Fresh air system and refrigeration equipment

Abstract

The present disclosure provides a fresh air system and a refrigeration device. The fresh air system comprises: a gas compartment comprising a compartment body and a first exhaust channel; an exhaust fan configured to drive gas inside the gas compartment to be discharged from the gas compartment through the first exhaust channel and a second gas outlet; a fresh air channel; a fresh air fan configured to drive fresh air into the compartment body through the fresh air channel; a refrigeration device comprising an evaporator and a condenser; a second exhaust channel, the condenser exchanges heat with the gas discharged from the gas compartment and the heat-exchanged gas is discharged from the fresh air system through the second exhaust channel, and the second exhaust channel is isolated from the air inlet of the fresh air channel. The control method comprises: adjusting the rotation speed F2 of the exhaust fan according to at least one of the humidity RHr of the compartment body, the temperature Tr of the compartment body and the temperature Tc of the condenser, so as to adjust the discharge speed of the gas inside the gas compartment. The scheme of the present disclosure can reduce the risk of condensation.

Description

Technical Field

[0001] This disclosure relates to the field of refrigeration equipment, and particularly to a fresh air system and refrigeration equipment. Background Technology

[0002] Currently, some cold storage facilities use fresh air systems. However, during the operation of these systems, there is a risk of condensation during the pre-cooling stage of the fresh air. When the condenser of the cold storage refrigeration system discharges heat dissipation air, this air mixes with the fresh air, leading to a reduction in refrigeration efficiency. Utility Model Content

[0003] The purpose of this disclosure is to provide a fresh air system and a cooling device to reduce the risk of condensation and improve cooling efficiency.

[0004] The first aspect of this disclosure provides a fresh air system, comprising:

[0005] A gas compartment has a first gas outlet, a second gas outlet, and a gas inlet. The fresh air system is configured to deliver fresh air to a target area through the first gas outlet and receive return air from the target area through the gas inlet. The gas compartment includes a compartment body and a first exhaust duct.

[0006] An exhaust fan is configured to drive the gas inside the gas compartment to exit the gas compartment through the first exhaust channel and the second gas outlet;

[0007] A fresh air duct and a fresh air fan, wherein the fresh air fan is configured to drive fresh air through the fresh air duct into the compartment body;

[0008] A refrigeration device, comprising an evaporator and a condenser, wherein the evaporator is disposed at the first gas outlet to cool fresh air; and

[0009] The second exhaust duct allows the condenser to exchange heat with the gas discharged from the gas compartment, and the heat-exchanged gas is then discharged outside the fresh air system through the second exhaust duct. The air inlets of the second exhaust duct and the fresh air duct are isolated from each other so that the air outlet path of the second exhaust duct and the air inlet path of the fresh air duct do not interfere with each other.

[0010] In some embodiments, a flow guiding component is included, the interior of which forms a second exhaust channel, and the flow guiding component isolates the second exhaust channel from the air inlet of the fresh air channel.

[0011] In some embodiments, at least a portion of the surface of the airflow guide is provided with a first heat-insulating material, the first heat-insulating material being configured to prevent heat transfer from the second exhaust channel to the outside of the airflow guide.

[0012] In some embodiments, the compartment body is disposed on one side of the condenser along a first direction, the air inlet of the fresh air duct is disposed on the side of the compartment body along the first direction near the air guide component, the air inlet of the fresh air duct and the air guide component are offset along the first direction and maintain a first distance, and the air inlet of the fresh air duct and the air guide component are offset along a second direction that is perpendicular to both the first direction and the air outlet direction of the condenser and maintain a second distance.

[0013] In some embodiments, the projection of the outer contour of the condenser's air outlet onto the flow cross section of the second exhaust channel coincides with the outer contour of the flow cross section of the second exhaust channel.

[0014] In some embodiments, the gas inlet is located in the area of ​​the side wall of the first exhaust duct opposite to the second gas outlet.

[0015] In some embodiments, at least a portion of the walls of the gas compartment are provided with a second heat-insulating material, the second heat-insulating material being configured to impede the transfer of heat from the gas compartment to the target area.

[0016] In some embodiments, at least one of a first humidity detection device, a first temperature detection device, and a second temperature detection device is included. The first humidity detection device is configured to detect the humidity RHr of the compartment body, the first temperature detection device is configured to detect the temperature Tr of the compartment body, and the second temperature detection device is configured to detect the temperature Tc of the condenser, so as to adjust the speed F2 of the exhaust fan according to at least one of the humidity RHr, the temperature Tr, and the temperature Tc.

[0017] In some embodiments, a third temperature detection device is included, which is configured to detect the temperature Te of the external environment in which the fresh air system is located, so as to adjust the speed F1 of the fresh air fan according to the temperature Te.

[0018] In some embodiments, a first pressure detection device and a second pressure detection device are included. The first pressure detection device is configured to detect the gas pressure in the fresh air duct, and the second pressure detection device is configured to detect the gas pressure in the first exhaust duct, so as to adjust the speed F1 of the fresh air fan according to the difference ΔP between the gas pressure in the fresh air duct and the gas pressure in the first exhaust duct.

[0019] In some embodiments, a second humidity detection device is included, which is configured to detect the humidity RHe of the external environment in which the fresh air system is located, so as to adjust the speed F1 of the fresh air fan and / or the speed F2 of the exhaust fan according to the humidity RHe.

[0020] A second aspect of this disclosure provides a refrigeration device, comprising:

[0021] Storage room; and

[0022] The fresh air system according to the first aspect of this disclosure, wherein the interior space of the storage room is the target area.

[0023] A third aspect of this disclosure provides a method for controlling a fresh air system, comprising: adjusting the rotational speed F2 of the exhaust fan based on at least one of the humidity RHr of the compartment body, the temperature Tr of the compartment body, and the temperature Tc of the condenser, so as to adjust the exhaust speed of the gas inside the gas compartment.

[0024] In some embodiments,

[0025] If the humidity RHr of the compartment body is greater than the first preset humidity value RH1, and the temperature Tr of the compartment body is less than the dew point temperature Tdp corresponding to the humidity RHr of the compartment body, the speed F2 of the exhaust fan is increased by the first preset speed value ΔF21; and / or

[0026] If the humidity RHr of the compartment body is less than or equal to the first preset humidity value RH1, and the rate of change of the temperature Tc of the condenser is greater than the preset rate of change value r0, the speed F2 of the exhaust fan is increased to the second preset speed value ΔF22; and / or

[0027] If the temperature Tr of the compartment body is greater than or equal to the dew point temperature Tdp corresponding to the humidity RHr of the compartment body, and the rate of change of the temperature Tc of the condenser is greater than the preset rate of change value r0, the speed F2 of the exhaust fan will be increased by the second preset speed value ΔF22.

