An indoor air heat exchange and dehumidification system

Abstract

This invention provides an indoor air heat exchange and dehumidification system, comprising a heat pump subsystem, a dehumidification subsystem, and an evaporative cooler connected in sequence. The dehumidification subsystem includes at least two sets of desiccant-coated heat exchange units arranged in parallel. The indoor space is connected to the input end of each desiccant-coated heat exchange unit, and the output end of the evaporative cooler is connected to the indoor air to form a dehumidification and cooling circulation channel. The heat pump subsystem includes a heating and regeneration unit that provides high-temperature air for desiccant regeneration, and a heat absorption and dehumidification unit that provides cooling water required for dehumidification. The heating and regeneration unit and the heat absorption and dehumidification unit are respectively connected to the desiccant-coated heat exchange units through corresponding on / off valves, so that the desiccant-coated heat exchange units are in either regeneration mode or dehumidification mode. The desiccant-coated heat exchange unit in dehumidification mode is connected to the indoor space through the dehumidification and cooling circulation channel. This invention has the advantages of ensuring indoor air dehumidification and cooling effect and efficiency while saving energy.

Description

TECHNICAL FIELD

[0001] The present application relates to the field of indoor air conditioning, and in particular to an indoor air heat exchange and dehumidification system. BACKGROUND

[0002] The increasingly deteriorating climate conditions, especially the frequent occurrence of temperature peaks, have led to a surge in demand for cooling equipment such as air conditioners, and the growth in demand has put tremendous pressure on energy supply. At the same time, global warming and ozone depletion have become a global disaster, leading to climate change and abnormal weather patterns. Greenhouse gas (GHG) emissions are the main factor leading to this crisis, and chlorofluorocarbons (CFCs) refrigerants used in traditional vapor compression cycle air conditioning systems are an important source of greenhouse gases. Compared to traditional vapor compression refrigeration systems, since the dew point evaporation cooling (DPEC) does not use refrigerants, it avoids damage to the environment, it uses the latent heat of water evaporation for cooling, it significantly reduces power consumption, and it can produce fresh air with a temperature close to the dew point or lower than the wet-bulb temperature, without adding additional moisture, providing efficient thermal comfort. The demand for thermal comfort and the reduction of refrigeration energy consumption (energy saving and emission reduction) have become problems to be solved for cooling equipment.

[0003] To solve the above problems, the existing way is to use a single heat pump driven DCHE system (compact heat pump DCHE system), the dehumidification capacity of the system can reach 10 g / kg dry air under high humidity conditions, and the COP is between 2.9~5.7, which is higher than that of ordinary vapor compression heat pump systems. But the existing DCHE system has low regeneration temperature, the heat pump driven DCHE system can usually achieve the regeneration temperature by using solar heat energy, at the same time the cooling water provided by the cooling tower is used as the cooling source of the DCHE system, but the temperature of the cooling water is limited by the ambient wet-bulb temperature, thereby limiting the dehumidification. For DCHE, dehumidification can be achieved when the temperature difference between heating and cooling exceeds 30℃, which is lower than the conventional adsorption dehumidification temperature difference requirement due to the advantage of internal cooling. But due to the limitation of condensation temperature, the compact heat pump DCHE system cannot achieve higher regeneration temperature, and the solar heat energy driven DCHE system cannot obtain lower dehumidification temperature due to the cooling tower. The temperature of the cooling water is limited by the ambient wet-bulb temperature, thereby limiting the dehumidification. It can be seen that the dehumidification and regeneration performance of the existing system is poor, resulting in poor dehumidification and cooling effect of indoor air. SUMMARY

[0004] The technical problem to be solved by the present application is to overcome the shortcomings of the prior art and provide an indoor air heat exchange and dehumidification system that ensures the dehumidification and cooling effect and efficiency of indoor air while saving energy.

[0005] To solve the above technical problems, the technical solution provided by the present application is:

[0006] The indoor air heat exchange dehumidification system for cooling indoor space comprises a heat pump subsystem, a dehumidification subsystem and an evaporative cooler connected in sequence, wherein the dehumidification subsystem comprises at least two groups of dry coating heat exchange units arranged in parallel, the indoor space is connected with the input end of each dry coating heat exchange unit, and the output end of the evaporative cooler is connected with the indoor air to form a dehumidification cooling circulation channel; the heat pump subsystem comprises a heating regeneration unit for providing dry regeneration high-temperature air and a heat absorption dehumidification unit for providing dry dehumidification required cooling water, and the heating regeneration unit and the heat absorption dehumidification unit are connected with the dry coating heat exchange unit through corresponding on-off valves respectively, so that the dry coating heat exchange unit is in a regeneration mode or a dehumidification mode; the dry coating heat exchange unit in the dehumidification mode is communicated with the indoor space through the dehumidification cooling circulation channel.

[0007] As a further improvement of the above technical solution:

[0008] The heating regeneration unit comprises a condensation heat basic heating module and a solar supplementary heating module connected in sequence, the condensation heat basic heating module comprises a condenser communicated with the first outdoor air and a heat exchanger connected between the condenser and the dry coating heat exchange unit, and the solar supplementary heating module is connected with the dry coating heat exchange unit through the heat exchanger.

[0009] The solar supplementary heating module comprises a solar heat collector, a water circulation channel and a first water pump, the solar heat collector and the first water pump are arranged in the water circulation channel, the heat exchanger is connected with the water circulation channel in series to form a supplementary heating circulation channel, and a first water valve is arranged at the connection position of the supplementary heating circulation channel and the water circulation channel.

[0010] The solar supplementary heating module further comprises a first controller, a temperature detection member for detecting the high-temperature air temperature of the input dry coating heat exchange unit and a heater for further increasing the air temperature, the temperature detection member is arranged between the heat exchanger and the dry coating heat exchange unit, and the heater is arranged in the supplementary heating circulation channel.

[0011] When the temperature detected by the temperature meter is lower than the optimal dry regeneration temperature, the heater is started by the first controller; when the temperature detected by the temperature meter is equal to or higher than the optimal dry regeneration temperature, the heater is turned off by the first controller.

[0012] The heat absorption dehumidification unit comprises a heat pump evaporator, which is connected in series with the condenser and in series with the desiccant coating heat exchange unit arranged in parallel; a compressor for compressing low-temperature and low-pressure refrigerant into high-temperature and high-pressure gas is arranged between the output end of the heat pump evaporator and the input end of the condenser, and an expansion valve for reducing high-pressure liquid to low-pressure liquid is arranged between the output end of the condenser and the input end of the heat pump evaporator to form a heat cycle system.

[0013] The evaporative cooler is a counterflow dew point evaporative cooler, which comprises a dry channel for cooling incoming air supply into a room, a wet channel for discharging exhaust air of the incoming air supply to the outside, and a temperature and humidity spraying assembly for driving sensible heat and latent heat in the air, wherein the dry channel and the wet channel are arranged side by side and communicate with each other; the temperature and humidity spraying assembly comprises a plurality of spraying heads arranged in the wet channel and arranged along the length direction of the wet channel, and the spraying direction of the spraying heads is arranged at an angle with the flow direction of the air in the wet channel.

