Fresh air system and control method thereof, refrigeration equipment, computer readable storage medium and control device

Abstract

The invention provides a fresh air system, a control method of the fresh air system, refrigeration equipment, a computer readable storage medium and a control device. The fresh air system comprises a gas compartment and a fresh air system, wherein the gas compartment comprises a compartment body and a first exhaust channel; the exhaust fan is configured to drive gas in the gas compartment to be exhausted out of the gas compartment through the first exhaust channel and the second gas outlet; a fresh air channel; the fresh air fan is configured to drive fresh air to enter the compartment body through the fresh air channel; the refrigerating device comprises an evaporator and a condenser; and the condenser exchanges heat with gas exhausted from the gas compartment, the gas subjected to heat exchange is exhausted out of the fresh air system through the second exhaust channel, and the second exhaust channel is isolated from an air inlet of the fresh air channel. The control method comprises the steps that the rotating speed F2 of the exhaust fan is adjusted 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 that the exhaust speed of gas in the gas compartment is adjusted. According to the scheme, the condensation risk can be reduced.

Description

TECHNICAL FIELD

[0001] The present disclosure relates to the field of refrigeration equipment, and in particular, to a fresh air system, a control method thereof, a refrigeration equipment, a computer readable storage medium, and a control device. BACKGROUND

[0002] Currently, some cold storage uses a fresh air system. However, during the operation of the fresh air system, the fresh air pre-cooling link has a risk of condensation. When the condenser of the cold storage refrigeration system discharges heat dissipation air, the condenser heat dissipation air will mix with the fresh air, resulting in reduced refrigeration efficiency. SUMMARY

[0003] The present disclosure aims to provide a fresh air system, a control method thereof, a refrigeration equipment, a computer readable storage medium, and a control device to reduce the risk of condensation and improve refrigeration efficiency.

[0004] A first aspect of the present disclosure provides a fresh air system, comprising:

[0005] a gas compartment having a first gas outlet, a second gas outlet, and a gas inlet, the fresh air system being 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 comprising a compartment body and a first exhaust air passage;

[0006] an exhaust air fan configured to drive gas inside the gas compartment to be discharged from the gas compartment through the first exhaust air passage and the second gas outlet;

[0007] a fresh air passage and a fresh air fan, the fresh air fan being configured to drive fresh air to enter the compartment body through the fresh air passage;

[0008] a refrigeration device comprising an evaporator and a condenser, the evaporator being arranged at the first gas outlet to cool the fresh air; and

[0009] a second exhaust air passage, the condenser being in heat exchange with the gas discharged from the gas compartment and discharging the heat-exchanged gas outside the fresh air system through the second exhaust air passage, the second exhaust air passage being isolated from the fresh air inlet of the fresh air passage, so that the air outlet path of the second exhaust air passage and the air inlet path of the fresh air passage do not interfere with each other.

[0010] In some embodiments, a flow guide component is included, the interior of the flow guide component forming the second exhaust air passage, and the flow guide component isolates the second exhaust air passage from the fresh air inlet of the fresh air passage.

[0011] In some embodiments, at least part of the surface of the flow guide component is provided with a first thermal insulation material configured to hinder heat transfer from the second exhaust air passage to the outside of the flow guide component.

[0012] In some embodiments, the compartment body is arranged at one side of the condenser along a first direction, the air inlet of the fresh air passage is arranged at one side of the compartment body along the first direction close to the flow guide component, the air inlet of the fresh air passage and the flow guide component are arranged staggered along a first direction and keep a first distance, and the air inlet of the fresh air passage and the flow guide component are arranged staggered along a second direction perpendicular to both the first direction and the air outlet direction of the condenser and keep a second distance.

[0013] In some embodiments, the outer contour of the air outlet of the condenser coincides with the projection of the throughflow section of the second exhaust air passage on the throughflow section of the second exhaust air passage.

[0014] In some embodiments, the gas inlet is arranged at an area of the side wall of the first exhaust air passage opposite to the second gas outlet.

[0015] In some embodiments, at least part of the wall surface of the gas compartment is provided with a second thermal insulation material configured to hinder heat transfer from the gas compartment to the target area.

[0016] In some embodiments, at least one of a first humidity detection device configured to detect the humidity RHr of the compartment body, a first temperature detection device configured to detect the temperature Tr of the compartment body, and a second temperature detection device configured to detect the temperature Tc of the condenser is included to adjust the rotation speed F2 of the exhaust air 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 configured to detect the temperature Te of the external environment in which the fresh air system is located is included to adjust the rotation speed F1 of the fresh air fan according to the temperature Te.

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

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

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

[0021] a storage compartment; and

[0022] The fresh air system of the first aspect of the present disclosure, wherein the internal space of the storage compartment is the target area.

[0023] A third aspect of the present disclosure provides a control method of a fresh air system, comprising: 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 exhaust speed of the gas in the gas compartment. In some embodiments,

[0024] If the humidity RHr of the compartment body is greater than a 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 rotation speed F2 of the exhaust fan is increased by a first preset rotation speed value ΔF21; and / or

[0025] If the humidity RHr of the compartment body is less than or equal to the first preset humidity value RH1, and the change rate of the temperature Tc of the condenser is greater than a preset change rate value r0, the rotation speed F2 of the exhaust fan is increased by a second preset rotation speed value ΔF22; and / or

[0026] 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 change rate of the temperature Tc of the condenser is greater than the preset change rate value r0, the rotation speed F2 of the exhaust fan is increased by the second preset rotation speed value ΔF22.

