Double-cold-source fresh air dehumidification system and control method

Abstract

According to the double-cold-source fresh air dehumidification system and the control method, two electric ball valves are adopted to replace a combination of a plurality of complex valves in related technologies, the system structure and the control logic are greatly simplified, and therefore the manufacturing cost and the control complexity of the system are effectively reduced, the hardware cost and the software development amount are reduced, and the system reliability is improved. The control strategy can be automatically switched according to the air inlet temperature, complex control program adjustment and shutdown restart are not needed, system faults caused by external condition changes such as cooling water supply interruption are effectively avoided, and stability and reliability are higher.

Description

Technical Field

[0001] This application relates to the technical field of air conditioners, in particular to a dual-cooling-source fresh air dehumidification system and a control method therefor. Background Art

[0002] The requirements for indoor air quality in modern buildings are increasing day by day, and thus fresh air systems are widely used. The fresh air system introduces outdoor fresh air, dilutes indoor pollutants, improves indoor air quality, and creates a healthier and more comfortable living environment for people. However, simply introducing untreated outdoor air often cannot directly meet people's comfort requirements. Especially in humid or dry seasons, directly introducing outdoor air without temperature and humidity adjustment will cause large fluctuations in indoor temperature and humidity, affecting human comfort and even potentially causing health problems.

[0003] To solve the above problems, dual-cooling-source fresh air dehumidification systems have emerged. Such systems usually use two cooling sources, namely cooling water and refrigerant (such as Freon), and pre-cool and reheat fresh air through a plate heat exchanger and a coil heat exchanger respectively, so as to achieve precise adjustment of the temperature and humidity of fresh air. Specifically, the cooling water is responsible for pre-cooling fresh air, reducing its temperature and humidity, thereby reducing the dehumidification burden on the refrigeration system; the refrigerant is used for deep dehumidification and reheats the air when necessary to ensure that the air sent into the room reaches the optimal temperature and humidity range.

[0004] However, in order to cope with complex operating conditions and achieve flexible switching between multiple modes, some existing dual-cooling-source fresh air dehumidification systems often need to use a large number of control valves, such as solenoid valves, expansion valves, etc. Complex control logic is required to coordinate between these valves, which not only increases the control difficulty and implementation cost of the system, but also makes it difficult to ensure the stability and reliability of the system under various working conditions. Summary of the Invention

[0005] To solve the above problems, this application provides a dual-cooling-source fresh air dehumidification system and a control method therefor that simplify the system structure and control logic.

[0006] To achieve the above object, in a first aspect, an embodiment of this application provides a dual-cooling-source fresh air dehumidification system, including a compressor, a plate heat exchanger, an air duct, and a water supply pipe for connecting to an external cooling water source. A coil heat exchanger, an evaporator, a condenser, and a fan are sequentially arranged in the air duct; the water inlet ends of the plate heat exchanger and the coil heat exchanger are both connected to the external cooling water source through the water supply pipe; one output end of the compressor is connected to the plate heat exchanger, and the other output end is connected to the condenser; the output ends of the condenser and the plate heat exchanger are both connected to the input end of the evaporator, and the output end of the evaporator is connected to the input end of the compressor. The system further includes:

[0007] The first electric ball valve is arranged between the output end of the compressor and the condenser, and is used to control the refrigerant flow rate flowing into the condenser;

[0008] The second electric ball valve is arranged between the output end of the compressor and the plate heat exchanger, and is used to control the refrigerant flow rate flowing into the plate heat exchanger;

[0009] The controller is electrically connected to the first electric ball valve and the second electric ball valve, and is used to control the opening degree and / or the opening and closing state of the first electric ball valve and the second electric ball valve according to the incoming air temperature of the air duct.