[0014] Further comprising a second controller, a thermometer and a hygrometer arranged downstream of the dry channel, and a variable frequency fan arranged upstream of the dry channel, and the temperature and humidity spraying assembly further comprises an adjusting valve for adjusting the water amount of the spraying heads; the input end of the controller is connected with the thermometer and the hygrometer, and the output end of the controller is connected with the adjusting valve and the variable frequency fan;

[0015] The thermometer and the hygrometer detect the temperature and humidity of the cooling air in real time, the controller receives the detection values of the thermometer and the hygrometer, and compares the detection values of the thermometer and the hygrometer with preset temperature detection values and preset humidity detection values respectively; when the detection value of the thermometer is higher than or equal to the preset air temperature, the opening of the adjusting valve is increased and / or the rotating speed of the variable frequency fan is reduced, otherwise, the opening of the adjusting valve is reduced and / or the rotating speed of the variable frequency fan is reduced; when the detection value of the hygrometer is higher than or equal to the preset humidity, the rotating speed of the variable frequency fan is reduced, otherwise, the rotating speed of the variable frequency fan is increased.

[0016] An air direct channel for communicating with the second outdoor air is arranged between the desiccant coating heat exchange unit and the evaporative cooler, and the air direct channel is provided with a first on-off valve; the dehumidification and cooling circulation channel is provided with a second on-off valve corresponding to each desiccant coating heat exchange unit;

[0017] When the humidity of the indoor air is less than the preset humidity, the first on-off valve is opened, and the second on-off valve is closed; when the humidity of the indoor air is greater than the preset humidity, the first on-off valve is closed, and the second on-off valve of the desiccant coating heat exchange unit in the dehumidification mode is opened.

[0018] A cooling water circulation path is provided between the heat pump evaporator and the desiccant coating heat exchange unit. The desiccant coating heat exchange unit is connected in parallel to the cooling water circulation path. A second water valve is provided at the connection between the desiccant coating heat exchange unit and the cooling water circulation path.

[0019] The heating and regeneration unit is connected to the input end of each of the desiccant coating heat exchange units arranged in parallel through an input regeneration air duct. Each input end of the desiccant coating heat exchange unit is equipped with a third on / off valve. The output end of each desiccant coating heat exchange unit is connected to the evaporative cooler through an output regeneration air duct.

[0020] The dehumidifying coating of the desiccant-coated heat exchange unit is composed of a carbon-based composite desiccant and a curing agent. The carbon-based composite desiccant is composed of silica gel and impregnated activated carbon, and the curing agent is epoxy polyester powder.

[0021] Compared with the prior art, the advantages of the present invention are as follows:

[0022] The present invention includes a heat pump subsystem, a dehumidification subsystem, and an evaporative cooler connected in sequence. The dehumidification subsystem includes a desiccant-coated heat exchange unit. The indoor space is connected to the input end of each desiccant-coated heat exchange unit, and the output end of the evaporative cooler is connected to the indoor air to form a dehumidification and cooling circulation channel. When the indoor air humidity is high, the air can enter the desiccant-coated heat exchange unit and the evaporative cooler in sequence through the dehumidification and cooling circulation channel for dehumidification and cooling. The invention has a simple and compact structure and occupies little space.

[0023] The desiccant coating heat exchange unit of the present invention is configured as at least two sets, arranged in parallel; the heat pump subsystem includes a heating and regeneration unit and a heat absorption and dehumidification unit, which are respectively connected to the desiccant coating heat exchange unit through corresponding on / off valves. This allows the desiccant coating heat exchange unit to be in regeneration mode by connecting to the heating and regeneration unit, in which the heating and regeneration unit provides the desiccant regeneration high-temperature air to the desiccant coating heat exchange unit; the desiccant coating heat exchange unit can also be in dehumidification mode by connecting to the heat absorption and dehumidification unit, which provides the desiccant coating heat exchange unit with cooling water required for dehumidification, so as to adsorb the adsorption heat generated by desiccant dehumidification, thereby enabling the desiccant coating heat exchange unit to be used efficiently in a cyclical manner. Meanwhile, the desiccant coating heat exchange unit in dehumidification mode can be connected to the indoor space through the dehumidification and cooling circulation channel to dehumidify and cool the high humidity indoor air. The desiccant coating heat exchange unit is set with at least two sets, so that when the indoor air is high in humidity, multiple sets of desiccant coating heat exchange units can be used to dehumidify alternately, thereby achieving efficient and rapid dehumidification of indoor space under different working conditions and different humidity levels. In addition, when the humidity is low, the dehumidification mode of turning on or off a single desiccant coating heat exchange unit can be flexibly adjusted to save energy while ensuring dehumidification effect and efficiency. Attached Figure Description

[0024] The invention will now be described in more detail with reference to embodiments and the accompanying drawings.

[0025] Figure 1 This is a schematic diagram of the indoor air heat exchange and dehumidification system of the present invention;

[0026] Figure 2 This is a schematic diagram of the working principle of the indoor air heat exchange and dehumidification system of the present invention;

[0027] Figure 3 This is a schematic diagram of the heating and regeneration unit of the present invention;

[0028] Figure 4 This is a schematic diagram of the evaporative cooler of the present invention;

[0029] Figure 5 This is a schematic diagram of the evaporative cooler of the present invention;

[0030] Figure 6 This is a schematic diagram of the structure of the present invention, which includes three sets of desiccant coating heat exchange units;

[0031] Figure 7 This is the enthalpy-humidity diagram of the evaporative cooler of this invention.

[0032] The labels in the diagram represent:

[0033] 1. Heat pump subsystem; 11. Heating and regeneration unit; 111. Condensing heat base heating module; 1111. Condenser; 1112. Heat exchanger of heat pump subsystem; 112. Solar supplementary heating module; 1121. Solar collector; 1122. Water circulation channel; 1123. First water pump; 1124. Supplementary heating circulation channel; 1125. Temperature detection device; 1126. Heater; 1127. First water valve; 113. Input regeneration air duct; 114. Output regeneration air duct; 12. Heat absorption and dehumidification unit; 121. Heat pump evaporator; 122. Compressor; 123. Expansion valve; 2. Dehumidification subsystem; 21. Desiccant coating heat exchanger unit; 22. Filter; 3. Evaporative cooler; 31. Dry passage 32. Wet channel; 33. Humidity spray assembly; 331. Spray head; 332. Regulating valve; 333. Spray water; 334. Water tank; 34. Thermometer; 35. Hygrometer; 36. Variable frequency fan; 37. Cooler gas; 371. Dehumidified air; 372. Product air; 373. Working air; 374. Exhaust gas; 4. Indoor space; 5. Dehumidification and cooling circulation channel; 6. On / off valve; 61. First on / off valve; 62. Second on / off valve; 63. Second water valve; 64. Third on / off valve; 65. Fourth on / off valve; 66. Fifth on / off valve; 7. Air direct supply channel; 8. Cooling circulation water circuit; 81. Second water pump; 9. Outdoor air; 91. First outdoor air; 92. Second outdoor air. Detailed Implementation

[0034] The present invention will now be described in further detail with reference to the accompanying drawings and specific embodiments, but this does not limit the scope of protection of the present invention.

