Dual-cold-source fresh air handling unit and air conditioner

Abstract

This utility model relates to the field of fresh air systems, providing a dual-source fresh air handling unit and air conditioner. The dual-source fresh air handling unit includes: a body, a total heat exchange core disposed within the body, a first water heat exchanger, a second water heat exchanger, a first refrigerant heat exchanger, a second refrigerant heat exchanger, a compressor unit, and a heat recovery heat exchanger. The total heat exchange core is disposed on the air inlet side of the body for heat exchange between fresh air and return air. A fresh air duct and a return air duct are formed within the body. Along the fresh air flow path, the first water heat exchanger, the first refrigerant heat exchanger, the second water heat exchanger, and the second refrigerant heat exchanger are arranged sequentially in the fresh air duct, and the heat recovery heat exchanger is disposed in the return air duct. The first refrigerant heat exchanger, the second refrigerant heat exchanger, the compressor unit, and the heat recovery heat exchanger are connected sequentially. A first regulating valve is provided between the heat recovery heat exchanger and the first refrigerant heat exchanger, and a second regulating valve is provided between the first refrigerant heat exchanger and the second refrigerant heat exchanger. This utility model can reduce energy consumption and achieve flexible control of the outlet air temperature.

Description

Technical Field

[0001] This utility model relates to the field of fresh air system technology, and in particular to a dual-cold-source fresh air unit and air conditioner. Background Technology

[0002] In the field of fresh air treatment, dual-source fresh air handling units, with their two independent cooling sources, can efficiently process fresh air. They not only achieve ventilation and air exchange between indoors and outdoors, ensuring indoor air quality, but also dehumidify through the cooling source, effectively improving the indoor humidity environment. Compared to traditional single-source fresh air handling units, their redundant dual-source design allows them to maintain some operational functions even in the event of a single cooling source failure, significantly improving system reliability.

[0003] However, current dual-source fresh air handling units still have some technical shortcomings in practical use: on the one hand, the system usually only focuses on the treatment of fresh air during operation, failing to effectively collect and reuse the waste heat carried by the indoor return air, resulting in this energy being directly discharged outdoors, causing unnecessary energy waste, which contradicts the current trend of energy conservation and environmental protection. On the other hand, in special scenarios such as the humid weather in southern China and the plum rain season, indoor environments not only require efficient dehumidification, but also precise control of the fresh air outlet temperature to avoid excessively low or high outlet temperatures affecting indoor comfort. However, existing dual-source fresh air handling units and combined systems of ordinary air conditioners and fresh air units often struggle to coordinate and regulate the cold source output and heat exchange process during dehumidification, making it difficult to accurately control the outlet temperature. Consequently, they cannot meet the usage requirements in such special scenarios, limiting the applicability of dual-source fresh air handling units. Utility Model Content

[0004] This utility model provides a dual-cold-source fresh air handling unit and air conditioner to solve the defects of existing fresh air systems that cannot effectively collect and reuse the waste heat of indoor return air during operation, resulting in some energy waste, and cannot accurately control the supply air temperature to meet the needs of different scenarios. It can improve the energy utilization of the fresh air handling unit during operation, reduce energy consumption, and achieve flexible control of the supply air temperature.

[0005] This utility model provides a dual-cooling-source fresh air handling unit, comprising: The machine body, a total heat exchange core disposed within the machine body, a first water heat exchanger, a second water heat exchanger, a first fluorine heat exchanger, a second fluorine heat exchanger, a compressor unit, and a heat recovery heat exchanger; The total heat exchange core is located on the air inlet side of the unit and is used for heat exchange between fresh air and return air; The machine body has a fresh air duct and a return air duct. Along the fresh air flow path, the first water heat exchanger, the first fluorine heat exchanger, the second water heat exchanger and the second fluorine heat exchanger are arranged in sequence in the fresh air duct, and the heat recovery heat exchanger is set in the return air duct. The first fluorine heat exchanger, the second fluorine heat exchanger, the compressor unit, and the heat recovery heat exchanger are connected in sequence. A first regulating valve is provided between the heat recovery heat exchanger and the first fluorine heat exchanger, and a second regulating valve is provided between the first fluorine heat exchanger and the second fluorine heat exchanger.