[0010] Preferably, the controller is specifically used for:

[0011] When the incoming air temperature is less than the first set temperature, control the first electric ball valve to open and close the second electric ball valve;

[0012] When the incoming air temperature is greater than the second set temperature, control the first electric ball valve to close and open the second electric ball valve;

[0013] When the incoming air temperature is between the first set temperature and the second set temperature, control both the first electric ball valve and the second electric ball valve to open, and adjust the opening degrees of the first electric ball valve and the second electric ball valve according to the outgoing air temperature of the air duct, wherein the sum of the opening degrees of the first electric ball valve and the second electric ball valve is 100%.

[0014] Preferably, it further includes a liquid storage tank and an electronic expansion valve. The output ends of the condenser and the plate heat exchanger are both connected to the input end of the liquid storage tank, and the output end of the liquid storage tank is connected to the input end of the evaporator through the electronic expansion valve.

[0015] Preferably, a first one-way valve is arranged on the pipeline between the output end of the plate heat exchanger and the input end of the liquid storage tank, and a second one-way valve is arranged on the pipeline between the output end of the condenser and the input end of the liquid storage tank.

[0016] Preferably, temperature sensors are arranged on both the incoming air side and the outgoing air side of the air duct, and the temperature sensors are electrically connected to the controller.

[0017] Preferably, proportional regulating valves are arranged on the water outlet pipes of the coil heat exchanger and the plate heat exchanger.

[0018] In a second aspect, an embodiment of the present application provides a dual-cooling-source fresh air dehumidification control method, which is applied to the dual-cooling-source fresh air dehumidification system according to any one of the embodiments in the first aspect. The method includes:

[0019] S1. Detect the incoming air temperature of the air duct;

[0020] S2. In response to the inlet air temperature, adjust the opening degree and / or the opening and closing state of the first electric ball valve and the second electric ball valve through a controller to control the refrigerant flow rate through the plate heat exchanger and the condenser.

[0021] Preferably, in step S2,

[0022] When the inlet air temperature is less than the first set temperature, control the first electric ball valve to open and close the second electric ball valve, so that all the refrigerant flows through the condenser for heating and dehumidification;

[0023] When the inlet air temperature is greater than the second set temperature, control the first electric ball valve to close and open the second electric ball valve, so that all the refrigerant flows through the plate heat exchanger for cooling and dehumidification;

[0024] When the inlet air temperature is between the first set temperature and the second set temperature, control both the first electric ball valve and the second electric ball valve to open, and adjust the opening degrees of the first electric ball valve and the second electric ball valve according to the outlet air temperature of the air duct, wherein the sum of the opening degrees of the first electric ball valve and the second electric ball valve is 100%.

[0025] Preferably, the first set temperature is 18 degrees and the second set temperature is 35 degrees.

[0026] The dual-cooling-source fresh air dehumidification system and control method designed in this application replace the combination of multiple complex valves in the related technology with two electric ball valves, greatly simplifying the system structure and control logic, thereby effectively reducing the manufacturing cost and control complexity of the system, reducing the hardware cost and software development volume, and realizing the automatic switching of the control strategy according to the inlet air temperature, without complex control program adjustment and shutdown and restart, effectively avoiding system failures caused by changes in external conditions such as interruption of cooling water supply, and having higher stability and reliability. Description of the Drawings

[0027] Figure 1 is the structural schematic diagram of the dual-cooling-source fresh air dehumidification system provided by the embodiment of this application.

[0028] Figure 2 is the flowchart of the dual-cooling-source fresh air dehumidification control method provided by the embodiment of this application.

[0029] Wherein: compressor 10, plate heat exchanger 20, air duct 30, coil heat exchanger 31, evaporator 32, condenser 33, fan 34, water supply pipe 40, first electric ball valve 50, second electric ball valve 60, liquid storage tank 70, electronic expansion valve 71, first check valve 80, second check valve 81, temperature sensor 90, proportional regulating valve 100. Detailed Embodiments

[0030] The preferred embodiments of the present application will be described below in conjunction with the accompanying drawings. It should be understood that the preferred embodiments described herein are only for the purpose of illustrating and explaining the present application, and are not used to limit the present application.