[0035] like Figures 1 to 6 An embodiment of the indoor air heat exchange and dehumidification system of the present invention is shown, which is used to dehumidify and cool an indoor space 4. In this embodiment, the indoor air heat exchange and dehumidification system includes a heat pump subsystem 1, a dehumidification subsystem 2, and an evaporative cooler 3 connected in sequence. The dehumidification subsystem 2 includes at least two sets of desiccant-coated heat exchange units 21 arranged in parallel. The indoor space 4 is connected to the input end of each desiccant-coated heat exchange unit 21, and the output end of the evaporative cooler 3 is connected to the indoor air to form a dehumidification and cooling circulation channel 5. When the indoor air humidity is high, the air can enter the desiccant-coated heat exchange unit 21 and the evaporative cooler 3 in sequence through the dehumidification and cooling circulation channel 5 for dehumidification and cooling. Its structure is simple, compact, and occupies little space.

[0036] Meanwhile, the desiccant coating heat exchange unit 21 of the present invention is configured as at least two sets, arranged in parallel; the heat pump subsystem 1 includes a heating regeneration unit 11 and a heat absorption dehumidification unit 12. The heating regeneration unit 11 and the heat absorption dehumidification unit 12 are respectively connected to the desiccant coating heat exchange unit 21 through corresponding on / off valves 6, which allows the desiccant coating heat exchange unit 21 to be in regeneration mode by connecting to the heating regeneration unit 11, whereby the heating regeneration unit 11 provides the desiccant coating heat exchange unit 21 with high-temperature air for desiccant regeneration; the desiccant coating heat exchange unit 21 can also be in dehumidification mode by connecting to the heat absorption dehumidification unit 12, whereby the heat absorption dehumidification unit 12 provides the desiccant coating heat exchange unit 21 with cooling water required for desiccant dehumidification, so as to adsorb the adsorption heat generated by desiccant dehumidification, thereby enabling the desiccant coating heat exchange unit 21 to be used efficiently in a cycle. The combined arrangement of the heating regeneration unit 11 and the heat absorption dehumidification unit 12 allows the desiccant coating heat exchange unit 21 to be in either regeneration mode or dehumidification mode.

[0037] Meanwhile, the desiccant coating heat exchange unit 21 in dehumidification mode can be connected to the indoor space 4 through the dehumidification cooling circulation channel 5 to dehumidify and cool the indoor air with high humidity. The desiccant coating heat exchange unit 21 is set to at least two sets, so that when the indoor air has high humidity, multiple sets of desiccant coating heat exchange units 21 can be used to dehumidify alternately, thereby achieving efficient and rapid dehumidification of the indoor space 4 under different working conditions and with different humidity levels. In addition, when the humidity is low, the dehumidification mode of turning on or off a single desiccant coating heat exchange unit 21 can be flexibly adjusted to save energy while ensuring dehumidification effect and efficiency.

[0038] The combination of the heating regeneration unit 11 and the heat absorption dehumidification unit 12 in this invention allows for better regeneration of the desiccant due to the high heat source temperature and better adsorption of moisture due to the low cooling water temperature. This effectively improves the moisture removal effect of the indoor air heat exchange and dehumidification system, giving the system excellent dehumidification performance.

[0039] Furthermore, such as Figure 1 and Figure 3As shown, the heating and regeneration unit 11 includes a condensation heat base heating module 111 and a solar supplementary heating module 112 connected in sequence. The condensation heat base heating module 111 includes a condenser 1111 and a heat pump subsystem heat exchanger 1112. The condenser 1111 is connected to the first outdoor air 91, and the first outdoor air 91 is heated by the condensation heat discharged from the condenser 1111. The heat pump subsystem heat exchanger 1112 is connected between the condenser 1111 and the desiccant coating heat exchange unit 21. The solar energy supplementary heating module 112 is connected to the desiccant coating heat exchange unit 21 through the heat pump subsystem heat exchanger 1112. The solar energy supplementary heating module 112 absorbs solar energy as driving energy and stores the heat in the intermediate medium water. The intermediate medium water enters the heat pump subsystem heat exchanger 1112. The first outdoor air 91, which was heated by the condenser 1111, is heated again through the heat pump subsystem heat exchanger 1112 and the intermediate medium water, becoming high-temperature air. The heated high-temperature air is sent to the desiccant coating heat exchange unit 21 in regeneration mode to desorb the moisture in the desiccant and regenerate the desiccant.

[0040] This invention uses a condensation heat base heating module 111 to heat the first outdoor air 91 with condensation heat, and a solar energy supplementary heating module 112 to further heat the first outdoor air 91 using solar energy as the driving energy. This combines the heat pump subsystem 1 with solar energy to generate a higher heat source temperature, thereby improving the regeneration of the desiccant. The combination of high-temperature solar regeneration and low-temperature cooling water generated by the heat pump results in superior dehumidification performance. Because the higher heat source temperature leads to better desiccant regeneration, and the lower cooling water temperature leads to better moisture adsorption, the system's moisture removal efficiency is improved.

[0041] Meanwhile, the heat absorption and dehumidification unit 12 includes a heat pump evaporator 121, which is connected in series with the condenser 1111. The heat pump evaporator 121 is also connected in series with a desiccant coating heat exchange unit 21 arranged in parallel. The heat pump evaporator 121 is used to change the refrigerant from a liquid to a gaseous state, absorbing heat and thus lowering the temperature of the surrounding air. This results in lower-temperature cooling water, allowing for better adsorption of moisture from the desiccant, effectively improving the system's moisture removal efficiency and removing the adsorption heat generated during the dehumidification process. Therefore, this invention combines high-temperature solar regeneration with the low-temperature cooling water generated by the heat pump evaporator 121, which is expected to provide better dehumidification performance for the indoor air heat exchange and dehumidification system and enhance the applicability of deep dehumidification.

[0042] Furthermore, a compressor 122 is provided between the output end of the heat pump evaporator 121 and the input end of the condenser 1111. The compressor 122 consumes mechanical energy to compress the low-temperature, low-pressure gaseous refrigerant into a high-temperature, high-pressure gas, providing power for the refrigerant circulation. That is, the compressor 122 converts mechanical energy into heat energy, raising the temperature of the refrigerant and laying the foundation for the subsequent heat exchange process. The condenser 1111 is a key component responsible for heat release in the heat pump subsystem 1. It receives the high-temperature, high-pressure gas from the compressor 122 and exchanges heat with the external environment (such as air or water) through the finned tube structure inside the condenser 1111, causing the high-temperature, high-pressure gas to condense into a liquid. In this process, the condenser 1111 releases heat and transfers the heat energy to the heating medium. In this application, the heating medium is fresh external air.

[0043] Meanwhile, an expansion valve 123 is provided between the output end of the condenser 1111 and the input end of the heat pump evaporator 121. The expansion valve 123 is a key component in the heat pump subsystem 1 that controls the refrigerant flow and pressure. It receives high-pressure liquid refrigerant from the condenser 1111 and reduces the pressure of the high-pressure liquid to a low-pressure liquid through throttling, so as to regulate the refrigerant flow to meet the load requirements of the system and create a low-pressure environment for the heat pump evaporator 121, enabling it to absorb more heat.

[0044] The heat pump evaporator 121 is a key component in the heat pump subsystem 1 responsible for heat absorption. It receives low-pressure liquid refrigerant from the expansion valve 123 and exchanges heat with the external environment (such as air or water) through the finned tube structure inside the heat pump evaporator 121, causing the low-pressure liquid to evaporate into gas. In this process, the heat pump evaporator 121 absorbs heat, extracts thermal energy from the medium that needs to be cooled, and converts it into the latent heat of the refrigerant. In this embodiment, the heat pump evaporator 121 consists of copper tubes and aluminum fins. The refrigerant flows in the copper tubes, and heat is transferred to the surrounding air through the aluminum fins.