[0006] According to the present invention, a dual-cold-source fresh air handling unit has a first dehumidification mode. In the first dehumidification mode, the first fluorine heat exchanger and the heat recovery heat exchanger are used as evaporators, the second fluorine heat exchanger is used as a condenser, and the first regulating valve has a maximum opening.

[0007] According to the present invention, a dual-cold-source fresh air handling unit is provided, wherein the dual-cold-source fresh air handling unit has a cooling mode, wherein in the cooling mode, the first fluorine heat exchanger and the second fluorine heat exchanger are used as evaporators, the heat recovery heat exchanger is used as a condenser, and the second regulating valve has a maximum opening degree.

[0008] According to the present invention, a dual-cold-source fresh air handling unit is provided, wherein the dual-cold-source fresh air handling unit has a heating mode, wherein in the heating mode, the first fluorine heat exchanger and the second fluorine heat exchanger are used as condensers, the heat recovery heat exchanger is used as an evaporator, and the second regulating valve has a maximum opening degree.

[0009] According to the present invention, a dual-cold-source fresh air handling unit is provided, wherein both the first regulating valve and the second regulating valve are electronic expansion valves.

[0010] According to the present invention, a dual-cold-source fresh air handling unit is provided, wherein the air inlet side of the unit is provided with a fresh air inlet and a return air inlet, the air outlet side of the unit is provided with a fresh air outlet and a return air outlet, a supply fan connected to the fresh air outlet is provided in the fresh air duct, and an exhaust fan connected to the return air outlet is provided in the return air duct.

[0011] According to the present invention, a dual-cold-source fresh air handling unit is provided, wherein the unit body is provided with a water inlet and a water outlet, and the water inlet, the second water heat exchanger, the first water heat exchanger and the water outlet are connected in sequence by pipelines.

[0012] According to the present invention, a dual-cold-source fresh air handling unit is provided, wherein a solenoid valve is provided on the pipeline.

[0013] According to the present invention, a dual-cold-source fresh air handling unit is provided, wherein the compressor unit includes a compressor and a four-way reversing valve.

[0014] This utility model also provides an air conditioner, including the dual-source fresh air unit as described above.

[0015] This utility model provides a dual-source fresh air handling unit and air conditioner. By incorporating a total heat exchange core, it can utilize the heat from the return air to pre-treat the heat and humidity load of the fresh air. For example, in summer, the low temperature of the return air pre-lowers the fresh air temperature, while in winter, the high temperature of the return air pre-raises the fresh air temperature, thereby reducing the dehumidification and heat exchange load of subsequent heat exchangers. The heat recovery heat exchanger can recover the heat from the return air and, through piping connected to the first refrigerant heat exchanger and the compressor unit, introduce the waste heat into the refrigerant circulation system for reuse. Through this energy recovery and utilization, subsequent heat exchangers do not need to operate at full load, reducing the operating frequency of the compressor unit and decreasing unit power consumption. This fundamentally solves the problem of waste heat from the return air and meets the requirements of energy conservation and environmental protection.

[0016] By setting up a first regulating valve and a second regulating valve, the flow path and flow rate of the refrigerant can be controlled by adjusting the opening of the two valves. Combined with the temperature compensation function of the water heat exchanger, this enables precise control of the fresh air treatment process and thus accurately controls the outlet air temperature to meet the usage needs of various scenarios. Attached Figure Description

[0017] To more clearly illustrate the technical solutions in this utility model or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of this utility model. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0018] Figure 1 This is a schematic diagram of the principle of the dual-cold-source fresh air handling unit provided by this utility model in dehumidification mode; Figure 2 This is a schematic diagram of the principle of the dual-cold-source fresh air handling unit provided by this utility model in cooling mode; Figure 3 This is a schematic diagram of the principle of the dual-cold-source fresh air handling unit provided by this utility model in heating mode.

[0019] Figure label: 10. Body; 11. Total heat exchange core; 12. First water heat exchanger; 13. Second water heat exchanger; 14. First refrigerant heat exchanger; 15. Second refrigerant heat exchanger; 16. Heat recovery heat exchanger; 17. Compressor; 18. Four-way reversing valve; 19. Fresh air duct; 20. Return air duct; 21. First regulating valve; 22. Second regulating valve; 101. Fresh air inlet; 102. Return air inlet; 103. Fresh air outlet; 104. Return air outlet; 105. Water inlet; 106. Water outlet. Detailed Implementation

[0020] To make the objectives, technical solutions, and advantages of this utility model clearer, the technical solutions of this utility model will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this utility model, not all embodiments. Based on the embodiments of this utility model, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this utility model.