[0031] In a first aspect, an embodiment of the present application provides a dual-cooling-source fresh air dehumidification system, which mainly consists of components such as a compressor 10, a plate heat exchanger 20, an air duct 30, and a water supply pipe 40. Inside the air duct 30, a coil heat exchanger 31, an evaporator 32, a condenser 33, and a fan 34 are sequentially arranged in the air flow direction. The water inlet ends of the plate heat exchanger 20 and the coil heat exchanger 31 are both connected to an external cooling water source through the water supply pipe 40, so as to pre-cool the refrigerant or fresh air with the cooling water. The output end of the compressor 10 is divided into two paths. One path is connected to the refrigerant inlet of the plate heat exchanger 20 through a refrigerant pipeline, and the other path is connected to the refrigerant inlet of the condenser 33 through a refrigerant pipeline. The refrigerant after heat exchange in the plate heat exchanger 20 and the condenser 33 all converges at the input end of the evaporator 32. Subsequently, the refrigerant after heat exchange in the evaporator 32 returns to the input end of the compressor 10, forming a complete refrigerant circulation loop.

[0032] The key improvement of this embodiment lies in that by respectively arranging a first electric ball valve 50 and a second electric ball valve 60 on the refrigerant pipeline, precise control of the refrigerant flow rate flowing through the condenser 33 and the plate heat exchanger 20 is achieved. Specifically, the first electric ball valve 50 is arranged between the output end of the compressor 10 and the condenser 33 to control the refrigerant flow rate flowing to the condenser 33; the second electric ball valve 60 is arranged between the output end of the compressor 10 and the plate heat exchanger 20 to control the refrigerant flow rate flowing to the plate heat exchanger 20. Both the first electric ball valve 50 and the second electric ball valve 60 can adopt two-way electric ball valves. By respectively arranging the first electric ball valve 50 and the second electric ball valve 60 on the corresponding pipelines, control of the refrigerant flow rate to the condenser 33 and the plate heat exchanger 20 is achieved. The overall control components are few, and anhydrous dehumidification can be realized, that is, the operation of only water-cooled refrigerant, only fluorine refrigerant, and water-fluorine refrigerant integration can be realized. In this way, flexible regulation of the refrigerant flow rate is achieved only by using two electric ball valves, greatly simplifying the system structure and control logic, reducing the manufacturing cost, and improving the reliability of the system.

[0033] In addition, the dual-cooling-source fresh air dehumidification system of this embodiment can flexibly switch between multiple operating modes by adjusting the opening degrees of the first electric ball valve 50 and the second electric ball valve 60 to adapt to different working conditions:

[0034] Dry mode: When the water supply pipe 40 fails to supply cooling water, the system can still operate normally. In this case, the pipelines related to the coil heat exchanger 31 are not used, and the system only uses fluorine as the refrigerant. By reasonably adjusting the opening degrees of the first electric ball valve 50 and the second electric ball valve 60, the heat dissipation capacity of the condenser 33 can be adjusted, thus ensuring the normal operation of the compressor 10 and the basic dehumidification effect.

[0035] Only water-cooled refrigerant mode: When there is only cooling water supply and it is not necessary to start the compressor for refrigeration, the compressor 10 can be stopped, and neither the evaporator 32 nor the condenser 33 is used. After the cooling water flows in from the water supply pipe 40, it successively flows through the coil heat exchanger 31 to cool and lower the temperature of the fresh air, and then flows out from the drain pipe of the coil heat exchanger 31. This mode is applicable to occasions where the requirement for air temperature is not high but a certain degree of cooling and dehumidification is needed.

[0036] Water-fluorine refrigerant mode: When there is cooling water supply and strong dehumidification is required, both the first electric ball valve 50 and the second electric ball valve 60 are opened. The cooling water flows through the coil heat exchanger 31 to pre-cool the fresh air. At the same time, the refrigerant flows through the plate heat exchanger 20 and the condenser 33 respectively to deeply dehumidify and regulate the temperature of the fresh air. This mode can make full use of the advantages of cooling water and refrigerant to achieve efficient temperature and humidity control.