[0028] Wherein, the first preset speed value ΔF21 is greater than the second preset speed value ΔF22.

[0029] In some embodiments, the first preset rotation speed value ΔF21 is determined based on the rate of change of the humidity RHr of the compartment body and the temperature Tc of the condenser, and / or the second preset rotation speed value ΔF22 is determined based on the rate of change of the temperature Tc of the condenser.

[0030] In some embodiments,

[0031] ΔF21 = b1 × (RHr - RH1) + c1 × (dTc / dt - r0), where b1 represents the first proportionality coefficient, c1 represents the second proportionality coefficient, dTc / dt represents the derivative of the condenser temperature Tc with respect to time t; and / or

[0032] ΔF22=c2×(dTc / dt-r0), where c2 represents the third proportionality coefficient and dTc / dt represents the derivative of the temperature Tc of the condenser with respect to time t.

[0033] In some embodiments, if the temperature Te of the external environment where the fresh air system is located is less than the preset temperature value T0, the rotational speed F1 of the fresh air fan will increase.

[0034] In some embodiments, in response to an increase in the rotational speed F2 of the exhaust fan, the rotational speed F1 of the fresh air fan is increased by a third preset speed value ΔF11 based on the difference ΔP between the gas pressure in the fresh air duct and the gas pressure in the first exhaust duct and the increase ΔF2 of the rotational speed F2 of the exhaust fan.

[0035] In some embodiments, ΔF11 = d1 × ΔP × ΔF2, where d1 represents the fourth proportionality coefficient.

[0036] In some embodiments, if the humidity RHe of the external environment where the fresh air system is located is less than the second preset humidity value RH2, the speed F2 of the exhaust fan will no longer increase, and the speed F1 of the fresh air fan will remain unchanged.

[0037] A fourth aspect of this disclosure provides a computer-readable storage medium having a computer program stored thereon that, when executed by a processor, implements the control method for a fresh air system according to a third aspect of this disclosure.

[0038] The fifth aspect of this disclosure provides a control device, comprising:

[0039] Memory; and

[0040] A processor coupled to the memory, the processor being configured to execute the control method as described in the third aspect of this disclosure based on instructions stored in the memory.

[0041] In the fresh air system provided in this disclosure, the airflow discharged from the gas compartment through the first exhaust duct can be adjusted by regulating the speed of the exhaust fan. Specifically, increasing the speed of the exhaust fan can accelerate the discharge of high-humidity gas from the gas compartment when the humidity is high, or prevent high-temperature or high-humidity gas generated by the condenser or other external gases from flowing back into the gas compartment through the first exhaust duct, thus avoiding increased humidity. Based on parameters such as temperature and humidity of the fresh air source, the airflow entering the compartment through the fresh air duct can be adjusted by regulating the speed of the fresh air fan, thereby regulating the temperature and humidity of the gas compartment. Therefore, by individually or in conjunction with adjusting the speed of the exhaust fan and the fresh air fan, the gas in the gas compartment can be kept within a suitable temperature and humidity range, preventing condensation and maintaining high cooling efficiency while reducing energy consumption.

[0042] Furthermore, the second exhaust duct serves as the condenser's outlet. By isolating the second exhaust duct from the fresh air duct's inlet, the risk of hot air exhausted from the condenser mixing into the fresh air duct through the inlet, leading to excessively high fresh air temperature and reduced cooling efficiency, can be reduced. In this way, the initial temperature of the fresh air entering the fresh air duct is essentially consistent with the external environment temperature of the fresh air system. Adjusting the fresh air fan speed also minimizes discrepancies between the actual and expected values ​​of temperature or humidity in the gas compartment.

[0043] The refrigeration equipment provided in this disclosure has the advantages of the fresh air system provided in this disclosure.

[0044] In the control method of the fresh air system provided in this disclosure, the humidity RHr and temperature Tr of the compartment body can be used to indicate whether the gas inside the compartment body has met the condensation conditions. For example, when the temperature Tr of the compartment body is close to or lower than the dew point temperature corresponding to its humidity RHr, it indicates that there is a risk of condensation in the compartment body. The change in the temperature Tc of the condenser can be used to indicate the change in the heat load of the condenser. For example, when the temperature Tc rises rapidly, it indicates that the heat load is also rising rapidly, and the temperature and pressure at the location of the condenser are high, which may cause the exhaust hot air to backflow into the compartment body through the first exhaust duct, causing a potential condensation hazard in the gas compartment. Adjusting the speed F2 of the exhaust fan according to these indications, and thus adjusting the exhaust speed of the gas in the gas compartment, can demonstrate the advantages of the fresh air system provided in this disclosure.

[0045] The computer-readable storage medium provided in this disclosure stores a program capable of executing the control method for the fresh air system provided in this disclosure, and therefore has the advantages of the control method for the fresh air system provided in this disclosure.

[0046] The control device provided in this disclosure can execute the control method of the fresh air system provided in this disclosure, and therefore has the advantages of the control method of the fresh air system provided in this disclosure.

[0047] Other features and advantages of this disclosure will become clear from the following detailed description of exemplary embodiments with reference to the accompanying drawings. Attached Figure Description

[0048] The accompanying drawings, which are included to provide a further understanding of this disclosure and form part of this application, illustrate exemplary embodiments of this disclosure and are used to explain this disclosure, but do not constitute an undue limitation of this disclosure. In the drawings:

[0049] Figure 1 This is a schematic diagram of the structure of a fresh air system according to some embodiments of this disclosure.

[0050] Figure 2 for Figure 1 The diagram shows the structure of the fresh air system.

[0051] Figure 3 for Figure 1 The diagram shows the structure of the fresh air system from another perspective.

[0052] Figure 4 This is a schematic diagram illustrating the working principle of a fresh air system according to some embodiments of this disclosure.

[0053] Figure 5 This is a schematic diagram of the structure of a fresh air duct according to some embodiments of this disclosure.

[0054] Figure 6 This is a schematic diagram illustrating the working principle of a fresh air system according to some embodiments of this disclosure.