[0021] In the description of this utility model, it should be understood that the terms "top", "bottom", "inner", "outer", "axial", "radial", "circumferential", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings. They are only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this utility model.

[0022] In this utility model, unless otherwise explicitly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection, an electrical connection, or a communication connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this utility model according to the specific circumstances.

[0023] In this utility model, unless otherwise expressly specified and limited, the first feature "on" or "below" the second feature may be in direct contact with the first and second features, or indirect contact through an intermediate medium. In the description of this specification, references to terms such as "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of this utility model. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0024] like Figures 1 to 3 As shown, this utility model provides a dual-cold-source fresh air handling unit, including: a body 10, a total heat exchange core 11 disposed in the body 10, a first water heat exchanger 12, a second water heat exchanger 13, a first fluorine heat exchanger 14, a second fluorine heat exchanger 15, a compressor unit, and a heat recovery heat exchanger 16.

[0025] The total heat exchange core 11 is located on the air inlet side of the body 10. The air inlet side of the body 10 is provided with a fresh air inlet 101 and a return air inlet 102. The total heat exchange core 11 is provided with a fresh air inlet connected to the fresh air inlet 101 and a fresh air outlet. The total heat exchange core 11 is also provided with a return air inlet connected to the return air inlet 102 and a return air outlet. During operation, outdoor fresh air flows through the total heat exchange core 11 through the fresh air inlet 101, the fresh air inlet and the fresh air outlet. Indoor return air flows through the total heat exchange core 11 through the return air inlet 102, the return air inlet and the return air outlet. The fresh air and the return air exchange heat and humidity through the total heat exchange core 11 to achieve pretreatment of the fresh air. The air outlet side of the body 10 is provided with a fresh air outlet 103 and a return air outlet 104. Finally, the fresh air flows out from the fresh air outlet 103 after temperature and humidity adjustment, and the return air flows out from the return air outlet 104 for exhaust.

[0026] The body 10 has a fresh air duct 19 and a return air duct 20. Along the fresh air flow path, the first water heat exchanger 12, the first fluorine heat exchanger 14, the second water heat exchanger 13 and the second fluorine heat exchanger 15 are arranged in sequence in the fresh air duct 19, and the heat recovery heat exchanger 16 is arranged in the return air duct 20. The first fluorine heat exchanger 14, the second fluorine heat exchanger 15, the compressor unit and the heat recovery heat exchanger 16 are connected in sequence. A first regulating valve 21 is provided between the heat recovery heat exchanger 16 and the first fluorine heat exchanger 14, and a second regulating valve 22 is provided between the first fluorine heat exchanger 14 and the second fluorine heat exchanger 15.

[0027] The dual-source fresh air handling unit provided by this utility model, by setting up a total heat exchange core 11, can utilize the heat from the return air to pre-treat the heat and humidity load of the fresh air. For example, in summer, the low temperature of the return air is used to pre-lower the temperature of the fresh air, and in winter, the high temperature of the return air is used to pre-higher the temperature of the fresh air, thereby reducing the dehumidification and heat exchange load of the subsequent heat exchangers. The heat recovery heat exchanger 16 can recover the heat from the return air and, through pipeline connection with the first refrigerant heat exchanger 14 and the compressor unit, introduce the waste heat into the refrigerant circulation system for reuse. Through the above-mentioned energy recovery and utilization, the subsequent heat exchangers do not need to operate at full load, which can reduce the operating frequency of the compressor unit, reduce the power consumption of the unit, fundamentally solve the problem of waste heat from the return air, and meet the requirements of energy conservation and environmental protection.

[0028] By setting the first regulating valve 21 and the second regulating valve 22, the flow path and flow rate of the cold medium can be controlled by adjusting the opening of the two valves. Combined with the temperature compensation function of the water heat exchanger, the fresh air treatment process can be finely controlled, thereby accurately controlling the outlet air temperature to meet the usage needs in multiple scenarios.