[0027] The first preset rotation speed value ΔF21 is greater than the second preset rotation speed value ΔF22.

[0028] In some embodiments, the first preset rotation speed value ΔF21 is determined according to the humidity RHr of the compartment body and the change rate of the temperature Tc of the condenser, and / or the second preset rotation speed value ΔF22 is determined according to the change rate of the temperature Tc of the condenser.

[0029] In some embodiments,

[0030] ΔF21 = b1 x (RHr - RH1) + c1 x (dTc / dt - r0), wherein b1 represents a first proportional coefficient, c1 represents a second proportional coefficient, and dTc / dt represents a derivative of the temperature Tc of the condenser with respect to time t; and / or

[0031] ΔF22 = c2 x (dTc / dt - r0), wherein c2 represents a third proportional coefficient, and dTc / dt represents a derivative of the temperature Tc of the condenser with respect to time t.

[0032] In some embodiments, if the temperature Te of the external environment in which the fresh air system is located is less than a preset temperature value T0, the rotational speed F1 of the fresh air fan is increased.

[0033] In some embodiments, in response to the rotational speed F2 of the exhaust fan being increased, the rotational speed F1 of the fresh air fan is increased by a third preset rotational speed value ΔF11 according to a difference ΔP between the gas pressure of the fresh air channel and the gas pressure of the first exhaust channel and an increase ΔF2 of the rotational speed F2 of the exhaust fan.

[0034] In some embodiments, ΔF11 = d1 x ΔP x ΔF2, wherein d1 represents a fourth proportional coefficient.

[0035] In some embodiments, if the humidity RHe of the external environment in which the fresh air system is located is less than a second preset humidity value RH2, the rotational speed F2 of the exhaust fan is no longer increased, and the rotational speed F1 of the fresh air fan remains unchanged.

[0036] A fourth aspect of the present disclosure provides a computer-readable storage medium having stored thereon a computer program, which, when executed by a processor, implements the control method of the fresh air system according to the third aspect of the present disclosure.

[0037] A fifth aspect of the present disclosure provides a control device, comprising:

[0038] a memory; and

[0039] a processor coupled to the memory, the processor being configured to execute the control method according to the third aspect of the present disclosure based on instructions stored in the memory.

[0040] The fresh air system provided by the present disclosure can adjust the air volume of the gas compartment through the first exhaust channel by adjusting the rotating speed of the exhaust fan. The high-humidity gas in the gas compartment can be discharged faster or the high-temperature or high-humidity gas generated by the condenser or from the external environment can be prevented from flowing back to the interior of the gas compartment through the first exhaust channel to avoid humidity rising, by increasing the rotating speed of the exhaust fan. The air volume of the compartment body through the fresh air channel can be adjusted by adjusting the rotating speed of the fresh air fan based on the temperature, humidity and other parameters of the fresh air source, so as to adjust the temperature and humidity of the gas compartment. It can be seen that the rotating speed of the exhaust fan and the rotating speed of the fresh air fan can be adjusted separately or in linkage, so that the gas in the gas compartment is in a suitable temperature and humidity range, the gas compartment is less likely to dew, the refrigeration efficiency is maintained at a high level, and the energy consumption is reduced.

[0041] In addition, the second exhaust channel is the air outlet channel of the condenser, and the risk that the hot air discharged by the condenser mixes into the fresh air channel through the air inlet of the fresh air channel to cause the temperature of the fresh air to be too high and the refrigeration efficiency to be reduced can be reduced by isolating the second exhaust channel from the air inlet of the fresh air channel. In this way, the initial temperature of the fresh air entering the fresh air channel is basically consistent with the temperature of the external environment where the fresh air system is located, and the actual value of the temperature or humidity of the gas compartment is less likely to deviate from the expected value after the rotating speed of the fresh air fan is adjusted.

[0042] The refrigeration equipment provided by the present disclosure has the advantages of the fresh air system provided by the present disclosure.

[0043] In the control method of the fresh air system provided by the present disclosure, the humidity RHr and the temperature Tr of the compartment body can be used to indicate whether the gas in the interior of the compartment body has met the dewing condition. For example, when the temperature Tr of the compartment body is close to or lower than the dew point temperature corresponding to the humidity RHr, it indicates that the compartment body has a dewing risk. The change of the temperature Tc of the condenser can be used to indicate the change of the heat load of the condenser. For example, when the temperature Tc rises rapidly, it indicates that the heat load also rises rapidly, the temperature at the position of the condenser is high, the pressure is large, and the hot air discharged by the condenser can flow back to the compartment body through the first exhaust channel, which can cause the gas compartment to dew. The rotating speed F2 of the exhaust fan can be adjusted according to the indication information, and the discharge speed of the gas in the gas compartment can be adjusted, so that the fresh air system provided by the present disclosure has the advantages.

[0044] The computer readable storage medium provided by the present disclosure stores a program capable of executing the control method of the fresh air system provided by the present disclosure, and therefore has the advantages of the control method of the fresh air system provided by the present disclosure.