[0055] In the attached figures, the various reference numerals represent:

[0056] A. Target area;

[0057] 1. Airflow guiding components;

[0058] 2. Condensing fan;

[0059] 3. Fresh air fan;

[0060] 4. Fresh air duct;

[0061] 5. Evaporator fan;

[0062] 6. Evaporator;

[0063] 7. The main body of the compartment;

[0064] 8. First exhaust duct;

[0065] 9. Exhaust fan;

[0066] 10. Condenser;

[0067] 11. Second exhaust duct;

[0068] 12. First gas outlet;

[0069] 13. Second gas outlet;

[0070] 14. Gas inlet;

[0071] 15. First humidity detection device;

[0072] 16. First temperature detection device;

[0073] 17. Second temperature detection device;

[0074] 18. Third temperature detection device;

[0075] 19. First pressure detection device;

[0076] 20. Second pressure detection device;

[0077] 21. Second humidity detection device;

[0078] 22. Separating net;

[0079] 23. Control device;

[0080] 24. Outer tube;

[0081] 25. Inner tube;

[0082] 26. Interlayer. Detailed Implementation

[0083] The technical solutions of the embodiments of this disclosure will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this disclosure, and not all embodiments. The following description of at least one exemplary embodiment is merely illustrative and is in no way intended to limit this disclosure or its application or use. All other embodiments obtained by those skilled in the art based on the embodiments of this disclosure without creative effort are within the scope of protection of this disclosure.

[0084] Unless otherwise specifically stated, the relative arrangement, numerical expressions, and values ​​of the components and steps set forth in these embodiments do not limit the scope of this disclosure. It should also be understood that, for ease of description, the dimensions of the various parts shown in the drawings are not drawn to actual scale. Techniques, methods, and devices known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and devices should be considered part of the specification. In all examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not as limitations. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters in the following drawings denote similar items; therefore, once an item is defined in one drawing, it need not be further discussed in subsequent drawings.

[0085] In the description of this disclosure, it should be understood that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore should not be construed as limiting the scope of protection of this disclosure.

[0086] In the description of this disclosure, it should be understood that the orientation or positional relationship indicated by directional terms such as "front, back, up, down, left, right", "horizontal, vertical, horizontal" and "top, bottom" is generally based on the orientation or positional relationship shown in the accompanying drawings and is only for the convenience of describing this disclosure and simplifying the description. Unless otherwise stated, these directional terms 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, and therefore should not be construed as a limitation on the scope of protection of this disclosure; the directional terms "inner" and "outer" refer to the inner and outer contours relative to the outline of each component itself.

[0087] refer to Figures 1 to 6 Some embodiments of this disclosure provide a fresh air system, including a gas compartment, an exhaust fan 9, a fresh air duct 4, a fresh air fan 3, a refrigeration unit, and a second exhaust duct 11.

[0088] Figures 1 to 3 The structure of the fresh air system and target area A is shown from different perspectives. Figure 4 The direction of gas flow in the fresh air system and target area A is shown in the form of arrows.

[0089] The gas compartment has a first gas outlet 12, a second gas outlet 13, and a gas inlet 14. The fresh air system is configured to supply fresh air to target area A through the first gas outlet 12 and receive return air from target area A through the gas inlet 14. The gas compartment includes a compartment body 7 and a first exhaust duct 8. An exhaust fan 9 is configured to drive the gas inside the gas compartment to exit the gas compartment through the first exhaust duct 8 and the second gas outlet 13. A fresh air fan 3 is configured to drive fresh air into the compartment body 7 through a fresh air duct 4. The cooling device includes an evaporator 6 and a condenser 10. The evaporator 6 is located at the first gas outlet 12 to cool the fresh air. The condenser 10 exchanges heat with the gas discharged from the gas compartment and discharges the heat-exchanged gas outside the fresh air system through the second exhaust duct 11. The second exhaust duct 11 is isolated from the air inlet of the fresh air duct 4 so that the air outlet path of the second exhaust duct 11 does not interfere with the air inlet path of the fresh air duct 4.

[0090] The compartment body 7 serves to pre-cool the fresh air. The fresh air duct 4 can be located inside the compartment body 7, for example, it can be arranged in a circuitous manner inside the compartment body 7 so that the fresh air can be fully pre-cooled as it flows along the fresh air duct 4. Optionally, the air inlet of the fresh air duct 4 is equipped with a filter. Optionally, refer to Figure 5 The fresh air duct 4 has a double-layer sleeve structure, including an outer pipe 24, an inner pipe 25, and a sandwich 26 formed between the outer pipe 24 and the inner pipe 25. Fresh air flows inside the inner pipe 25. The sandwich 26 is filled with a cooling medium, such as a phase change material like paraffin or hydrated salt, to pre-cool the fresh air.

[0091] Optionally, the fresh air fan 3 is located at the air inlet of the fresh air duct 4. Optionally, the exhaust fan 9 is located at the second gas outlet 13. Both the exhaust fan 9 and the fresh air fan 3 can be driven by motors, and both can be equipped with spare drive motors to ensure continuous operation of the fresh air system.

[0092] Optionally, the fresh air system includes an evaporator fan 5 and a condenser fan 2, with the evaporator fan 5 located at the air inlet of the evaporator 6 and the condenser fan 2 located at the air outlet of the condenser 10.

[0093] In the fresh air system provided by the embodiments of this disclosure, the airflow discharged from the gas compartment through the first exhaust duct 8 can be adjusted by regulating the rotation speed of the exhaust fan 9. Specifically, increasing the rotation speed of the exhaust fan 9 can accelerate the discharge of high-humidity gas from the gas compartment when the humidity is high, or suppress the backflow of high-temperature or high-humidity gas generated by the condenser 10 or other external gases into the gas compartment through the first exhaust duct 8, thus preventing humidity rise. Based on parameters such as temperature and humidity of the fresh air source, the airflow entering the compartment body 7 through the fresh air duct 4 can be adjusted by regulating the rotation speed of the fresh air fan 3, thereby regulating the temperature and humidity of the gas compartment. Therefore, by adjusting the rotation speed of the exhaust fan 9 and the fresh air fan 3 individually or in conjunction, the gas in the gas compartment can be kept within a suitable temperature and humidity range, preventing condensation in the gas compartment, maintaining high cooling efficiency, and reducing energy consumption.