[0029] Preferably, the first regulating valve 21 and the second regulating valve 22 can be electronic expansion valves. By controlling the opening of the first regulating valve 21 and the second regulating valve 22, the flow rate of the refrigerant entering the first fluorine heat exchanger 14, the second fluorine heat exchanger 15 and the heat recovery heat exchanger 16 in the fluorine circulation system can be precisely controlled to match the requirements of different operating conditions.

[0030] Furthermore, the fresh air duct 19 is equipped with a supply fan that communicates with the fresh air outlet 103, and the return air duct 20 is equipped with an exhaust fan that communicates with the return air outlet 104.

[0031] Furthermore, the body 10 is provided with a water inlet 105 and a water outlet 106, and the water inlet 105, the second water heat exchanger 13, the first water heat exchanger 12, and the water outlet 106 are connected in sequence by pipelines. The water system can supply cold water and hot water as needed to regulate the temperature and humidity of the fresh air. Preferably, a solenoid valve is provided on the water system connecting pipeline to adjust the water flow rate and thus regulate the required outlet air temperature.

[0032] Furthermore, the compressor unit includes a compressor 17 and a four-way reversing valve 18.

[0033] This utility model's dual-cold-source fresh air unit can operate in multiple modes, such as dehumidification mode, cooling mode, heating mode, and transitional season ventilation mode, to adjust the temperature and humidity of the fresh air outlet in multiple scenarios, thereby improving the comfort of the indoor environment.

[0034] Example 1: The dual-source fresh air handling unit operates in the first dehumidification mode (i.e., heating and dehumidification mode): The dual-source fresh air handling unit has a first dehumidification mode. In the first dehumidification mode, the first fluorine heat exchanger 14 and the heat recovery heat exchanger 16 are used as evaporators, the second fluorine heat exchanger 15 is used as a condenser, and the first regulating valve 21 has a maximum opening.

[0035] This mode requires a heating process after dehumidification, and the target temperature for heating and dehumidification must be higher than the inlet air temperature.

[0036] Heating and dehumidifying is suitable for scenarios with low outdoor temperatures and high humidity. Therefore, the circulation process involves heating and dehumidifying. Due to the temperature difference between indoors and outdoors, the exhaust fan is activated to recover indoor heat. Cold water at approximately 20°C (this temperature can be adjusted according to actual needs) flows through the inlet of the second water heat exchanger 13. Fresh air first passes through the total heat exchange core 11, exchanging heat and moisture with the return air. At this point, the indoor return air temperature is comfortable and the humidity is low, while the outdoor fresh air temperature is low and the humidity is high. This pre-dehumidification treatment of the fresh air reduces the dehumidification load on subsequent heat exchangers, lowers the compressor frequency, and reduces power consumption. After pre-cooling by the first water heat exchanger 12, the fresh air undergoes further cooling and dehumidification by the first refrigerant heat exchanger 14 (evaporator), and then is heated before being discharged into the room. For detailed principles, please refer to [link / reference needed]. Figure 1 .

[0037] The fresh air circulation path is as follows: fresh air inlet 101 - total heat exchange core 11 (heat and humidity pretreatment) - first water heat exchanger 12 (pre-cooling and dehumidification) - first refrigerant heat exchanger 14 (evaporator deep dehumidification) - second water heat exchanger 13 (preheating) - second refrigerant heat exchanger 15 (condenser reheating) - fresh air outlet 103.

[0038] The refrigerant flow path is as follows: after compression by compressor 17 - four-way reversing valve 18 - second refrigerant heat exchanger 15 (condenser) - second regulating valve 22 (opening control) - first refrigerant heat exchanger 14 (evaporator) - first regulating valve 21 (fully open) - heat recovery heat exchanger 16 (evaporator) - four-way reversing valve 18 - compressor 17.