[0045] The control device provided by the present disclosure can execute the control method of the fresh air system provided by the present disclosure, and thus has the advantages of the control method of the fresh air system provided by the present disclosure.

[0046] Other features and advantages of the present disclosure will become apparent from the following detailed description of exemplary embodiments of the present disclosure with reference to the drawings. BRIEF DESCRIPTION OF DRAWINGS

[0047] The accompanying drawings, which are included to provide a further understanding of the present disclosure and constitute a part of this application, illustrate certain exemplary embodiments of the present disclosure and are used to explain the present disclosure, but do not limit the present disclosure. In the drawings:

[0048] Figure 1 A structural schematic diagram of a fresh air system according to some embodiments of the present disclosure.

[0049] Figure 2 A structural schematic diagram of a fresh air system according to some embodiments of the present disclosure. Figure 1 A structural schematic diagram of a fresh air system according to some embodiments of the present disclosure.

[0050] Figure 3 A structural schematic diagram of a fresh air system according to some embodiments of the present disclosure. Figure 1 A structural schematic diagram of a fresh air system according to some embodiments of the present disclosure.

[0051] Figure 4 A working principle schematic diagram of a fresh air system according to some embodiments of the present disclosure.

[0052] Figure 5 A working principle schematic diagram of a fresh air system according to some embodiments of the present disclosure.

[0053] Figure 6 A structural schematic diagram of a fresh air passage according to some embodiments of the present disclosure.

[0054] In the drawings, the respective reference signs represent:

[0055] A, target area;

[0056] 1, flow guide component;

[0057] 2, condensation fan;

[0058] 3, fresh air fan;

[0059] 4, fresh air passage;

[0060] 5, evaporation fan;

[0061] 6, evaporator;

[0062] 7, compartment body;

[0063] 8, first exhaust passage;

[0064] 9, exhaust fan;

[0065] 10. Condenser;

[0066] 11. Second air exhaust passage;

[0067] 12. First gas outlet;

[0068] 13. Second gas outlet;

[0069] 14. Gas inlet;

[0070] 15. First humidity detecting device;

[0071] 16. First temperature detecting device;

[0072] 17. Second temperature detecting device;

[0073] 18. Third temperature detecting device;

[0074] 19. First pressure detecting device;

[0075] 20. Second pressure detecting device;

[0076] 21. Second humidity detecting device;

[0077] 22. Partition net;

[0078] 23. Control device;

[0079] 24. Outer tube;

[0080] 25. Inner tube;

[0081] 26. Interlayer. DETAILED DESCRIPTION

[0083] The technical solutions in the embodiments of the present disclosure will be described clearly and completely below in combination with the drawings in the embodiments of the present disclosure. Obviously, the described embodiments are only part of the embodiments of the present disclosure, rather than all the embodiments. The description of the at least one exemplary embodiment is actually only illustrative, but not as any limitation on the present disclosure and its application or use. Based on the embodiments in the present disclosure, all other embodiments obtained by those of ordinary skill in the art without any creative work, are within the scope of protection of the present disclosure.

[0084] The relative arrangement of parts and steps, numerical expressions, and numerical values set forth in the examples herein are not meant to limit the scope of the present disclosure unless otherwise specifically stated. Also, it is to be understood that the dimensions of the various parts shown in the drawings are not necessarily to scale, for the sake of convenience in illustration. Techniques, methods, and devices known to those of ordinary skill in the relevant art can not be discussed in detail, but should be considered part of the specification, where appropriate. In all examples shown and discussed herein, any specific values should be interpreted as merely illustrative and not as a limitation. Thus, other examples of exemplary embodiments can have different values. It is to be noted that like numbers and letters refer to like elements throughout the several views of the drawings, and that the use of or reference to certain terms in various places of the specification are not meant to limit the scope of the present disclosure, but rather, should be considered as part of the specification.

[0085] In the description of the present disclosure, it should be understood that the use of the words "first", "second", etc. to describe a component is merely intended to distinguish that component from another component, and does not have a special meaning unless otherwise stated. Therefore, it cannot be understood as a limitation on the scope of protection of the present disclosure.

[0086] In the description of the present disclosure, it should be understood that the orientation words such as "front, back, up, down, left, right", "horizontal, vertical, perpendicular, horizontal" and "top, bottom" and the like indicate the orientation or positional relationship shown in the drawings, which is only for the convenience of describing the present disclosure and simplifying the description. Unless otherwise stated, these orientation words do not indicate and imply that the devices or elements referred to must have a particular orientation or be constructed and operated in a particular orientation, and therefore cannot be understood as a limitation on the scope of protection of the present disclosure; the orientation words "inner, outer" refer to the inner and outer relative to the contour of each component.

[0087] Reference Figures 1 to 6 Some embodiments of the present disclosure provide a fresh air system, which includes a gas compartment, an exhaust fan 9, a fresh air channel 4, a fresh air fan 3, a refrigeration device, and a second exhaust channel 11.

