Double-cold-source fresh air dehumidification system

Abstract

The invention relates to a double-cold-source fresh air dehumidification system which is characterized in that a first reheating coil pipe and a second reheating coil pipe are arranged in an air duct, and the first reheating coil pipe and the second reheating coil pipe are arranged in parallel; when no water is supplied to the water supply pipe, the condenser merging electromagnetic valve is opened, and the condenser-to-evaporator expansion valve is closed, so that the first reheating coil pipe and the second reheating coil pipe are connected in parallel to jointly form the condenser; when water is supplied to the water supply pipe, the condenser merging electromagnetic valve is closed, and the condenser-to-evaporator expansion valve is opened, so that the first reheating coil independently forms the condenser, and the output end of the second reheating coil is connected with the input end of the evaporator to jointly form the evaporator. According to the designed double-cold-source fresh air dehumidification system, the two reheating coils are arranged in parallel, combined configuration of the reheating coils is dynamically switched according to whether water supply exists or not, stable operation under the water working condition and the water-free working condition is considered, and the reliability and stability of the system are effectively improved.

Description

Technical Field

[0001] The invention relates to the technical field of air dehumidification, in particular to a dual-cold-source fresh air dehumidification system. Background Art

[0002] With the improvement of people's living standards and the increasing requirements for indoor air quality, fresh air systems have become an indispensable part of modern buildings. By introducing fresh outdoor air, indoor pollutants are diluted and indoor air quality is improved. However, simply introducing outdoor air, especially in humid or dry seasons, will cause indoor temperature and humidity fluctuations and affect comfort. Therefore, fresh air systems usually need to be combined with temperature and humidity control functions.

[0003] The dual-cooling source fresh air system came into being. It usually uses two cold sources, cooling water and refrigerant, to perform heat exchange through plate heat exchangers and coil heat exchangers respectively to pre-cool and dehumidify the fresh air. The cooling water is responsible for pre-cooling the fresh air, reducing its temperature and humidity, and reducing the burden on the refrigeration system; while the refrigerant performs deep dehumidification and adjusts the supply air temperature.

[0004] However, the existing dual-cooling source fresh air system still has some shortcomings. For example, when the cooling water supply is interrupted, the pressure on the high-pressure side of the compressor will increase in some systems, triggering a high-pressure alarm, which seriously affects the user experience and leads to an increase in complaints. In addition, many system control strategies are simple and cannot accurately adjust the temperature and humidity of the air supply according to actual needs, which also reduces user comfort.

[0005] Therefore, there is an urgent need for a dual-cold-source fresh air dehumidification system that can adapt to both water and water-free supply conditions and can accurately control the supply air temperature and humidity to improve system reliability and user comfort. Summary of the invention

[0006] In order to solve the above problems, the present invention provides a dual-cold source fresh air dehumidification system which realizes stable operation under water or no water conditions by dynamically switching the combination configuration of two parallel reheat coils.

[0007] In order to achieve the above-mentioned purpose, the dual-cold-source fresh air dehumidification system designed by the present invention includes a compressor, a plate heat exchanger, an air duct and a water supply pipe for connecting to an external cooling water source, wherein 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 connected to the external cooling water source through the water supply pipe; the output end of the compressor is connected to the plate heat exchanger in one way and to the condenser in the other way; the output end of the condenser and the output end of 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, and a first reheat coil and a second reheat coil are arranged in parallel in the air duct. tube, a condenser merging solenoid valve and a condenser-to-evaporator expansion valve are arranged between the first reheat coil and the second reheat coil; wherein, when there is no water supply in the water supply pipe, the condenser merging solenoid valve is opened and the condenser-to-evaporator expansion valve is closed, so that the first reheat coil and the second reheat coil are connected in parallel to form the condenser together; when there is water supply in the water supply pipe, the condenser merging solenoid valve is closed and the condenser-to-evaporator expansion valve is opened, so that the first reheat coil alone constitutes the condenser, and the output end of the second reheat coil is connected to the input end of the evaporator, and the second reheat coil constitutes a part of the evaporator.