[0094] Furthermore, the second exhaust duct 11 serves as the outlet duct for the condenser 10. By isolating the second exhaust duct 11 from the inlet of the fresh air duct 4, the risk of hot air discharged from the condenser 10 mixing into the fresh air duct 4 through its inlet, leading to excessively high fresh air temperature and reduced cooling efficiency, can be reduced. In this way, the initial temperature of the fresh air entering the fresh air duct 4 is essentially consistent with the temperature of the external environment where the fresh air system is located. After adjusting the speed of the fresh air fan 3, the actual temperature or humidity values ​​in the gas compartment are less likely to deviate from the expected values.

[0095] In the process of developing this disclosure, the inventors discovered that for refrigeration equipment such as cold storage rooms equipped with fresh air systems, the space for setting up the fresh air system is limited. For example, the gas compartment and the location of the condenser 10 are restricted to the same side of the storage room of the cold storage room. Correspondingly, the inlet of the fresh air duct 4 is also restricted to a location adjacent to the condenser 10. Considering that the heat dissipation air of the condenser 10 is the main heat source of the surrounding air, and that in related technologies, the fresh air system relies on gravity and inertia to separate the fresh air from the hot air, this is the main reason why the heat dissipation air of the condenser easily mixes with the fresh air.

[0096] In view of this, in some embodiments of the fresh air system, the fresh air system includes a flow guiding component 1, the interior of which forms a second exhaust channel 11, and the flow guiding component 1 isolates the second exhaust channel 11 from the air inlet of the fresh air channel 4.

[0097] Optionally, the airflow guiding component 1 is a shell-shaped component, such as an airflow guide shroud. The airflow guiding component 1 forms a second exhaust channel 11 through the hollow part of its own shell structure, and isolates the second exhaust channel 11 from the air inlet of the fresh air channel 4 through its own shell structure. Optionally, a partition 22 is provided downstream of the air outlet of the condenser 10, and the air outlet end of the airflow guiding component 1 abuts against the partition 22.

[0098] In this embodiment, by setting the airflow guide component 1, the air inlets of the second exhaust duct 11 and the fresh air duct 4 can be separated into different areas, achieving physical isolation. The exhaust path of the condenser cooling air and the intake path of the fresh air will not intersect, which helps reduce the risk of condenser cooling air mixing with fresh air and maintains high cooling efficiency. When the space for the fresh air system is limited, this isolation method is simple and reliable, and does not require additional space.

[0099] In some embodiments of the fresh air system, at least a portion of the surface of the airflow guide 1 is provided with a first heat insulation material, which is configured to prevent heat from being transferred from the second exhaust duct 11 to the outside of the airflow guide 1.

[0100] Optionally, the first heat insulation material is a high-temperature resistant ceramic coating, which may be applied, for example, to the circumferential inner surface or circumferential outer surface of the fairing.

[0101] In this embodiment, the first heat insulation material can prevent heat from being transferred to the outside of the guide component 1 through the second exhaust channel 11. The heat in the hot air discharged from the condenser 10 can not only physically isolate the exhaust path of the condenser heat dissipation air from the intake path of the fresh air, but also suppress the exchange of heat between the exhaust path of the condenser heat dissipation air and the intake path of the fresh air.

[0102] In some embodiments of the fresh air system, the partition body 7 is disposed on one side of the condenser 10 along the first direction z, and the air inlet of the fresh air duct 4 is disposed on the side of the partition body 7 along the first direction z near the guide component 1. The air inlet of the fresh air duct 4 and the guide component 1 are offset along the first direction z and maintain a first distance. The air inlet of the fresh air duct 4 and the guide component 1 are offset along a second direction y that is perpendicular to both the first direction z and the air outlet direction of the condenser 10 and maintain a second distance.

[0103] Optionally, the first direction z is Figures 1 to 4 The vertical direction within. Optionally, the first distance is greater than or equal to 25mm, and the second distance is greater than or equal to 30mm.

[0104] Given the limited space for the fresh air system, based on the arrangement of the air inlet and the guide component 1 of the fresh air duct 4 in this embodiment, the air inlet of the fresh air duct 4 maintains a sufficient distance along both the first direction z and the second direction y, so that the position of the air inlet of the fresh air duct 4 is as far away from the second exhaust duct 11 as possible and is offset from the second exhaust duct 11, which helps to further prevent the mixing of hot air and fresh air.

[0105] In some embodiments of the fresh air system, the projection of the outer contour of the air outlet of the condenser 10 onto the flow cross section of the second exhaust duct 11 coincides with the outer contour of the flow cross section of the second exhaust duct 11.

[0106] Optionally, the flow cross-section of the second exhaust duct 11 is a cross-section perpendicular to the gas flow direction of the inner contour of the guide shroud. Optionally, the air outlet of the condenser is rectangular, and correspondingly, the guide shroud has a square cylindrical structure.

[0107] In this embodiment, the outer contour of the air outlet of the condenser 10 is the same as the shape and size of the flow cross section of the second exhaust channel 11. When hot air flows from the air outlet of the condenser into the second exhaust channel 11, the flow area and flow direction remain basically unchanged, which helps to reduce airflow resistance, increase the exhaust speed of hot air, and the flow area is not too large, which can reduce the risk that some hot air will still mix with fresh air.

[0108] In some embodiments of the fresh air system, the gas inlet 14 is located in the area opposite to the second gas outlet 13 on the side wall of the first exhaust duct 8.

[0109] Optionally, refer to Figure 3 and Figure 4 The second gas outlet 13 and the gas inlet 14 are arranged opposite each other on both sides of the first exhaust duct 8 along a third direction x. The third direction x is perpendicular to both the first direction z and the second direction y. Optionally, refer to... Figure 4 The gas inlet 14 is parallel to the gas outlet 13. Optionally, refer to... Figure 4 The second exhaust duct 11 extends along the third direction x, and the air intake direction of the gas inlet 14 and the exhaust direction of the second gas outlet 13 extend along the third direction x, that is, the same as the air outlet direction of the condenser 10.

[0110] Optionally, there are multiple gas inlets 14, which are arranged in a rectangular array and form a grid structure in the arrangement area.

[0111] In this embodiment, by setting the gas inlet 14 at a position opposite to the second gas outlet 13, the airflow channel of the return air can be made straighter, reducing the bend in the airflow direction when the return airflow from the target area A enters the first exhaust channel 8, reducing airflow resistance, facilitating the smooth discharge of the return airflow, and reducing the interference between the return airflow and the gas in the compartment body 7.