[0088] Figures 1 to 3 The structure of the fresh air system and the target area A is shown from different perspectives. Figure 4 The flow direction of the gas in the fresh air system and the 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 deliver fresh air to the 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 comprises a compartment body 7 and a first exhaust air passage 8. The exhaust air fan 9 is configured to drive the gas inside the gas compartment to be discharged from the gas compartment through the first exhaust air passage 8 and the second gas outlet 13. The fresh air fan 3 is configured to drive fresh air to enter the compartment body 7 through the fresh air passage 4. The refrigeration device comprises an evaporator 6 and a condenser 10, the evaporator 6 is arranged 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 a second exhaust air passage 11, the second exhaust air passage 11 is isolated from the air inlet of the fresh air passage 4, so that the air outlet path of the second exhaust air passage 11 and the air inlet path of the fresh air passage 4 do not interfere with each other.

[0090] The compartment body 7 functions to pre-cool fresh air. The fresh air passage 4 can be arranged inside the compartment body 7, for example, can be arranged inside the compartment body 7 in a meandering manner, so that the fresh air can be fully pre-cooled during flowing along the fresh air passage 4. Optionally, the air inlet of the fresh air passage 4 is provided with a filter. Optionally, referring to Figure 5 , the fresh air passage 4 has a double-layer sleeve structure, comprising an outer tube 24, an inner tube 25 and a interlayer 26 formed between the outer tube 24 and the inner tube 25, the fresh air flows inside the inner tube 25, and the interlayer 26 is filled with a cooling medium, such as a phase change material, such as paraffin, hydrated salt, etc., to pre-cool the fresh air through the cooling medium.

[0091] Optionally, the fresh air fan 3 is arranged at the air inlet of the fresh air passage 4. Optionally, the exhaust air fan 9 is arranged at the second gas outlet 13. The exhaust air fan 9 and the fresh air fan 3 can be driven by motors, and each can be configured with a backup drive motor to ensure continuous operation of the fresh air system.

[0092] Optionally, the fresh air system comprises an evaporative fan 5 and a condensing fan 2, the evaporative fan 5 is arranged at the air inlet of the evaporator 6, and the condensing fan 2 is arranged at the air outlet of the condenser 10.

[0093] The new air system provided by the embodiments of the present disclosure can adjust the air volume of the gas compartment through the first exhaust channel 8 by adjusting the rotating speed of the exhaust fan 9. By increasing the rotating speed of the exhaust fan 9, the high-humidity gas in the gas compartment can be discharged faster, or the high-temperature or high-humidity gas generated by the condenser 10 or from the external environment can be prevented from flowing back to the interior of the gas compartment through the first exhaust channel 8, thereby avoiding the increase of humidity. Based on the temperature, humidity and other parameters of the new air source, the air volume of the compartment body 7 through the new air channel 4 can be adjusted by adjusting the rotating speed of the new air fan 3, and then the temperature and humidity of the gas compartment can be adjusted. As can be seen, by adjusting the rotating speed of the exhaust fan 9 and the rotating speed of the new air fan 3 separately or in linkage, the gas in the gas compartment can be kept in a suitable temperature and humidity range, the gas compartment is less likely to dew, and the refrigeration efficiency is higher and the energy consumption is lower.

[0094] In addition, the second exhaust channel 11 is the air outlet channel of the condenser 10. By isolating the second exhaust channel 11 from the air inlet of the new air channel 4, the hot air discharged from the condenser 10 can be prevented from mixing into the new air channel 4 through the air inlet of the new air channel 4, thereby reducing the risk of high temperature of the new air and the decrease of the refrigeration efficiency. In this way, the initial temperature of the new air entering the new air channel 4 is basically consistent with the temperature of the external environment where the new air system is located, and the actual value of the temperature or humidity of the gas compartment is less likely to deviate from the expected value after adjusting the rotating speed of the new air fan 3.

[0095] In the process of implementing the present disclosure, the inventors found that for the refrigeration equipment such as refrigerators provided with a new air system, the space for the new air system is limited, for example, the gas compartment and the position for placing the condenser 10 are limited to the same side of the storage compartment of the refrigerator, and accordingly, the inlet of the new air channel 4 is also limited to the position adjacent to the condenser 10. Considering that the heat dissipation air of the condenser 10 is the main heat source of the surrounding area, and in the related art, the new air system relies on gravity and inertia to separate the new air and the hot air, which is the main reason for the mixing of the condenser heat dissipation air and the new air.

[0096] Therefore, in some embodiments of the new air system, the new air system comprises a flow guide component 1, the inside of the flow guide component 1 forms the second exhaust channel 11, and the flow guide component 1 isolates the second exhaust channel 11 from the air inlet of the new air channel 4.

[0097] Optionally, the flow guide component 1 is a shell-shaped component, for example, a flow guide cover, the flow guide component 1 forms the second exhaust channel 11 through the hollow part of the shell structure of the flow guide component 1, and isolates the second exhaust channel 11 from the air inlet of the new air channel 4 through the shell structure of the flow guide component 1. Optionally, a screen 22 is arranged downstream of the air outlet of the condenser 10, and the air outlet end of the flow guide component 1 abuts against the screen 22.

[0098] In this embodiment, by arranging the flow guide component 1, the second exhaust air passage 11 and the air inlet of the fresh air passage 4 can be separated in different areas, achieving physical isolation. The air outlet path of the condenser heat dissipation air and the air inlet path of the fresh air will not cross, which is beneficial to reduce the risk of mixing the condenser heat dissipation air into the fresh air, and maintain high refrigeration efficiency. In the case of limited space for the fresh air system, this isolation method is simple and reliable, and does not require additional space.

