Temperature control dehumidification duct type air conditioner, air conditioner and control method

Abstract

The invention relates to a temperature control dehumidification duct type air conditioner, an air conditioner and a control method. The temperature-control dehumidification duct type air conditioner comprises a complete machine box body and an air guide mechanism, a volute, a backheating heat exchanger and a dehumidification heat exchanger are installed in the complete machine box body, and the backheating heat exchanger and the dehumidification heat exchanger are oppositely arranged up and down; the air guide mechanism is installed at an air outlet of the volute in a crossing mode and arranged opposite to the regenerative heat exchanger and the dehumidification heat exchanger, the air guide mechanism comprises an air guide plate, and the air guide plate is used for separating an air channel between the volute and the regenerative heat exchanger and an air channel between the volute and the dehumidification heat exchanger into an upper independent flow channel and a lower independent flow channel. The heat exchangers correspond to the regenerative heat exchanger and the dehumidification heat exchanger respectively; one end of the air guide plate is configured to move up and down at the air outlet of the volute so as to adjust the air distribution proportion of the two independent flow channels.

Description

TECHNICAL FIELD

[0001] The present disclosure relates to the field of air conditioners with temperature control and dehumidification ducted air conditioner, and particularly relates to a temperature control and dehumidification ducted air conditioner, an air conditioner and a control method. BACKGROUND

[0002] In the field of HVAC, ducted air conditioners are widely used in residential, office and other places due to their wide range of air supply and concealed installation. To achieve temperature control and dehumidification, the prior art proposes a scheme in which two evaporators are used to undertake evaporation and heat recovery functions respectively, and temperature and humidity are preliminarily controlled through the cooperation of the two evaporators. However, this scheme has obvious technical defects. On the one hand, the heat exchange capacity of the two evaporators is relatively fixed, and the distribution ratio of air flow in the two evaporators cannot be dynamically adjusted, which leads to the problem that the indoor temperature is prone to overfall or insufficient during dehumidification, and it is difficult to achieve precise temperature control. On the other hand, when the unit defrosts, the four-way valve switches to refrigeration mode, the indoor fan is turned off and there is no continuous heating path, which causes the interruption of heat transfer to the indoor environment, resulting in large fluctuations in indoor environment temperature and seriously affecting the comfort of use.

[0003] Therefore, there is an urgent need for a technical solution that can flexibly adjust the air volume distribution of the two evaporators, and balance the precise temperature control and dehumidification and defrosting stability, to solve the core pain points of existing products. SUMMARY

[0004] The present disclosure provides a temperature control and dehumidification ducted air conditioner, an air conditioner and a control method to solve the technical problem that the existing ducted air conditioner cannot balance precise temperature control and dehumidification and defrosting stability in the prior art.

[0005] The temperature control and dehumidification ducted air conditioner provided by the embodiments of the present disclosure comprises: a whole machine box and an air guide mechanism, a volute, a heat recovery heat exchanger and a dehumidification heat exchanger are installed in the whole machine box, and the heat recovery heat exchanger and the dehumidification heat exchanger are arranged oppositely in an up-down manner; the air guide mechanism is installed across the air outlet of the volute and is arranged opposite to the heat recovery heat exchanger and the dehumidification heat exchanger, and the air guide mechanism comprises an air guide plate, which is used to isolate the air duct between the volute and the heat recovery heat exchanger and the dehumidification heat exchanger into two independent flow channels in an up-down manner, corresponding to the heat recovery heat exchanger and the dehumidification heat exchanger respectively. One end of the air guide plate is configured to move up and down on the air outlet of the volute to adjust the air volume distribution ratio of the two independent flow channels.

[0006] The above technical solution provided by the embodiments of the present disclosure has the following advantages compared with the prior art: The temperature control dehumidification duct type air conditioner, air conditioner and control method provided by the embodiments of the present disclosure, by installing the air deflector at the outlet of the volute, and the air deflector is arranged opposite to the heat recovery heat exchanger and the dehumidification heat exchanger, by isolating the air duct into two independent flow channels, the airflow is forced to be divided into the corresponding heat recovery heat exchanger or dehumidification heat exchanger, avoiding the heat exchange efficiency decline caused by airflow mixing; one end of the air deflector can move up and down along the outlet of the volute, by changing the moving position to adjust the cross-sectional area of the two independent flow channels: when the air deflector moves upward, the cross-sectional area of the flow channel corresponding to the heat recovery heat exchanger increases, and the cross-sectional area of the flow channel corresponding to the dehumidification heat exchanger decreases, and the proportion of the air volume flowing through the heat recovery heat exchanger increases; when the air deflector moves downward, the cross-sectional area of the flow channel corresponding to the dehumidification heat exchanger increases, and the cross-sectional area of the flow channel corresponding to the heat recovery heat exchanger decreases, and the proportion of the air volume flowing through the dehumidification heat exchanger increases, thereby dynamically regulating the air volume distribution ratio of the two heat exchangers.

[0007] In this way, in combination with the original temperature control dehumidification mode of the duct type air conditioner, when the environmental humidity is higher than the set value, the air deflector can move downward to increase the cross-sectional area of the flow channel corresponding to the dehumidification heat exchanger, so that most of the air volume flows through the dehumidification heat exchanger to preferentially complete dehumidification; when the environmental temperature decreases, the air deflector can move upward to increase the cross-sectional area of the flow channel corresponding to the heat recovery heat exchanger, thereby increasing the proportion of heat recovery and compensating for the temperature loss. Ultimately, precise regulation with a small difference between the actual humidity and the set humidity and a small difference between the actual temperature and the initial temperature is achieved, that is, the temperature can be controlled to slowly decrease. BRIEF DESCRIPTION OF DRAWINGS

[0008] The accompanying drawings, which are incorporated into and form part of the specification, illustrate embodiments consistent with the present disclosure and, together with the specification, serve to explain the principles of the present disclosure.

[0009] In order to more clearly illustrate the technical solutions in the embodiments of the present disclosure or the prior art, brief introductions will be given to the drawings needed to be used in the embodiments or prior art descriptions. Obviously, for those skilled in the art, other drawings can also be obtained from these drawings without creative labor.

[0010] One or more embodiments are exemplarily illustrated by the pictures in the drawings corresponding thereto, and these exemplary illustrations do not constitute a limitation on the embodiments. Elements with the same reference numerals in the drawings represent similar elements, unless otherwise specified. The drawings in the drawings do not constitute a proportional limitation.

[0011] Figure 1 A system diagram of the temperature control dehumidification duct type air conditioner provided by the embodiments of the present disclosure; Figure 2 A structural schematic diagram of the air deflector installed in the temperature control dehumidification duct type air conditioner provided by the embodiments of the present disclosure; Figure 3A structure diagram of the air guide mechanism provided by the embodiment of the present disclosure is shown, in which the air guide plate rotates to the minimum angle a1. Figure 4 A structure diagram of the air guide mechanism provided by the embodiment of the present disclosure is shown, in which the air guide plate rotates to the intermediate angle a2. Figure 5 A structure diagram of the air guide mechanism provided by the embodiment of the present disclosure is shown, in which the air guide plate rotates to the maximum angle a3.

[0012] Explanation of reference signs: 1, whole machine box; 11, volute, 111, air outlet; 12, heat recovery heat exchanger; 13, dehumidification heat exchanger; 14, air guide plate; 15, gear; 16, rack; 17, stepping motor; 2, compressor; A, indoor side; B, outdoor side; 3, fan; 4, on-off valve; 5, throttling device. DETAILED DESCRIPTION

[0013] To make the purpose, technical solutions and advantages of the embodiments of the present disclosure clearer, the technical solutions in the embodiments of the present disclosure will be described clearly and completely below with reference to the drawings in the embodiments of the present disclosure. Obviously, the described embodiments are part of the embodiments of the present disclosure, rather than all the embodiments. Based on the embodiments in the present disclosure, all other embodiments obtained by those of ordinary skill in the art without creative work fall within the scope of protection of the present disclosure.

[0014] In the temperature and humidity control of the conventional existing temperature control dehumidification air duct machine, the heat exchange capacity of the heat exchanger is fixed, and the air distribution ratio cannot be dynamically adjusted, which leads to the problem that the indoor temperature is prone to over-decrease or deficiency in the dehumidification process, and it is difficult to achieve precise temperature control. In addition, when the unit defrosts, the four-way valve switches to the refrigeration mode, the indoor fan is turned off and there is no continuous heating path, which leads to the interruption of heat delivery to the indoor environment, the indoor environment temperature fluctuates greatly, and the use comfort is seriously affected.

[0015] To this end, with reference to Figures 1-5 , the present disclosure provides a temperature control dehumidification air duct machine, comprising: a whole machine box 1 and an air guide mechanism 3, the whole machine box 1 is internally provided with a volute 11, a heat recovery heat exchanger 12 and a dehumidification heat exchanger 13, the heat recovery heat exchanger 12 and the dehumidification heat exchanger 13 are arranged oppositely; the air guide mechanism 3 is installed across the air outlet of the volute 11, and is arranged opposite to the heat recovery heat exchanger 12 and the dehumidification heat exchanger 13, the air guide mechanism 3 comprises an air guide plate 14, the air guide plate 14 is used for isolating the air duct between the volute 11 and the heat recovery heat exchanger 12 and the dehumidification heat exchanger 13 into two independent flow channels above and below, corresponding to the heat recovery heat exchanger 12 and the dehumidification heat exchanger 13 respectively; one end of the air guide plate 14 is configured to move up and down on the air outlet of the volute 11 to adjust the air distribution ratio of the two independent flow channels.

[0016] For ease of understanding, some key terms in this embodiment are explained as follows: The whole machine box 1 serves to provide a closed installation space and protective structure for the internal components of the temperature control and dehumidification duct type air handling unit, ensuring stable operation of the equipment.

[0017] The volute 11 generally provides a diverging flow passage for the fan 3, which is used to collect the airflow generated by the fan 3 and efficiently guide it to the subsequent heat exchanger or air outlet, so as to improve the air supply efficiency of the fan 3.

[0018] The regenerative heat exchanger 12 mainly functions to reheat the low-temperature and low-humidity air treated by the dehumidification heat exchanger 13 during the dehumidification process, so as to avoid excessively low indoor temperature while maintaining comfortable air supply temperature.

[0019] The dehumidification heat exchanger 13 mainly functions to condense water vapor in the air through refrigeration cycle, thereby reducing the humidity of the air and achieving the dehumidification effect of indoor air.

[0020] The fan 3 structure serves to guide and distribute the airflow path, so as to achieve accurate control of the air volume to different functional areas or heat exchangers.

[0021] The air guide plate 14, as the core component of the fan 3 structure, can physically separate or adjust the flow direction and flow rate of the airflow by changing its position or angle, thereby achieving adjustment of the air volume distribution ratio.

[0022] The independent flow passage refers to the airflow channel separated by the air guide plate 14 and not interfering with each other. Each flow passage can independently guide the airflow to a specific heat exchanger to achieve different processing functions.

[0023] The air volume distribution ratio refers to the distribution of the total airflow among different independent flow passages or heat exchangers in a certain ratio. By adjusting the ratio, the intensity control of different functions (such as dehumidification and heat recovery) can be achieved.

[0024] The present embodiment provides a temperature control and dehumidification duct type air handling unit. The temperature control and dehumidification duct type air handling unit comprises a whole machine box 1, which is internally configured to install a plurality of core components. Specifically, the whole machine box 1 is installed with a volute 11, a regenerative heat exchanger 12 and a dehumidification heat exchanger 13. The regenerative heat exchanger 12 and the dehumidification heat exchanger 13 are arranged in an upper-lower opposite position relationship to form a specific airflow path. For example, the whole machine box 1 can be a rectangular or square metal shell, and the volute 11, the regenerative heat exchanger 12 and the dehumidification heat exchanger 13 are fixed in the preset positions by the partition or support inside the whole machine box 1. The regenerative heat exchanger 12 and the dehumidification heat exchanger 13 can adopt finned tube heat exchanger structure and be arranged in an upper-lower stacking manner.