[0045] As can be seen, the compressor 122 of this invention compresses the low-temperature, low-pressure refrigerant into a high-temperature, high-pressure gas; the condenser 1111 condenses the high-temperature, high-pressure gas into a liquid and releases heat; the expansion valve 123 depressurizes the high-pressure liquid into a low-pressure liquid; and the heat pump evaporator 121 evaporates the low-pressure liquid into a gas and absorbs heat. The heat pump evaporator 121, compressor 122, condenser 1111, and expansion valve 123, connected in sequence, form a heat pump thermodynamic cycle system, which can absorb heat from a low-temperature environment and transfer it to a high-temperature environment, achieving efficient utilization of thermal energy.

[0046] Furthermore, the solar supplementary heating module 112 includes a solar collector 1121, a water circulation channel 1122, and a first water pump 1123. The solar collector 1121 and the first water pump 1123 are located in the water circulation channel 1122. The heat exchanger 1112 of the heat pump subsystem is connected in series with the water circulation channel 1122 to form a supplementary heating circulation channel 1124. A first water valve 1127 is provided at the connection between the supplementary heating circulation channel 1124 and the water circulation channel 1122 to control the opening and closing of the solar supplementary heating module 112. In this embodiment, the solar collector 1121 is an ETC (Employment-Transfer-Cellular) collector with internal reflection concentration to improve solar energy utilization efficiency; the first water valve 1127 is a three-way water valve.

[0047] Preferably, the solar supplementary heating module 112 further includes a first controller, a temperature detection element 1125, and a heater 1126. The temperature detection element 1125 is located between the heat exchanger 1112 of the heat pump subsystem and the desiccant coating heat exchange unit 21 to detect the high temperature of the air input to the desiccant coating heat exchange unit 21. The heater 1126 is located in the supplementary heating circulation channel 1124 to further supplement and increase the air temperature.

[0048] When the temperature of the temperature sensor 1125 is lower than the optimal temperature for desiccant regeneration, the heater 1126 is activated by the first controller; when the temperature of the temperature sensor 1125 is equal to or higher than the optimal temperature for desiccant regeneration, the heater 1126 is deactivated by the first controller. The optimal temperature for desiccant regeneration is typically set to 60℃-65℃. Specifically, if solar energy resources are sufficient and can be combined with the heat pump subsystem 1 to reach the required regeneration temperature, the heater 1126 does not need to be activated; if the outdoor air is heated by the condenser 1111 and reheated by the heat exchanger 1112 of the heat pump subsystem, and the temperature does not reach the optimal temperature for desiccant regeneration, then the heater 1126 is activated.

[0049] Renewable energy sources like solar power are affected by weather conditions; cloudy or rainy weather can impact regeneration temperatures. The intermittency and instability of solar energy are significant factors limiting system performance. The intensity of solar radiation varies with time and weather, leading to unstable heat supply from the system. This invention combines a condensation heat base heating module 111 and a solar supplementary heating module 112. When solar energy is unstable, the heater 1126 can heat the hot water in the heat exchanger 1112 of the heat pump subsystem, thereby improving the desiccant regeneration effect and the system's cooling capacity.

[0050] like Figures 3 to 5As shown, the evaporative cooler 3 is a counter-current dew point evaporative cooler, which includes a dry channel 31, a wet channel 32, and a warm and wet spray assembly 33. The dry channel 31 and the wet channel 32 are arranged side-by-side and interconnected. High-temperature air after dehumidification is sent into the dry channel 31, where latent heat exchange cools the air. Part of the cooled air is sent into the room, and the other part enters the wet channel 32. The wet channel 32 is used to discharge the exhaust gas 374 into the outdoor environment. Simultaneously, convective heat exchange occurs through the warm and wet spray assembly 33, further cooling the air in the dry channel 31.

[0051] Furthermore, the temperature and humidity spray assembly 33 includes multiple spray heads 331, which are disposed within the wet channel 32 and arranged along the length of the wet channel 32. The spray direction of the spray heads 331 is perpendicular to the airflow direction within the wet channel 32, causing the spray water 333 to flow in opposite directions to the air. By spraying water into the air, the air temperature is reduced through the heat absorption effect of water evaporation, i.e., sensible heat (dry-bulb temperature) and latent heat (wet-bulb temperature) are carried away through phase change evaporation, thereby achieving effective air cooling. The counter-current dew point evaporative cooler of the present invention can effectively reduce the temperature and humidity of the air and is suitable for air conditioning systems in high-humidity areas. In other embodiments, as long as the spray water 333 flows in opposite directions to the air, the spray direction of the spray heads 331 can also be set at a certain angle to the airflow direction within the wet channel 32, such as 30°, 60°, etc.

[0052] In this embodiment, the warm and humid spray assembly 33 is located at the top end of the wet channel 32. In other embodiments, as long as the evaporation and heat absorption effect of water is ensured to reduce the air temperature, it can also be arranged circumferentially in the wet channel 32. Preferably, the spray density of the warm and humid spray assembly 33 is ≥0.02 m³ / (m²·h).

[0053] Figure 5 The flow direction of the cooler gas 37 in the counter-current dew point evaporative cooler is shown. Figure 7 The enthalpy-humidity diagram of the countercurrent dew point evaporative cooler is shown. Figure 7 In the diagram, W1 represents the humidity of the dehumidified air 371, W2 represents the humidity of the product air 372, W3 represents the humidity of the exhaust gas 374, T1 represents the temperature of the dehumidified air 371, and T... WB T represents the wet-bulb temperature, T2 represents the product air temperature at 37°C, T DP This represents the dew point temperature. As shown in the diagram, the dehumidified air 371, after being dehumidified by the desiccant-coated heat exchange unit 21, is drawn into the dry channel 31, transferring sensible heat to the wet channel 32. This causes the temperature of the outlet air leaving the system (i.e., the product air 372) to be lower than the ambient temperature, as shown in the enthalpy-humidity diagram path. As shown in the diagram, a portion of the product air 372 is transferred to the humidification channel 32 as working air 373. Because the working air 373 is humidified and absorbs heat, it will further reduce the temperature of the air in the dry channel 31, as shown in the enthalpy-humidity diagram path. As shown in the diagram. Ultimately, the high-temperature, high-humidity exhaust gas 374 is released into the atmosphere, as shown in the enthalpy-humidity diagram path. As shown, the counter-current dew point evaporative cooler of the present invention reduces the outlet air temperature to below the ambient wet-bulb temperature while maintaining the same humidity. In an ideal cycle, the outlet temperature can theoretically be reduced to the dew point temperature of the inlet air. It consumes less energy, thus achieving optimal cooling effect while saving energy.

[0054] like Figure 4 As shown, the countercurrent dew point evaporative cooler can adopt a modular countercurrent heat exchange coil. The number of dry channels 31 and wet channels 32 can be set according to the actual cooling requirements, such as one group, two groups, three groups, etc. When there are more than two groups, the dry channels 31 and wet channels 32 are arranged alternately to form a modular countercurrent heat exchange coil.