[0099] In some embodiments of the fresh air system, at least part of the surface of the flow guide component 1 is provided with a first heat insulation material configured to hinder heat transfer from the second exhaust air passage 11 to the outside of the flow guide component 1.

[0100] Optionally, the first heat insulation material is a high-temperature-resistant ceramic coating, which can be coated on the circumferential inner surface or circumferential outer surface of the flow guide cover, for example.

[0101] In this embodiment, the first heat insulation material can hinder heat transfer from the second exhaust air passage 11 to the outside of the flow guide component 1, so that the heat in the heat dissipation air discharged by the condenser 10 can not only achieve physical isolation of the discharge path of the condenser heat dissipation air and the air inlet path of the fresh air, but also inhibit heat exchange between the discharge path of the condenser heat dissipation air and the air inlet path of the fresh air.

[0102] In some embodiments of the fresh air system, the compartment body 7 is arranged on one side of the condenser 10 along the first direction z, and the air inlet of the fresh air passage 4 is arranged on the side of the compartment body 7 close to the flow guide component 1 along the first direction z. The air inlet of the fresh air passage 4 and the flow guide component 1 are arranged in a staggered manner along the first direction z and maintain a first distance. The air inlet of the fresh air passage 4 and the flow guide component 1 are arranged in a staggered manner along the second direction y perpendicular to 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 the up-down direction in the above equation. Optionally, the first distance is greater than or equal to 25 mm, and the second distance is greater than or equal to 30 mm. Figures 1 to 4

[0104] In the case of limited space for the fresh air system, based on the arrangement of the air inlet of the fresh air passage 4 and the flow guide component 1 in this embodiment, the air inlet of the fresh air passage 4 maintains a sufficient distance along the first direction z and the second direction y, so that the position of the air inlet of the fresh air passage 4 is as far away from the second exhaust air passage 11 as possible and is arranged in a staggered manner with the second exhaust air passage 11, which is beneficial to further prevent the mixing of the heat dissipation air and the fresh air.

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

[0106] Optionally, the flow section of the second air exhaust channel 11 is a section of the inner contour of the fairing perpendicular to the direction of the gas flow. Optionally, the air outlet of the condenser is rectangular, and the fairing is a square tube structure.

[0107] In this embodiment, the outer contour of the air outlet of the condenser 10 is the same in shape and size as the flow section of the second air exhaust channel 11, and when the hot air flows from the air outlet of the condenser into the second air exhaust channel 11, the flow area and the flow direction are basically unchanged, which helps to reduce the air flow resistance, improve the exhaust speed of the hot air, and the flow area is not too large, which can reduce the risk of mixing some hot air with fresh air.

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

[0109] Optionally, referring to Figure 3 and Figure 4 , the second gas outlet 13 and the gas inlet 14 are oppositely arranged on both sides of the first air exhaust channel 8 along the third direction x. Wherein, the third direction x is perpendicular to the first direction z and the second direction y. Optionally, referring to Figure 4 , the gas inlet direction of the gas inlet 14 is parallel to the air outlet direction of the second gas outlet 13. Optionally, referring to Figure 4 , the second air exhaust channel 11 extends along the third direction x, and the gas inlet direction of the gas inlet 14 and the air outlet 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, the gas inlet 14 is a plurality of gas inlets, and the plurality of gas inlets 14 are arranged in a rectangular array, and the plurality of gas inlets 14 form a grid structure in the arrangement area.

[0111] In this embodiment, by arranging the gas inlet 14 at a position opposite to the second gas outlet 13, the air flow channel of the return air can be relatively straight, reducing the bending of the return air flow from the target area A when entering the first air exhaust channel 8, reducing the air flow resistance, and helping to smoothly exhaust the return air flow and reducing the interference between the return air flow and the gas of the compartment body 7.

[0112] In some embodiments of the fresh air system, at least part of the wall surface of the gas compartment is provided with a second heat insulation material, and the second heat insulation material is configured to hinder the heat transfer from the gas compartment to the target area A.

[0113] Optionally, the wall surface of the gas compartment adjacent to the target area A is provided with a second heat insulation material, for example, the wall surface adjacent to the target area A can be Figures 1 to 4The wall surface on the right side of the partition body 7 and the wall surface on the right side of the first exhaust channel 8. Optionally, the wall surface of the gas partition adjacent to the target area A is made of a metal plate (for example, a galvanized steel plate), and the second thermal insulation material is thermal insulation cotton lined on the wall surface of the gas partition. Optionally, in order to have sufficient thermal insulation effect, the thickness of the thermal insulation cotton is greater than or equal to 20 mm.

[0114] In this embodiment, by arranging the second thermal insulation material, the heat transfer from the gas partition to the target area A can be hindered, so that the temperature of the gas in the gas partition does not drop too low, thereby reducing the risk of condensation.

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

[0116] The refrigeration device may, for example, be a cold storage, or other devices or facilities that store goods in a frozen or refrigerated manner.