[0025] Further, the temperature-controlled dehumidification air pipe machine further comprises a guide fan 3 structure. The guide fan 3 structure is installed across the air outlet of the volute 11 and is arranged opposite to the heat recovery heat exchanger 12 and the dehumidification heat exchanger 13. The core component of the guide fan 3 structure comprises a guide plate 14. The main function of the guide plate 14 is to isolate the air duct between the volute 11 and the heat recovery heat exchanger 12 and the dehumidification heat exchanger 13 into two independent flow channels. The two independent flow channels correspond to the heat recovery heat exchanger 12 and the dehumidification heat exchanger 13, respectively. For example, the guide fan 3 structure can be composed of a simple pivot structure and a guide plate 14. The guide plate 14 is fixed by a pivot near the air outlet of the volute 11, and the free end can swing. The guide plate 14 can be a flat plate structure, which is long and wide enough to cover the area between the air outlet of the volute 11 and the two heat exchangers, so as to realize the physical isolation of the air duct.

[0026] Specifically, one end of the guide plate 14 is configured to move up and down at the air outlet of the volute 11. By moving up and down of the guide plate 14, the adjustment of the air distribution ratio of the two independent flow channels can be realized. For example, one end of the guide plate 14 can be manually operated, and by a simple push-pull mechanism, it slides up and down in the guide rail at the air outlet of the volute 11. When the guide plate 14 moves upward, the air volume flowing through the lower dehumidification heat exchanger 13 increases, and the air volume flowing through the upper heat recovery heat exchanger 12 decreases; on the contrary, when the guide plate 14 moves downward, the air volume flowing through the upper heat recovery heat exchanger 12 increases, and the air volume flowing through the lower dehumidification heat exchanger 13 decreases. In this way, the distribution of air flow between the two heat exchangers can be adjusted according to actual needs.

[0027] The embodiment realizes dynamic adjustment of the air distribution between the heat recovery heat exchanger 12 and the dehumidification heat exchanger 13 by setting the movable guide plate 14, thereby effectively solving the problem of inaccurate temperature and humidity regulation in the traditional scheme. In addition, the structure provides the possibility of continuously delivering heat to the indoor environment in the defrosting mode, avoids the sharp fluctuation of the indoor environment temperature, and improves the use comfort.

[0028] In some embodiments of the present disclosure, one end of the guide plate 14 is configured to move up and down at the air outlet of the volute 11 to adjust the air distribution ratio of the two independent flow channels. However, in actual operation, if the movement of the guide plate 14 lacks effective guidance and support, the other end of the guide plate 14 may shake or deviate from the preset path, thereby affecting the accuracy and stability of the air distribution, and even causing the guide plate 14 to be stuck or worn, reducing the reliability and service life of the equipment.

[0029] To this end, the present disclosure further proposes that the temperature-controlled dehumidification air pipe machine comprises a transmission member installed at the air outlet of the volute 11, which is engaged with the guide vane 14 for providing a stable movement path for the other end of the guide vane 14.

[0030] Specifically, the transmission member is a mechanical component capable of transmitting motion and / or force, which functions to transmit driving force or motion form to the guide vane 14 while providing structural support and guidance. The transmission member can take various forms, such as a gear 15, a rack 16, a linkage mechanism, a slider mechanism, or a cam mechanism, etc., the selection of which depends on the specific structural design and the required transmission characteristics. The transmission member is installed at the air outlet area of the volute 11, which ensures its direct and effective connection with the moving end of the guide vane 14. By fixing the transmission member at the air outlet of the volute 11, the structure of the volute 11 can be used as a support to provide a stable installation foundation for the transmission member, thereby ensuring the positional accuracy and stability of the transmission member during operation. The transmission member and the guide vane 14 are connected through engagement, which means that there is a close and cooperative connection between the two, capable of reliably transmitting motion. For example, if the transmission member is a gear 15, the guide vane 14 can be provided with a corresponding rack 16 or toothed structure to cooperate with it; if the transmission member is a linkage, the guide vane 14 can be provided with a connection point.

[0031] This engagement transmission method can ensure that the guide vane 14 is always accurately controlled by the transmission member during movement, avoiding sliding or disengagement, thereby ensuring the accuracy of the motion. The core function of the transmission member is to provide a clear and stable movement trajectory for the other end of the guide vane 14. When one end of the guide vane 14 moves up and down at the air outlet of the volute 11, the other end moves along a predetermined path under the guidance of the transmission member. This stable movement path can effectively prevent the guide vane 14 from irregular swinging, tilting, or jamming during adjustment, ensuring that the guide vane 14 is always in the correct working position, thereby achieving precise control of the air volume distribution ratio.

[0032] By the above technical solution, the transmission member is introduced and installed at the air outlet of the volute 11, and engages with the air deflector 14 to provide a stable movement path for the other end of the air deflector 14, effectively solving the problems of shaking, deviating from the preset path or sticking of the air deflector 14 during adjustment. The arrangement of the transmission member ensures that the overall posture and movement trajectory of the air deflector 14 remain accurate and stable during up and down movement. This not only improves the accuracy of the air deflector 14 in adjusting the air distribution ratio, but also makes the air distribution between the heat recovery heat exchanger 12 and the dehumidification heat exchanger 13 more precise and controllable, thereby optimizing the performance of the temperature control and dehumidification ducted air conditioner in different operating modes. At the same time, the stable movement path also reduces the friction and wear between the air deflector 14 and the surrounding components, prolongs the service life of the equipment, and improves the reliability and durability of the system.

[0033] In some embodiments of the present disclosure described above, a temperature control and dehumidification ducted air conditioner is proposed, one end of the air deflector 14 of which can move up and down on the air outlet of the volute 11 to adjust the air distribution ratio of the two independent flow channels, and the transmission member provides a stable movement path for the other end of the air deflector 14. However, in actual application, how to effectively drive the air deflector 14 to move accurately and stably to ensure the accuracy of air distribution is a technical problem that needs to be further solved.

[0034] To this end, the present disclosure further proposes that a preset installation site is provided inside the intersection between the heat recovery heat exchanger 12 and the dehumidification heat exchanger 13, and the air deflector 3 further includes a driving member installed at the preset installation site, and the other end of the air deflector 14 is drivingly connected to the driving member through a rotating shaft. The driving member is used to drive the air deflector 14 to rotate around the rotating shaft, so that one end of the air deflector 14 moves up and down along the movement path of the transmission member.

[0035] Specifically, the pre-installed mounting position is a structure that provides fixed support for the drive component. It is usually located in the inner area adjacent to the regenerating heat exchanger 12 and the dehumidifying heat exchanger 13. This area is typically a relatively stable and easy-to-install location within the duct air conditioner's internal structure. It can be a pre-drilled hole, a welded bracket, or an integrally formed groove, designed to ensure the stability and precision of the drive component's installation, preventing displacement or vibration during operation that could affect the rotational accuracy of the air guide plate 14. The drive component is an actuator that provides power to drive the air guide plate 14 to rotate. It can be a motor, such as a stepper motor 17, a servo motor, or a DC motor, whose rotation angle or speed is controlled by electrical signals. Its core function is to convert the input control signals into mechanical motion, thereby precisely controlling the posture of the air guide plate 14. The rotating shaft is a mechanical component connecting the drive component and the air guide plate 14. Its function is to transmit the rotational torque of the drive component and serve as the center of rotation for the air guide plate 14. The rotating shaft is typically made of high-strength, wear-resistant metal materials, such as stainless steel or alloy steel, to ensure sufficient rigidity and reliability during long-term operation. One end of the rotating shaft is connected to the output shaft of the drive unit, while the other end is fixed to the other end of the air guide plate 14, allowing the air guide plate 14 to rotate precisely around this axis. The drive unit transmits its rotational motion to the rotating shaft through the connection between its output shaft and the rotating shaft, thereby driving the air guide plate 14 fixed on the rotating shaft to rotate. This rotational motion is the basis for the air guide plate 14 to achieve airflow distribution and adjustment. By precisely controlling the rotation angle of the drive unit, the air guide plate 14 can be positioned arbitrarily within a preset angle range, thereby finely adjusting the size of the air duct opening. When the air guide plate 14 rotates around the rotating shaft, due to the geometry of the air guide plate 14 and its meshing relationship with the transmission unit, the end of the air guide plate 14 away from the rotating shaft (i.e., its other end) will move vertically along the stable path provided by the transmission unit. This rotation-linear motion conversion mechanism allows the air guide plate 14 to change its position at the air outlet of the volute 11 in a smooth and controllable manner, thereby achieving precise adjustment of the air volume distribution ratio of the upper and lower independent flow channels.

[0036] Through the above technical solution, a preset installation position is set on the inner side of the junction between the regenerating heat exchanger 12 and the dehumidifying heat exchanger 13, and a driving component is installed there, so that the other end of the air guide plate 14 can be driven and connected to the driving component through a rotating shaft. The driving component can precisely drive the air guide plate 14 to rotate around the rotating shaft, thereby converting the rotational motion of the driving component into the up-and-down reciprocating movement of one end of the air guide plate 14. This design provides a reliable mechanical basis for the precise control of the air guide plate 14, and solves the problem of uneven air volume distribution caused by inaccurate or unstable driving of the air guide plate 14. Through the precise control of the driving component, the air guide plate 14 can be stably positioned at a preset rotation angle, ensuring that one end of it runs smoothly along the moving path of the transmission component, thereby realizing the fine and dynamic adjustment of the air volume distribution ratio of the two independent flow channels, and improving the performance and efficiency of the temperature-controlled dehumidifying duct air conditioner in different operating modes.

[0037] In some embodiments of this disclosure, a technical solution is proposed to achieve the rotation of the air guide plate 14 to adjust the airflow distribution in the duct by cooperating with the air guide fan 3-component, transmission component, and drive component. However, in actual operation, how to accurately and intelligently control the rotation of the air guide plate 14 according to different working modes (such as temperature control dehumidification mode and defrosting mode) to optimize the operating state of each heat exchanger and avoid drastic temperature changes is the key to improving system performance. In this regard, this disclosure further proposes that the temperature control dehumidification duct unit also includes a controller, which is signal-connected to the drive component; by controlling the rotation angle of the air guide plate 14, the airflow distribution ratio of the two independent flow channels is adjusted so that the temperature drop frequency of each heat exchanger is slowed down in temperature control dehumidification mode and defrosting mode.

[0038] Specifically, the controller is the core control unit of the temperature-controlled dehumidification duct air conditioner. It is responsible for receiving various sensor signals, executing preset control logic, and outputting control commands to the actuators (such as drive components). This controller can be implemented in the form of a microcontroller (MCU), programmable logic controller (PLC), or application-specific integrated circuit (ASIC). It typically integrates a processor, memory, and various input / output interfaces to achieve intelligent management of the entire system.

[0039] A signal connection is established between the controller and the driver to ensure that the controller can accurately send commands to the driver, and the driver can receive and execute these commands. This signal connection can be an electrical signal connection, such as communication via pulse width modulation (PWM), digital, or analog signals; or it can be a bus-based communication method, such as CAN bus, Modbus, I2C, or SPI, to achieve efficient data transmission and accurate command execution. Through this signal connection, the controller can perform real-time, precise control of the driver.

[0040] Based on this, the controller precisely controls the rotation angle of the air guide plate 14 by sending commands to the drive components. The rotation angle of the air guide plate 14 directly determines the airflow distribution ratio of the two independent flow channels passing through the regenerating heat exchanger 12 and the dehumidifying heat exchanger 13. The controller can calculate the optimal rotation angle of the air guide plate 14 according to preset control strategies, real-time environmental parameters, or user settings, and instruct the drive components (such as the stepper motor 17 or a servo motor) to adjust the air guide plate 14 to that target angle. This precise angle control is the core means of achieving refined airflow distribution.

[0041] By precisely controlling the rotation angle of the air guide plate 14, this disclosure aims to slow down the temperature drop frequency of each heat exchanger in both the temperature-controlled dehumidification mode and the defrosting mode. In the temperature-controlled dehumidification mode, the controller can dynamically adjust the airflow ratio between the dehumidification heat exchanger 13 and the regenerating heat exchanger 12 according to the ambient temperature and humidity parameters. This prevents the dehumidification heat exchanger 13 from becoming too cold and frosting due to excessive airflow, or the regenerating heat exchanger 12 from having insufficient airflow, thus ensuring dehumidification efficiency while maintaining stable indoor temperature and preventing a sharp drop in temperature. In the defrosting mode, the controller precisely controls the air guide plate 14 to concentrate the airflow of the indoor fan 3 to the regenerating heat exchanger 12, enabling more efficient use of heat for defrosting while effectively preventing cold air from blowing directly into the room, thereby maintaining a relatively stable indoor temperature.