[0008] Furthermore, it also includes a controller, the condenser merging solenoid valve and the condenser-to-evaporator expansion valve are electrically connected to the controller, and the condenser merging solenoid valve and the condenser-to-evaporator expansion valve are configured to be opened or closed under the control of the controller.

[0009] Furthermore, it also includes a first sensor electrically connected to the controller, wherein the first sensor is used to detect the water temperature in the water supply pipe or the opening and closing state of the water inlet valve on the water supply pipe; the controller controls the opening and closing state of the condenser combined solenoid valve and the condenser-to-evaporator expansion valve according to the detection result of the first sensor.

[0010] Furthermore, the air supply end of the air duct is provided with a first temperature sensor and a humidity sensor electrically connected to the controller; the output end of the plate heat exchanger is connected to a first electronic expansion valve, the output end of the condenser is connected to a second electronic expansion valve, the output ends of the first electronic expansion valve and the second electronic expansion valve are connected in parallel to the input end of the evaporator; the first electronic expansion valve and the second electronic expansion valve are both electrically connected to the controller.

[0011] Furthermore, the output ends of the first electronic expansion valve and the second electronic expansion valve are both provided with a one-way valve.

[0012] Furthermore, the output end of the compressor is connected to a three-way valve, one end of the three-way valve is connected to the plate heat exchanger through a third electronic expansion valve, and the other end of the three-way valve is connected to the condenser through a fourth electronic expansion valve.

[0013] Furthermore, the output end of the compressor is provided with a second temperature sensor and a first pressure sensor electrically connected to the controller, and the input end of the compressor is provided with a third temperature sensor and a second pressure sensor electrically connected to the controller.

[0014] Furthermore, the water outlet end of the plate heat exchanger is connected to a first liquid outlet pipe, the water outlet end of the coil heat exchanger is connected to a second liquid outlet pipe, and both the first liquid outlet pipe and the second liquid outlet pipe are provided with proportional regulating valves.

[0015] Furthermore, the number of heat exchange pipes of the first reheat coil is less than or equal to the number of heat exchange pipes of the second reheat coil, and the sum of the number of heat exchange pipes of the first reheat coil and the number of heat exchange pipes of the second reheat coil is less than or equal to the number of heat exchange pipes of the evaporator.

[0016] Furthermore, it also includes a wet film humidifier, which is arranged in the air duct and located between the condenser and the fan.

[0017] The dual-cold-source fresh air dehumidification system designed by the present invention takes into account the stable operation of both water- and water-free conditions by setting two reheat coils in parallel and dynamically switching their combination configuration according to the availability of water supply, thereby effectively improving the reliability and stability of the system. At the same time, the system can choose to use the water inlet pipeline sensor / valve or the compressor suction pressure to automatically determine the water supply situation according to actual needs, and no matter which judgment method is used, the present invention can effectively prevent excessive accumulation or deficiency of refrigerant in the condenser, ensure stable operation of the system, and enhance user experience. In addition, since the switching of the reheat coil combination configuration can be achieved by opening and closing two valves, the system does not require complex software control, thereby simplifying the system structure and reducing control costs. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] Figure 1 This is a structural principle diagram of a dual cold source fresh air dehumidification system provided in a ratio in this application.

[0019] Figure 2 It is a structural principle diagram of the dual cold source fresh air dehumidification system provided in an embodiment of the present application.