[0112] In some embodiments of the fresh air system, at least a portion of the walls of the gas compartment are provided with a second thermal insulation material, which is configured to impede the transfer of heat from the gas compartment to the target area A.

[0113] Optionally, the wall of the gas compartment adjacent to the target area A is provided with a second thermal insulation material. For example, the wall adjacent to the target area A could be... Figures 1 to 4 The right wall of the central partition 7 and the right wall of the first exhaust duct 8. Optionally, the wall of the gas compartment adjacent to the target area A is made of sheet metal (e.g., galvanized steel sheet), and the second insulation material is insulation cotton lining the wall of the gas compartment. Optionally, to achieve sufficient insulation effect, the thickness of the insulation cotton is greater than or equal to 20 mm.

[0114] In this embodiment, by providing a second heat insulation material, heat can be prevented from being transferred from the gas compartment to the target area A, so that the temperature of the gas in the gas compartment does not drop too low, thereby reducing the risk of condensation.

[0115] Some embodiments of this disclosure provide a refrigeration device, including a storage room and a fresh air system provided by embodiments of this disclosure, wherein the interior space of the storage room is a target area A.

[0116] Refrigeration equipment can be, for example, cold storage facilities, or other equipment or facilities that store goods by freezing or refrigeration.

[0117] The refrigeration equipment provided in the embodiments of this disclosure has the advantages of the fresh air system provided in the embodiments of this disclosure.

[0118] Some embodiments of this disclosure provide a control method for a fresh air system provided by an embodiment of this disclosure, including: adjusting the rotational speed F2 of the exhaust fan 9 according to at least one of the humidity RHr of the compartment body 7, the temperature Tr of the compartment body 7 and the temperature Tc of the condenser 10, so as to adjust the exhaust speed of the gas inside the gas compartment.

[0119] In the control method of the fresh air system provided in the embodiments of this disclosure, the humidity RHr and temperature Tr of the compartment body 7 can be used to indicate whether the gas inside the compartment body 7 has met the condensation conditions. For example, when the temperature Tr of the compartment body 7 is close to or lower than the dew point temperature corresponding to its humidity RHr, it indicates that there is a risk of condensation in the compartment body 7. The change in the temperature Tc of the condenser 10 can be used to indicate the change in the heat load of the condenser 10. For example, when the temperature Tc rises rapidly, it indicates that the heat load also rises rapidly, and the temperature and pressure at the location of the condenser 10 are high, which may cause the discharged hot air to backflow into the compartment body 7 through the first exhaust channel 8, causing a potential condensation hazard in the gas compartment. Adjusting the speed F2 of the exhaust fan 9 according to these indications, thereby adjusting the exhaust speed of the gas in the gas compartment, can demonstrate the advantages of the fresh air system provided in the embodiments of this disclosure.

[0120] In some embodiments of the fresh air system, the fresh air system includes at least one of a first humidity detection device 15, a first temperature detection device 16, and a second temperature detection device 17. The first humidity detection device 15 is configured to detect the humidity RHr of the compartment body 7, the first temperature detection device 16 is configured to detect the temperature Tr of the compartment body 7, and the second temperature detection device 17 is configured to detect the temperature Tc of the condenser 10, so as to adjust the speed F2 of the exhaust fan 9 according to at least one of the humidity RHr, temperature Tr, and temperature Tc.

[0121] In this embodiment, the fresh air system can obtain the humidity RHr through the first humidity detection device 15 and the temperature Tr through the first temperature detection device 16, and determine whether the humidity and temperature of the compartment body 7 are within the range that can cause condensation. The fresh air system can also obtain the temperature Tc through the second temperature detection device 17, and determine whether the change in the heat load of the condenser 10 causes the gas pressure in the area where the condenser 10 is located to increase or hot air to flow back into the gas compartment. Then, by adjusting the speed F2 of the exhaust fan 9, the risk of condensation and hot air backflow can be reduced.

[0122] In the control method of the fresh air system in some embodiments, if the humidity RHr of the partition body 7 is greater than the first preset humidity value RH1, and the temperature Tr of the partition body 7 is less than the dew point temperature Tdp corresponding to the humidity RHr of the partition body 7, the speed F2 of the exhaust fan 9 is increased to the first preset speed value ΔF21.

[0123] In the control method of the fresh air system in some embodiments, if the humidity RHr of the compartment body 7 is less than or equal to the first preset humidity value RH1, and the rate of change of the temperature Tc of the condenser 10 is greater than the preset rate of change value r0, the speed F2 of the exhaust fan 9 is increased to the second preset speed value ΔF22.

[0124] In the control method of the fresh air system in some embodiments, if the temperature Tr of the compartment body 7 is greater than or equal to the dew point temperature Tdp corresponding to the humidity RHr of the compartment body 7, and the rate of change of the temperature Tc of the condenser 10 is greater than the preset rate of change value r0, the speed F2 of the exhaust fan 9 is increased to a second preset speed value ΔF22.

[0125] In the above embodiment, the first preset rotational speed value ΔF21 is greater than the second preset rotational speed value ΔF22.

[0126] In this embodiment, the first preset humidity value RH1 can be used to indicate whether the humidity RHr of the compartment body 7 is too high; the dew point temperature Tdp can be used to indicate whether the temperature Tr of the compartment body 7 is too low, resulting in the precipitation and condensation of humid gas; the rate of change of the temperature Tc of the condenser 10 can be used to indicate the rate of change of the heat load of the condenser 10.

[0127] Optionally, the first preset humidity value RH1 can be 65%, and the preset rate of change value r0 can be 0.5℃ / min.

[0128] If the humidity RHr of the compartment body 7 is greater than the first preset humidity value RH1, and the temperature Tr of the compartment body 7 is less than the dew point temperature Tdp corresponding to the humidity RHr of the compartment body 7, it indicates that the humidity of the compartment body 7 is not only too high, but the temperature is also below the dew point temperature. The gas compartment has the conditions for condensation, and the risk of condensation is high. By increasing the speed F2 of the exhaust fan 9 to the first preset speed value ΔF21, the exhaust of gas with high moisture content in the gas compartment can be accelerated, thereby improving the condensation problem by reducing the humidity RHr of the compartment body 7.