[0042] By introducing a controller and connecting it to the drive unit via signals, this disclosure enables precise control of the rotation angle of the air guide plate 14, thereby dynamically adjusting the airflow distribution ratio between the regenerating heat exchanger 12 and the dehumidifying heat exchanger 13. In temperature-controlled dehumidification mode, the controller can intelligently adjust the airflow according to environmental parameters to prevent the temperature of the dehumidifying heat exchanger 13 from being too low or the temperature of the regenerating heat exchanger 12 from being too high, ensuring dehumidification effect while maintaining stable indoor temperature. In defrosting mode, by precisely controlling the air guide plate 14 to concentrate the airflow to the regenerating heat exchanger 12, heat can be efficiently utilized for defrosting, while effectively preventing cold air from blowing directly into the room. This refined airflow distribution management significantly reduces the frequency of temperature drop in each heat exchanger in both temperature-controlled dehumidification and defrosting modes, thereby improving the system's operational stability, energy efficiency, and user comfort.

[0043] The aforementioned temperature-controlled dehumidifying ducted air conditioner uses a drive component to rotate the air guide plate 14, thereby adjusting the airflow distribution ratio of the two independent flow channels. This reduces the frequency of temperature drop in each heat exchanger during both temperature-controlled dehumidification and defrosting modes. However, in practical applications, if the rotation angle of the air guide plate 14 lacks a clear, continuously adjustable range and key reference point, the airflow distribution adjustment may not be precise enough or the dynamic response may be insufficient. This makes it difficult to achieve smooth and accurate airflow control, thus affecting the optimized operation of the system under different operating conditions.

[0044] In this regard, this disclosure further proposes to denot the included angle between the air guide plate 14 and the regenerating heat exchanger 12 as a, and the adjustable range of the included angle a includes the minimum angle a1, the intermediate angle a2 and the maximum angle a3, and a1 < a2 < a3. The dynamic control of the air volume ratio of the two independent flow channels is obtained by the continuous change of the included angle a.

[0045] Specifically, the angle between the air guide plate 14 and the regenerating heat exchanger 12 is denoted as 'a'. This angle 'a' is a key parameter used to quantify the relative position of the air guide plate 14, defining the relative angular relationship between them. By accurately measuring or controlling this angle, the degree of influence of the air guide plate 14 on airflow distribution can be intuitively reflected. For example, the value of the angle 'a' can be obtained in real time by installing an angle sensor or encoder on the rotation axis of the air guide plate 14, or the angle 'a' can be calculated by the number of steps of a drive component (such as a stepper motor 17). The adjustable range of the angle 'a' includes a minimum angle 'a1', an intermediate angle 'a2', and a maximum angle 'a3', where a1 < a2 < a3. The minimum angle 'a1' indicates that the air guide plate 14 is in an extreme position, for example, minimizing the airflow through the regenerating heat exchanger 12 and maximizing the airflow through the dehumidifying heat exchanger 13. This typically corresponds to the air guide plate 14 being biased to the regenerating heat exchanger 12 to the maximum extent. The intermediate angle a2 indicates that the air guide plate 14 is in an intermediate position, for example, so that the airflow through the regenerating heat exchanger 12 and the dehumidifying heat exchanger 13 reaches a certain balance, such as being evenly distributed, or meeting a preset ratio under specific operating conditions. This usually corresponds to a specific angle between two extreme positions for the air guide plate 14. The maximum angle a3 indicates that the air guide plate 14 is in another extreme position, for example, so that the airflow through the regenerating heat exchanger 12 is the maximum, while the airflow through the dehumidifying heat exchanger 13 is the minimum. This usually corresponds to the air guide plate 14 being biased to the dehumidifying heat exchanger 13 to the maximum extent. The setting of a1 < a2 < a3 ensures that the air guide plate 14 has clear physical boundaries and logical order throughout the adjustment process, providing a basis for subsequent precise control. The dynamic control of the airflow ratio of the two independent flow channels is obtained by the continuous change of the included angle a. This means that the rotation of the air guide plate 14 is not a simple multi-level switching, but can be smoothly and steplessly adjusted within the entire range from a1 to a3. This continuous variation allows the system to make fine and dynamic adjustments to the airflow distribution ratio according to real-time needs. For example, the controller can instruct the drive components to adjust the angle of the air guide vane 14 in very small steps or continuously according to changes in environmental parameters, thereby achieving a gradual change in the airflow ratio, avoiding abrupt changes in airflow distribution, and improving the system's adaptability and comfort.

[0046] Through the above technical solution, the included angle α between the air guide plate 14 and the regenerating heat exchanger 12 is identified as a key control parameter, and a continuously adjustable range including the minimum angle α1, the intermediate angle α2, and the maximum angle α3 is set for it. This design allows the air guide plate 14 to achieve smooth, stepless rotation from α1 to α3, thereby dynamically and precisely controlling the airflow distribution ratio of the two independent flow channels. Compared with the solution that only adjusts by rotation angle, this solution can avoid abrupt changes in airflow distribution and ensure the stability of the airflow regulation process. In temperature control and dehumidification modes and defrosting modes, this dynamic control capability allows the system to accurately adjust the airflow through each heat exchanger according to actual operating conditions, effectively reducing the frequency of heat exchanger temperature drop, optimizing heat exchange efficiency, and improving system stability and comfort. For example, when rapid dehumidification is needed, the included angle α can be adjusted to be close to α1, so that most of the airflow flows through the dehumidification heat exchanger 13; when heat recovery is needed, the included angle α can be adjusted to be close to α3, so that most of the airflow flows through the heat recovery heat exchanger 12. This continuous and dynamic adjustment capability significantly improves the adaptability and performance of the temperature-controlled dehumidification duct air conditioner in complex environments.

[0047] In some embodiments of this disclosure, a temperature-controlled dehumidifying duct air conditioner is proposed, wherein the air guide plate 14 can dynamically adjust the airflow distribution ratio between the regenerating heat exchanger 12 and the dehumidifying heat exchanger 13. However, in practical applications, for conventional operating modes such as cooling, heating, or ventilation, the system often requires a stable and balanced airflow distribution strategy to ensure the efficient and coordinated operation of the heat exchangers and avoid increasing control complexity or affecting system stability due to excessive dynamic adjustment.

[0048] In this regard, this disclosure further proposes that, in cooling mode, heating mode and air supply mode, the controller controls the included angle of the air guide plate 14 to be maintained at a2, and the air volume of the two independent flow channels is evenly distributed to the regenerating heat exchanger 12 and the dehumidifying heat exchanger 13.

[0049] Specifically, cooling mode, heating mode, and air supply mode represent the main operating states of the temperature-controlled dehumidifying duct air conditioner in daily use. Cooling mode aims to lower the indoor temperature, heating mode aims to raise the indoor temperature, and air supply mode is mainly used for indoor air circulation without active temperature regulation. In these modes, the system's airflow distribution requirements emphasize stability and balance to optimize overall heat exchange efficiency and comfort. The controller is responsible for receiving system operation commands and sensor data, and controlling the temperature-controlled dehumidifying duct air conditioner according to preset logic. Here, the controller sends commands to the drive components to precisely position the air guide plate 14 at angle a2. Angle a2 is a preset intermediate angle for the air guide plate 14 to achieve even airflow distribution between the regenerating heat exchanger 12 and the dehumidifying heat exchanger 13; its specific value can be determined through system design and experimental calibration. When the included angle of the air guide plate 14 is precisely maintained at a2, the cross-sectional area and airflow resistance of the two independent flow channels formed by the air guide plate 14, namely the air channels leading to the regenerating heat exchanger 12 and the dehumidifying heat exchanger 13 respectively, are designed to be approximately equal, so that the air volume through the two flow channels can be roughly evenly distributed.

[0050] Through the above technical solution, when the temperature-controlled dehumidifying ducted air conditioner is operating in conventional modes such as cooling, heating, or air supply, the air guide plate 14 is stably fixed at the included angle a2, ensuring that the airflow can be evenly distributed to the regenerating heat exchanger 12 and the dehumidifying heat exchanger 13. This evenly distributed airflow strategy allows both heat exchangers to obtain sufficient and stable airflow in these modes, thereby avoiding the problem of decreased heat exchange efficiency or local overload caused by uneven airflow distribution. This not only helps to improve the overall operating efficiency and stability of the temperature-controlled dehumidifying ducted air conditioner in conventional modes, but also simplifies the control logic, reduces system energy consumption, and extends the service life of the heat exchangers, providing users with a more comfortable and reliable indoor environment.

[0051] In some embodiments of this disclosure, a method is proposed to isolate the air duct between the volute 11 and the regenerating heat exchanger 12 and the dehumidifying heat exchanger 13 into two independent upper and lower flow channels using a guide vane 14, and to adjust one end of the guide vane 14 to control the airflow distribution ratio. However, in actual operation, if there is a gap between the guide vane 14 and the duct wall, the airflow may mix between the two independent flow channels, thereby affecting the accuracy of airflow distribution, reducing heat exchange efficiency, and potentially causing energy loss.

[0052] In this regard, this disclosure further proposes that the air guide plate 14 is designed as an arc-shaped structure, the curvature of which matches the curvature of the inner wall of the volute 11, and the edge of the air guide plate 14 is provided with a sealing strip, which is tightly fitted to the sheet metal to avoid airflow mixing between the two independent flow channels. Specifically, the air guide plate 14 is designed as an arc with a specific curvature, rather than a simple planar structure. This arc-shaped design can better adapt to the internal contour of the volute 11, so that when the air guide plate 14 moves or rotates, the gap between its edge and the inner wall of the volute 11 or the sheet metal of the air duct is minimized, thereby optimizing the airflow guidance path and reducing eddies and pressure loss. The curvature of the air guide plate 14 is precisely matched and customized according to the shape of the inner wall of the volute 11. This adaptability ensures that the surface of the air guide plate 14 can form a continuous and smooth transition with the inner wall of the volute 11 at different positions, minimizing airflow disturbance and providing a good foundation for subsequent sealing. A sealing strip made of an elastic material is installed at the circumferential edge of the air guide plate 14, such as in the area contacting the inner wall of the volute 11 or the sheet metal of the air duct. This sealing strip is typically made of rubber, silicone, or other polymer materials with good elasticity and abrasion resistance, and its function is to form a flexible seal between the air guide plate 14 and the fixed structure. The sealing strip is configured to achieve a tight contact and fit with the sheet metal structure inside the air duct (e.g., the inner wall of the volute 11 or the air duct partition). This tight fit compensates for minor manufacturing tolerances or movement gaps between the air guide plate 14 and the sheet metal through the elastic deformation of the sealing strip, thereby effectively preventing airflow leakage from one flow channel to another.

[0053] Through the above technical solution, the air guide plate 14 adopts an arc-shaped structure, and its curvature is adapted to the inner wall curvature of the volute 11. This minimizes the gap between the edge of the air guide plate 14 and the duct wall when it moves or rotates within the duct, thereby optimizing the airflow guidance path. Furthermore, the sealing strips on the edge of the air guide plate 14 can fit tightly against the duct sheet metal, effectively filling any possible tiny gaps through their elastic deformation. This combined effect significantly avoids airflow mixing between the two independent flow channels, ensuring the accuracy and stability of airflow distribution. Therefore, in temperature and humidity control mode, the airflow ratio flowing through the regenerator 12 and dehumidifier 13 can be controlled more accurately, thereby improving heat exchange efficiency, reducing energy loss, and achieving more precise temperature and humidity control.

[0054] In some embodiments of this disclosure, the temperature-controlled dehumidifying duct air conditioner adjusts the airflow distribution ratio by moving one end of the air guide plate 14 up and down at the air outlet of the volute 11, and provides a stable movement path for the other end of the air guide plate 14 through a transmission component. However, in practical applications, how to ensure the stable and precise movement of the air guide plate 14 and effectively achieve fine control of airflow distribution is a technical problem that needs further improvement.

[0055] In this regard, the present disclosure further proposes that the above-mentioned transmission component is a gear 15, and a rack 16 is provided on the side of the volute 11. The gear 15 and the rack 16 are meshed and connected. When the air guide plate 14 rotates, it drives the gear 15 to slide along the rack 16.

[0056] Specifically, gear 15, as a common mechanical transmission element, transmits motion and power through the meshing of its teeth. In this embodiment, gear 15, as a transmission component, can convert the rotational motion of the air guide plate 14 into linear motion, or convert the rotational motion of the driving component into the rotation of the air guide plate 14, thereby achieving precise position control of the air guide plate 14. The advantages of gear 15 are stable transmission ratio, high transmission efficiency, compact structure, and long service life, ensuring the reliability and accuracy of the air guide plate 14's movement. Gear 15 can be in various forms, such as spur gear 15, helical gear 15, or herringbone gear 15, and the specific selection can be optimized based on factors such as transmission accuracy, load-bearing capacity, and space constraints. Meanwhile, rack 16, a toothed straight rod, is typically used in conjunction with gear 15 to form a gear 15 and rack 16 mechanism.