[0117] The refrigeration device provided by embodiments of the present disclosure has the advantages of the fresh air system provided by embodiments of the present disclosure.

[0118] Some embodiments of the present disclosure provide a control method of the fresh air system provided by embodiments of the present disclosure, comprising: adjusting the rotating speed F2 of the exhaust fan 9 according to at least one of the humidity RHr of the partition body 7, the temperature Tr of the partition body 7, and the temperature Tc of the condenser 10, to adjust the exhaust speed of the gas in the gas partition.

[0119] In the control method of the fresh air system provided by embodiments of the present disclosure, the humidity RHr and the temperature Tr of the partition body 7 can be used to indicate whether the gas in the partition body 7 has met the condensation condition, for example, when the temperature Tr of the partition body 7 approaches or is lower than the dew point temperature corresponding to the humidity RHr of the partition body 7, it indicates that the partition body 7 has a condensation risk; the change of the temperature Tc of the condenser 10 can be used to indicate the change of the heat load of the condenser 10, for example, when the temperature Tc rises rapidly, it indicates that the heat load also rises rapidly, the temperature at the position of the condenser 10 is higher and the pressure is larger, which may cause the exhaust hot air to flow back to the partition body 7 through the first exhaust channel 8, causing the hidden danger of condensation in the gas partition. Adjusting the rotating speed F2 of the exhaust fan 9 according to these indication information, and then adjusting the exhaust speed of the gas in the gas partition, can reflect the advantages of the fresh air system provided by embodiments of the present disclosure.

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

[0121] In the embodiments, the fresh air system can acquire the humidity RHr through the first humidity detection device 15 and the temperature Tr through the first temperature detection device 16, so as to determine whether the humidity and the temperature of the compartment body 7 are in a range that can cause condensation. The fresh air system can acquire the temperature Tc through the second temperature detection device 17, so as to determine whether the change of the heat load of the condenser 10 causes the gas pressure in the area where the condenser 10 is located to increase and the hot air to backflow to the gas compartment, and further reduce the risk of condensation and hot air backflow by adjusting the rotating speed F2 of the exhaust fan 9.

[0122] In the control method of the fresh air system of some embodiments, if the humidity RHr of the compartment body 7 is greater than a 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, the rotating speed F2 of the exhaust fan 9 is increased by a first preset rotating speed value ΔF21.

[0123] In the control method of the fresh air system of 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 change rate of the temperature Tc of the condenser 10 is greater than a preset change rate value r0, the rotating speed F2 of the exhaust fan 9 is increased by a second preset rotating speed value ΔF22.

[0124] In the control method of the fresh air system of 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 change rate of the temperature Tc of the condenser 10 is greater than the preset change rate value r0, the rotating speed F2 of the exhaust fan 9 is increased by the second preset rotating speed value ΔF22.

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

[0126] In the embodiments, 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 to cause the condensation of the gas containing humidity, and the change rate of the temperature Tc of the condenser 10 can be used to indicate the change rate of the heat load of the condenser 10.

[0127] Optionally, the first preset humidity value RH1 can be 65%, and the preset rate 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 high, but also the temperature is below the dew point temperature, and the gas compartment has the condition of dewing and the risk of dewing is high. By increasing the speed F2 of the exhaust fan 9 by the first preset speed value ΔF21, the gas with high moisture content in the gas compartment can be accelerated to be discharged, so as to improve the dewing 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 value r0, it indicates that although the humidity of the compartment body 7 is in the normal range, the heat load of the condenser 10 is increased, the condensing temperature is increased, which may cause the gas pressure in the area where the condenser 10 is located to increase, and the hot air may flow back into the compartment body 7 from the second gas outlet 13 and the first exhaust channel 8, so that the gas compartment may still cause dewing due to the increase of humidity. By increasing the speed F2 of the exhaust fan 9 by the second preset speed value ΔF22, the gas with high moisture content in the gas compartment can be accelerated to be discharged, and the backflow of hot air can be inhibited, so as to intervene in the risk factors of dewing in advance.

[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 value r0, it indicates that although the temperature T of the compartment body 7 is in the normal range, the heat load of the condenser 10 is increased, the condensing temperature is increased, which may cause the gas pressure in the area where the condenser 10 is located to increase, and the hot air may flow back into the compartment body 7 from the second gas outlet 13 and the first exhaust channel 8, so that the gas compartment may still cause dewing due to the increase of humidity. By increasing the speed F2 of the exhaust fan 9 by the second preset speed value ΔF22, the gas with high moisture content in the gas compartment can be accelerated to be discharged, and the backflow of hot air can be inhibited, so as to intervene in the risk factors of dewing in advance.

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

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

[0133] In this embodiment, the first preset rotation speed value ΔF21 corresponds to a situation with a higher risk of dew condensation, the humidity RHr of the compartment body 7 can indicate the degree of deviation of the humidity, temperature and other parameters directly leading to the risk of dew condensation from the normal range, and the change rate of the temperature Tc of the condenser 10 can indicate the change degree of the risk factor of potential dew condensation, so that the first preset rotation speed value ΔF21 is determined accordingly to timely curb the risk of dew condensation; the second preset rotation speed value ΔF22 corresponds to a situation with a lower risk of dew condensation, at this time the temperature and / or humidity of the compartment body 7 is in the normal range, and the second preset rotation speed value ΔF22 is determined according to the change rate of the temperature Tc of the condenser 10 to timely curb the risk of dew condensation.