[0020] Among them: compressor 10, plate heat exchanger 20, first electronic expansion valve 21, first liquid outlet pipe 22, one-way valve 23, third electronic expansion valve 24, fourth electronic expansion valve 25, air duct 30, coil heat exchanger 31, second electronic expansion valve 311, second liquid outlet pipe 312, evaporator 32, condenser 33, fan 34, air filter 35, wet film humidifier 36, water supply pipe 40, first reheat coil 50, second reheat coil 60, condenser combined solenoid valve 70, condenser to evaporator expansion valve 80, proportional control valve 90, first sensor 91, first temperature sensor 92, humidity sensor 93, second temperature sensor 94, first pressure sensor 95, third temperature sensor 96, second pressure sensor 97. DETAILED DESCRIPTION

[0021] The preferred embodiments of the present invention are described below in conjunction with the accompanying drawings. It should be understood that the preferred embodiments described herein are only used to illustrate and explain the present invention, and are not used to limit the present invention.

[0022] like Figure 1 As shown, Figure 1 The structural principle diagram of the dual-cold source fresh air dehumidification system provided by a pair of ratios is shown, which includes a surface cooler coil, a compressor, an evaporator, a condenser, a plate heat exchanger and a throttling device; generally speaking, the condenser and the evaporator contain a large number of energy exchange heat exchange pipelines, and the number of heat exchange pipelines of the condenser is usually greater than or equal to the number of heat exchange pipelines of the evaporator; since the surface cooler coil is set on the air inlet side of the condenser for precooling the air, the size of the reheat coil (condenser) can be reduced accordingly, and the number of its heat exchange pipelines can also be less than the number of heat exchange pipelines of the evaporator. However, this design of reducing the size of the condenser also brings some problems: a smaller condenser means that the heat exchange pipeline has a smaller diameter and a relatively longer length, which makes it easy for the refrigerant to accumulate and liquefy in it, resulting in a lack of fluorine in the system, and eventually triggering the low-pressure side alarm of the compressor. In addition, due to the presence of the plate heat exchanger, only half of the refrigerant flows through the reheat coil, which further exacerbates the trend of refrigerant liquefaction. In order to make up for the insufficient cooling capacity caused by the reduction in the size of the condenser, the system needs to increase the refrigerant charge. However, when the cooling water supply is interrupted, the increased refrigerant charge will cause the pressure on the high-pressure side of the compressor to increase, thereby triggering a high-pressure alarm. Therefore, the dual-cold source fresh air dehumidification system provided in the comparative example has obvious defects: it can only work when the cooling water supply is normal, and once the cooling water supply is interrupted, the system will stop working due to the high-pressure alarm, and cannot meet actual needs.

[0023] like Figure 2As shown, the dual cold source fresh air dehumidification system described in this embodiment includes a compressor 10, a plate heat exchanger 20, an air duct 30 and a water supply pipe 40 for connecting to an external cooling water source, and a coil heat exchanger 31, an evaporator 32, a condenser 33 and a fan 34 are sequentially arranged in the air duct 30; the water inlet ends of the plate heat exchanger 20 and the coil heat exchanger 31 are connected to the external cooling water source through the water supply pipe 40; the output end of the compressor 10 is connected to the plate heat exchanger 20 in one way and to the condenser 33 in the other way; the output end of the condenser 33 and the output end of the plate heat exchanger 20 are both connected to the input end of the evaporator 32, and the output end of the evaporator 32 is connected to the input end of the compressor 10.