[0057] In this embodiment, rack 16 is disposed on the side of volute 11, providing a fixed linear track for meshing with gear 15. The placement and fixing method of rack 16 must ensure stable and reliable meshing with gear 15 and be able to withstand the reaction force generated when the air guide plate 14 moves. The tooth profile and module of rack 16 should match the mating gear 15 to ensure smooth and accurate transmission. The meshing connection between gear 15 and rack 16 refers to the interlocking of the teeth of gear 15 and rack 16, thereby realizing the transmission of motion. This meshing connection method has advantages such as no slippage, constant transmission ratio, and accurate positioning. Through precise meshing, it can be ensured that the air guide plate 14 will not have positional deviation or vibration during movement, thereby ensuring the accuracy of airflow distribution. The accuracy of the meshing connection directly affects the accuracy of the position control of air guide plate 14, therefore, the machining tolerances of gear 15 and rack 16 need to be strictly controlled during design and manufacturing. When the air guide plate 14 rotates under the action of the driving component, its rotation drives the gear 15 to rotate synchronously through a certain connection method (for example, the other end of the air guide plate 14 is fixedly connected to the gear 15 or connected through a linkage mechanism). Since the gear 15 meshes with the rack 16 fixed on the side of the volute 11, the rotation of the gear 15 will produce linear sliding along the rack 16, thereby realizing the up and down movement of one end of the air guide plate 14. This linkage mechanism effectively converts the rotational motion of the air guide plate 14 into linear reciprocating motion at one end, providing a reliable mechanical basis for accurately adjusting the air volume distribution ratio.

[0058] Through the above technical solution, the transmission component is specifically defined as a gear 15, and a rack 16 is provided on the side of the volute 11, so that the gear 15 and the rack 16 mesh and connect, thereby driving the gear 15 to slide along the rack 16 when the air guide plate 14 rotates. The introduction of this gear 15 and rack 16 mechanism provides a stable and high-precision linear movement path for one end of the air guide plate 14. Compared with other transmission methods, the gear 15 and rack 16 mechanism has the advantages of high transmission efficiency, accurate positioning, smooth movement and less slippage, effectively solving the problem of inaccurate positioning or unstable movement that may occur during the movement of the air guide plate 14. This allows the air guide plate 14 to adjust its vertical position at the air outlet of the volute 11 in a more precise manner, thereby achieving fine control of the air volume distribution ratio of the two independent flow channels between the regenerating heat exchanger 12 and the dehumidifying heat exchanger 13. Ultimately, this precise air volume adjustment capability helps to optimize the performance of the temperature-controlled dehumidifying duct air conditioner in different operating modes, and improve the system's energy efficiency and comfort.

[0059] In some embodiments of this disclosure, a scheme is proposed to drive the air guide plate 14 to rotate by a driving component to adjust the air volume distribution ratio. However, in practical applications, if the control precision of the driving component is insufficient, the air guide plate 14 may be mispositioned, thereby affecting the accuracy of air volume distribution and reducing the operating efficiency and effect in temperature control, dehumidification or defrosting modes.

[0060] In this regard, the present disclosure further proposes to configure the driving component as a stepper motor 17, which is connected to the rotating shaft of the air guide plate 14. The controller adjusts the rotation angle of the air guide plate 14 by controlling the rotation angle of the stepper motor 17.

[0061] Specifically, the driving component is a stepper motor 17. The stepper motor 17 is an open-loop controlled motor that converts electrical pulse signals into angular or linear displacement. It receives a series of electrical pulse signals and converts these signals into precise, discrete angular displacements; that is, for each input pulse signal, the motor rotates by a fixed angle (step angle). The stepper motor 17 typically consists of a stator and a rotor. Coils are wound on the stator, and the rotation of the rotor can be precisely controlled by controlling the energizing sequence and current magnitude of the coils. For example, a two-phase or five-phase hybrid stepper motor 17 can be selected, with a step angle typically between 0.72° and 1.8°, providing high positioning accuracy to ensure the accurate positioning of the air guide plate 14. The main function of the stepper motor 17 is to provide precise and controllable rotational power to drive the air guide plate 14 for angle adjustment. Its open-loop control characteristics allow for precise position control even without feedback, simplifying the control system design.

[0062] The stepper motor 17 is connected to the rotating shaft of the air guide plate 14 via a transmission connection. This transmission connection can be achieved through various mechanical methods. For example, the output shaft of the stepper motor 17 can be directly connected to the rotating shaft of the air guide plate 14 via a coupling to ensure synchronous rotation. Alternatively, a gear transmission mechanism 15 can be used, such as a small gear 15 mounted on the shaft of the stepper motor 17 and a large gear 15 mounted on the rotating shaft of the air guide plate 14. The meshing of the gears 15 achieves speed reduction and torque increase or changes the speed ratio to meet the rotational requirements of the air guide plate 14. Furthermore, a synchronous belt pulley transmission can be used, connecting the shaft of the stepper motor 17 and the rotating shaft of the air guide plate 14 via a synchronous belt to achieve precise synchronous transmission. This transmission connection ensures that the precise rotational motion of the stepper motor 17 can be effectively and losslessly transmitted to the air guide plate 14, thereby enabling precise angle adjustment of the air guide plate 14.

[0063] The controller adjusts the rotation angle of the air guide plate 14 by controlling the rotation angle of the stepper motor 17. The controller (e.g., a microcontroller or a dedicated stepper motor 17 driver) generates a pulse sequence based on a preset control strategy or real-time detected parameters. These pulse signals are amplified by the drive circuit and applied to the windings of the stepper motor 17. By controlling the number and frequency of the pulses, the rotation angle and speed of the stepper motor 17 can be controlled. For example, if the step angle of the stepper motor 17 is 1.8°, sending 100 pulses will cause the stepper motor 17 to rotate 180°. The controller can calculate the required angle of the air guide plate 14 based on parameters such as ambient temperature and humidity, and operating mode, by looking up a preset mapping table or executing a specific algorithm, and then convert this into the corresponding number of pulses sent to the stepper motor 17. This control method achieves precise, digital control of the air guide plate 14 angle, making the adjustment of the airflow distribution ratio more refined and intelligent, adaptable to different operating conditions and optimized control strategies.

[0064] Through the above technical solution, a stepper motor 17 is used as the driving component. Its inherent high precision, repeatable positioning, and open-loop control characteristics enable precise execution of every minute angle adjustment of the air guide plate 14. The controller can send precise pulse signals to the stepper motor 17 according to preset control logic or real-time feedback, thereby achieving fine-grained control of the rotation angle of the air guide plate 14. This precise angle adjustment capability ensures that the airflow distribution ratio of the two independent flow channels between the volute 11 and the regenerating heat exchanger 12 and the dehumidifying heat exchanger 13 can be accurately set and maintained. For example, in temperature-controlled dehumidification mode, the angle of the air guide plate 14 can be precisely adjusted according to the ambient temperature and humidity parameters, so that most of the airflow flows through the dehumidifying heat exchanger 13 or the regenerating heat exchanger 12, thereby optimizing the dehumidification and reheating effects. In defrosting mode, it can ensure that all the airflow of the indoor fan 3 flows precisely through the regenerating heat exchanger 12, improving defrosting efficiency and reducing the impact on indoor temperature. Therefore, this solution significantly improves the air volume distribution accuracy and control stability of the temperature-controlled dehumidifying duct air conditioner under different operating modes, thereby optimizing the overall performance and energy efficiency of the system.

[0065] In some embodiments of this disclosure, the airflow distribution ratio of the two independent flow channels is dynamically adjusted by rotating the air guide plate 14 to achieve a slow temperature drop frequency in the heat exchanger under temperature-controlled dehumidification mode. However, in actual temperature-controlled dehumidification operation, how to intelligently and precisely adjust the angle of the air guide plate 14 according to real-time changes in ambient temperature and humidity to ensure the best match between dehumidification and heat recovery effects while avoiding unnecessary energy loss is a technical problem that needs further resolution.

[0066] In response, this disclosure further proposes that in the temperature-controlled dehumidification mode, the controller detects ambient temperature and humidity parameters and controls the angle of the air guide plate 14 according to the dehumidification period and the heat recovery period. Specifically, during the dehumidification period, the angle of the air guide plate 14 is adjusted towards the minimum angle a1 according to a preset formula, so that most of the airflow flows through the dehumidification heat exchanger 13; during the heat recovery period, the angle of the air guide plate 14 is adjusted towards the maximum angle a3 according to a preset formula, so that most of the airflow flows through the heat recovery heat exchanger 12. The temperature-controlled dehumidification mode is an air conditioning operation mode designed to simultaneously control indoor temperature and humidity, and is particularly suitable for humid environments that require maintaining a specific temperature.

[0067] In this mode, the system not only reduces the moisture content in the air but also ensures a suitable supply air temperature, avoiding excessive cooling or heating. The controller, as the core of the system, is responsible for receiving signals from detection components such as ambient temperature and humidity sensors, executing preset control logic, and sending commands to the drive components to adjust the angle of the air guide vane 14. Detecting ambient temperature and humidity parameters refers to acquiring real-time indoor or return air temperature and humidity data through corresponding sensors. These parameters form the basis for the controller's intelligent decision-making and reflect the actual state of the current environment. The dehumidification period and the heat recovery period are two phases that typically alternate or work in tandem under the temperature-controlled dehumidification mode. During the dehumidification period, the air humidity is mainly reduced by the dehumidification heat exchanger 13, while during the heat recovery period, the dehumidified cold air is heated by the heat recovery heat exchanger 12 to prevent the supply air temperature from being too low and maintain indoor comfort. The controller executes different air guide vane 14 angle control strategies according to these period divisions, precisely adjusting the rotation angle of the air guide vane 14 to achieve fine adjustment of dehumidification and heat recovery.

[0068] During the dehumidification period, the primary goal of the system is to efficiently remove moisture from the air. At this time, the angle of the air guide vane 14 is adjusted towards the minimum angle a1 according to a preset formula. The minimum angle a1 typically corresponds to the position where the air guide vane 14 deflects most of the airflow towards the dehumidification heat exchanger 13. This preset formula can be a function based on empirical data, mathematical models, or fuzzy logic, mapping ambient humidity parameters (such as humidity difference) to the target angle of the air guide vane 14. For example, when the ambient humidity is high, the formula guides the air guide vane 14 closer to the minimum angle a1 to maximize the dehumidification effect. By adjusting the air guide vane 14 to near the minimum angle a1, the airflow through the dehumidification heat exchanger 13 can be effectively increased, thereby improving dehumidification efficiency and helping to quickly reduce indoor humidity to meet dehumidification needs.

[0069] During the heat recovery period, the system's primary objective is to heat the dehumidified cold air to prevent excessively low supply air temperatures and maintain indoor comfort. At this time, the angle of the air guide vane 14 is adjusted towards the maximum angle a3 according to a preset formula. The maximum angle a3 typically corresponds to the position where the air guide vane 14 directs most of the airflow towards the heat exchanger 12. This preset formula can also be a function based on empirical data, mathematical models, or fuzzy logic, mapping ambient temperature parameters (such as temperature difference) to the target angle of the air guide vane 14. For example, when the supply air temperature is too low, the formula guides the air guide vane 14 closer to the maximum angle a3 to maximize the heat recovery effect. By adjusting the air guide vane 14 to near the maximum angle a3, the airflow through the heat exchanger 12 is effectively increased, thereby improving heat recovery efficiency and helping to raise the supply air temperature to a comfortable range, preventing excessively low indoor temperatures.

[0070] Through the above technical solution, in temperature-controlled dehumidification mode, the controller can intelligently adjust the angle of the air guide plate 14 during dehumidification and reheating periods based on the real-time detected ambient temperature and humidity parameters. Specifically, during dehumidification, the angle of the air guide plate 14 is adjusted towards the minimum angle a1, allowing most of the airflow to preferentially flow through the dehumidification heat exchanger 13, thereby efficiently removing moisture from the air. During reheating, the angle of the air guide plate 14 is adjusted towards the maximum angle a3, allowing most of the airflow to preferentially flow through the reheating heat exchanger 12, fully heating the dehumidified cold air. This dynamic and refined airflow distribution strategy based on environmental parameters overcomes the limitations of traditional fixed airflow distribution or simple mode switching, enabling more precise matching of actual temperature and humidity requirements and optimizing the temperature-controlled dehumidification effect. By adjusting the angle of the air guide plate 14 in real time, the system can avoid over-dehumidification or over-reheating, effectively reducing energy consumption while ensuring indoor environmental comfort, avoiding excessively low or high supply air temperatures, and significantly improving the operating efficiency and user experience of the temperature-controlled dehumidification duct air conditioner.