[0134] In the control method of the fresh air system in some embodiments, ΔF21 = b1 × (RHr - RH1) + c1 × (dTc / dt - r0), wherein b1 represents a first proportional coefficient, c1 represents a 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, and r0 = 0.5 ℃ / min, i.e. ΔF21 = 0.2 × (RH1 - 65%) + 0.1 × (dTc / dt - 0.5). RH1 is the first preset humidity value mentioned above, and r0 is the preset change rate value mentioned above.

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

[0137] In the control method of the fresh air system in some embodiments, ΔF22 = c2 × (dTc / dt - r0), wherein c2 represents a third proportional 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 and r0 = 0.5 ℃ / min, i.e. ΔF22 = 0.1 × (dTc / dt - 0.5). r0 is the preset change rate value mentioned above. 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 rotational speed of the exhaust fan 9, so as to adjust the speed of the exhaust gas of the first exhaust passage 8 according to the degree of risk of condensation.

[0140] In the fresh air system of some embodiments, the fresh air system comprises a third temperature detection device 18 configured to detect the temperature Te of the external environment in which the fresh air system is located, so as to adjust the rotational 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 low, and whether the moisture contained in the fresh air will freeze during the continuous fresh air intake process under the current environmental conditions, and then adjust the rotational speed F1 to make the fresh air not easy to freeze during the intake process, thereby reducing the risk of clogging of the fresh air passage 4.

[0142] In the control method of the fresh air system of some embodiments, if the temperature Te of the external environment in which the fresh air system is located is less than a preset temperature value T0, the rotational 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 temperature Te of the external environment is low, which may cause the fresh air to freeze during the process of entering the gas compartment through the fresh air passage 4. If the temperature Te of the external environment in which the fresh air system is located is less than the preset temperature value T0, it indicates that there is a risk of freezing of the fresh air. At this time, by increasing the rotational speed F1 of the fresh air fan 3, the flow rate of the fresh air can be increased, thereby reducing the residence time of the moisture in the fresh air and inhibiting the aggregation of tiny ice crystals to form an ice layer. It can be seen that the control method of this embodiment can reduce the risk of freezing and clogging of the fresh air passage 4.

[0144] Optionally, the preset temperature value T0 can be 0°C. Optionally, if the temperature Te of the external environment in which the fresh air system is located is less than the preset temperature value T0, the rotational speed F1 of the fresh air fan 3 is increased by a preset proportion. In order to reduce the fluctuation of the fresh air intake amount as much as possible, the preset proportion can be a relatively small value, for example, it can be 4%, 5%, 6%, 8%, etc.

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

[0146] In the embodiment, the fresh air system can acquire the gas pressure of the fresh air channel 4 and the gas pressure of the first exhaust air channel 8 through the first pressure detection device 19 and the second pressure detection device 20 respectively, and then acquire the difference ΔP between the two, and determine whether the gas pressure in the gas compartment under the current condition is in the normal range, so as to match the air intake speed of the fresh air with the demand of maintaining appropriate air pressure inside the gas compartment.

[0147] For example, when the rotating speed of the exhaust air fan 9 increases, the gas in the gas compartment is accelerated to be exhausted, and the gas pressure in the gas compartment tends to decrease. In response to the increase of the rotating speed of the exhaust air fan 9, the rotating speed F1 of the fresh air fan 3 is increased. In this way, after the exhaust air volume of the gas compartment increases, the air intake volume of the fresh air is also increased, so as to reduce 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 rotating speed F2 of the exhaust air fan 9, the rotating speed F1 of the fresh air fan 3 is increased by a third preset rotating speed value ΔF11 according to the difference ΔP between the gas pressure of the fresh air channel 4 and the gas pressure of the first exhaust air channel 8 and the increase ΔF2 of the rotating speed F2 of the exhaust air fan 9.

[0149] Optionally, the rotating speed F1 of the fresh air fan 3 is increased by the third preset rotating speed value ΔF11 from the initial rotating speed F10, that is, the adjusted rotating speed F11=F10+ΔF11. The initial rotating speed F10 can be used as the rotating speed of the fresh air fan 3 in a normal working state. In order to ensure the air volume of the fresh air, the working rotating speed of the fresh air fan 3 is greater than or equal to the initial rotating speed F10 when the fresh air fan 3 is running. For example, the operating frequency corresponding to F10 can be 50 Hz, and the corresponding fresh air volume can be 100 m 3 / h.

[0150] In the embodiment, the gas pressure in the gas compartment decreases with the increase of the rotating speed F2 of the exhaust air fan 9, and the gas compartment can be in a negative pressure state, which causes the air in the external environment to directly enter the gas compartment through the weak sealing parts of the gas compartment and / or the fresh air duct 4 without being sufficiently pre-cooled. At this time, the temperature in the gas compartment can be relatively high. By increasing the rotating speed F1 of the fresh air fan 3, the air volume of the fresh air can be appropriately increased, so as to maintain sufficient gas pressure in the gas compartment. The difference ΔP and the increase ΔF2 of the rotating speed F2 can be used to indicate the degree of demand for maintaining the normal pressure of the gas compartment, and the third preset rotating speed value ΔF11 is determined accordingly, which is beneficial to quickly restore the gas pressure in the gas compartment to the normal range.