[0055] Furthermore, the present invention also includes a second controller, a thermometer 34, a hygrometer 35, and a variable frequency fan 36. The thermometer 34 and hygrometer 35 are located downstream of the dry channel 31 to monitor the temperature and humidity of the cooling air in real time; the variable frequency fan 36 is located upstream of the dry channel 31; the temperature and humidity spray assembly 33 also includes a regulating valve 332 for adjusting the water volume of the spray head 331, and a water tank 334 for providing spray water 333, the water tank 334 being connected to the spray head 331, and the regulating valve 332 being located between the water tank 334 and the spray head 331; the input terminal of the second controller is connected to the thermometer 34 and the hygrometer 35, and the output terminal of the second controller is connected to the regulating valve 332 and the variable frequency fan 36. In this embodiment, the regulating valve 332 is an electric water valve.

[0056] The second controller receives the detection values ​​from thermometer 34 and hygrometer 35, and compares these values ​​with preset temperature and humidity values, respectively. When the temperature reading of thermometer 34 is higher than the preset air temperature, the controller increases the opening of regulating valve 332 and / or decreases the speed of variable frequency fan 36. The increased opening of regulating valve 332 increases the volume of spray water 333, thus better reducing the air temperature. Decreasing the speed of variable frequency fan 36 allows the dehumidified air 371 to pass through slowly, providing more time for heat exchange with the desiccant, thereby lowering the temperature of the product air 372. When the temperature reading of thermometer 34 is lower than the preset air temperature, the controller decreases the opening of regulating valve 332 and / or increases the speed of variable frequency fan 36, thereby reducing the amount of spray water 333 and the time spent in heat exchange with the desiccant.

[0057] When the humidity reading of the hygrometer 35 is higher than the preset humidity, the speed of the variable frequency fan 36 is reduced, thereby reducing the airflow and allowing the air in the desiccant coating heat exchange unit 21 to pass through slowly and achieve sufficient dehumidification. When the humidity reading of the hygrometer 35 is lower than the preset humidity, the speed of the variable frequency fan 36 is increased, thereby increasing the airflow and allowing the air in the desiccant coating heat exchange unit 21 to pass through quickly, thereby reducing the dehumidification time and reducing air dehumidification. This invention controls the amount of spray water 333 by controlling the opening of the regulating valve 332 and adjusts the airflow by controlling the speed of the variable frequency fan 36. This allows for adjustment of the counter-current dew point evaporative cooler based on the temperature and humidity feedback of the cooling air, meeting the temperature and humidity requirements of the indoor air. It is convenient to adjust and has high accuracy.

[0058] In this embodiment, the indoor air heat exchange and dehumidification system is used in high-temperature and high-humidity areas requiring cooling and dehumidification. The preset air temperature is set to 26°C, and the preset air humidity is set to 55%. The speed of the variable frequency fan 36 is set to 20~100%, and the opening degree of the regulating valve 332 is set to 0~100%. In other embodiments, the preset air temperature and preset air humidity can be set according to human comfort. Human comfort mainly refers to thermal environment conditions, including factors such as temperature, humidity, and airflow. For example, the ASHRAE (American Society of Heating, Ventilating, Air-conditioning and Refrigerating Engineers) standard can be referenced. ASHRAE defines the comfortable temperature range as 23°C~26°C in summer and 20°C~24°C in winter. The comfortable humidity range is defined as 40%~60% in summer and 30%~40% in winter. The specific values ​​of the preset air temperature and preset air humidity can be set according to personal preferences, activity level, clothing, etc., and are not limited here.

[0059] Specifically, the temperature of the product air 372 at the outlet of the dry channel 31 is measured by thermometer 34, and the real-time indoor temperature is compared with the preset temperature detection value. If the real-time indoor temperature is 26°C higher than the preset temperature detection value, the opening of the electric water valve is dynamically adjusted through a PID algorithm. That is, when the real-time indoor temperature is higher than the preset air temperature (T>26°C), the second controller controls the regulating valve 332, increasing the water volume of the spray water 333 to 80~100% opening, utilizing the counter-current evaporation effect to enhance sensible heat exchange; the variable frequency fan 36 speed is increased to over 90% to improve the contact efficiency between the accelerated air and the spray water 333, at which time the evaporative cooling of the evaporative cooler 3 is enhanced. When the real-time indoor temperature is lower than the preset air temperature (T<24°C), the second controller controls the regulating valve 332, reducing the water volume of the spray water 333 to below 20%, reducing the intensity of evaporative cooling; the variable frequency fan 36 switches to low-frequency operation (40% speed) to avoid excessive cooling, thereby weakening the cooling of the evaporative cooler 3.

[0060] In this embodiment, the thermometer 34 can adopt a PT100 temperature sensor (accuracy of ±0.2°C), and the hygrometer 35 can adopt a capacitive humidity sensor (accuracy of ±3%RH). The second controller is a DDC controller. The thermometer 34 and the hygrometer 35 collect data every second and transmit it to the DDC controller. In other embodiments, as long as the thermometer 34 and the hygrometer 35 can ensure the effective collection of temperature and humidity data, any sensor can be used, and no limitation is made here.

[0061] The adjustment of the DDC controller is through the proportional-integral (PID) algorithm to achieve precise adjustment of parameters such as temperature and humidity. The DDC dynamically adjusts the opening degree of the electric water valve according to the PID algorithm. The DDC controller can receive sensor data (such as temperature, humidity, pressure, etc.), perform real-time analysis through a preset logic program, and issue control instructions to drive the actuators (such as the variable-frequency fan 36, the regulating valve 332, etc.), and finally achieve the automatic adjustment of the equipment operation.

[0062] The present invention adopts humidity stratified control. When the indoor air is in the high-humidity area (RH>80%), the desiccant-coated heat exchange units 21 work alternately. One desiccant-coated heat exchange unit 21 is in the dehumidification mode, adsorbing the moisture in the air and maintaining the coating humidity <30%; the other desiccant-coated heat exchange unit 21 is in the regeneration mode, heating the air through the solar collector 1121, the condenser 1111 in the heat pump subsystem 1, and the heater 1126 to make the air temperature reach the preset temperature to desorb the moisture. At this time, the heat pump evaporator 121 is started synchronously to remove the adsorption heat generated in the dehumidification mode by using the condensed water.

[0063] When the indoor air is in the medium-humidity area (60%<RH<80%), a single desiccant-coated heat exchange unit 21 dehumidifies, and the adsorption intensity is dynamically adjusted according to the humidity difference (for example, when RH = 70%, the adsorption rate is 50%RH / min). When the indoor air is in the low-humidity area (RH<40%), the dehumidification mode of the desiccant-coated heat exchange unit 21 is turned off.

[0064] When the temperature and humidity are coupled and in conflict, for example, when T = 26°C and RH = 55%, the system standby state is maintained, neither the desiccant-coated heat exchange unit 21 nor the spray water 333 is turned on, and the first on-off valve 61 is open to allow the outdoor air 9 (the second outdoor air 92) to enter the room and provide fresh indoor air. For example, when T = 26°C and RH = 65%, the desiccant-coated heat exchange unit 21 is preferentially started for dehumidification. At the same time, the water volume of the spray water 333 is finely adjusted to maintain the temperature.