[0071] In some embodiments of this disclosure, it is proposed that in the temperature-controlled dehumidification mode, the controller detects ambient temperature and humidity parameters and controls the angle of the air guide plate 14 during the dehumidification and heat recovery periods, so that most of the airflow flows through the dehumidification heat exchanger 13 or the heat recovery heat exchanger 12. However, if only a rough adjustment is made based on a preset relationship, it may be difficult to accurately respond to the dynamic changes in ambient temperature and humidity, resulting in poor dehumidification or heat recovery effects, affecting system energy efficiency and user comfort. In this regard, this disclosure further proposes that in the temperature-controlled dehumidification mode, the controller is configured such that: during the dehumidification period, the angle 'a' of the air guide plate 14 satisfies the relationship: a = a2 - ΔRA, where ΔR is the difference between the initial ambient humidity and the set humidity, A is the preset humidity coefficient, and a1 ≤ a ≤ a2; during the heat recovery period, the angle 'a' of the air guide plate 14 satisfies the relationship: a = a2 + ΔTB, where ΔT is the difference between the initial ambient temperature and the real-time ambient temperature, B is the preset temperature coefficient, and a2 ≤ a ≤ a3.

[0072] Specifically, during the dehumidification period, the controller is configured to calculate and set the angle 'a' of the air guide plate 14 based on the difference ΔR between the initial ambient humidity and the set humidity, combined with a preset humidity coefficient A, using the formula a = a2 - ΔRA. Here, ΔR represents the deviation between the current ambient humidity and the desired set humidity, while the preset humidity coefficient A quantifies this humidity deviation into the adjustment range of the air guide plate 14 angle. The air guide plate 14 angle 'a' is limited to between the minimum angle 'a1' and the intermediate angle 'a2', ensuring that most of the airflow can be precisely guided to the dehumidification heat exchanger 13 during dehumidification, thereby achieving efficient dehumidification. For example, the controller can have a built-in algorithm module that acquires ambient humidity data in real time, compares it with the user-set target humidity, calculates ΔR, and then dynamically adjusts the rotation angle of the air guide plate 14 according to the preset value of A.

[0073] During the heat recovery period, the controller is configured to calculate and set the angle 'a' of the air guide vane 14 based on the difference ΔT between the initial and real-time ambient temperatures, combined with a preset temperature coefficient B, using the formula a = a2 + ΔTB. Here, ΔT represents the deviation between the current ambient temperature and the initial temperature, and the preset temperature coefficient B quantifies this temperature deviation into the adjustment range of the air guide vane 14 angle. The air guide vane angle 'a' is limited to between the intermediate angle a2 and the maximum angle a3, ensuring that most of the airflow can be precisely guided to the heat exchanger 12 during the heat recovery process to compensate for the cooling caused by dehumidification and maintain indoor temperature comfort. For example, the controller can periodically acquire the real-time ambient temperature and compare it with the initial ambient temperature to calculate ΔT, and then dynamically adjust the rotation angle of the air guide vane 14 according to the preset B value.

[0074] Through the above technical solution, in temperature-controlled dehumidification mode, the controller can dynamically adjust the angle of the air guide plate 14 based on real-time ambient temperature and humidity parameters using precise mathematical formulas, achieving refined control of the airflow distribution ratio between the two independent flow channels. During the dehumidification period, the angle α of the air guide plate 14 is calculated and adjusted based on the difference ΔR between the initial ambient humidity and the set humidity, ensuring that most of the airflow can accurately flow through the dehumidification heat exchanger 13, thereby improving dehumidification efficiency and avoiding excessively low indoor temperatures due to over-dehumidification. During the heat recovery period, the angle α of the air guide plate 14 is calculated and adjusted based on the difference ΔT between the initial ambient temperature and the real-time ambient temperature, ensuring that most of the airflow can accurately flow through the heat recovery heat exchanger 12, effectively compensating for the temperature drop during dehumidification, maintaining indoor temperature comfort, and avoiding unnecessary heat recovery energy consumption. This precise angle adjustment mechanism based on real-time feedback enables the temperature-controlled dehumidification duct air conditioner to adapt to environmental changes more intelligently and efficiently, providing a more stable and comfortable indoor environment, significantly improving the system's energy efficiency ratio and user experience.

[0075] In some embodiments of this disclosure, a method is proposed to dynamically adjust the airflow distribution ratio using the air guide plate 14 to achieve temperature control and dehumidification. However, during air conditioner operation, especially in low-temperature and high-humidity environments, the heat exchanger surface is prone to frost formation, requiring defrosting. Traditional defrosting methods may suffer from low defrosting efficiency and excessively low indoor air temperature during defrosting, leading to user discomfort. Simply distributing airflow to the regenerating heat exchanger 12 may not fully utilize its heat and is also insufficient to effectively prevent direct cold airflow.

[0076] In response, this disclosure further proposes that in defrosting mode, the controller controls the air guide plate 14 to rotate to the maximum angle a3, so that all the air volume of the internal fan 3 flows through the regenerating heat exchanger 12, and at the same time, the air speed of the internal fan 3 is adjusted according to the internal pipe temperature of the regenerating heat exchanger 12.

[0077] Specifically, defrosting mode refers to an operating state that an air conditioner automatically enters when frost builds up on the surface of the outdoor heat exchanger during heating operation, affecting heat exchange efficiency. In this mode, the refrigerant flow is usually changed, turning the outdoor heat exchanger into an evaporator. Indoor heat or auxiliary electric heating is used to heat the outdoor heat exchanger to melt the frost layer on its surface.

[0078] The controller is the core control unit of the temperature-controlled dehumidifying duct air conditioner, responsible for receiving sensor signals, executing control logic, and outputting control commands. Here, the controller sends commands to the drive unit according to the preset defrosting strategy, causing the drive unit to rotate the air guide plate 14. The maximum angle a3 is the angle between the air guide plate 14 and the regenerating heat exchanger 12. When the air guide plate 14 rotates to this angle, it means that the air guide plate 14 has been adjusted to a position that directs most or even all of the airflow to the regenerating heat exchanger 12. The internal fan 3 is the component inside the duct air conditioner used to circulate indoor air. In defrosting mode, by adjusting the air guide plate 14 to the maximum angle a3, it can be ensured that all the airflow generated by the internal fan 3 is guided to the regenerating heat exchanger 12. In defrosting mode, the regenerating heat exchanger 12 typically acts as a condenser, receiving high-temperature, high-pressure refrigerant from the compressor 2 and transferring heat to the flowing air, thereby increasing the supply air temperature.

[0079] The internal pipe temperature refers to the temperature of the refrigerant flowing through the pipes inside the regenerator 12. The graded adjustment of the internal fan 3 speed refers to dividing the operating speed of the internal fan 3 into different levels based on the real-time value of the internal pipe temperature, and selecting the appropriate speed according to the level of the internal pipe temperature. This adjustment method can dynamically adjust the air volume according to the actual heating capacity of the regenerator 12 to optimize defrosting effect and indoor comfort.

[0080] Through the above technical solution, in defrost mode, the controller precisely controls the air guide plate 14 to rotate to the maximum angle a3, ensuring that all the airflow generated by the indoor fan 3 flows through the regenerator 12. This allows the regenerator 12 to fully absorb the heat released by the refrigerant, thereby maximizing the supply air temperature and effectively avoiding the phenomenon of cold air blowing directly during defrost, significantly improving user comfort. Simultaneously, based on the temperature-controlled internal pipes of the regenerator 12, the fan speed of the indoor fan 3 is adjusted in stages, ensuring that the airflow matches the actual heating capacity of the regenerator 12. When the temperature of the regenerator 12 is high, the fan speed can be appropriately increased to accelerate heat transfer and improve defrost efficiency; when the temperature of the regenerator 12 is low, the fan speed is reduced to avoid delivering excessively cold air. This dynamic and intelligent adjustment mechanism not only optimizes the heat utilization efficiency during defrost and shortens the defrost cycle, but also continuously delivers air at a suitable temperature to the room while ensuring defrost effectiveness, greatly improving indoor environmental comfort during defrost mode.

[0081] In defrosting mode, the controller controls the air guide plate 14 to rotate to its maximum angle a3, so that all the airflow from the internal fan 3 flows through the regenerating heat exchanger 12, and adjusts the fan speed of the internal fan 3 according to the internal pipe temperature of the regenerating heat exchanger 12. However, if the adjustment of the fan speed of the internal fan 3 lacks fine-grained and hierarchical management, it may lead to poor defrosting effect. For example, if the fan speed is too high when the pipe temperature is low, it will carry away too much heat, affecting defrosting efficiency; while if the fan speed is too low when the pipe temperature is high, it may cause heat accumulation, making it impossible to effectively utilize heat for defrosting, and even affecting system stability. Therefore, a more refined internal fan speed adjustment mechanism is needed to optimize the heat transfer and utilization efficiency during the defrosting process.

[0082] In this regard, this disclosure further proposes that the preset tube temperature thresholds of the regenerative heat exchanger 12 include Ta, Tb, and Tc, and Ta < Tb < Tc; when the inner tube temperature T_inner_tube ≤ Ta, the inner fan 3 operates at a low speed; when Ta < T_inner_tube ≤ Tb, it operates at a medium speed; when Tb < T_inner_tube ≤ Tc, it operates at a high speed; and when T_inner_tube > Tc, it operates at an ultra-high speed.

[0083] Specifically, the preset pipe temperature thresholds Ta, Tb, and Tc are critical points used to divide the internal pipe temperature (inner pipe temperature) of the regenerating heat exchanger 12 into multiple intervals. These thresholds can be calibrated based on the design parameters of the ducted air conditioner, the performance of the heat exchanger, the defrosting strategy, and actual operation test data, and stored in the controller. For example, experiments can be conducted to determine the optimal airflow speed of the inner fan 3 at different pipe temperatures to achieve the best defrosting effect and indoor air supply comfort.

[0084] When the inner tube temperature T is at a low level (less than or equal to Ta), it indicates that the heat exchanger surface temperature is low, there may be a thick layer of frost, or the initial defrosting process requires slow heating. At this time, the controller will instruct the inner fan 3 to operate at a low speed to reduce the amount of airflow that carries away heat from the heat exchanger surface. This helps heat accumulate inside the heat exchanger, promotes the melting of the frost, and prevents excessively cold air from blowing directly into the room, thus improving indoor comfort.

[0085] As the defrosting process progresses, when the inner tube temperature T is between Ta and Tb, it indicates that the heat exchanger surface temperature has increased, and the frost layer may begin to melt. At this time, the controller instructs the inner fan 3 to switch to medium speed operation, which can moderately increase the indoor air volume while ensuring defrosting efficiency, so as to more effectively transfer the heat generated by defrosting to the room and increase the indoor temperature.

[0086] When the inner tube temperature T is between Tb and Tc, it indicates that the defrosting process is nearing completion, the heat exchanger surface temperature is high, and most of the frost has melted. At this time, the controller instructs the inner fan 3 to operate at high speed, which can maximize the transfer of heat generated by the regenerative heat exchanger 12 to the room, quickly raise the indoor temperature, compensate for the heat that may be lost during the defrosting process, and prepare for the subsequent normal operation mode.

[0087] When the inner tube temperature T exceeds the maximum threshold Tc, it indicates that defrosting is basically complete, the heat exchanger surface temperature is very high, and there may even be a risk of overheating. At this time, the controller instructs the inner fan 3 to operate at the highest fan speed, which can quickly remove the heat from the heat exchanger, avoid local overheating, and at the same time send a large amount of hot air into the room, quickly improving indoor comfort and providing sufficient heat dissipation for the system to return to normal operating mode.