[0039] The working principle is as follows: During this cycle, the opening degree of the second regulating valve 22 needs to be controlled according to the superheat, acting as a throttling device. The first regulating valve 21 is fully open. Both the first refrigerant heat exchanger 14 and the heat recovery heat exchanger 16 are evaporators, while the second refrigerant heat exchanger 15 is a condenser. The refrigerant only condenses and releases heat in the second refrigerant heat exchanger 15, but it needs to evaporate in the first refrigerant heat exchanger 14 and the heat recovery heat exchanger 16. Therefore, the heat released by condensation in the second refrigerant heat exchanger 15 is greater than the heat absorbed by evaporation in the first refrigerant heat exchanger 14, thus achieving the effect of heating and dehumidification. During the heating and dehumidification process, the indoor return air temperature is relatively high, which can be recovered by evaporating and absorbing heat through the heat recovery heat exchanger 16. Simultaneously, cold water at approximately 20°C flows through the water inlet 105. First, it exchanges heat with the low-temperature air, which has undergone deep dehumidification by the first refrigerant heat exchanger 14, in the second water heat exchanger 13, preheating the air. After the heat exchange, the water temperature is approximately 14°C. Then, it enters the first water heat exchanger 12 to pre-cool the outdoor fresh air before finally flowing out through the outlet 106. Throughout the operation, the supply fan operates according to the user-set speed to ensure sufficient airflow. The evaporation rate of the refrigerant in the heat recovery heat exchanger 16 can be adjusted by regulating the exhaust fan speed, thereby controlling the heat exchange between the refrigerant and the air in the first refrigerant heat exchanger 14, ensuring the outlet air temperature reaches the set requirements and achieving the heating and dehumidification effect.

[0040] Example 2: The dual-source fresh air handling unit operates in the second dehumidification mode (i.e., constant temperature dehumidification mode): This mode requires a heating process after dehumidification, and the target temperature for constant temperature dehumidification is the same as the inlet air temperature.

[0041] Constant temperature dehumidification is suitable for scenarios where the outdoor temperature is suitable but the humidity is high. In this situation, the indoor and outdoor temperatures are similar, but the humidity difference is significant. The exhaust fan is turned off, thus achieving a constant temperature dehumidification effect. The circulation principle of constant temperature dehumidification and heating dehumidification systems is as follows. Figure 1 The difference lies in the fact that the temperature difference between the indoor and outdoor areas of the constant temperature dehumidifier is smaller, and the exhaust fan is turned off.

[0042] Example 3: The dual-source fresh air handling unit operates in cooling mode (i.e., cooling and dehumidification mode): The dual-source fresh air handling unit has a cooling mode. In the cooling mode, the first fluorinated heat exchanger 14 and the second fluorinated heat exchanger 15 are used as evaporators, the heat recovery heat exchanger 16 is used as a condenser, and the second regulating valve 22 has a maximum opening.

[0043] The cooling mode is suitable for scenarios where the outdoor temperature is high and the indoor temperature is lower than the outdoor temperature. When this occurs, the exhaust fan turns on. First, the total heat exchange core 11 allows for heat exchange between the high-temperature outdoor fresh air and the indoor return air. Then, the return air passes through the heat recovery heat exchanger 16 for further heat exchange, recovering indoor cooling capacity in a stepped manner. The fresh air is cooled by passing through the total heat exchange core 11, the first refrigerant heat exchanger 14 (evaporator), the second refrigerant heat exchanger 15 (evaporator), the first water heat exchanger 12, and the second water heat exchanger 13 (with 7℃ cold water) before being discharged into the room. For detailed principles, please refer to [link / reference needed]. Figure 2 .

[0044] Fresh air circulation path: Fresh air inlet 101 - Total heat exchange core 11 (heat and humidity pretreatment) - First water heat exchanger 12 (precooling) - First refrigerant heat exchanger 14 (evaporator cooling) - Second water heat exchanger 13 (cooling) - Second refrigerant heat exchanger 15 (evaporator cooling) - Fresh air outlet 103.

[0045] Refrigerant flow path: after compression by compressor 17 - four-way reversing valve 18 - heat recovery heat exchanger 16 (condenser) - first regulating valve 21 (opening control) - first refrigerant heat exchanger 14 (evaporator) - second regulating valve 22 (fully open) - second refrigerant heat exchanger 15 (evaporator) - four-way reversing valve 18 - compressor 17.