[0065] In this embodiment, an air direct supply channel 7 communicating with the second outdoor air 92 is provided between the desiccant coating heat exchange unit 21 and the evaporative cooler 3. The air direct supply channel 7 is equipped with a first on / off valve 61. The dehumidification cooling circulation channel 5 is equipped with a second on / off valve 62 corresponding to each desiccant coating heat exchange unit 21 for air path switching. When the indoor air humidity is less than the preset humidity, the first on / off valve 61 is opened and the second on / off valve 62 is closed; when the indoor air humidity is greater than the preset humidity, the first on / off valve 61 is closed and the second on / off valve 62 of the desiccant coating heat exchange unit 21 in dehumidification mode is opened.

[0066] A cooling water circulation path 8 is provided between the heat pump evaporator 121 and the desiccant coating heat exchange unit 21. The desiccant coating heat exchange unit 21 is connected in parallel to the cooling water circulation path 8. A second water valve 63 is provided at the connection between each desiccant coating heat exchange unit 21 and the cooling water circulation path 8 for water path switching. The cooling water circulation path 8 is provided with a second water pump 81 to provide power for cooling water transportation. The cooling water is delivered to the carbon-based desiccant coating heat exchanger in the dehumidification state through the second water pump 81 to remove the adsorption heat generated by dehumidification, thereby improving the dehumidification efficiency.

[0067] The heating regeneration unit 11 is connected to the input end of each desiccant coating heat exchange unit 21 arranged in parallel through the input regeneration air duct 113. Each desiccant coating heat exchange unit 21 is equipped with a third on / off valve 64 for switching the air path. The output end of each desiccant coating heat exchange unit 21 is connected to the evaporative cooler 3 through the output regeneration air duct 114.

[0068] This invention controls the dehumidification and regeneration modes of each desiccant coating heat exchange unit 21 through a second on / off valve 62, a third on / off valve 64, and a second water valve 63. Specifically, in regeneration mode, the third on / off valve 64 corresponding to the desiccant coating heat exchange unit 21 is open, the second on / off valve 62 is closed, and the second water valve 63 is closed; in dehumidification mode, the third on / off valve 64 corresponding to the desiccant coating heat exchange unit 21 is closed, the second on / off valve 62 is open, and the second water valve 63 is open, thereby achieving the switching between adsorption and regeneration modes.

[0069] In this embodiment, the desiccant coating heat exchange unit 21 is a carbon-based desiccant coating heat exchanger. The carbon-based desiccant coating heat exchanger includes multiple heat exchange fins arranged side by side. The heat exchange fins are corrugated heat exchange fins, which can handle sensible heat and latent heat loads simultaneously.

[0070] In this embodiment, two sets of desiccant coating heat exchange units 21 are configured. The alternating operation of the two sets of desiccant coating heat exchange units 21 is as follows: the input first outdoor air 91 is first heated by the condensation heat discharged from the condenser 1111, and then absorbs solar energy as driving energy through the solar supplementary heating module 112, storing the heat in the intermediate medium water, so that the heated first outdoor air 91 is reheated into high-temperature air in the heat pump subsystem heat exchanger 1112. The heated air is sent to the carbon-based desiccant coating heat exchanger in regeneration mode, where the heated air absorbs moisture from the desiccant, restoring the dehumidifying capacity of the desiccant. Indoor air enters the carbon-based desiccant coating heat exchanger in dehumidification mode for dehumidification. After a period of time (e.g., 300s), the carbon-based desiccant coating heat exchangers in regeneration mode and dehumidification mode change mode by linking the opening and closing of the second on / off valve 62 and the third on / off valve 64, so that the two sets of carbon-based desiccant coating heat exchangers alternately enter dehumidification mode and regeneration mode respectively, so as to carry out continuous dehumidification.

[0071] Existing dehumidification systems integrate evaporative cooling air conditioning with membrane dehumidification. Membrane dehumidification relies on the selectivity of the membrane and the vapor pressure difference across it, and its dehumidification efficiency may be limited by membrane performance and pressure difference. In contrast, this invention uses a carbon-based dehumidifying coating applied to the surface of the heat exchange fins. This carbon-based dehumidifying coating (adsorbent) is in direct contact with the air, achieving dehumidification through a physical adsorption / desorption cycle, thus adsorbing moisture from the air and achieving high dehumidification efficiency. The carbon-based dehumidifying coating is directly applied to the surface of the heat exchange fins, forming a compact whole. This avoids the bulky rotary structure of traditional rotary dehumidifiers, making it easier to integrate into air conditioning systems, especially in space-constrained environments.

[0072] Preferably, the dehumidifying coating of the desiccant-coated heat exchange unit 21 is composed of a carbon-based composite desiccant and a curing agent. The carbon-based composite desiccant consists of silica gel and LiCl-impregnated activated carbon, and the curing agent is epoxy polyester powder. The carbon-based material has a large specific surface area and good hygroscopic properties, effectively removing moisture from the air. The hygroscopic properties and stability of the carbon-based material can be improved through modification. Simultaneously, activated carbon has a rich porous structure and can support hygroscopic salts such as LiCl, thereby effectively improving the hygroscopic capacity of the heat exchanger 1112 in the heat pump subsystem. It has advantages such as high hygroscopicity and stability, and renewability. Preferably, the mixing ratio of the carbon-based composite desiccant to the curing agent is 6:4, thus giving the carbon-based material excellent hygroscopic properties, thereby better removing moisture from the air.

[0073] Existing dehumidification systems often suffer from membrane surface contamination by dust particles carried in humid air, reducing dehumidification efficiency. This contamination also hinders water vapor transfer through the membrane, lowering overall system performance. Membrane dehumidification primarily targets moisture, with limited ability to remove other pollutants. Furthermore, without regular cleaning and maintenance, it can lead to air quality problems. High-performance dehumidification membranes are also expensive, raising environmental concerns during production and use. In contrast, the desiccant-coated heat exchange unit 21 of this invention not only dehumidifies but also improves indoor air quality by adsorbing pollutants. Carbon-based materials possess the ability to adsorb volatile organic compounds (VOCs) and other harmful gases, thus achieving air purification. The use of solid adsorbents avoids the risks of leakage and system corrosion associated with liquid desiccant solutions (such as lithium chloride solution), thereby achieving air purification and improving indoor air quality. Moreover, carbon-based materials are widely available, and carbon-based composite desiccants are less expensive than dehumidification membranes.

[0074] Preferably, the spacing of the corrugated heat exchange fins is 3-5 mm, and the waveform height is 6-9 mm. The corrugated heat exchange fins can be made of aluminum flat tubes. In this case, the hydraulic diameter of the channel is only 1-100 μm, and the heat exchange efficiency is more than 30% higher than that of traditional copper tubes. This reduces the weight of the heat exchanger 1112 in the heat pump subsystem while effectively reducing the amount of refrigerant charged.

[0075] At the same time, such as Figure 2 As shown, the desiccant-coated heat exchange unit 21 is equipped with a filter 22 to intercept various solid contaminants in the air, thereby protecting the delicate and core desiccant coating and heat exchange surface from clogging, wear, and contamination. This ultimately ensures that the dehumidification / energy recovery system can continuously operate at its designed high efficiency and stability, and output clean air. This protects the desiccant coating and heat exchange surface, ensuring the system's long-term, efficient, and stable operation.

