Double-cold-source fresh air dehumidifier

Abstract

The invention relates to a double-cold-source fresh air dehumidifier which comprises a compressor, a plate heat exchanger, an air duct and a water supply pipe used for being connected with an external cooling water source, and a coil heat exchanger, an evaporator, a condenser and a fan are sequentially arranged in the air duct. According to the double-cold-source fresh air dehumidifier designed by the invention, a surface cooling proportional valve and a plate exchange proportional valve on a drainage pipeline are omitted, so that the material cost and the installation difficulty are greatly reduced, the installation is more convenient and faster, the required installation space is reduced, and the miniaturization of a machine body is facilitated. Besides, the condenser can automatically adjust the heat exchange area according to the water supply state, faults or performance reduction of the system under the condition of water shortage are effectively avoided, the system adaptability is enhanced, it is ensured that the system can normally work and keep excellent dehumidification performance no matter whether an external cooling water source exists or not, and the energy consumption is reduced. And finally, a more stable and energy-saving dehumidification effect is provided under different environmental conditions, and the user experience is improved.

Description

Technical Field

[0001] The invention relates to the technical field of air dehumidification, in particular to a double-cold-source fresh air dehumidifier. 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] In order to overcome the limitations of traditional fresh air systems, dual cold source technology has been introduced into the fresh air system. Dual cold source technology refers to the use of two cold sources with different temperatures (such as cooling water and chilled water) to process fresh air, which can achieve precise control of fresh air temperature and humidity and improve energy efficiency.

[0004] However, the existing dual-cooling source fresh air system still has room for improvement in terms of temperature and humidity control accuracy, energy efficiency, and user experience. For example, the proportion of chilled water is not accurately controlled, resulting in large fluctuations in the air supply temperature and the inability to achieve precise temperature control. In addition, 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. Summary of the invention

[0005] In order to solve the above problems, the present invention provides a dual-cold-source fresh air dehumidifier which simplifies the system structure and reduces the cost.

[0006] In order to achieve the above-mentioned purpose, the dual-cold source fresh air dehumidifier 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, and 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 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, and 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 output end of the evaporator is connected to the input end of the compressor; the water supply pipe is connected to the water inlet end of the coil heat exchanger through a total water ratio regulating valve, and the water outlet end of the coil heat exchanger is connected to the water inlet end of the plate heat exchanger through a pipeline.

[0007] Furthermore, 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 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, and the total water ratio regulating valve, the condenser merging solenoid valve and the condenser-to-evaporator expansion valve are all electrically connected to and controlled by 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, and controls the valve opening of the total water ratio regulating valve.

[0010] Furthermore, a second sensor electrically connected to the controller is provided at the air supply end of the air duct, and the second sensor is used to detect the temperature and humidity of the air supplied by the air duct.

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

[0013] Furthermore, an air filter is provided on the air inlet side of the coil heat exchanger.

[0014] Furthermore, it also includes a wet film humidifier, which is arranged in the air duct and located between the condenser and the fan.

[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] The dual-cold-source fresh air dehumidifier designed by the present invention eliminates the surface cooling proportional valve and plate exchange proportional valve on the drainage pipeline, thereby greatly reducing material costs and installation difficulty, making installation more convenient, and reducing the required installation space, which is conducive to the miniaturization of the machine body. In addition, the condenser can automatically adjust the heat exchange area according to the water supply status, effectively avoiding system failure or performance degradation in the case of water shortage, enhancing the system adaptability, ensuring that it can work normally and maintain excellent dehumidification performance regardless of the presence or absence of an external cooling water source, and ultimately providing a more stable and energy-saving dehumidification effect under different environmental conditions, improving user experience. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] Figure 1 This is a structural principle diagram of a dual cold source fresh air dehumidification system provided in a ratio in this application.

[0018] Figure 2 It is a structural schematic diagram of a dual-cold source fresh air dehumidifier provided in an embodiment of the present application.

[0019] Figure 3 It is a structural principle diagram of a dual cold source fresh air dehumidifier provided in an embodiment of the present application.