[0037] In addition, both the first electric ball valve 50 and the second electric ball valve 60 are electrically connected to the controller (not shown in the figure) provided in this embodiment, and are used to control the opening degree and / or opening and closing state of the first electric ball valve 50 and the second electric ball valve 60 according to the inlet air temperature of the air duct 30. Specifically, temperature sensors 90 are provided on both the inlet side and the outlet side of the air duct 30, and the temperature sensors 90 are electrically connected to the controller. The controller then automatically adjusts the opening and closing and the opening degree of the first electric ball valve 50 and the second electric ball valve 60 according to these data in combination with the preset control strategy, so as to achieve precise control of the refrigerant flow rate.

[0038] In this embodiment, the controller is specifically used for:

[0039] When the inlet air temperature is lower than the first set temperature (for example, 18 degrees Celsius), control the first electric ball valve 50 to open and close the second electric ball valve 60; at this time, all the refrigerant output by the compressor 10 flows to the condenser 33 to heat the air that has been cooled and dehumidified by the evaporator 32, so as to increase the supply air temperature, prevent the indoor temperature from being too low, and ensure human comfort.

[0040] When the inlet air temperature is greater than the second set temperature (e.g., 35 degrees Celsius), control the first electric ball valve 50 to close and open the second electric ball valve 60; at this time, all the refrigerant output by the compressor 10 flows to the condenser 33 to heat the air that has been cooled and dehumidified by the evaporator 32, so as to increase the supply air temperature. The second set temperature is set to be greater than the first set temperature.

[0041] When the inlet air temperature is between the first set temperature and the second set temperature, control both the first electric ball valve 50 and the second electric ball valve 60 to open, and adjust the opening degrees of the first electric ball valve 50 and the second electric ball valve 60 according to the outlet air temperature of the air duct 30 to achieve precise temperature and humidity control. Specifically, the user can set the target outlet air temperature according to their own needs. When the actual outlet air temperature is higher than the target outlet air temperature, the controller will reduce the opening degree of the first electric ball valve 50 and increase the opening degree of the second electric ball valve 60, thereby reducing the refrigerant flow rate through the condenser 33, reducing the heating amount, and lowering the supply air temperature; conversely, when the actual outlet air temperature is lower than the target outlet air temperature, the controller will increase the opening degree of the first electric ball valve 50 and reduce the opening degree of the second electric ball valve 60, thereby increasing the refrigerant flow rate through the condenser 33, increasing the heating amount, and raising the supply air temperature. In this process, the sum of the opening degrees of the first electric ball valve 50 and the second electric ball valve 60 always remains 100%.

[0042] In this way, by using two two-way electric ball valves instead of the combination of multiple complex valves in the related art, the system structure and control logic are greatly simplified, thereby effectively reducing the manufacturing cost and control complexity of the system, and reducing the hardware cost and software development volume. At the same time, the dual cold source fresh air dehumidification system of this embodiment can automatically switch the control strategy according to the inlet air temperature, without complex control program adjustment and shutdown restart, effectively avoiding system failures caused by changes in external conditions such as interruption of cooling water supply, and having higher stability and reliability, bringing a more comfortable and energy-saving indoor environment experience to users.