[0076] In this embodiment, an electrostatic spraying method can be used to uniformly coat the carbon-based dehumidifying coating onto the surface of the heat exchanger 1112 of the heat pump subsystem. Compared with the rotary dehumidifier which uses an overall impregnation or mixing method, this method can more precisely control the distribution and thickness of the desiccant, thereby optimizing the heat and mass transfer performance.

[0077] The carbon-based desiccant-coated heat exchanger of this invention enables decoupling control of sensible and latent heat loads, thereby improving the energy efficiency of the air conditioning system. This allows for independent adjustment of temperature and humidity according to actual needs, avoiding overcooling or overheating. The carbon-based desiccant-coated heat exchanger can use the heating regeneration unit 11 for desiccant regeneration, effectively reducing energy dependence, achieving energy conservation and emission reduction, and allowing for the use of low regeneration temperatures, thus reducing energy consumption. By selecting suitable desiccant materials and optimizing system parameters, the carbon-based desiccant-coated heat exchanger can achieve efficient dehumidification in high-humidity areas and energy-saving cooling in dry areas, making it suitable for various climatic conditions and building types, with a wide range of applications. The carbon-based desiccant-coated heat exchanger achieves efficient dehumidification by removing adsorbed heat through internal cooling. This internal cooling method significantly improves the moisture absorption capacity of the desiccant, making the carbon-based desiccant-coated heat exchanger superior to traditional rotary dehumidification systems in dehumidification performance.

[0078] In this embodiment, when the indoor air is in a low humidity zone (RH<40%), the dehumidification mode of the desiccant coating heat exchange unit 21 is turned off. When the summer air humidity is 40%~60%, which is a comfortable environment, all carbon-based desiccant coating heat exchangers are suspended. Indoor air mixes with outdoor air, the second on / off valve 62 is closed, and the first on / off valve 61 is opened. The outdoor air mixes directly pass through the counter-current dew point evaporative cooler to cool the air.

[0079] When the summer air humidity is 60%~80%, only one carbon-based desiccant-coated heat exchanger is turned on, and the first on / off valve 61 is closed. At this time, one carbon-based desiccant-coated heat exchanger is in dehumidification mode. The third on / off valve 64 corresponding to the carbon-based desiccant-coated heat exchanger is closed, and the second on / off valve 62 is open. Indoor air passes through the carbon-based desiccant-coated heat exchanger and is dehumidifies the indoor air through an isenthalpic dehumidification process. At the same time, the cooling water in the heat pump evaporator 121 in the heat pump subsystem 1 is powered by the second water pump 81 and sent to the carbon-based desiccant-coated heat exchanger to remove the adsorption heat generated during the dehumidification process. Then, it is sent to the counter-current dew point evaporative cooler by the variable frequency fan 36, and after an enthalpy reduction and cooling process, it is sent into the room. The other carbon-based desiccant-coated heat exchanger is in a suspended state, and the second on / off valve 62 and the third on / off valve 64 corresponding to the suspended carbon-based desiccant-coated heat exchanger are closed.

[0080] When the carbon-based desiccant coating heat exchanger in dehumidification mode enters regeneration mode, it stops working, and the suspended carbon-based desiccant coating heat exchanger also stops dehumidifying. Specifically, the second shut-off valve 62 is closed, and the third shut-off valve 64 corresponding to the regeneration mode carbon-based desiccant coating heat exchanger is opened. Outdoor air is first heated by the condensation heat discharged from the condenser 1111, and then further heated to high temperature by the heat pump subsystem heat exchanger 1112. The generated high-temperature gas is then sent into the regeneration mode carbon-based desiccant coating heat exchanger to absorb moisture from the desiccant, allowing the desiccant to be regenerated and reused.

[0081] When the summer air humidity exceeds 80%, two carbon-based desiccant-coated heat exchangers are activated, one for dehumidification and the other for regeneration, alternating between them. First, the first on / off valve 61 is closed. The incoming fresh air is heated by the condensation heat discharged from the condenser 1111, and then absorbs solar energy through the solar collector 1121 as driving energy, storing the heat in the intermediate medium water. This heated fresh air is then reheated into high-temperature air in the heat pump subsystem heat exchanger 1112. The heated air is then sent to the corresponding carbon-based desiccant-coated heat exchanger in regeneration mode through the corresponding third on / off valve 64. The heated air absorbs moisture from the desiccant in the carbon-based desiccant-coated heat exchanger, restoring the dehumidifier's dehumidification capacity.

[0082] Simultaneously, the second on / off valve 62 corresponding to the carbon-based desiccant coating heat exchanger in dehumidification mode is opened, and the second on / off valve 62 corresponding to the carbon-based desiccant coating heat exchanger in regeneration mode is closed. Indoor air enters the carbon-based desiccant coating heat exchanger for dehumidification. At the same time as dehumidification, the cooling water in the evaporator in the heat pump subsystem 1 is transported to the carbon-based desiccant coating heat exchanger to remove the adsorption heat generated during the dehumidification process. The dehumidified air is sent to the countercurrent dew point evaporative cooler for cooling and finally sent into the room. The carbon-based desiccant coating heat exchangers of the present invention, in regeneration and dehumidification modes, change mode by linking the opening and closing of the second on / off valve 62 and the third on / off valve 64. Specifically, by opening the third on / off valve 64 corresponding to the carbon-based desiccant coating heat exchanger in regeneration mode and closing the second on / off valve 62 corresponding to the carbon-based desiccant coating heat exchanger in regeneration mode, opening the second on / off valve 62 corresponding to the carbon-based desiccant coating heat exchanger in dehumidification mode and closing the third on / off valve 64 corresponding to the carbon-based desiccant coating heat exchanger in dehumidification mode, the two sets of desiccant coating heat exchange units 21 are respectively in dehumidification mode and regeneration mode for continuous dehumidification. Example 2

[0083] Figure 6Another embodiment of the indoor air heat exchange and dehumidification system of the present invention is shown. This embodiment is basically the same as the previous embodiment, except that the desiccant coating heat exchange unit 21 in this embodiment can also be set to three or more groups. The two groups of desiccant coating heat exchange units 21 are set in the same way as in embodiment 1. The output regeneration air duct 114 between the two groups of desiccant coating heat exchange units 21 and the variable frequency fan 36 is connected in parallel with the number of other desiccant coating heat exchange units 21. Each connecting pipe is equipped with an on / off valve to control the opening and closing of each desiccant coating heat exchange unit 21, thereby achieving a better dehumidification and heat exchange effect of the system.

[0084] In this embodiment, three sets of desiccant coating heat exchange units 21 are configured. A connecting pipe is set in parallel between two sets of desiccant coating heat exchange units 21 and the variable frequency fan 36 in the dehumidification and cooling circulation channel 5. Another set of desiccant coating heat exchange units 21 is located in the connecting pipe. A fourth on / off valve 65 is provided in the dehumidification and cooling circulation channel 5 between the desiccant coating heat exchange units 21 and the variable frequency fan 36. A fifth on / off valve 66 is provided upstream of the desiccant coating heat exchange units 21 in the connecting pipe. The air from the two sets of desiccant coating heat exchange units 21 enters the evaporative cooler 3 for cooling through the fourth on / off valve 65. The other set of desiccant coating heat exchange units 21 is opened and closed through the fifth on / off valve 66. In other embodiments, the number of desiccant coating heat exchange units 21 can be set according to actual needs, such as four or five sets. The remaining sets of desiccant coating heat exchange units 21 are also set in parallel through connecting pipes.