[0024] Specifically, in the dehumidification mode, the compressor 10 is started to compress the refrigerant into a high-temperature and high-pressure gas. This high-temperature and high-pressure gas refrigerant is divided into two paths. One path directly enters the condenser 33, exchanges heat with the fresh air in the air duct 30, releases part of the heat, and condenses into a medium-temperature and high-pressure liquid. The other path enters the plate heat exchanger 20, exchanges heat with the cooling water, releases part of the heat, and is also converted into a medium-temperature and high-pressure liquid. At this time, the two paths of medium-temperature and high-pressure liquids meet at the inlet of the evaporator 32, and enter the evaporator after throttling and reducing the pressure by the expansion valve. 32. In the evaporator 32, the refrigerant absorbs the heat of the fresh air and evaporates into a low-temperature and low-pressure gas state, that is, the water vapor in the fresh air passing through the evaporator 32 condenses into dew to complete dehumidification. The fresh air after dehumidification and cooling continues to flow and enters the condenser 33. In the condenser 33, the fresh air absorbs the heat released by the refrigerant and the temperature is increased. Finally, the heated fresh air is sent into the room by the fan 34 to ensure the stability of the indoor temperature and humidity, and the low-temperature and low-pressure refrigerant vapor in the evaporator 32 is sucked by the compressor 10 to start the next cycle. In this process, the water supply pipe 40 is connected to the external cooling water source, one way enters the plate heat exchanger 20 to exchange heat with the refrigerant, and the other way enters the coil heat exchanger 31 to pre-cool the fresh air and reduce its temperature. Then the pre-cooled fresh air enters the evaporator 50 to further reduce the temperature and humidity, and achieve the dehumidification effect. The pre-cooling of the fresh air can reduce the dehumidification load of the evaporator 50 and improve the energy efficiency of the system.

[0025] A first reheat coil 50 and a second reheat coil 60 are arranged in parallel in the air duct 30 , and a condenser merging solenoid valve 70 and a condenser-to-evaporator expansion valve 80 are arranged between the first reheat coil 50 and the second reheat coil 60 .

[0026] When there is no water supply in the water supply pipe 40, the condenser combined solenoid valve 70 is opened and the condenser-to-evaporator expansion valve 80 is closed, so that the first reheat coil 50 and the second reheat coil 60 are connected in parallel to form a condenser 33. Specifically, in the case of no water supply, since the plate heat exchanger 20 stops working, the refrigerant cannot be cooled by cooling water, and the exhaust pressure of the compressor 10 will increase. At this time, the first reheat coil 50 and the second reheat coil 60 connected in parallel are equivalent to increasing the effective heat exchange area of ​​the condenser 33. The larger heat exchange area provides more sufficient condensation space for the refrigerant, so that it can release heat and condense more effectively, thereby reducing the temperature and pressure of the refrigerant, which effectively alleviates the pressure increase trend on the high-pressure side of the compressor 10, avoids triggering a high-pressure alarm, and ensures that the system can continue to operate in the absence of water. In addition, the larger condensation area also improves the condensation efficiency, allowing the refrigerant to condense more quickly and fully. Even in the absence of cooling water, the system can maintain a certain dehumidification capacity, thereby ensuring the comfort of the indoor environment.

[0027] When water is supplied to the water supply pipe 40, the condenser combined solenoid valve 70 is closed and the condenser-to-evaporator expansion valve 80 is opened, so that the first reheat coil 50 alone constitutes the condenser 33, and the output end of the second reheat coil 60, the second reheat coil 60 constitutes a part of the evaporator 32. Specifically, in the case of water supply, since the participation of cooling water shares part of the refrigeration load, the heat exchange area required by the condenser 33 is relatively small, so only the first reheat coil 50 is needed to meet the condensation demand. At the same time, compared with the first reheat coil 50 and the second reheat coil 60 jointly constituting the condenser 33 in the absence of water, when the first reheat coil 50 is used alone as the condenser 33, its coil length is shorter, that is, the shorter coil length can effectively avoid the accumulation and liquefaction of the refrigerant, thereby preventing the compressor 10 from triggering the low-pressure side alarm. In addition, after the second reheat coil 60 is connected in series with the evaporator 32, the effective heat exchange area of ​​the evaporator 32 is increased, that is, the larger evaporation heat exchange area enables the refrigerant to absorb more heat and evaporate into a low-temperature and low-pressure gas, thereby absorbing more moisture from the fresh air, significantly improving the dehumidification efficiency and effectively reducing the indoor humidity.

[0028] In this embodiment, the number of heat exchange pipes of the first reheat coil 50 is less than or equal to the number of heat exchange pipes of the second reheat coil 60, and the sum of the number of heat exchange pipes of the first reheat coil 50 and the number of heat exchange pipes of the second reheat coil 60 is less than or equal to the number of heat exchange pipes of the evaporator 32.