[0088] Through the above technical solution, preset pipe temperature thresholds Ta, Tb, and Tc are introduced for the regenerating heat exchanger 12. Based on the comparison between the inner pipe temperature T and these thresholds, the operating speed of the inner fan 3 is divided into low, medium, high, and ultra-high speeds for graded adjustment. This refined airflow control mechanism allows the inner fan 3 to dynamically adjust the airflow according to the actual temperature of the regenerating heat exchanger 12 during defrosting mode. Operating at a low speed during the initial defrosting stage or when the pipe temperature is low helps heat accumulate on the heat exchanger surface, promoting frost melting and preventing premature heat loss, thereby improving defrosting efficiency and reducing indoor coldness. As defrosting progresses and the pipe temperature rises, the fan speed is gradually increased, more effectively transferring the heat generated during defrosting to the room, rapidly raising the indoor temperature and compensating for heat loss during the defrosting process. Especially during the final stages of defrosting or when pipe temperatures are high, operating at high or even ultra-high fan speeds not only maximizes heat utilization and quickly warms the room, but also effectively prevents localized overheating of the heat exchanger, ensuring stable system operation. This tiered adjustment strategy significantly optimizes heat utilization efficiency and indoor comfort in defrosting mode, avoiding incomplete defrosting or heat waste that may result from using a single fan speed, making the defrosting process more efficient, energy-saving, and providing a better user experience.

[0089] The aforementioned temperature-controlled dehumidifying ducted air conditioner adjusts the airflow distribution ratio between the regenerating heat exchanger 12 and the dehumidifying heat exchanger 13 via the air guide plate 14 in the air guide fan 3 structure to achieve functions such as temperature control, dehumidification, or defrosting. However, in actual operation, the ambient temperature, humidity, and internal operating conditions of the heat exchangers are dynamically changing. Relying solely on preset control logic or fixed adjustment parameters may fail to accurately detect and respond to these changes, resulting in low system operating efficiency or failure to achieve optimal temperature control and dehumidification effects under specific operating conditions, and may even affect the timeliness and thoroughness of defrosting. To enable the temperature-controlled dehumidifying ducted air conditioner to intelligently and accurately adjust according to the actual operating environment and internal operating conditions, thereby optimizing its performance and improving the user experience, a real-time data feedback mechanism needs to be introduced.

[0090] In this regard, this disclosure further proposes that the above-mentioned temperature-controlled dehumidifying duct air conditioner also includes a detection component, which includes an ambient temperature sensor for detecting ambient temperature, a humidity sensor for detecting ambient humidity, and an inner pipe temperature sensor for detecting the inner pipe temperature of the regenerating heat exchanger 12. The ambient temperature sensor, humidity sensor, and inner pipe temperature sensor are all connected to the controller signal.

[0091] The detection component is a hardware suite used to monitor the operating environment and key internal parameters of the temperature-controlled dehumidification duct air conditioner in real time. Its main function is to collect necessary data and transmit this data to the controller, which then uses it as the basis for intelligent decision-making and precise control.

[0092] An ambient temperature sensor is used to detect the air temperature in the environment surrounding the temperature-controlled dehumidifying duct air conditioner in real time. It can be implemented using various technologies, such as thermistors, platinum resistance thermometers (RTDs), or thermocouples. Thermistors are often chosen due to their high sensitivity and cost-effectiveness; their resistance changes with temperature, and the controller can calculate the ambient temperature by measuring the resistance value. Ambient temperature sensors are typically installed near the return air vent of the duct air conditioner to accurately obtain indoor ambient temperature information.

[0093] Humidity sensors are used to monitor the air humidity in the environment of a temperature-controlled dehumidifying duct air conditioner in real time. Common humidity sensors include capacitive and resistive humidity sensors. Capacitive humidity sensors reflect humidity by measuring changes in the dielectric constant, while resistive humidity sensors reflect humidity by measuring changes in the resistance of a conductive polymer. Humidity sensors are often installed in conjunction with ambient temperature sensors to provide comprehensive environmental parameters.

[0094] The internal pipe temperature sensor of the regenerator heat exchanger 12 is used to monitor the temperature of the refrigerant or heat transfer medium inside the regenerator heat exchanger 12 in real time. This sensor typically uses a thermistor or thermocouple and is in direct or indirect contact with the pipe wall or internal fluid of the regenerator heat exchanger 12. Its installation location is usually at a critical part of the regenerator heat exchanger 12, such as near the refrigerant inlet or outlet, to accurately reflect the operating status of the heat exchanger. Especially in defrost mode, its temperature data is crucial for judging the frosting condition and defrosting effect.

[0095] The ambient temperature sensor, humidity sensor, and inner tube temperature sensor establish signal connections with the controller via wired or wireless means. Wired connections typically use analog signal lines or digital communication buses (such as I2C, SPI, RS485, etc.) to transmit the analog or digital signals collected by the sensors to the controller. After receiving these signals, the controller performs necessary processing and analysis to obtain real-time data on ambient temperature, humidity, and the inner tube temperature of the regenerating heat exchanger 12.

[0096] By introducing detection components, including an ambient temperature sensor, a humidity sensor, and an internal pipe temperature sensor for the regenerating heat exchanger 12, and connecting them to the controller signal, the temperature-controlled dehumidifying duct air conditioner can acquire accurate real-time data on ambient temperature, ambient humidity, and the internal temperature of the regenerating heat exchanger 12. This real-time data provides the controller with a basis for dynamically adjusting the angle of the air guide vane 14, allowing the airflow distribution ratio to be adjusted adaptively based on actual operating conditions, rather than relying on preset fixed parameters. For example, in temperature-controlled dehumidification mode, the controller can more accurately adjust the angle of the air guide vane 14 based on real-time ambient temperature and humidity parameters to optimize the airflow distribution during dehumidification and regeneration, avoiding over-dehumidification or insufficient regeneration, thereby improving dehumidification efficiency and comfort. In defrosting mode, the internal pipe temperature data provided by the internal pipe temperature sensor allows the controller to more accurately determine the frosting situation and defrosting process, and then finely adjust the fan speed of the internal fan 3 to ensure the timeliness and thoroughness of the defrosting process, while avoiding unnecessary energy consumption. This intelligent control based on real-time feedback significantly improves the operating accuracy, energy efficiency, and user experience of temperature-controlled and dehumidifying duct air conditioners.

[0097] In the HVAC field, ducted air conditioners are widely used in residential and office spaces due to their wide air delivery range and concealed installation. To achieve temperature and humidity control, existing technologies propose using two evaporators, one for evaporation and the other for heat recovery, to initially regulate temperature and humidity through their collaboration. However, this approach has significant technical drawbacks: firstly, the heat exchange capacity of the two evaporators is relatively fixed, and the airflow distribution ratio between them cannot be dynamically adjusted, leading to excessive or insufficient temperature drop during dehumidification, making precise temperature control difficult; secondly, during defrosting, the four-way valve switches to cooling mode, the indoor fan 3 shuts down, and there is no continuous heating path, resulting in interrupted heat delivery and significant fluctuations in indoor temperature, severely impacting user comfort. Therefore, a technical solution is urgently needed that can flexibly adjust the airflow distribution between the two evaporators while maintaining precise temperature and humidity control and defrosting stability, addressing the core pain points of existing products.

[0098] In this regard, the present disclosure also discloses an air conditioner, including the temperature-controlled and dehumidifying duct air conditioner as described above.

[0099] This embodiment integrates a temperature-controlled dehumidifying duct unit with dynamic airflow distribution adjustment capability into an air conditioner, thereby solving the problem of inaccurate temperature control caused by fixed airflow distribution of the heat exchanger in traditional solutions, as well as the temperature fluctuation problem caused by heat interruption during defrosting, achieving the effect of improving the accuracy of dehumidification and temperature control and the comfort of the defrosting process. Specifically, the temperature-controlled dehumidifying duct air conditioner includes a main unit housing 1, within which a volute 11, a regenerating heat exchanger 12, and a dehumidifying heat exchanger 13 are installed, arranged vertically opposite to each other. A guide fan 3 is installed across the air outlet of the volute 11 and is positioned opposite to the regenerating heat exchanger 12 and the dehumidifying heat exchanger 13. The guide fan 3 includes a guide plate 14, which is used to isolate the air duct between the volute 11 and the regenerating heat exchanger 12 and the dehumidifying heat exchanger 13 into two independent flow channels, one above the other, corresponding to the regenerating heat exchanger 12 and the other to the dehumidifying heat exchanger 13. One end of the guide plate 14 is configured to move vertically at the air outlet of the volute 11 to adjust the airflow distribution ratio of the two independent flow channels.

[0100] In some embodiments of this disclosure, the technical feature of dynamically adjusting the airflow distribution of the air guide plate 14 is proposed. However, in its implementation, it is necessary to ensure the reliability and adjustment accuracy of the airflow isolation. In specific implementation, the whole unit housing 1 serves as a closed installation space, and the volute 11, the regenerating heat exchanger 12, and the dehumidifying heat exchanger 13 are fixed inside by brackets. The regenerating heat exchanger 12 and the dehumidifying heat exchanger 13 adopt a stacked finned tube structure. The air guide plate 14 of the air guide fan 3 spans the air outlet of the volute 11. One end of it moves up and down through a transmission component, and the other end is connected to the drive component via a rotating shaft. When the air guide plate 14 moves, the cross-sectional area of ​​the upper and lower independent flow channels changes dynamically. For example, when the air guide plate 14 moves upward, it increases the flow channel area of ​​the dehumidifying heat exchanger 13, allowing more airflow to pass through the dehumidifying heat exchanger 13 to enhance the dehumidification effect; when it moves downward, it increases the flow channel area of ​​the regenerating heat exchanger 12, improving the reheat capacity to avoid excessive temperature drop. This design effectively solves the temperature control deviation problem caused by fixed air volume distribution in traditional solutions by physically isolating the air duct and dynamically adjusting the distribution ratio.

[0101] Furthermore, this technical solution demonstrates significant advantages in defrosting mode. When the unit enters the defrosting stage, the air guide plate 14 is driven to its maximum angle, allowing all the airflow from the indoor fan 3 to flow through the regenerating heat exchanger 12. Simultaneously, the controller adjusts the fan speed of the indoor fan 3 in stages based on the internal pipe temperature of the regenerating heat exchanger 12. Specifically, the internal pipe temperature sensor monitors the temperature in real time. When the internal pipe temperature is below the threshold Ta, the low fan speed is activated; when it is between Ta and Tb, the medium fan speed is switched, and so on until the ultra-high fan speed is activated. This coordinated control of airflow and speed ensures that heat is continuously transferred to the room during the defrosting process, avoiding the heat interruption caused by the reversal of the four-way valve in traditional solutions, thereby significantly suppressing indoor temperature fluctuations.

[0102] Through the above technical solution, this air conditioner not only achieves precise temperature and humidity control during the dehumidification process but also ensures thermal stability during the defrosting stage. In temperature-controlled dehumidification mode, the angle of the air guide plate 14 is dynamically adjusted according to the ambient temperature and humidity parameters: during the dehumidification period, the angle is adjusted towards the minimum angle a1 to concentrate the airflow on the dehumidification heat exchanger 13, while during the heat recovery period, it is adjusted towards the maximum angle a3 to enhance the heat recovery effect. In defrosting mode, the air guide plate 14 fully opens the flow channel of the heat recovery heat exchanger 12 and, in conjunction with graded airflow control, forms a complete thermal management closed loop. Overall, this technical concept, by integrating a temperature-controlled dehumidification duct unit with dynamic airflow distribution capabilities, fundamentally optimizes the temperature and humidity control performance and defrosting continuity of the air conditioner, providing users with a more stable and comfortable environment.

[0103] In the HVAC field, existing ducted air conditioners suffer from fixed heat exchange capacity of two evaporators, resulting in an inability to dynamically adjust the airflow distribution ratio. This leads to problems such as excessive or insufficient indoor temperature drop during dehumidification. Furthermore, during defrosting, the four-way valve switches to cooling mode, shutting down the indoor fan and eliminating a continuous heating path, causing an interruption in heat delivery and significant fluctuations in indoor temperature, severely impacting user comfort. To address these issues, this disclosure also provides a control method for the aforementioned temperature-controlled dehumidification ducted air conditioner. This method includes: activating the temperature-controlled dehumidification mode; Obtain the difference between the initial ambient humidity R and the set humidity Rset, ΔR = RsetRset. The angle of the air guide vane 14 is adjusted towards the minimum angle a1 according to the control angle ΔR, so that most of the airflow flows through the dehumidification heat exchanger 13 (until ΔR ≤ 5%). This embodiment combines the difference in ambient humidity ΔR with the angle adjustment of the air guide plate 14 according to a preset formula, thereby dynamically distributing airflow to the dehumidification heat exchanger 13 during the dehumidification period. This solves the problem of excessive or insufficient indoor temperature drop caused by fixed airflow distribution in the prior art. Specifically, when the system detects the difference ΔR between the initial ambient humidity and the set humidity, the controller adjusts the angle of the air guide plate 14 in real time based on this difference, so that the airflow distribution ratio is precisely matched with the dehumidification demand. Since the angle of the air guide plate 14 is continuously adjusted towards the minimum angle a1, most of the airflow is guided to the dehumidification heat exchanger 13 for efficient dehumidification, while avoiding temperature fluctuations caused by fixed airflow distribution in traditional solutions.