[0085] Although the invention has been described with reference to preferred embodiments, various modifications can be made and components can be replaced with equivalents without departing from the scope of the invention. In particular, the technical features mentioned in the various embodiments can be combined in any manner as long as there is no structural conflict. The invention is not limited to the specific embodiments disclosed herein, but includes all technical solutions falling within the scope of the claims.

Claims

1. An indoor air heat exchange dehumidifying system for cooling an indoor space, characterized by, The system comprises a heat pump subsystem, a dehumidification subsystem and an evaporative cooler connected in sequence, wherein the dehumidification subsystem comprises at least two groups of desiccant-coated heat exchange units arranged in parallel, the indoor space is connected to the input end of each desiccant-coated heat exchange unit, and the output end of the evaporative cooler is connected to the indoor air to form a dehumidification and cooling circulation channel; the heat pump subsystem comprises a heating regeneration unit for providing high-temperature air for desiccant regeneration and an endothermic dehumidification unit for providing cooling water required for desiccant dehumidification, the heating regeneration unit and the endothermic dehumidification unit are connected to the desiccant-coated heat exchange units through corresponding on-off valves, so that the desiccant-coated heat exchange units are in a regeneration mode or a dehumidification mode; the desiccant-coated heat exchange units in the dehumidification mode are communicated with the indoor space through the dehumidification and cooling circulation channel; the heating regeneration unit comprises a condensation heat basic heating module and a solar supplementary heating module connected in sequence, the solar supplementary heating module is connected to the desiccant-coated heat exchange unit through a heat exchanger; the solar supplementary heating module comprises a solar collector, a water circulation channel and a first water pump, the solar collector and the first water pump are arranged in the water circulation channel, and the heat exchanger is connected to the water circulation channel in series to form a supplementary heating circulation channel; a first water valve is arranged at the connection between the supplementary heating circulation channel and the water circulation channel; the solar supplementary heating module absorbs solar energy as a driving energy and stores heat in intermediate medium water, and the intermediate medium water enters the heat pump subsystem heat exchanger, and the first outdoor air heated by the condenser is heated again through heat exchange between the heat pump subsystem heat exchanger and the intermediate medium water.

2. The indoor air heat-recovery dehumidification system of claim 1, wherein, The condensation heat basic heating module comprises a condenser communicated with the first outdoor air and a heat exchanger connected between the condenser and the desiccant-coated heat exchange unit.

3. The indoor air heat-recovery dehumidification system of claim 2, wherein, The solar supplementary heating module further comprises a first controller, a temperature detection member for detecting the temperature of the input desiccant-coated heat exchange unit high-temperature air, and a heater for further increasing the air temperature, the temperature detection member is arranged between the heat exchanger and the desiccant-coated heat exchange unit, and the heater is arranged in the supplementary heating circulation channel; When the temperature detected by the temperature detection member is lower than the optimal temperature for desiccant regeneration, the heater is started through the first controller; when the temperature detected by the temperature detection member is equal to or higher than the optimal temperature for desiccant regeneration, the heater is turned off through the first controller.

4. The indoor air heat-recovery dehumidification system of claim 1, wherein, The endothermic dehumidification unit comprises a heat pump evaporator, the heat pump evaporator is connected to the condenser in series and connected to the desiccant-coated heat exchange units arranged in parallel in series; a compressor for compressing low-temperature and low-pressure refrigerant into high-temperature and high-pressure gas is arranged between the output end of the heat pump evaporator and the input end of the condenser, and an expansion valve for reducing high-pressure liquid into low-pressure liquid is arranged between the output end of the condenser and the input end of the heat pump evaporator to form a thermodynamic cycle system.

5. The indoor air heat-recovery dehumidification system according to any one of claims 1 to 4, wherein The evaporative cooler is a counterflow dew point evaporative cooler, which comprises a dry channel for cooling incoming air supply into a room, a wet channel for discharging exhaust gas of the incoming air supply to the outside, and a temperature and humidity spray assembly for driving sensible heat and latent heat in the air, wherein the dry channel and the wet channel are arranged side by side and communicated with each other; the temperature and humidity spray assembly comprises a plurality of spray heads arranged in the wet channel and arranged along the length direction of the wet channel, and the spray direction of the spray heads is arranged at an angle with the flow direction of the air in the wet channel.

6. The indoor air heat-recovery dehumidification system of claim 5, wherein, Further comprising a second controller, a thermometer and a hygrometer arranged downstream of the dry channel, and a variable frequency fan arranged upstream of the dry channel, and the temperature and humidity spray assembly further comprises an adjusting valve for adjusting the water amount of the spray heads; the input end of the controller is connected with the thermometer and the hygrometer, and the output end is connected with the adjusting valve and the variable frequency fan; The thermometer and the hygrometer detect the temperature and humidity of the cooling air in real time, the controller receives the detection values of the thermometer and the hygrometer, and compares the detection values of the thermometer and the hygrometer with preset temperature detection value and preset humidity detection value respectively; when the detection value of the thermometer is higher than or equal to the preset air temperature, the opening of the adjusting valve is increased and / or the rotating speed of the variable frequency fan is reduced, otherwise, the opening of the adjusting valve is reduced and / or the rotating speed of the variable frequency fan is reduced; when the detection value of the hygrometer is higher than or equal to the preset humidity, the rotating speed of the variable frequency fan is reduced, otherwise, the rotating speed of the variable frequency fan is increased.

7. The indoor air heat-recovery dehumidification system according to any one of claims 1 to 4, wherein An air direct channel is arranged between the desiccant coating heat exchange unit and the evaporative cooler, and the air direct channel is communicated with the second outdoor air, and the air direct channel is provided with a first on-off valve; the dehumidification and cooling circulation channel is provided with a second on-off valve corresponding to each desiccant coating heat exchange unit; When the humidity of the indoor air is less than the preset humidity, the first on-off valve is opened, and the second on-off valve is closed; when the humidity of the indoor air is greater than the preset humidity, the first on-off valve is closed, and the second on-off valve of the desiccant coating heat exchange unit in the dehumidification mode is opened.

8. The room air heat exchanging dehumidifying system according to claim 7, wherein, The heat absorption and dehumidification unit comprises a heat pump evaporator, and a cooling circulation waterway is arranged between the heat pump evaporator and the desiccant coating heat exchange unit, the desiccant coating heat exchange units are connected in parallel to the cooling circulation waterway, and a second water valve is arranged at the connection position of the desiccant coating heat exchange unit and the cooling circulation waterway; The heating regeneration unit is connected with the input end of each desiccant coating heat exchange unit arranged in parallel through an input regeneration air pipe, and the input end of each desiccant coating heat exchange unit is provided with a third on-off valve; the output end of each desiccant coating heat exchange unit is connected with the evaporative cooler through an output regeneration air pipe.

9. The indoor air heat recovery dehumidification system according to any one of claims 1 to 4, wherein The dehumidification coating of the desiccant coating heat exchange unit is composed of a carbon-based composite desiccant and a curing agent, the carbon-based composite desiccant is composed of silica gel and impregnated activated carbon, and the curing agent is an epoxy polyester powder.

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