[0020] Among them: compressor 10, plate heat exchanger 20, first electronic expansion valve 21, one-way valve 22, air duct 30, coil heat exchanger 31, evaporator 32, condenser 33, second electronic expansion valve 331, fan 34, air filter 35, wet film humidifier 36, water supply pipe 40, total water ratio regulating valve 41, first reheat coil 50, second reheat coil 60, condenser merging solenoid valve 70, condenser to evaporator expansion valve 80, controller 90, first sensor 91, second sensor 92, first temperature sensor 93, first pressure sensor 94, second temperature sensor 95, second pressure sensor 96. 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 1A pair of proportional dual-cold source fresh air dehumidification system structural principle diagrams are shown, which include surface cooler coil, compressor, evaporator, condenser, plate heat exchanger and throttling device. On the one hand, the outlet ends of the surface cooler coil and the plate heat exchanger are both provided with drainage pipes, and the surface cooler proportional valve and the plate heat exchanger proportional valve are respectively provided on the corresponding drainage pipes, that is, when this type of dual-cold source fresh air dehumidification system is working, the cooling water flow through the plate heat exchanger and the surface cooler coil can be adjusted by controlling the surface cooler proportional valve and the plate heat exchanger proportional valve respectively, thereby adjusting the refrigerant temperature and realizing fine adjustment of the supply air temperature; however, since this type of dehumidification system is usually installed in the ceiling of the building, the proportional valve is relatively expensive, the corresponding components and pipelines are cumbersome to install, and occupy a large space, it is difficult to install in practice. On the other hand, the condenser and the evaporator usually 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 comparative example sets a surface cooler coil on the air inlet side of the condenser for pre-cooling 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: first, 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 therein, resulting in a lack of fluorine in the system, and eventually triggering the low-pressure side alarm of the compressor; secondly, due to the presence of the plate heat exchanger, only half of the refrigerant flows through the reheat coil, which further aggravates 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 the 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] The dual cold source fresh air dehumidifier described in this embodiment is described in detail below with reference to the accompanying drawings.

[0024] like Figure 2 (The top panel and part of the side panel of the chassis are removed in the picture), Figure 3As shown, the dual cold source fresh air dehumidifier 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. A coil heat exchanger 31, an evaporator 32, a condenser 33 and a fan 34 are sequentially arranged in the air duct 30. 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 plate heat exchanger 20 is connected to the first electronic expansion valve 21, and the output end of the condenser 33 is connected to the second electronic expansion valve 331. The output ends of the first electronic expansion valve 21 and the second electronic expansion valve 331 are connected in parallel to the input end of the evaporator 32; the output end of the evaporator 32 is connected to the input end of the compressor 10; the water supply pipe 40 is connected to the water inlet end of the coil heat exchanger 31 through a total water ratio regulating valve 41, and the water outlet end of the coil heat exchanger 31 is connected to the water inlet end of the plate heat exchanger 20 through a pipeline.

[0025] Specifically, in the dehumidification mode, the compressor 10 is started to compress the refrigerant into a high-temperature and high-pressure gas. The 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 are condensed through the first electronic expansion valve 21 and the second electronic expansion valve 331. After the pressure is reduced, the fresh air enters the evaporator 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, enters the coil heat exchanger 31 to pre-cool the fresh air and reduce its temperature, and then enters the plate heat exchanger 20 to exchange heat with the refrigerant to achieve pre-cooling of the air entering the air duct 30. Then the pre-cooled fresh air enters the evaporator 32 to further reduce the temperature and humidity, and achieve the dehumidification effect. The pre-cooled fresh air can reduce the dehumidification load of the evaporator 32 and improve the energy efficiency of the system.

[0026] Among them, the total water ratio regulating valve 41 provided on the water supply pipe 40 can control the cooling water flow entering the plate heat exchanger 20. The greater the cooling water flow, the greater the degree of cooling of the refrigerant in the plate heat exchanger 20, resulting in a lower temperature of the refrigerant entering the evaporator 32, thereby reducing the enthalpy value of the air supply and ultimately reducing the air supply temperature; conversely, reducing the cooling water flow can increase the air supply temperature. Therefore, by adjusting the total water ratio regulating valve 41, the enthalpy value change of the air supply can be accurately controlled to achieve precise control of the temperature. In addition, the first electronic expansion valve 21 and the second electronic expansion valve 331 can control the refrigerant flow entering the evaporator 32 and the condenser 33 respectively. Increasing the refrigerant flow entering the evaporator 32 can enhance the effect of evaporation heat absorption, thereby reducing the absolute water content of the air supply and reducing the humidity (enhancing the dehumidification effect). Therefore, by adjusting the first electronic expansion valve 21 and the second electronic expansion valve 331, the change of the absolute water content of the air supply can be accurately controlled to achieve precise control of the humidity.