[0129] If the humidity RHr of the compartment body 7 is less than or equal to the first preset humidity value RH1, and the rate of change of the temperature Tc of the condenser 10 is greater than the preset rate of change value r0, it indicates that although the humidity of the compartment body 7 is within the normal range, the heat load of the condenser 10 is increasing, and the condensation temperature is rising. This may lead to an increase in the gas pressure in the area where the condenser 10 is located. Hot air may backflow into the compartment body 7 from the second gas outlet 13 and the first exhaust duct 8, and condensation may still occur in the gas compartment due to the increased humidity. By increasing the speed F2 of the exhaust fan 9 to the second preset speed value ΔF22, the exhaust of gas with high moisture content in the gas compartment can be accelerated, and the backflow of hot air can be suppressed, so as to intervene in advance against the risk factors of condensation.

[0130] If the temperature Tr of the compartment body 7 is greater than or equal to the dew point temperature Tdp corresponding to the humidity RHr of the compartment body 7, and the rate of change of the temperature Tc of the condenser 10 is greater than the preset rate of change value r0, it indicates that although the temperature T of the compartment body 7 is within the normal range, the heat load of the condenser 10 has increased, and the condensation temperature has risen, which may lead to an increase in the gas pressure in the area where the condenser 10 is located. Hot air may backflow into the compartment body 7 from the second gas outlet 13 and the first exhaust channel 8, and condensation may still occur in the gas compartment due to the increase in humidity. By increasing the speed F2 of the exhaust fan 9 to the second preset speed value ΔF22, the exhaust of gas with high moisture content in the gas compartment can be accelerated, and the backflow of hot air can be suppressed, so as to intervene in advance on the risk factors of condensation.

[0131] Furthermore, by making the first preset speed value ΔF21 greater than the second preset speed value ΔF22, when the risk of gas condensation in the gas compartment is high, the increase in the speed F2 of the exhaust fan 9 is greater than when the risk of gas condensation is low. This allows the fresh air system to adjust the speed of the gas discharged from the first exhaust channel 8 according to the degree of condensation risk, and effectively curb the trend of the condensation risk continuing to increase.

[0132] In some embodiments of the fresh air system control method, a first preset rotation speed value ΔF21 is determined based on the rate of change of humidity RHr of the compartment body 7 and temperature Tc of the condenser 10, and / or a second preset rotation speed value ΔF22 is determined based on the rate of change of temperature Tc of the condenser 10.

[0133] In this embodiment, the first preset rotation speed value ΔF21 corresponds to a situation with a high risk of condensation. The humidity RHr of the compartment body 7 can indicate the degree to which parameters such as humidity and temperature that directly cause the risk of condensation deviate from the normal range. The rate of change of the temperature Tc of the condenser 10 can indicate the degree of change of potential condensation risk factors. Based on this, the first preset rotation speed value ΔF21 is determined in a targeted manner to help to curb the risk of condensation in a timely manner. The second preset rotation speed value ΔF22 corresponds to a situation with a low risk of condensation. At this time, the temperature and / or humidity of the compartment body 7 are within the normal range. The second preset rotation speed value ΔF22 can be determined based on the rate of change of the temperature Tc of the condenser 10 to curb the risk of condensation in a timely manner.

[0134] In some embodiments of the fresh air system control method, ΔF21=b1×(RHr-RH1)+c1×(dTc / dt-r0), where b1 represents the first proportional coefficient, c1 represents the second proportional coefficient, and dTc / dt represents the derivative of the temperature Tc of the condenser 10 with respect to time t.

[0135] Optionally, b1=0.2, RH1=65%, c1=0.1, r0=0.5℃ / min, i.e., ΔF21=0.2×(RH1-65%)+0.1×(dTc / dt-0.5). Where RH1 is the first preset humidity value mentioned above, and r0 is the preset rate of change value mentioned above.

[0136] In this embodiment, the higher the humidity RHr of the compartment body 7, the higher the risk of condensation, the greater the increase in the speed of the exhaust fan 9, the greater the rate of change of the temperature Tc of the condenser 10, the higher the risk of hot air backflow, and the greater the increase in the speed of the exhaust fan 9.

[0137] In some embodiments of the fresh air system control method, ΔF22=c2×(dTc / dt-r0), where c2 represents the third proportionality coefficient and dTc / dt represents the derivative of the temperature Tc of the condenser 10 with respect to time t.

[0138] Optionally, c2 = 0.1, r0 = 0.5℃ / min, i.e., ΔF22 = 0.1 × (dTc / dt - 0.5). Where r0 is the preset rate of change value mentioned earlier. Optionally, c2 = c1.

[0139] In this embodiment, the greater the rate of change of the temperature Tc of the condenser 10, the higher the risk of hot air backflow, and the greater the increase in the rotation speed of the exhaust fan 9, so as to adjust the speed of the gas discharged from the first exhaust channel 8 in a targeted manner according to the degree of condensation risk.

[0140] In some embodiments of the fresh air system, the fresh air system includes a third temperature detection device 18, which is configured to detect the temperature Te of the external environment where the fresh air system is located, so as to adjust the speed F1 of the fresh air fan 3 according to the temperature Te.

[0141] In this embodiment, the fresh air system can obtain the temperature Te through the third temperature detection device 18 and determine whether the ambient temperature is too low. Under the current environmental conditions, during the continuous intake of fresh air, will the moisture contained in the fresh air freeze? Then, by adjusting the speed F1, the fresh air is less likely to freeze during the intake process, reducing the risk of blockage of the fresh air duct 4.

[0142] In some embodiments of the control method for the fresh air system, if the temperature Te of the external environment where the fresh air system is located is less than the preset temperature value T0, the speed F1 of the fresh air fan 3 is increased.

[0143] In this embodiment, the preset temperature value T0 can be used to indicate whether the ambient temperature Te is too low, which may cause the fresh air to freeze as it enters the gas compartment through the fresh air duct 4. If the ambient temperature Te of the fresh air system is less than the preset temperature value T0, it indicates that there is a risk of icing in the fresh air. At this time, by increasing the rotational speed F1 of the fresh air fan 3, the airflow rate can be increased, thereby reducing the residence time of moisture in the fresh air and inhibiting the accumulation of tiny ice crystals to form an ice layer. Therefore, the control method of this embodiment can reduce the risk of icing and blockage in the fresh air duct 4.

[0144] Optionally, the preset temperature value T0 can be 0℃. Optionally, if the temperature Te of the external environment where the fresh air system is located is lower than the preset temperature value T0, the speed F1 of the fresh air fan 3 is increased by a preset percentage. In order to minimize the fluctuation of the fresh air intake volume, the preset percentage can be a relatively small value, such as 4%, 5%, 6%, 8%, etc.