[0043] In some embodiments, such as Figure 1As shown in the figure, it further includes a liquid storage tank 70 and an electronic expansion valve 71. The output ends of the condenser 33 and the plate heat exchanger 20 are both connected to the input end of the liquid storage tank 70, and the output end of the liquid storage tank 70 is connected to the input end of the evaporator 32 through the electronic expansion valve 71. By setting the liquid storage tank 70, on the one hand, the refrigerant from different pipelines can be fully mixed, so that the temperature of the refrigerant entering the electronic expansion valve 71 tends to be stable, thereby improving the control accuracy and service life of the electronic expansion valve 71 and ensuring the reliability of the system operation; on the other hand, under certain working conditions (for example, when only using cooling water for refrigeration), it may be necessary to close the refrigerant pipeline flowing through the plate heat exchanger 20 and make the refrigerant all flow to the condenser 33. At this time, if the refrigerant cannot be drained smoothly, liquid accumulation may occur in the refrigerant pipeline behind the plate heat exchanger 20, especially inside the reheating coil. Therefore, by setting the liquid storage tank 70, the refrigerant remaining in the refrigerant pipeline behind the plate heat exchanger 20 can be stored, thus effectively avoiding the liquid accumulation phenomenon of the reheating coil and ensuring the stable operation of the system.

[0044] In some embodiments, as Figure 1 shown, a first one-way valve 80 is provided on the pipeline between the output end of the plate heat exchanger 20 and the input end of the liquid storage tank 70, and a second one-way valve 81 is provided on the pipeline between the output end of the condenser 33 and the input end of the liquid storage tank 70. By setting the first one-way valve 80 and the second one-way valve 81, it is avoided that the refrigerant outlet pressure of the plate heat exchanger 20 and the condenser 33 fluctuates due to the change of the operating conditions, which may cause the refrigerant to flow backward, ensuring that the refrigerant always flows in the predetermined direction and guaranteeing the stability and reliability of the system operation.

[0045] In some embodiments, as Figure 1 shown, proportional regulating valves 100 are provided on the outlet pipes of the coil heat exchanger 31 and the plate heat exchanger 20. By setting the proportional regulating valves 100, the precise control of the cooling water flow rate is realized, so as to more flexibly adjust the precooling effect of the fresh air and the temperature of the refrigerant, and finally improve the temperature and humidity control accuracy and energy saving of the system, bringing a more comfortable and energy-saving indoor environment experience to users.

[0046] In the second aspect, the embodiments of the present application provide a dual-cooling-source fresh air dehumidification control method, which is applied to the dual-cooling-source fresh air dehumidification system of any one of the embodiments in the first aspect, as Figure 2 shown, the method includes:

[0047] S1. Detect the inlet air temperature of the air duct 30;

[0048] S2. In response to the inlet air temperature, adjust the opening degree and / or opening and closing state of the first electric ball valve 50 and the second electric ball valve 60 through the controller to control the refrigerant flow rate flowing through the plate heat exchanger 20 and the condenser 33.

[0049] In step S2, the specific control process is as follows:

[0050] S21. When the incoming air temperature is lower than the first set temperature, control the first electric ball valve 50 to open and close the second electric ball valve 60, so that all the refrigerant flows through the condenser 33 for heating and dehumidification; at this time, all the refrigerant output by the compressor 10 flows to the condenser 33 to heat the air that has been cooled and dehumidified by the evaporator 32, so as to increase the supply air temperature and prevent the indoor temperature from being too low.

[0051] S22. When the incoming air temperature is higher than the second set temperature, control the first electric ball valve 50 to close and open the second electric ball valve 60, so that all the refrigerant flows through the plate heat exchanger 20 for cooling and dehumidification; at this time, all the refrigerant output by the compressor 10 flows to the plate heat exchanger 20 to exchange heat with the cooling water to reduce the refrigerant temperature, thereby improving the dehumidification capacity of the evaporator 32 and reducing the supply air temperature. The second set temperature is set to be higher than the first set temperature. Specifically, the first set temperature can be set to 18 degrees, and the second set temperature can be set to 35 degrees.

[0052] S23. When the incoming air temperature is between the first set temperature and the second set temperature, control both the first electric ball valve 50 and the second electric ball valve 60 to open, and adjust the opening degrees of the first electric ball valve 50 and the second electric ball valve 60 according to the outlet air temperature of the air duct 30. Among them, the sum of the opening degrees of the first electric ball valve 50 and the second electric ball valve 60 is 100%.