[0027] In summary, precise control of the supply air temperature and humidity can be achieved through the total water proportional regulating valve 41, the first electronic expansion valve 21 and the second electronic expansion valve 331, eliminating the surface cooling proportional valve and the plate change proportional valve on the drainage pipeline, thereby greatly reducing material costs and installation difficulty, making installation more convenient, and reducing the required installation space, which is conducive to the miniaturization of the fuselage.

[0028] In this embodiment, 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; wherein, when there is no water supply in the water supply pipe 40, the condenser merging 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 jointly constitute the condenser 33; when there is water supply in the water supply pipe 40, the condenser merging solenoid valve 70 is closed and the condenser-to-evaporator expansion valve 80 is opened, so that the first reheat coil 50 and the second reheat coil 60 constitute the condenser 33 alone, and the output end of the second reheat coil 60 is connected to the input end of the evaporator 32 to jointly constitute the evaporator 32.

[0029] With this structural design, 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.

[0030] 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 is connected to the input end of the evaporator 32, and the second reheat coil 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.

[0031] 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.

[0032] 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 its total heat exchange area should be greater than the heat exchange area of ​​the evaporator; when there is water supply, part of the reheat coils constitutes a condenser, and its heat exchange area should be less than 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 selected to be connected in series with the evaporator to increase the evaporation area.

[0033] In some embodiments, Figure 2 , Figure 3 As shown, the controller 90 is also included, and the total water ratio regulating valve 41, the condenser merging solenoid valve 70 and the condenser-to-evaporator expansion valve 80 are all electrically connected to the controller 90 and controlled by the controller 90. In this embodiment, the controller 90 realizes the automatic control of the condenser merging solenoid valve 70 and the condenser-to-evaporator expansion valve 80 without manual intervention, and the controller 90 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, so as to dynamically adjust 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.

[0034] In this embodiment, if Figure 2 , Figure 3 As shown, it also includes a first sensor 91 electrically connected to the controller 90, and the first sensor 91 is used to detect the water temperature in the water supply pipe 40 or the opening and closing state of the water inlet valve on the water supply pipe 40; the controller 90 controls the opening and closing state 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, and controls the valve opening of the total water ratio regulating valve 41.

[0035] In specific implementation, the controller 90 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.

[0036] In this way, by detecting the water temperature in the water supply pipe 40, the controller 90 can adjust the opening of the total water ratio regulating valve 41 according to the actual water temperature, and control the cooling water flow entering the plate heat exchanger 20, so as to more accurately control the temperature of the refrigerant and optimize the cooling efficiency and dehumidification effect of the system. For example, when the water temperature is high, the cooling water flow can be increased to enhance the cooling effect; when the water temperature is low, the cooling water flow can be reduced to avoid overcooling and save energy.

[0037] In addition, 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 90 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 90 will switch the system to the waterless mode (the condenser combined solenoid valve 70 is open, 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 90 will switch the system to the water mode (the condenser combined solenoid valve 70 is closed, and the condenser-to-evaporator expansion valve 80 is opened).

[0038] 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 90 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 90 will still switch the system to the waterless mode to avoid triggering an alarm due to lack of water.

[0039] In some embodiments, Figure 2 , Figure 3 As shown, the air supply end of the air duct 30 is provided with a second sensor 92 electrically connected to the controller 90, and the second sensor 92 is used to detect the temperature and humidity of the air supplied by the air duct 30. In this way, the second sensor 92 monitors the air supply temperature and humidity in real time, and transmits the data to the controller 90. The controller 90 determines whether the current temperature and humidity meet the set values ​​according to the sensor data and the preset parameters. If the temperature and humidity are too high or too low, the controller 90 will adjust the opening of the first electronic expansion valve 21 and the second electronic expansion valve 331, so as to accurately control the refrigerant flow entering the evaporator 32 or adjust the valve opening of the total water ratio regulating valve 41, and finally realize the precise control of the air supply temperature and humidity.