[0145] In some embodiments of the fresh air system, the fresh air system includes a first pressure detection device 19 and a second pressure detection device 20. The first pressure detection device 19 is configured to detect the gas pressure of the fresh air duct 4, and the second pressure detection device 20 is configured to detect the gas pressure of the first exhaust duct 8, so as to adjust the speed F1 of the fresh air fan 3 according to the difference ΔP between the gas pressure of the fresh air duct 4 and the gas pressure of the first exhaust duct 8.

[0146] In this embodiment, the fresh air system can obtain the gas pressure of the fresh air channel 4 and the gas pressure of the first exhaust channel 8 through the first pressure detection device 19 and the second pressure detection device 20 respectively, and then obtain the difference ΔP between the two, and determine whether the gas pressure in the gas compartment is within the normal range under the current conditions, so that the fresh air intake speed and the gas exhaust speed in the gas compartment match the requirement of maintaining an appropriate air pressure inside the gas compartment.

[0147] For example, when the speed of the exhaust fan 9 increases, the gas in the gas compartment is discharged more rapidly, and the gas pressure in the gas compartment tends to decrease. In response to the increase in the speed of the exhaust fan 9, the speed F1 of the fresh air fan 3 also increases. This allows the fresh air intake to increase as the exhaust volume of the gas compartment increases, reducing the risk of the gas compartment being in a negative pressure state.

[0148] In the control method of the fresh air system in some embodiments, in response to the increase of the rotational speed F2 of the exhaust fan 9, the rotational speed F1 of the fresh air fan 3 is increased by a third preset rotational speed value ΔF11 based on the difference ΔP between the gas pressure in the fresh air duct 4 and the gas pressure in the first exhaust duct 8 and the increase ΔF2 of the rotational speed F2 of the exhaust fan 9.

[0149] Optionally, the speed F1 of the fresh air fan 3 is increased from the initial speed F10 to a third preset speed value ΔF11, i.e., the adjusted speed F11 = F10 + ΔF11. The initial speed F10 can be used as the speed of the fresh air fan 3 in normal operating conditions. To ensure the air volume of fresh air, the operating speed of the fresh air fan 3 is greater than or equal to the initial speed F10 during operation. The operating frequency corresponding to F10 can be, for example, 50Hz, and the corresponding fresh air volume can be, for example, 100m³ / h. 3 / h.

[0150] In this embodiment, the gas pressure in the gas compartment decreases as the rotational speed F2 of the exhaust fan 9 increases, potentially causing the gas compartment to be under negative pressure. This results in external air entering the gas compartment directly through weak points in the seal of the gas compartment and / or the fresh air duct 4 without sufficient pre-cooling. In this situation, the temperature inside the gas compartment may be too high. By increasing the rotational speed F1 of the fresh air fan 3, the airflow of fresh air can be appropriately increased, maintaining sufficient gas pressure in the gas compartment. The difference ΔP and the increase in rotational speed F2 ΔF2 can be used to indicate the required level of pressure maintenance in the gas compartment. Based on this, a third preset rotational speed value ΔF11 is determined to help restore the gas pressure in the gas compartment to the normal range as quickly as possible.

[0151] In some embodiments of the control method for the fresh air system, ΔF11 = d1 × ΔP × ΔF2, where d1 represents the fourth proportional coefficient.

[0152] Optionally, the value of the fourth proportional coefficient d1 can be 1%, and the adjusted speed F11 = 50 + 0.01 × ΔP × ΔF2.

[0153] In this embodiment, the greater the difference ΔP between the gas pressure in the fresh air duct 4 and the gas pressure in the first exhaust duct 8, the greater the increase ΔF2 in the rotational speed F2 of the exhaust fan 9, and the greater the increase in the rotational speed F1 of the fresh air fan 3, so as to adjust the increase in the rotational speed F1 of the fresh air fan 3 in a targeted manner according to the requirement of maintaining normal pressure in the gas compartment.

[0154] In some embodiments of the fresh air system, the fresh air system includes a second humidity detection device 21, which is configured to detect the humidity RHe of the external environment in which the fresh air system is located, so as to adjust the speed F1 of the fresh air fan 3 and / or the speed F2 of the exhaust fan 9 according to the humidity RHe.

[0155] In this embodiment, the fresh air system can obtain the humidity RHe through the second humidity detection device 21, and determine whether the ambient humidity is too low, whether the continuous intake of fresh air under the current conditions will cause the humidity of the gas compartment to deviate from the normal range, and then adjust the rotation speed F1 and / or rotation speed F2 to match the intake speed of fresh air and the exhaust speed of gas in the gas compartment with the humidity and temperature requirements inside the gas compartment.

[0156] In some embodiments of the control method for the fresh air system, if the humidity RHe of the external environment where the fresh air system is located is less than the second preset humidity value RH2, the speed F2 of the exhaust fan 9 will no longer increase, and the speed F1 of the fresh air fan 3 will remain unchanged.

[0157] The second preset humidity value RH2 can be determined based on the ventilation requirements of target area A and the requirements for preventing condensation in the gas compartment. For example, when the requirement for preventing condensation is strong, while the humidity requirement of target area A is relatively weak, RH2 can be taken as a smaller value; when the humidity requirement of target area A is relatively strong, RH2 can be taken as a larger value. The second preset humidity value RH2 can be 25%, 30%, 35%, etc.

[0158] In this embodiment, the second preset humidity value RH2 can be used to indicate whether the humidity RHe of the external environment is too low. If the humidity RHe of the external environment where the fresh air system is located is less than the second preset humidity value RH2, it indicates that the humidity RHe of the external environment is too low. In this state, by making the speed F2 of the exhaust fan 9 no longer increase and the speed F1 of the fresh air fan 3 remain unchanged, the acceleration of the exhaust fan 9 can be suppressed while maintaining the ability to deliver fresh air. This suppresses the exhaust speed of the original gas in the gas compartment, plays a moisturizing role, and avoids the humidity of the gas in the gas compartment being too low, which would also cause the humidity of the fresh air to be too low.

[0159] The embodiments of this disclosure provide a computer-readable storage medium storing a computer program that, when executed by a processor, implements the control method for the fresh air system provided in the embodiments of this disclosure.

[0160] The computer-readable storage medium provided in the embodiments of this disclosure stores a program capable of executing the control method of the fresh air system provided in the embodiments of this disclosure, and therefore has the advantages of the control method of the fresh air system provided in the embodiments of this disclosure.