[0053] Exemplarily, in spring and autumn, the detected incoming air temperature is 25 degrees Celsius, which is between the first set temperature of 18 degrees Celsius and the second set temperature of 35 degrees Celsius. At this time, the controller will control both the first electric ball valve 50 and the second electric ball valve 60 to open. The specific opening ratio will be determined according to the outlet air temperature collected by the temperature sensor 90 at the outlet of the air duct 30.

[0054] Suppose the target air outlet temperature set by the user is 22 °C, while the actual air outlet temperature is 24 °C. At this time, the controller will reduce the opening degree of the first electric ball valve 50, for example, from 50% to 40%, and at the same time increase the opening degree of the second electric ball valve 60, for example, from 50% to 60%. In this way, the refrigerant flow rate through the condenser 33 decreases, the heating amount decreases, the refrigerant flow rate through the plate heat exchanger 20 increases, the cooling amount increases, and finally the air supply temperature decreases and gradually approaches the target air outlet temperature of 22 °C. On the contrary, suppose the target air outlet temperature set by the user is 22 °C, while the actual air outlet temperature is 20 °C. At this time, the controller will increase the opening degree of the first electric ball valve 50 and decrease the opening degree of the second electric ball valve 60, so as to increase the air supply temperature and gradually approach the target air outlet temperature of 22 °C. For example, in the period of returning damp or plum rain season when the air outlet temperature is relatively low, the opening degree of the first electric ball valve can be set to 90%, and the opening degree of the second electric ball valve can be set to 10%.

[0055] Through the above control process, this embodiment can dynamically adjust the opening degrees of the first electric ball valve 50 and the second electric ball valve 60 according to the inlet air temperature of the air duct 30, realize the precise control of the refrigerant flow rate through the plate heat exchanger 20 and the condenser 33, and thus ensure the stability and comfort of the air outlet temperature.

[0056] The dual-cooling-source fresh air dehumidification system and control method provided by this embodiment greatly simplify the system structure and control logic by using two electric ball valves to replace the combination of multiple complex valves in the related technology, thereby effectively reducing the manufacturing cost and control complexity of the system, reducing the hardware cost and software development volume, and realizing the automatic switching of the control strategy according to the inlet air temperature without complex control program adjustment and shutdown restart, effectively avoiding system failures caused by changes in external conditions such as interruption of cooling water supply, and having higher stability and reliability.

[0057] In the description of this application, it should be noted that the orientation or positional relationship indicated by the terms "vertical", "upper", "lower", "horizontal", etc. is based on the orientation or positional relationship shown in the drawings. It is only for the convenience of describing this application and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be construed as a limitation to this application.

[0058] In the description of the present application, it should also be noted that, unless otherwise clearly specified and defined, the terms "arranged", "installed", "connected", and "coupled" should be understood in a broad sense. For example, it may be a fixed connection, a detachable connection, or an integral connection; it may be a mechanical connection or an electrical connection; it may be directly connected or indirectly connected through an intermediate medium, and it may be the communication inside two components. For those of ordinary skill in the art, the specific meanings of the above terms in the present application can be understood according to specific circumstances.

[0059] Finally, it should be noted that the above are only the preferred embodiments of the present application and are not used to limit the present application. Although the present application has been described in detail with reference to the foregoing embodiments, those skilled in the art can still modify the technical solutions described in the foregoing embodiments or perform equivalent replacements for some of the technical features. Any modifications, equivalent replacements, improvements, etc. made within the spirit and principle of the present application shall be included in the protection scope of the present application.