[0104] Through the above technical solution, a dynamic response mechanism for airflow distribution is achieved in the temperature control and dehumidification process. During the dehumidification period, the angle of the air guide plate 14 is continuously optimized according to the change in the value of ΔR, ensuring that the dehumidification heat exchanger 13 receives sufficient airflow to quickly reduce humidity; when ΔR gradually decreases to within 5%, the system automatically terminates angle adjustment to maintain a stable humidity control state. This method not only effectively suppresses excessive drop in indoor temperature, but also improves dehumidification efficiency through precise airflow control, thereby solving the core pain point of inaccurate temperature and humidity coordinated control in existing technologies while ensuring comfort.

[0105] In some of the embodiments described above, the temperature control and dehumidification mode mainly controls humidity by adjusting the angle of the air guide plate 14. However, in its implementation, if dehumidification is carried out for a long time, the indoor temperature may continue to drop, causing users to feel uncomfortable and failing to achieve an ideal temperature and humidity balance.

[0106] In response, this disclosure further proposes a temperature-controlled dehumidification method, which includes: activating the temperature-controlled dehumidification mode; obtaining the difference ΔT = T0 - T between the initial ambient temperature T0 and the real-time ambient temperature T; and adjusting the angle of the air guide plate 14 towards the maximum angle a3 according to ΔT, so that most of the airflow flows through the regenerating heat exchanger 12 (until ΔT ≤ 0.5℃).

[0107] In temperature-controlled dehumidification mode, to effectively manage indoor temperature, the controller continuously acquires the real-time ambient temperature T. Simultaneously, the controller records the initial ambient temperature T0 when the temperature-controlled dehumidification mode is activated. By calculating the difference ΔT between the initial ambient temperature T0 and the real-time ambient temperature T, the deviation of the current indoor temperature can be accurately assessed, providing a quantitative basis for subsequent temperature adjustments. For example, when ΔT is positive, it indicates that the real-time ambient temperature T is lower than the initial ambient temperature T0, requiring temperature increase.

[0108] Based on the calculated temperature difference ΔT, the controller intelligently adjusts the angle of the air guide vane 14. Specifically, when the real-time ambient temperature T is detected to be lower than the initial ambient temperature T0, and ΔT exceeds a preset threshold (e.g., 0.5℃), the controller drives the air guide vane 14 to rotate towards the maximum angle a3. The maximum angle a3 is set to ensure that most of the airflow generated by the indoor fan 3 can flow through the regenerating heat exchanger 12, thereby heating the airflow using the regenerating heat exchanger 12. This adjustment process continues until ΔT decreases to less than or equal to 0.5℃, meaning the indoor temperature has essentially returned to the initial or target temperature level, thus ensuring that the indoor temperature remains within a comfortable range while dehumidifying.

[0109] Through the above technical solution, the temperature-controlled dehumidifying duct air conditioner can monitor indoor temperature changes in real time during dehumidification operation and dynamically adjust the angle of the air guide plate 14 according to temperature deviations, directing the airflow to the regenerating heat exchanger 12 for heating. This effectively avoids excessive drop in indoor temperature during prolonged dehumidification, significantly improving user comfort. This solution achieves a synergistic effect of humidity control and temperature maintenance, making the indoor environment more stable and pleasant in temperature-controlled dehumidification mode, and optimizing the overall operating performance of the air conditioner.

[0110] In temperature-controlled dehumidification mode, the above method obtains the difference ΔR between the initial ambient humidity and the set humidity, and adjusts the angle of the air guide plate 14 towards the minimum angle a1 based on ΔR, so that most of the airflow flows through the dehumidification heat exchanger 13 to achieve preliminary humidity control. However, in actual operation, relying solely on the airflow distribution adjustment of the air guide plate 14 may not be able to accurately and stably maintain the ambient humidity within the ideal set range, easily leading to insufficient humidity control accuracy or large humidity fluctuations, affecting user experience and system energy efficiency.

[0111] In response, this disclosure further proposes that after adjusting the air guide plate 14 to the minimum angle a1 according to ΔR, ΔR is checked. If ΔR exceeds the preset range (-3% to 3%), the opening of the indoor electronic expansion valve is adjusted to bring ΔR back to the preset range (-3% to 3%).

[0112] The verification ΔR refers to the process where, after adjusting the air guide vane angle 14 based on the initial humidity difference, the controller re-detects the current actual ambient humidity and compares it with the set humidity to recalculate the current humidity difference ΔR. This step ensures that the system can monitor the effectiveness of humidity control in real time, providing an accurate basis for subsequent fine-tuning. Verification can be performed periodically, such as collecting humidity data and calculating the difference every few seconds or tens of seconds; or it can be triggered by events, such as after the air guide vane angle 14 is adjusted or when a humidity change exceeds a certain threshold.

[0113] The preset range (-3% to 3%) refers to the allowable fluctuation range of the humidity difference ΔR. When the verified ΔR value is less than -3% or greater than 3%, the current ambient humidity is considered to deviate too much from the set humidity, requiring further intervention and adjustment. This range is designed to balance control precision and system response speed, avoiding overly frequent or unnecessary adjustments while ensuring the effectiveness of humidity control. This range can be flexibly configured according to the actual application scenario, user comfort requirements, and system performance.

[0114] An indoor electronic expansion valve is a throttling device used to precisely control the refrigerant flow rate. By adjusting its opening, the refrigerant flow rate and evaporation pressure flowing through the indoor heat exchanger can be altered, thus affecting the evaporation temperature and cooling capacity of the heat exchanger. In dehumidification mode, lowering the evaporation temperature enhances dehumidification capacity, while raising the evaporation temperature weakens it. Adjusting the opening of the indoor electronic expansion valve allows for precise control of the refrigeration system's dehumidification capacity, thereby indirectly and effectively regulating indoor humidity. Its opening adjustment is typically calculated and output by the controller using an algorithm to achieve continuous and smooth regulation.

[0115] Bringing ΔR back to the preset range (-3% to 3%) means adjusting the opening of the indoor electronic expansion valve to readjust the difference between the current ambient humidity and the set humidity to an acceptable fluctuation range. This means that when the humidity is too high (ΔR is too large), the system will adjust the opening of the electronic expansion valve to enhance dehumidification; when the humidity is too low (ΔR is too small, i.e., the ambient humidity is too far below the set humidity), the system will adjust the opening of the electronic expansion valve to reduce dehumidification, and may even use other means (such as heat recovery) to avoid over-dehumidification. This aims to achieve precise control of indoor humidity and ensure that it is stably maintained within the user-set comfort range.

[0116] By adjusting the angle of the air guide plate 14 according to the humidity difference, further verifying the humidity difference ΔR, and introducing an indoor electronic expansion valve opening adjustment mechanism, this disclosure enables more precise and dynamic control of indoor humidity. When adjusting the air guide plate 14 alone cannot maintain the humidity within the preset comfort range, the intervention of the electronic expansion valve provides an additional adjustment dimension, enabling precise adjustment of the dehumidification capacity of the refrigeration system. This effectively avoids problems such as insufficient humidity control accuracy or excessive humidity fluctuations, ensuring that the indoor ambient humidity can stably return to and be maintained within the target preset range, significantly improving user comfort and system operational stability under temperature control and dehumidification modes.

[0117] In the HVAC field, there is a significant technical defect in the defrosting process of ducted air conditioners: when the four-way valve switches to cooling mode, the indoor fan 3 in the traditional solution is shut down and there is no continuous heating path, which leads to the interruption of heat delivery to the room, resulting in large fluctuations in the indoor ambient temperature and seriously affecting user comfort.

[0118] In this regard, the present disclosure also discloses a control method applied to the above-mentioned air conditioner, the method including a defrosting control method: Activate defrost mode; Control the air guide plate 14 to rotate to the maximum angle a3 so that all the air volume of the internal fan 3 flows through the heat exchanger 12; The temperature of the inner tube of the regenerating heat exchanger 12, T_inner tube, is obtained. The speed of the inner fan 3 is adjusted according to the value of T_inner tube to ensure that heat is continuously delivered to the room during the defrosting process.

[0119] This embodiment combines the angle control of the air guide plate 14 with the feedback adjustment of the inner pipe temperature to maintain a continuous supply of heat to the room during defrosting, avoiding the heat interruption problem caused by the reversal of the four-way valve in traditional solutions. Specifically, when the air guide plate 14 rotates to its maximum angle a3, all the airflow of the inner fan 3 is guided to the regenerating heat exchanger 12, forming a stable heating airflow path. At the same time, based on the real-time monitoring data of the inner pipe temperature T of the regenerating heat exchanger 12, the fan speed of the inner fan 3 is adjusted in stages to dynamically match the heat demand during defrosting. Due to the graded control mechanism of the inner pipe temperature threshold, the system can accurately adjust the fan speed according to the specific value of T, ensuring the continuity and stability of heat output, thereby effectively suppressing indoor temperature fluctuations.

[0120] The above technical solution not only solves the fundamental problem of heat supply interruption during defrosting, but also achieves precise control of indoor ambient temperature. Compared with the basic solution, this disclosure significantly improves the ability to continuously deliver heat to the room in defrosting mode, avoiding the decrease in comfort caused by the shutdown of fan 3 in traditional technology, and providing users with a more stable thermal environment experience.

[0121] The following example will provide a more detailed explanation of the above technical solution: In an office area, User A installed a temperature-controlled dehumidifying ducted air conditioner to maintain indoor environmental comfort. The ducted air conditioner has a compact internal structure, with a volute 11, a regenerative heat exchanger 12, and a dehumidifying heat exchanger 13 arranged in a reasonable manner within the unit housing 1, wherein the regenerative heat exchanger 12 and the dehumidifying heat exchanger 13 are arranged vertically opposite each other.

[0122] A guide fan 3 is installed across the air outlet of the volute 11. This guide fan 3 is positioned opposite the regenerating heat exchanger 12 and the dehumidifying heat exchanger 13, and its core component is the guide vane 14. The function of the guide vane 14 is to effectively isolate the air duct between the volute 11 and the two heat exchangers into two independent upper and lower flow channels, corresponding to the regenerating heat exchanger 12 and the dehumidifying heat exchanger 13 respectively. One end of the guide vane 14 is designed to move up and down at the air outlet of the volute 11, thereby achieving precise adjustment of the airflow distribution ratio between these two independent flow channels. Unlike existing technologies where the airflow distribution ratio remains constant, this ducted air conditioner, through the dynamic adjustment of the guide vane 14, avoids the problem of excessive or insufficient indoor temperature drop during dehumidification, providing a foundation for achieving precise temperature control and dehumidification.

[0123] To ensure the stability of the air guide plate 14's movement, the temperature-controlled dehumidifying duct air conditioner also includes a transmission component. This transmission component is installed at the air outlet of the volute 11 and meshes with the air guide plate 14, providing a stable movement path for the other end of the air guide plate 14. Specifically, the transmission component can be a gear 15, with a rack 16 meshing with it on the side of the volute 11. When the air guide plate 14 rotates, it drives the gear 15 to slide along the rack 16. A preset mounting position is provided on the inner side of the junction between the regenerating heat exchanger 12 and the dehumidifying heat exchanger 13, where a driving component (e.g., a stepper motor 17) is installed. The other end of the air guide plate 14 is driven and connected to the stepper motor 17 via a rotating shaft. By precisely controlling its rotation angle, the stepper motor 17 drives the air guide plate 14 to rotate around the rotating shaft, thereby causing one end of the air guide plate 14 to move up and down along the movement path of the transmission component formed by the gear 15 and the rack 16.