[0161] The control device 23 provided in the embodiments of this disclosure includes a memory and a processor coupled to the memory, the processor being configured to execute the control method of the fresh air system provided in the embodiments of this disclosure based on instructions stored in the memory.

[0162] The control device provided in the embodiments of this disclosure is capable of executing the control method of the fresh air system provided in the embodiments of this disclosure, and therefore has the advantages of the control method of the fresh air system provided in the embodiments of this disclosure.

[0163] Optionally, refer to Figure 6The control device 23 is signal-connected to the aforementioned first humidity detection device 15, first temperature detection device 16, second temperature detection device 17, third temperature detection device 18, first pressure detection device 19, second pressure detection device 20, and second humidity detection device 21 to obtain corresponding detection parameters. The control device 23 is operably connected to the fresh air fan 3 and the exhaust fan 9, thereby enabling the adjustment of speeds F1 and F2 based on the control logic of the above control method. Optionally, the control device 23 is equipped with a display, which is configured to display the aforementioned detection parameters, as well as the speed F1 of the fresh air fan 3 and the speed F2 of the exhaust fan 9.

[0164] In some embodiments, the control device described above may be implemented as a general-purpose processor, a programmable logic controller (PLC), a digital signal processor (DSP), an application-specific integrated circuit (ASIC), a field-programmable gate array (FPGA), or other programmable logic devices, discrete gate or transistor logic devices, discrete hardware components, or any suitable combination thereof for performing the functions described herein.

[0165] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of this disclosure and not to limit them; although this disclosure has been described in detail with reference to preferred embodiments, those skilled in the art should understand that modifications can still be made to the specific implementation of this disclosure or equivalent substitutions can be made to some technical features, all of which should be covered within the scope of the technical solutions claimed in this disclosure.

Claims

1. A fresh air system, characterized in that, include: The gas compartment has a first gas outlet (12), a second gas outlet (13) and a gas inlet (14). The fresh air system is configured to deliver fresh air to a target area (A) through the first gas outlet (12) and receive return air from the target area (A) through the gas inlet (14). The gas compartment includes a compartment body (7) and a first exhaust duct (8). An exhaust fan (9) is configured to drive the gas inside the gas compartment to be discharged from the gas compartment through the first exhaust channel (8) and the second gas outlet (13); A fresh air duct (4) and a fresh air fan (3), wherein the fresh air fan (3) is configured to drive fresh air through the fresh air duct (4) into the compartment body (7). The refrigeration device includes an evaporator (6) and a condenser (10), wherein the evaporator (6) is disposed at the first gas outlet (12) to cool fresh air; and The second exhaust duct (11) is used to exchange heat with the gas discharged from the gas compartment and discharge the gas after heat exchange outside the fresh air system through the second exhaust duct (11). The air inlet of the second exhaust duct (11) is isolated from the air inlet of the fresh air duct (4) so ​​that the air outlet path of the second exhaust duct (11) and the air inlet path of the fresh air duct (4) do not interfere with each other.

2. The fresh air system according to claim 1, characterized in that, Includes a flow guide component (1), the interior of which forms the second exhaust channel (11), and the flow guide component (1) isolates the second exhaust channel (11) from the air inlet of the fresh air channel (4).

3. The fresh air system according to claim 2, characterized in that, At least a portion of the surface of the flow guide (1) is provided with a first heat insulation material, which is configured to prevent heat from being transferred from the second exhaust channel (11) to the outside of the flow guide (1).

4. The fresh air system according to claim 2, characterized in that, The compartment body (7) is disposed on one side of the condenser (10) along the first direction (z), and the air inlet of the fresh air duct (4) is disposed on the side of the compartment body (7) along the first direction (z) close to the guide component (1). The air inlet of the fresh air duct (4) and the guide component (1) are offset along the first direction (z) and maintain a first distance. The air inlet of the fresh air duct (4) and the guide component (1) are offset along a second direction (y) perpendicular to both the first direction (z) and the air outlet direction of the condenser (10) and maintain a second distance.

5. The fresh air system according to claim 1, characterized in that, The projection of the outer contour of the air outlet of the condenser (10) onto the flow section of the second exhaust channel (11) coincides with the outer contour of the flow section of the second exhaust channel (11).

6. The fresh air system according to claim 1, characterized in that, The gas inlet (14) is located in the area opposite to the second gas outlet (13) on the side wall of the first exhaust duct (8).

7. The fresh air system according to claim 1, characterized in that, At least a portion of the walls of the gas compartment are provided with a second heat insulation material, which is configured to impede the transfer of heat from the gas compartment to the target area (A).

8. The fresh air system according to any one of claims 1 to 7, characterized in that, The device includes at least one of a first humidity detection device (15), a first temperature detection device (16), and a second temperature detection device (17). The first humidity detection device (15) is configured to detect the humidity RHr of the compartment body (7), the first temperature detection device (16) is configured to detect the temperature Tr of the compartment body (7), and the second temperature detection device (17) is configured to detect the temperature Tc of the condenser (10) to adjust the rotational speed F2 of the exhaust fan (9) according to at least one of the humidity RHr, the temperature Tr, and the temperature Tc.

9. The fresh air system according to any one of claims 1 to 7, characterized in that, Includes a third temperature detection device (18), which is configured to detect the temperature Te of the external environment where the fresh air system is located, so as to adjust the speed F1 of the fresh air fan (3) according to the temperature Te.

10. The fresh air system according to any one of claims 1 to 7, characterized in that, Includes a first pressure detection device (19) and a second pressure detection device (20), the first pressure detection device (19) being configured to detect the gas pressure of the fresh air duct (4), and the second pressure detection device (20) being configured to detect the gas pressure of the first exhaust duct (8), so as to adjust the speed F1 of the fresh air fan (3) according to the difference ΔP between the gas pressure of the fresh air duct (4) and the gas pressure of the first exhaust duct (8).

11. The fresh air system according to any one of claims 1 to 7, characterized in that, Includes a second humidity detection device (21), which is configured to detect the humidity RHe of the external environment where the fresh air system is located, so as to adjust the speed F1 of the fresh air fan (3) and / or the speed F2 of the exhaust fan (9) according to the humidity RHe.

12. A refrigeration device, characterized in that, include: Storage room; and The fresh air system according to any one of claims 1 to 11, wherein the interior space of the storage room is the target area (A).

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