[0046] Working principle: During this cycle, the opening of the first regulating valve 21 needs to be controlled according to the superheat, acting as a throttling device. The second regulating valve 22 is fully open. The first and second refrigerant heat exchangers 14 and 15 are both evaporators, and the heat recovery heat exchanger 16 is the condenser. The refrigerant simultaneously evaporates and absorbs heat in the first and second refrigerant heat exchangers 14 and 15, and only condenses and releases heat in the heat recovery heat exchanger 16, thus achieving the cooling effect. During the cooling process, the indoor return air temperature is low. The fresh air can be pre-treated using the total heat exchange core 11, and then condensed and released heat through the heat recovery heat exchanger 16 to recover the cold air from the indoor return air. Simultaneously, 7℃ (this temperature can be adjusted according to actual needs) cold water flows through the water inlet 105. First, it exchanges heat with the low-temperature air, which has been cooled by the first refrigerant heat exchanger 14, in the second water heat exchanger 13, further cooling the air. After the heat exchange, the water temperature is approximately 13℃. Then, it enters the first water heat exchanger 12 to pre-cool the outdoor fresh air before finally flowing out through the outlet 106. Throughout the entire operation, the supply and exhaust fans operate according to the user-set speeds, thereby achieving the cooling effect.

[0047] Example 4: Dual-source fresh air handling unit operating in heating mode: The dual-source fresh air handling unit has a heating mode. In the heating mode, the first refrigerant heat exchanger 14 and the second refrigerant heat exchanger 15 are used as condensers, the heat recovery heat exchanger 16 is used as an evaporator, and the second regulating valve 22 has a maximum opening.

[0048] The heating mode is suitable for scenarios where the outdoor temperature is low and the indoor temperature is higher than the outdoor temperature. When this occurs, the exhaust fan turns on, first using the total heat exchange core 11 to exchange heat between the low-temperature outdoor fresh air and the indoor return air. Then, the return air passes through the heat recovery heat exchanger 16 to recover indoor heat. The fresh air is then heated by passing through the first refrigerant heat exchanger 14 (condenser), the second refrigerant heat exchanger 15 (condenser), the first water heat exchanger 12, and the second water heat exchanger 13 (passed with hot water at 40℃ or other temperatures) before being discharged into the room. For detailed principles, please refer to [link / reference needed]. Figure 3 .

[0049] Fresh air circulation path: Fresh air inlet 101 - Total heat exchange core 11 (heat and humidity pretreatment) - First water heat exchanger 12 (preheating) - First refrigerant heat exchanger 14 (condenser heating) - Second water heat exchanger 13 (heating) - Second refrigerant heat exchanger 15 (condenser heating) - Fresh air outlet 103.

[0050] Refrigerant flow path: after compression by compressor 17 - four-way reversing valve 18 - second refrigerant heat exchanger 15 (condenser) - second regulating valve 22 (fully open) - first refrigerant heat exchanger 14 (condenser) - first regulating valve 21 (opening control) - heat recovery heat exchanger 16 (evaporator) - four-way reversing valve 18 - compressor 17.

[0051] Working principle: During this cycle, the opening of the first regulating valve 21 needs to be controlled according to the superheat, which is used for throttling. The second regulating valve 22 is fully open. The first fluorine heat exchanger 14 and the second fluorine heat exchanger 15 are both condensers, and the heat recovery heat exchanger 16 is an evaporator. The refrigerant condenses and releases heat in the first fluorine heat exchanger 14 and the second fluorine heat exchanger 15 at the same time, and evaporates and absorbs heat only in the heat recovery heat exchanger 16, thereby achieving the heating effect.

[0052] Example 5: Dual-source fresh air handling units operating in transitional season ventilation mode: During the transitional season, the difference between indoor and outdoor temperature and humidity is small. Heat recovery is achieved solely through the total heat exchange core 11, using indoor return air to process the temperature and humidity of the fresh air before it is discharged indoors. In this mode, the compressor does not need to be started, meaning the refrigerant system does not participate in operation, significantly reducing energy consumption. The ventilation mode during the transitional season can selectively activate the water system to assist in processing the temperature and humidity of the fresh air. If cooling is required, cold water is supplied to the water path; if heating is required, hot water is supplied. The desired outlet air temperature can be adjusted by controlling the water flow using a water path solenoid valve.

[0053] This utility model also provides an air conditioner, including the dual-cold-source fresh air unit of the above-described embodiments and examples, which has all the beneficial effects of the above-described embodiments and examples, and will not be repeated here.