[0029] In addition, it should be noted that, in this embodiment, the first reheat coil 50 and the second reheat coil 60 are used as examples for explanation, but the present invention is not limited to this. In other embodiments, a third reheat coil, a fourth reheat coil, or even more may be provided. The core of the present invention is that by controlling the combination of the valve and the reheat coil, the effective heat exchange area of ​​the condenser and the evaporator is dynamically adjusted according to the water supply state of the water supply pipe 40. Specifically, when there is no water supply, part or all of the reheat coils are connected in parallel to form a condenser, and the total heat exchange area thereof should be greater than or equal to the heat exchange area of ​​the evaporator; when there is water supply, part of the reheat coils constitutes a condenser, and the heat exchange area thereof should be less than or equal to the heat exchange area of ​​the evaporator, and the remaining reheat coils are connected in series with the evaporator to jointly increase the heat exchange area of ​​the evaporator. Therefore, which configuration method is selected depends on the specific system design and performance requirements. For example, if the dehumidification performance is required to be high, more reheat coils can be connected in series with the evaporator to increase the evaporation area.

[0030] In some embodiments, Figure 2 As shown, a controller (not shown) is also included, and the condenser combined solenoid valve 70 and the condenser-to-evaporator expansion valve 80 are both electrically connected to the controller, and the condenser combined solenoid valve 70 and the condenser-to-evaporator expansion valve 80 are both configured to be opened or closed under the control of the controller. In this embodiment, the controller realizes automatic control of the condenser combined solenoid valve 70 and the condenser-to-evaporator expansion valve 80 without manual intervention, and the controller automatically controls the opening and closing states of the two valves according to the current working conditions of the system, especially whether there is water supply in the water supply pipe 40, thereby dynamically adjusting the combination configuration of the first reheat coil 50 and the second reheat coil 60, so that the system is always kept in the best working state.

[0031] In some embodiments, Figure 2 As shown, it also includes a first sensor 91 electrically connected to the controller. The controller controls the opening and closing states of the condenser merging solenoid valve 70 and the condenser-to-evaporator expansion valve 80 according to the detection result of the first sensor 91.

[0032] In this embodiment, the first sensor 91 is used to detect the water temperature in the water supply pipe 40; by real-time monitoring of the water temperature, the controller can determine whether there is water flowing in the water supply pipe 40. For example, when the water temperature is close to the ambient temperature, it indicates that there is no water flowing in the water supply pipe 40 or the water flow is very slow. At this time, the controller will switch the system to the waterless mode, that is, the condenser combined solenoid valve 70 is opened, and the condenser-to-evaporator expansion valve 80 is closed. On the contrary, when the water temperature is significantly lower than the ambient temperature, it indicates that there is water flowing in the water supply pipe 40, and the controller will switch the system to the water mode, that is, the condenser combined solenoid valve 70 is closed, and the condenser-to-evaporator expansion valve 80 is opened.

[0033] In another example, the first sensor 91 is used to detect the open and closed state of the water inlet valve on the water supply pipe 40; thus, by monitoring the valve state, the controller can more accurately determine whether the water supply pipeline is connected. Of course, the above two detection methods can be used alone or in combination to improve the reliability of the judgment. For example, even if the water inlet valve is in an open state, if the temperature sensor detects that the water temperature is close to the ambient temperature, it indicates that the water flow in the water supply pipe 40 is unstable, or even intermittent water outage occurs. At this time, the controller will still switch the system to the waterless mode to avoid triggering an alarm due to lack of water.

[0034] In some embodiments, Figure 2 As shown, the air supply end of the air duct 30 is provided with a first temperature sensor 92 and a humidity sensor 93 electrically connected to the controller; the output end of the plate heat exchanger 20 is connected to the first electronic expansion valve 21, the output end of the condenser 33 is connected to the second electronic expansion valve 311, and the output ends of the first electronic expansion valve 21 and the second electronic expansion valve 311 are connected in parallel to the input end of the evaporator 32; the first electronic expansion valve 21 and the second electronic expansion valve 311 are both electrically connected to the controller.

