant circulation assembly includes heat exchanger inlet and outlet pipes and an electronic expansion valve. It is connected to the first heat exchanger 20 and the second heat exchanger 30 respectively through the heat exchanger inlet and outlet pipes, so that the refrigerant can be distributed to the first heat exchanger 20 and the second heat exchanger 30.

[0113] It should also be noted that, such as Figure 1 As shown, a partition plate 1302 is provided inside the heat exchange and dehumidification chamber 130, dividing the heat exchange and dehumidification chamber 130 into a main chamber and a sub-chamber. The first heat exchanger 20 and the second heat exchanger 30 are both located in the main chamber, and the first fan 40 and the second fan 50 are both connected to the main chamber. The refrigerant circulation assembly is located in the sub-chamber; in addition, as Figure 1 As shown, the main cavity and the sub-cavities are arranged at intervals along the length direction.

[0114] In summary, this application achieves independent control of dehumidification and heat exchange functions through a dual heat exchanger structure: when condensation occurs in the mixed air, the first heat exchanger 20 performs deep dehumidification, while the second heat exchanger 30 completes heat exchange, fundamentally eliminating condensation; when there is no condensation in the mixed air, only a single heat exchanger can be activated, reducing overall energy consumption. Furthermore, the operating modes of the first heat exchanger 20 and the second heat exchanger 30 can be automatically switched according to the condensation status of the mixed air, ensuring stable operation under different humidity conditions, effectively reducing indoor temperature and humidity fluctuations, and improving comfort.

[0115] Example 5 This application also provides an air conditioner, including the air outlet structure provided in the foregoing embodiments of this application.

[0116] It should be noted that air conditioning can include, but is not limited to, fresh air conditioning systems.

[0117] It should be understood that the terminology used herein is for the purpose of describing particular exemplary embodiments only and is not intended to be limiting. Unless the context clearly indicates otherwise, the singular forms “a,” “an,” and “described” as used herein may also include the plural forms. The terms “comprising,” “including,” “containing,” and “having” are inclusive and therefore indicate the presence of the stated features, steps, operations, elements, and / or components, but do not exclude the presence or addition of one or more other features, steps, operations, elements, components, and / or combinations thereof. The method steps, processes, and operations described herein are not construed as requiring them to be performed in a particular order described or illustrated unless the order of performance is explicitly indicated. It should also be understood that additional or alternative steps may be used.

[0118] Although terms such as first, second, third, etc., may be used in this document to describe multiple elements, components, regions, layers, and / or segments, these elements, components, regions, layers, and / or segments should not be limited by these terms. These terms may be used only to distinguish one element, component, region, layer, or segment from another. Unless the context clearly indicates otherwise, terms such as "first," "second," and other numerical terms used herein do not imply order or sequence. Therefore, the first element, component, region, layer, or segment discussed below may be referred to as the second element, component, region, layer, or segment without departing from the teachings of the exemplary embodiments.

[0119] The above description is merely a specific embodiment of the present invention, enabling those skilled in the art to understand or implement the present invention. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the general principles defined herein may be implemented in other embodiments without departing from the spirit or scope of the present invention. Therefore, the present invention is not to be limited to the embodiments shown herein, but is to be accorded the widest scope consistent with the principles and novel features claimed herein.

Claims

1. An air outlet structure, characterized in that, include: The housing includes a phase-separated fresh air chamber, a return air chamber, and a heat exchange and dehumidification chamber; The first heat exchanger is disposed inside the heat exchange and dehumidification chamber; The second heat exchanger is disposed in the heat exchange and dehumidification chamber and is located downstream of the airflow of the first heat exchanger; The first fan is installed inside the fresh air cavity and is used to transport fresh air from the fresh air cavity to the heat exchange and dehumidification cavity; The second fan is disposed in the return air cavity and is used to transport the return air from the return air cavity to the heat exchange and dehumidification cavity; the air outlets of the first fan and the second fan are constructed to be inclined towards each other so that the fresh air and the return air are mixed in the heat exchange and dehumidification cavity and upstream of the airflow of the first heat exchanger to form mixed air.

2. The air outlet structure according to claim 1, characterized in that, The fresh air chamber and the return air chamber are arranged side by side adjacent to each other. The heat exchange and dehumidification chamber is arranged adjacent to the return air chamber and the fresh air chamber respectively. The first fan and the second fan are arranged side by side and are symmetrical about a plane perpendicular to the arrangement direction of the fresh air chamber and the return air chamber.

3. The air outlet structure according to claim 2, characterized in that, The angle between the central axis of the air outlet of the first fan and the central axis of the air outlet of the second fan is 45°-90°.

4. The air outlet structure according to claim 1, characterized in that, The air outlet structure also includes: A temperature and humidity sensor is installed on the windward side of the first heat exchanger and is used to detect the temperature and humidity of the mixed air. The controller is electrically connected to the first heat exchanger, the second heat exchanger, and the temperature and humidity sensor, respectively. The controller is configured to control the operation of the first heat exchanger and the second heat exchanger based on the detection values ​​of the temperature and humidity sensor.

5. The air outlet structure according to claim 1, characterized in that, The housing is provided with a main partition to divide the housing into an air inlet chamber and a heat exchange and dehumidification chamber; the air inlet chamber is provided with a secondary partition to divide the air inlet chamber into a fresh air chamber and a return air chamber. The fresh air chamber is provided with a fresh air inlet for introducing fresh air, and the return air chamber is provided with a return air inlet for introducing return air; The sub-partition is configured to selectively isolate or connect the fresh air cavity with the return air cavity.

6. The air outlet structure according to claim 5, characterized in that, The secondary partition includes: The main body is connected to the main partition and the inner wall of the shell, and the main body is provided with through holes; A baffle is rotatably disposed on the main body. The baffle is configured to allow the through hole to be opened by rotation to connect the fresh air chamber and the return air chamber, or to close the through hole to isolate the fresh air chamber and the return air chamber.

7. The air outlet structure according to claim 6, characterized in that, The baffle includes a first working position, a second working position, and a third working position; in the first working position, the baffle closes the through hole to isolate the fresh air cavity from the return air cavity; In the second working position, the baffle opens the through hole and tilts toward the fresh air cavity so that the return air introduced by the return air inlet can flow to the first fan and the second fan respectively; In the third working position, the baffle opens the through hole and tilts towards the return air cavity so that the fresh air introduced by the fresh air inlet can flow to the first fan and the second fan respectively.

8. The air outlet structure according to any one of claims 5-7, characterized in that, The air outlet structure also includes: An air pretreatment module is respectively installed at the fresh air inlet and the return air inlet; An air guide plate is disposed inside the heat exchange and dehumidification chamber and located upstream of the airflow of the first heat exchanger.

9. The air outlet structure according to any one of claims 1-7, characterized in that, The air outlet structure also includes a refrigerant circulation component, which is connected to the first heat exchanger and the second heat exchanger respectively.

10. An air conditioner, characterized in that, Includes the air outlet structure as described in any one of claims 1-9.

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