[0124] The temperature-controlled dehumidifying duct air conditioner is equipped with a controller that is connected to the stepper motor 17. The controller receives signals from detection components (including an ambient temperature sensor, a humidity sensor, and an inner pipe temperature sensor) to acquire real-time ambient temperature and humidity parameters and the inner pipe temperature of the regenerating heat exchanger 12. By controlling the rotation angle of the air guide plate 14, the airflow distribution ratio of the two independent flow channels can be adjusted. The angle between the air guide plate 14 and the regenerating heat exchanger 12 is denoted as 'a', and its adjustable range includes a minimum angle a1, a middle angle a2, and a maximum angle a3, where a1 < a2 < a3. This continuous change in angle 'a' allows for dynamic control of the airflow ratio of the two independent flow channels, resulting in a slower temperature drop frequency for each heat exchanger in both the temperature-controlled dehumidifying and defrosting modes. For example, in cooling, heating, and air supply modes, the controller maintains the angle of the air guide plate 14 at a2, at which point the airflow of the upper and lower independent flow channels is evenly distributed to the regenerating heat exchanger 12 and the dehumidifying heat exchanger 13.

[0125] To prevent airflow mixing between the two independent flow channels, the air guide plate 14 is designed with an arc shape, the curvature of which matches the inner wall curvature of the volute 11. The edge of the air guide plate 14 is also equipped with a sealing strip, which fits tightly against the sheet metal to ensure effective airflow isolation and improve heat exchange efficiency.

[0126] When user A activates the temperature control and dehumidification mode, the controller starts working.

[0127] During the dehumidification period, the controller first obtains the difference ΔR between the initial ambient humidity R and the set humidity Rset. Based on ΔR, the controller adjusts the angle of the air guide vane 14 towards the minimum angle a1 according to a preset formula, so that most of the airflow flows through the dehumidification heat exchanger 13. Specifically, the angle a of the air guide vane 14 satisfies the formula: a = a2 - ΔRA, where ΔR is the difference between the initial ambient humidity and the set humidity, A is the preset humidity coefficient, and a1 ≤ a ≤ a2. When ΔR exceeds the preset range (e.g., -3% to 3%), the controller also adjusts the opening of the indoor electronic expansion valve to bring ΔR back to the preset range, ensuring the accuracy of humidity control.

[0128] During the heat recovery period, the controller obtains the difference ΔT between the initial ambient temperature T0 and the real-time ambient temperature T. Based on ΔT, the controller adjusts the angle of the air guide plate 14 towards the maximum angle a3 according to a preset formula, so that most of the airflow flows through the heat exchanger 12. At this time, the angle a of the air guide plate 14 satisfies the formula: a = a2 + ΔTB, where ΔT is the difference between the initial ambient temperature and the real-time ambient temperature, B is the preset temperature coefficient, and a2 ≤ a ≤ a3. This mechanism of dynamically adjusting airflow distribution based on environmental parameters overcomes the shortcomings of existing technologies where heat exchange capacity is fixed and it is difficult to achieve precise temperature and humidity control, enabling refined management of indoor temperature and humidity.

[0129] In defrost mode, the controller rotates the air guide plate 14 to its maximum angle a3, ensuring that all airflow from the indoor fan 3 passes through the regenerating heat exchanger 12. Simultaneously, the controller continuously monitors the inner pipe temperature Tinner pipe of the regenerating heat exchanger 12 and adjusts the indoor fan speed 3 in stages based on this temperature. For example, the preset pipe temperature thresholds for the regenerating heat exchanger 12 include Ta, Tb, and Tc, where Ta < Tb < Tc. When the inner pipe temperature Tinner pipe ≤ Ta, the indoor fan 3 operates at a low speed; when Ta < Tinner pipe ≤ Tb, it operates at a medium speed; when Tb < Tinner pipe ≤ Tc, it operates at a high speed; and when Tinner pipe > Tc, it operates at an ultra-high speed. This staged adjustment ensures continuous heat delivery to the room during defrosting, avoiding the problems of interrupted indoor heating and large temperature fluctuations during defrosting in existing technologies, significantly improving user comfort.

[0130] In addition, in this embodiment of the present disclosure, the temperature-controlled dehumidifying duct air conditioner also includes a valve group and an expansion valve group. The valve group includes a regenerative switching valve 4, a dehumidifying switching valve 4, and a four-way valve. The expansion valve group includes an indoor electronic expansion valve and an outdoor expansion valve. The controller is connected to the regenerative switching valve 4, the dehumidifying switching valve 4, the four-way valve, the indoor electronic expansion valve, and the outdoor expansion valve respectively. In the temperature-controlled dehumidifying mode and the defrosting mode, the precise temperature control and stable defrosting are achieved by controlling the action of the valve group and the expansion valve group in conjunction with the angle adjustment of the air guide plate 14.

[0131] After the high-temperature and high-pressure gaseous refrigerant compressed by compressor 2 defrosts in the outdoor unit's frosting area, it flows into the regenerating heat exchanger 12 to exchange heat with the airflow. After heat exchange, the refrigerant flows into the dehumidifying heat exchanger 13 after being throttled by the indoor electronic expansion valve, and no airflow exchanges heat with the dehumidifying heat exchanger 13.

[0132] The above description is merely a specific embodiment of this disclosure, enabling those skilled in the art to understand or implement it. 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 this disclosure. Therefore, this disclosure 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 disclosed herein.

Claims

1. A temperature-controlled dehumidifying duct air conditioner, characterized in that, include: The unit housing contains a volute, a regenerative heat exchanger, and a dehumidifying heat exchanger, which are arranged vertically opposite each other. An air guiding mechanism is installed across the air outlet of the volute and is positioned opposite to the regenerating heat exchanger and the dehumidifying heat exchanger. The air guiding mechanism includes an air guide plate, which is used to isolate the air duct between the volute and the regenerating heat exchanger and the dehumidifying heat exchanger into two independent upper and lower flow channels, respectively corresponding to the regenerating heat exchanger and the dehumidifying heat exchanger. One end of the air guide plate is configured to move up and down at the air outlet of the volute to adjust the air volume distribution ratio of the two independent flow channels.

2. The temperature-controlled dehumidifying duct air conditioner according to claim 1, characterized in that, The temperature-controlled dehumidifying duct air conditioner includes a transmission component, which is installed at the air outlet of the volute. The transmission component engages with the air guide plate to provide a stable movement path for the other end of the air guide plate.

3. The temperature-controlled dehumidifying duct air conditioner according to claim 2, characterized in that, The regenerating heat exchanger and the dehumidifying heat exchanger have a preset installation position on the inner side of the junction. The air guide mechanism also includes a driving component, which is installed at the preset installation position. The other end of the air guide plate is driven to the driving component through a rotating shaft. The driving component is used to drive the air guide plate to rotate around the rotating shaft so that one end of the air guide plate moves up and down along the moving path of the transmission component.

4. The temperature-controlled dehumidifying duct air conditioner according to claim 3, characterized in that, The temperature-controlled dehumidification duct unit also includes a controller, which is signal-connected to the drive unit; The airflow distribution ratio of the two independent flow channels is adjusted by controlling the rotation angle of the air guide plate, so that the temperature drop frequency of each heat exchanger in the temperature control and dehumidification modes and the defrosting mode is slow.

5. The temperature-controlled dehumidifying duct air conditioner according to claim 4, characterized in that, The angle between the air guide plate and the regenerating heat exchanger is denoted as a. The adjustable range of the angle a includes the minimum angle a1, the intermediate angle a2, and the maximum angle a3, and a1 < a2 < a3. The dynamic control of the air volume ratio of the two independent flow channels is obtained by the continuous change of the angle a.

6. The temperature-controlled dehumidifying duct air conditioner according to claim 5, characterized in that, In cooling mode, heating mode, and air supply mode, the controller controls the included angle of the air guide plate to be maintained at a2, and the air volume of the upper and lower independent flow channels is evenly distributed to the regenerating heat exchanger and the dehumidifying heat exchanger.

7. The temperature-controlled dehumidifying duct air conditioner according to claim 1, characterized in that, The air guide plate has an arc-shaped structure, and the arc of the air guide plate is adapted to the arc of the inner wall of the volute. The edge of the air guide plate is provided with a sealing strip, which is tightly attached to the sheet metal to avoid airflow mixing between the two independent flow channels.

8. The temperature-controlled dehumidifying duct air conditioner according to claim 2, characterized in that, The transmission component is a gear, and a rack is provided on the side of the volute. The gear meshes with the rack, and when the air guide plate rotates, it drives the gear to slide along the rack.

9. The temperature-controlled dehumidifying duct air conditioner according to claim 4, characterized in that, The driving component is a stepper motor, which is connected to the rotating shaft of the air guide plate. The controller adjusts the rotation angle of the air guide plate by controlling the rotation angle of the stepper motor.

10. The temperature-controlled dehumidifying duct air conditioner according to claim 5, characterized in that, In temperature and humidity control mode, the controller detects ambient temperature and humidity parameters and controls the angle of the air guide plate according to the dehumidification period and the heat recovery period: During the dehumidification period, the angle of the air guide plate is adjusted towards the minimum angle a1 according to a preset formula, so that most of the air volume flows through the dehumidification heat exchanger. During the heat recovery period, the angle of the air guide plate is adjusted towards the maximum angle a3 according to a preset formula, so that most of the air volume flows through the heat recovery heat exchanger.

11. The temperature-controlled dehumidifying duct air conditioner according to claim 10, characterized in that, The controller is configured to: During the dehumidification period, the angle α of the air guide plate satisfies the following relationship: a = a2 - ΔRA, where ΔR is the difference between the initial ambient humidity and the set humidity, A is the preset humidity coefficient, and a1 ≤ a ≤ a2. During the heat recovery period, the angle α of the air guide plate satisfies the following relationship: a = a2 + ΔTB, where ΔT is the difference between the initial ambient temperature and the real-time ambient temperature, B is the preset temperature coefficient, and a2 ≤ a ≤ a3.

12. The temperature-controlled dehumidifying duct air conditioner according to claim 10, characterized in that, The controller is configured to: In defrosting mode, the controller controls the air guide plate to rotate to the maximum angle a3, so that all the air volume of the internal fan flows through the heat exchanger, and at the same time, the fan speed is adjusted according to the internal pipe temperature of the heat exchanger.

13. The temperature-controlled dehumidifying duct air conditioner according to claim 12, characterized in that, The preset tube temperature threshold of the regenerative heat exchanger includes Ta, Tb, and Tc, and Ta < Tb < Tc. When the temperature of the inner pipe T is less than or equal to Ta, the inner fan operates at a low speed. When Ta < T_inner tube ≤ Tb, operate at medium speed. When Tb < T_inner pipe ≤ Tc, operate at high speed; When T_inner pipe > T_c, operate at ultra-high wind speed.

14. The temperature-controlled dehumidifying duct air conditioner according to claim 5, characterized in that, It also includes a detection component, which includes an ambient temperature sensor for detecting ambient temperature, a humidity sensor for detecting ambient humidity, and an inner tube temperature sensor for detecting the inner tube temperature of the regenerating heat exchanger. The ambient temperature sensor, the humidity sensor, and the inner tube temperature sensor are all signal-connected to the controller.

15. An air conditioner, characterized in that, Including the temperature-controlled dehumidifying duct air conditioner as described in any one of claims 1-14.

16. A control method applied to the air conditioner of claim 15, characterized in that, The method includes a temperature control and dehumidification method: Activate the temperature control and dehumidification mode; Obtain the difference between the initial ambient humidity R and the set humidity Rset, ΔR = RsetRset. The angle of the air guide plate is adjusted according to ΔR towards the minimum angle a1, so that most of the airflow flows through the dehumidification heat exchanger.

17. The control method according to claim 16, characterized in that, The method includes a temperature control and dehumidification method: Activate the temperature control and dehumidification mode; Obtain the difference between the initial ambient temperature T0 and the real-time ambient temperature T, ΔT = T0 - T; The angle of the air guide plate is adjusted according to ΔT towards the maximum angle a3, so that most of the air volume flows through the regenerating heat exchanger.

18. The control method according to claim 16, characterized in that, After the step of adjusting the air guide plate angle towards the minimum angle a1 according to ΔR, ΔR is checked. If ΔR exceeds the preset range, the opening of the indoor electronic expansion valve is adjusted to bring ΔR back to the preset range.

19. A control method applied to the air conditioner of claim 15, characterized in that, The method includes a defrosting control method: Activate defrost mode; Control the air guide plate to rotate to the maximum angle a3 so that all the air volume of the internal fan flows through the heat exchanger; The temperature of the inner tube of the regenerative heat exchanger, Tinner tube, is obtained. Based on the value of Tinner tube, the speed of the inner fan is adjusted in stages to ensure that heat is continuously delivered to the room during the defrosting process.

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