[0035] In specific implementation, the controller serves as the control center of the system, and is used to receive data from various sensors, and control the operating status of various components according to preset programs or user-set parameters. When working, the first temperature sensor 92 and the humidity sensor 93 monitor the supply air temperature and humidity in real time, and transmit the data to the controller. The controller determines whether the current temperature and humidity meet the set values ​​based on the sensor data and preset parameters. If the temperature and humidity are too high or too low, the controller will adjust the opening of the first electronic expansion valve 21 and the second electronic expansion valve 311, thereby accurately controlling the refrigerant flow entering the evaporator 32, and finally achieving accurate control of the supply air temperature and humidity.

[0036] In this embodiment, if Figure 2 As shown, the output ends of the first electronic expansion valve 21 and the second electronic expansion valve 311 are both provided with a check valve 23. The check valve 23 allows the refrigerant to flow from the first electronic expansion valve 21 and the second electronic expansion valve 311 to the evaporator 32, but prevents the refrigerant from flowing back from the evaporator 32. Especially in the case of compressor shutdown or system pressure fluctuation, the check valve can effectively prevent the refrigerant from flowing back to the compressor 10, protecting the compressor 10 from damage by liquid hammer.

[0037] In some embodiments, Figure 2As shown, the output end of the compressor 10 is connected to a three-way valve, one end of the three-way valve is connected to the plate heat exchanger 20 through the third electronic expansion valve 24, and the other end is connected to the condenser 33 through the fourth electronic expansion valve 25. In conjunction with the third electronic expansion valve 24 and the fourth electronic expansion valve 25, the refrigerant flow to the plate heat exchanger 20 and the condenser 33 can be more accurately controlled, thereby achieving more accurate temperature and humidity control.

[0038] In some embodiments, Figure 2 As shown, the output end of the compressor 10 is provided with a second temperature sensor 94 and a first pressure sensor 95 electrically connected to the controller, and the input end of the compressor 10 is provided with a third temperature sensor 96 and a second pressure sensor 97 electrically connected to the controller. The exhaust temperature, exhaust pressure, suction temperature and suction pressure of the compressor 10 are monitored in real time by the second temperature sensor 94, the first pressure sensor 95, the third temperature sensor 96 and the second pressure sensor 97, and the data are transmitted to the controller. In combination with the preset safety threshold, it is determined whether the operating state of the compressor 10 is normal. If the compressor exhaust temperature is too high, the exhaust pressure is too high, the suction temperature is too low or the suction pressure is too low, the controller will issue a warning signal to remind the user to conduct inspection and maintenance in time. At the same time, if the operating state of the compressor 10 exceeds the safety range, for example, the exhaust temperature exceeds the maximum limit, the controller will issue a command to stop the operation of the compressor 10 to avoid overheating and damage of the compressor 10 and improve the reliability of the system.

[0039] In this embodiment, the controller can also detect the exhaust pressure and suction pressure of the compressor 10 according to the first pressure sensor 95 and the second pressure sensor 97, and control the opening and closing of the condenser combined solenoid valve 70 and the condenser-to-evaporator expansion valve 80. For example, when the suction pressure is too low, it may indicate that the system refrigerant is insufficient. At this time, the controller can control the condenser combined solenoid valve 70 to close and the condenser-to-evaporator expansion valve 80 to open, so that the first reheat coil 50 alone constitutes the condenser 33; and when the exhaust pressure is too high, it may indicate that the condenser 33 has poor heat dissipation. At this time, the controller can control the condenser combined solenoid valve 70 to open and the condenser-to-evaporator expansion valve 80 to close, so that the first reheat coil 50 and the second reheat coil 60 are connected in parallel to form the condenser 33 to enhance heat dissipation, thereby reducing the exhaust pressure.