Claims

1. A dual-cooling-source fresh air dehumidification system, comprising a compressor, a plate heat exchanger, an air duct, and a water supply pipe for connecting to an external cooling water source. A coil heat exchanger, an evaporator, a condenser, and a fan are sequentially arranged in the air duct. The water inlet ends of the plate heat exchanger and the coil heat exchanger are both connected to the external cooling water source through the water supply pipe. One output end of the compressor is connected to the plate heat exchanger, and the other output end is connected to the condenser. The output ends of the condenser and the plate heat exchanger are both connected to the input end of the evaporator, and the output end of the evaporator is connected to the input end of the compressor, characterized in that, It further includes: A first electric ball valve, which is arranged between the output end of the compressor and the condenser, and is used to control the refrigerant flow rate flowing to the condenser; A second electric ball valve, which is arranged between the output end of the compressor and the plate heat exchanger, and is used to control the refrigerant flow rate flowing to the plate heat exchanger; A controller, which is electrically connected to the first electric ball valve and the second electric ball valve, and is used to control the opening degree and / or opening and closing state of the first electric ball valve and the second electric ball valve according to the inlet air temperature of the air duct.

2. The dual cold source fresh air dehumidification system according to claim 1, wherein, Specifically, the controller is used for: When the inlet air temperature is lower than the first set temperature, controlling the first electric ball valve to open and closing the second electric ball valve; When the inlet air temperature is higher than the second set temperature, controlling the first electric ball valve to close and opening the second electric ball valve; When the inlet air temperature is between the first set temperature and the second set temperature, controlling both the first electric ball valve and the second electric ball valve to open, and regulating the opening degrees of the first electric ball valve and the second electric ball valve according to the outlet air temperature of the air duct, wherein the sum of the opening degrees of the first electric ball valve and the second electric ball valve is 100%.

3. The dual cold source fresh air dehumidification system according to claim 1, characterized in that, It further includes a liquid storage tank and an electronic expansion valve. The output ends of the condenser and the plate heat exchanger are both connected to the input end of the liquid storage tank, and the output end of the liquid storage tank is connected to the input end of the evaporator through the electronic expansion valve.

4. The dual cold source fresh air dehumidification system according to claim 3, characterized in that, A first one-way valve is arranged on the pipeline between the output end of the plate heat exchanger and the input end of the liquid storage tank, and a second one-way valve is arranged on the pipeline between the output end of the condenser and the input end of the liquid storage tank.

5. The dual cold source fresh air dehumidification system according to claim 1, characterized in that, Temperature sensors are arranged on both the inlet side and the outlet side of the air duct, and the temperature sensors are electrically connected to the controller.

6. The dual-cooling-source fresh air dehumidification system according to claim 1, wherein Proportional regulating valves are arranged on the water outlet pipes of the coil heat exchanger and the plate heat exchanger.

7. A fresh air dehumidification control method with dual cold sources, characterized in that, Applied to the dual-cooling-source fresh air dehumidification system according to claims 1-6, the method includes: S1. Detect the inlet air temperature of the air duct; S2. In response to the inlet air temperature, adjust the opening degree and / or opening and closing state of the first electric ball valve and the second electric ball valve through the controller to control the refrigerant flow rate flowing through the plate heat exchanger and the condenser.

8. The dual cold source fresh air dehumidification control method according to claim 7, wherein In step S2, when the inlet air temperature is lower than the first set temperature, control the first electric ball valve to open and close the second electric ball valve, so that all the refrigerant flows through the condenser for heating and dehumidification; When the inlet air temperature is higher than the second set temperature, control the first electric ball valve to close and open the second electric ball valve, so that all the refrigerant flows through the plate heat exchanger for cooling and dehumidification; When the inlet air temperature is between the first set temperature and the second set temperature, control both the first electric ball valve and the second electric ball valve to open, and regulate the opening degrees of the first electric ball valve and the second electric ball valve according to the outlet air temperature of the air duct, wherein the sum of the opening degrees of the first electric ball valve and the second electric ball valve is 100%.

9. The dual-cooling-source fresh air dehumidification control method according to claim 8, characterized in that The first set temperature is 18 degrees, and the second set temperature is 35 degrees.

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