[0040] In some embodiments, Figure 2 , Figure 3As shown, the output ends of the first electronic expansion valve 21 and the second electronic expansion valve 331 are both provided with a check valve 22. The check valve 22 allows the refrigerant to flow from the electronic expansion valve (21, 331) to the evaporator 32, but prevents the refrigerant from flowing back from the evaporator 32. Especially when the compressor is shut down or the system pressure fluctuates, the check valve can effectively prevent the refrigerant from flowing back to the compressor 10, protecting the compressor 10 from damage caused by liquid hammer.

[0041] In some embodiments, Figure 2 , Figure 3 As shown, the output end of the compressor 10 is provided with a first temperature sensor 93 and a first pressure sensor 94 electrically connected to the controller 90, and the input end of the compressor 10 is provided with a second temperature sensor 95 and a second pressure sensor 96 electrically connected to the controller 90. The exhaust temperature, exhaust pressure, suction temperature and suction pressure of the compressor 10 are monitored in real time by the first temperature sensor 93, the first pressure sensor 94, the second temperature sensor 95 and the second pressure sensor 96, and the data are transmitted to the controller 90. 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 90 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 90 will issue an instruction to stop the operation of the compressor 10 to avoid overheating and damage of the compressor 10 and improve the reliability of the system.

[0042] In this embodiment, the controller 90 can also detect the exhaust pressure and suction pressure of the compressor 10 according to the first pressure sensor 94 and the second pressure sensor 96, 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 90 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 90 can open the condenser combined solenoid valve 70 and close the condenser-to-evaporator expansion valve 80, 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.

[0043] In some embodiments, Figure 2 , Figure 3As 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.

[0044] In some embodiments, Figure 2 , Figure 3 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.

[0045] The dual-cold source fresh air dehumidifier provided in this embodiment eliminates the surface cooling proportional valve and plate exchange proportional valve on the drainage pipeline, thereby greatly reducing material costs and installation difficulty, making installation more convenient, and reducing the required installation space, which is conducive to miniaturization of the machine body. In addition, the condenser can automatically adjust the heat exchange area according to the water supply status, effectively avoiding system failure or performance degradation in the case of water shortage, enhancing the system adaptability, ensuring that it can work normally and maintain excellent dehumidification performance regardless of whether there is an external cooling water source, and ultimately providing a more stable and energy-saving dehumidification effect under different environmental conditions, improving user experience.

[0046] 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.

[0047] 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.

[0048] 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 dehumidifier, 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, characterized in that: 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 plate heat exchanger is connected to the first electronic expansion valve, the output end of the condenser is connected to the 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 output end of the evaporator is connected to the input end of the compressor; the water supply pipe is connected to the water inlet end of the coil heat exchanger through a total water ratio regulating valve, and the water outlet end of the coil heat exchanger is connected to the water inlet end of the plate heat exchanger through a pipeline.

2. The dual cold source fresh air dehumidifier according to claim 1, 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.

3. The dual cold source fresh air dehumidifier according to claim 2, characterized in that: It also includes a controller, and the total water ratio regulating valve, the condenser merging solenoid valve and the condenser-to-evaporator expansion valve are all electrically connected to and controlled by the controller.

4. The dual cold source fresh air dehumidifier according to claim 3, 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, and controls the valve opening of the total water ratio regulating valve.

5. The dual cold source fresh air dehumidifier according to claim 3, characterized in that: The air supply end of the air duct is provided with a second sensor electrically connected to the controller, and the second sensor is used to detect the temperature and humidity of the air supplied by the air duct.

6. The dual cold source fresh air dehumidifier according to claim 2, 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.

7. The dual cold source fresh air dehumidifier according to claim 3, characterized in that: The output end of the compressor is provided with a first temperature sensor and a first pressure sensor electrically connected to the controller, and the input end of the compressor is provided with a second temperature sensor and a second pressure sensor electrically connected to the controller.

8. The dual cold source fresh air dehumidifier according to any one of claims 1 to 7, characterized in that: An air filter is arranged on the air inlet side of the coil heat exchanger.

9. The dual cold source fresh air dehumidifier 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.

10. The dual cold source fresh air dehumidifier according to any one of claims 2 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.

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