[0040] In some embodiments, Figure 2As shown, the water outlet of the plate heat exchanger 20 is connected to the first liquid outlet pipe 22, and the water outlet of the coil heat exchanger 31 is connected to the second liquid outlet pipe 312. The first liquid outlet pipe 22 and the second liquid outlet pipe 312 are both provided with a proportional regulating valve 90. The proportional valve 90 can accurately adjust the valve opening, so as to achieve accurate control of the cooling water flow through the plate heat exchanger 20 and the coil heat exchanger 31. Assuming that the indoor temperature is too high and the supply air temperature needs to be lowered, at this time, the proportional valve 90 on the first liquid outlet pipe 22 can be controlled to increase the opening, increase the cooling water flow through the plate heat exchanger 20, reduce the refrigerant temperature, and thus reduce the supply air temperature; and assuming that the indoor humidity is too high and the dehumidification effect needs to be enhanced, at this time, the proportional valve 90 on the second liquid outlet pipe 312 can be controlled to decrease the opening, reduce the cooling water flow through the coil heat exchanger 31, and increase the refrigerant temperature entering the evaporator 50, thereby enhancing the dehumidification effect. In this way, different from the extensive temperature and humidity adjustment method of the double condensation dehumidification system in the related art, a proportional valve 90 is set on the first liquid outlet pipe 22 and the second liquid outlet pipe 312, which can achieve precise control of the cooling water flow rate, giving the system more precise control over the supply air temperature and humidity, and effectively improving the user experience.

[0041] In some embodiments, Figure 2 As shown, an air filter 35 is provided on the air inlet side of the coil heat exchanger 31. In actual implementation, the provision of the air filter 35 is a simple but effective measure, which can effectively filter out dust, pollen, PM2.5 and other particles entering the air, thereby improving the quality of the air entering the air duct 30 and providing the user with cleaner fresh air. In addition, the filtered clean air can reduce the dust and impurities entering the system, thereby protecting the service life of various components in the air duct 30 and reducing maintenance costs.

[0042] In some embodiments, Figure 2 As shown, a wet film humidifier 36 is also included, which is arranged in the air duct 30 and between the condenser 33 and the fan 34. In this embodiment, the wet film humidifier 36 can evenly distribute water on the surface of the wet film to form a large evaporation area with high humidification efficiency, so as to effectively increase the indoor humidity, actively alleviate the problem of indoor air dryness, and provide users with a more comfortable indoor environment.

[0043] The dual-cold-source fresh air dehumidification system provided in this embodiment takes into account the stable operation of both water- and water-free conditions by setting two reheat coils in parallel and dynamically switching their combination configuration according to the presence or absence of water supply, thereby effectively improving the reliability and stability of the system. At the same time, the system can choose to use the water inlet pipeline sensor / valve or the compressor suction pressure to automatically determine the water supply situation according to actual needs, and no matter which judgment method is used, the present invention can effectively prevent excessive accumulation or deficiency of refrigerant in the condenser, ensure stable operation of the system, and improve user experience. In addition, since the switching of the reheat coil combination configuration can be achieved by opening and closing two valves, the system does not require complex software control, thereby simplifying the system structure and reducing control costs.

[0044] In the description of the present invention, it should be noted that the terms "vertical", "up", "down", "horizontal", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention 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 cannot be understood as a limitation on the present invention.

[0045] In the description of the present invention, it is also necessary to explain that, unless otherwise clearly specified and limited, the terms "set", "install", "connect", and "connect" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection, or it can be indirectly connected through an intermediate medium, or it can be the internal communication of two elements. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0046] Finally, it should be noted that the above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Although the present invention has been described in detail with reference to the aforementioned embodiments, those skilled in the art can still modify the technical solutions described in the aforementioned embodiments or replace some of the technical features therein by equivalents. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention shall be included in the protection scope of the present invention.