[0054] The dual-source fresh air handling unit and air conditioner provided by this utility model, by setting up a total heat exchange core 11, can utilize the heat from the return air to pre-treat the heat and humidity load of the fresh air. For example, in summer, the low temperature of the return air can be used to pre-lower the temperature of the fresh air, and in winter, the high temperature of the return air can be used to pre-higher the temperature of the fresh air, thereby reducing the dehumidification and heat exchange load of the subsequent heat exchanger. The heat recovery heat exchanger 16 can recover the heat from the return air and, through pipeline connection with the first refrigerant heat exchanger 14 and the compressor unit, introduce the waste heat into the refrigerant circulation system for reuse. Through the above-mentioned energy recovery and utilization, the subsequent heat exchanger does not need to operate at full load, which can reduce the operating frequency of the compressor unit, reduce the power consumption of the unit, fundamentally solve the problem of waste heat from the return air, and meet the requirements of energy conservation and environmental protection.

[0055] By setting the first regulating valve 21 and the second regulating valve 22, the flow path and flow rate of the cold medium can be controlled by adjusting the opening of the two valves. Combined with the temperature compensation function of the water heat exchanger, the fresh air treatment process can be finely controlled, thereby accurately controlling the outlet air temperature to meet the usage needs in multiple scenarios.

[0056] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of this utility model, and not to limit it. Although this utility model has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some of the technical features. Such modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the spirit and scope of the technical solutions of the embodiments of this utility model.

Claims

1. A dual-cold-source fresh air handling unit, characterized in that, include: The machine body, a total heat exchange core disposed within the machine body, a first water heat exchanger, a second water heat exchanger, a first fluorine heat exchanger, a second fluorine heat exchanger, a compressor unit, and a heat recovery heat exchanger; The total heat exchange core is located on the air inlet side of the unit and is used for heat exchange between fresh air and return air; The machine body has a fresh air duct and a return air duct. Along the fresh air flow path, the first water heat exchanger, the first fluorine heat exchanger, the second water heat exchanger and the second fluorine heat exchanger are arranged in sequence in the fresh air duct, and the heat recovery heat exchanger is set in the return air duct. The first fluorine heat exchanger, the second fluorine heat exchanger, the compressor unit, and the heat recovery heat exchanger are connected in sequence. A first regulating valve is provided between the heat recovery heat exchanger and the first fluorine heat exchanger, and a second regulating valve is provided between the first fluorine heat exchanger and the second fluorine heat exchanger.

2. The dual-cold-source fresh air handling unit according to claim 1, characterized in that, The dual-source fresh air handling unit has a first dehumidification mode. In the first dehumidification mode, the first fluorine heat exchanger and the heat recovery heat exchanger are used as evaporators, the second fluorine heat exchanger is used as a condenser, and the first regulating valve has a maximum opening.

3. The dual-cold-source fresh air handling unit according to claim 1, characterized in that, The dual-source fresh air handling unit has a cooling mode. In the cooling mode, the first and second refrigerant heat exchangers are used as evaporators, the heat recovery heat exchanger is used as a condenser, and the second regulating valve has a maximum opening.

4. The dual-cold-source fresh air handling unit according to claim 1, characterized in that, The dual-source fresh air handling unit has a heating mode. In the heating mode, the first and second refrigerant heat exchangers are used as condensers, the heat recovery heat exchanger is used as an evaporator, and the second regulating valve has a maximum opening.

5. The dual-cooling-source fresh air handling unit according to any one of claims 2-4, characterized in that, Both the first regulating valve and the second regulating valve are electronic expansion valves.

6. The dual-cold-source fresh air handling unit according to claim 1, characterized in that, The air intake side of the unit is provided with a fresh air inlet and a return air inlet, and the air outlet side of the unit is provided with a fresh air outlet and a return air outlet. A supply fan connected to the fresh air outlet is provided in the fresh air duct, and an exhaust fan connected to the return air outlet is provided in the return air duct.

7. The dual-cold-source fresh air handling unit according to claim 1, characterized in that, The machine body is provided with a water inlet and a water outlet, and the water inlet, the second water heat exchanger, the first water heat exchanger and the water outlet are connected in sequence through pipelines.

8. The dual-cold-source fresh air handling unit according to claim 7, characterized in that, The pipeline is equipped with a solenoid valve.

9. The dual-cooling-source fresh air handling unit according to any one of claims 1-4 and 6-8, characterized in that, The compressor unit includes a compressor and a four-way reversing valve.

10. An air conditioner, characterized in that, Including the dual-cooling-source fresh air handling unit as described in any one of claims 1-9.

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