Claims

1. A dual-cold-source fresh air dehumidification system, comprising a compressor, a plate heat exchanger, an air duct and a water supply pipe for connecting an external cooling water source, wherein 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 connected to the external cooling water source through the water supply pipe; the output end of the compressor is connected to the plate heat exchanger in one way and to the condenser in the other way; the output end of the condenser and the output end of 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: A first reheat coil and a second reheat coil are arranged in parallel in the air duct, and a condenser merging solenoid valve and a condenser-to-evaporator expansion valve are arranged between the first reheat coil and the second reheat coil; wherein, when there is no water supply in the water supply pipe, the condenser merging solenoid valve is opened and the condenser-to-evaporator expansion valve is closed, so that the first reheat coil and the second reheat coil are connected in parallel to form the condenser together; when there is water supply in the water supply pipe, the condenser merging solenoid valve is closed and the condenser-to-evaporator expansion valve is opened, so that the first reheat coil alone forms the condenser, and the output end of the second reheat coil is connected to the input end of the evaporator, and the second reheat coil forms a part of the evaporator.

2. The dual cold source fresh air dehumidification system according to claim 1 is characterized in that: It also includes a controller, and the condenser merging solenoid valve and the condenser-to-evaporator expansion valve are both electrically connected to the controller, and the condenser merging solenoid valve and the condenser-to-evaporator expansion valve are both configured to be opened or closed under the control of the controller.

3. The dual cold source fresh air dehumidification system according to claim 2 is characterized in that: It also includes a first sensor electrically connected to the controller, which is used to detect the water temperature in the water supply pipe or the opening and closing state of the water inlet valve on the water supply pipe; the controller controls the opening and closing state of the condenser combined solenoid valve and the condenser-to-evaporator expansion valve according to the detection result of the first sensor.

4. The dual cold source fresh air dehumidification system according to claim 2, characterized in that: The air supply end of the air duct is provided with a first temperature sensor and a humidity sensor electrically connected to the controller; the output end of the plate heat exchanger is connected to a first electronic expansion valve, the output end of the condenser is connected to a second electronic expansion valve, the output ends of the first electronic expansion valve and the second electronic expansion valve are connected in parallel to the input end of the evaporator; the first electronic expansion valve and the second electronic expansion valve are both electrically connected to the controller.

5. The dual cold source fresh air dehumidification system according to claim 4 is characterized in that: The output ends of the first electronic expansion valve and the second electronic expansion valve are both provided with a one-way valve.

6. According to the dual cold source fresh air dehumidification system of claim 4, the output end of the compressor is connected to a three-way valve, one end of the three-way valve is connected to the plate heat exchanger through a third electronic expansion valve, and the other end is connected to the condenser through a fourth electronic expansion valve.

7. The dual cold source fresh air dehumidification system according to claim 2, characterized in that: The output end of the compressor is provided with a second temperature sensor and a first pressure sensor electrically connected to the controller, and the input end of the compressor is provided with a third temperature sensor and a second pressure sensor electrically connected to the controller.

8. The dual cold source fresh air dehumidification system according to any one of claims 1 to 7, characterized in that: The water outlet end of the plate heat exchanger is connected to a first liquid outlet pipe, and the water outlet end of the coil heat exchanger is connected to a second liquid outlet pipe. The first liquid outlet pipe and the second liquid outlet pipe are both provided with proportional regulating valves.

9. The dual cold source fresh air dehumidification system according to any one of claims 1 to 7, characterized in that: The number of heat exchange pipes of the first reheat coil is less than or equal to the number of heat exchange pipes of the second reheat coil, and the sum of the number of heat exchange pipes of the first reheat coil and the number of heat exchange pipes of the second reheat coil is less than or equal to the number of heat exchange pipes of the evaporator.

10. The dual cold source fresh air dehumidification system according to any one of claims 1 to 7, characterized in that: It also includes a wet film humidifier, which is arranged in the air duct and located between the condenser and the fan.

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