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

[0152] Optionally, the fourth proportional coefficient d1 can be 1%, and the adjusted rotating speed F11=50+0.01*AP*AF2.

[0153] In this embodiment, the greater the difference AP between the gas pressure of the fresh air channel 4 and the gas pressure of the first exhaust air channel 8, the greater the rising amount AF2 of the rotating speed F2 of the exhaust air fan 9, and the greater the increasing amount of the rotating speed F1 of the fresh air fan 3, so as to adjust the increasing amount of the rotating speed F1 of the fresh air fan 3 according to the degree of the requirement of maintaining the normal pressure of the gas compartment.

[0154] In the fresh air system of some embodiments, the fresh air system comprises a second humidity detection device 21 configured to detect the humidity RHe of the external environment where the fresh air system is located, so as to adjust the rotating speed F1 of the fresh air fan 3 and / or the rotating speed F2 of the exhaust air 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 environmental humidity is low and whether the continuous fresh air intake under the current condition will cause the humidity of the gas compartment to deviate from the normal range, and then adjust the rotating speed F1 and / or the rotating speed F2, so as to match the fresh air intake speed and the exhaust speed of the gas in the gas compartment with the humidity requirement and the temperature requirement of the internal environment of the gas compartment.

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

[0157] The value of the second preset humidity value RH2 can be determined according to the requirement of ventilation of the target area A and the requirement of preventing the gas compartment from dewing, for example, when the requirement of preventing dewing is strong and the humidity requirement of the target area A is relatively weak, RH2 can take a smaller value; when the humidity requirement of the target area A is relatively strong, RH2 can take a larger value. The value of 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 low, and 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 low. In this state, by making the rotating speed F2 of the exhaust air fan 9 no longer increase and the rotating speed F1 of the fresh air fan 3 remain unchanged, the speed of the exhaust air fan 9 can be inhibited under the premise of maintaining the ability of delivering fresh air, so as to inhibit the exhaust speed of the original gas in the gas compartment, thereby playing a role in humidifying and avoiding the humidity of the fresh air being too low due to the humidity of the gas in the gas compartment being too low.

[0159] The computer readable storage medium provided by the embodiments of the present disclosure stores a computer program, and the program is executed by a processor to implement the control method of the fresh air system provided by the embodiments of the present disclosure.

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

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

[0162] The control device provided by the embodiments of the present disclosure can execute the control method of the fresh air system provided by the embodiments of the present disclosure, and thus has the advantages of the control method of the fresh air system provided by the embodiments of the present disclosure.

[0163] Optionally, referring to Figure 6 , the control device 23 is signal connected with the first humidity detection device 15, the first temperature detection device 16, the second temperature detection device 17, the third temperature detection device 18, the first pressure detection device 19, the second pressure detection device 20, and the second humidity detection device 21 mentioned above, to obtain corresponding detection parameters; the control device 23 is operatively connected to the fresh air fan 3 and the exhaust fan 9, so as to be able to adjust the rotation speed F1 and the rotation speed F2 based on the control logic of the above control method. Optionally, the control device 23 is configured with a display configured to display the detection parameters mentioned above, and the rotation speed F1 of the fresh air fan 3 and the rotation speed F2 of the exhaust fan 9.

[0164] In some embodiments, the control device described above can 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 device, a discrete gate or transistor logic device, a discrete hardware component, or any appropriate combination thereof, for executing the functions described in the present disclosure.

[0165] It should be noted that the above examples are only used to illustrate the technical solutions of the present disclosure rather than limit them; although the present disclosure has been described in detail with reference to the preferred embodiments, it should be understood by those skilled in the art that the specific embodiments of the present disclosure can be modified or some technical features can be replaced by equivalent ones, which should be covered in the technical solution range of the present disclosure claimed.

Claims

1. A fresh air system, characterized in that The air chamber comprises: an air chamber having a first air outlet (12), a second air outlet (13) and an air inlet (14), the fresh air system being configured to deliver fresh air to a target area (A) through the first air outlet (12) and receive return air from the target area (A) through the air inlet (14), the air chamber comprising an air chamber body (7) and a first exhaust air passage (8); an exhaust air fan (9) configured to drive air inside the air chamber to be exhausted out of the air chamber through the first exhaust air passage (8) and the second air outlet (13); a fresh air passage (4) and a fresh air fan (3), the fresh air fan (3) being configured to drive fresh air to enter the air chamber body (7) through the fresh air passage (4); a refrigeration device comprising an evaporator (6) and a condenser (10), the evaporator (6) being arranged at the first air outlet (12) to cool fresh air; and a second exhaust air passage (11), the condenser (10) being in heat exchange with air exhausted out of the air chamber and exhausting the air out of the fresh air system through the second exhaust air passage (11), the second exhaust air passage (11) being isolated from an air inlet of the fresh air passage (4) so that an air outlet path of the second exhaust air passage (11) and an air inlet path of the fresh air passage (4) do not interfere with each other. The air chamber comprises a flow guide component (1), an inside of the flow guide component (1) forming the second exhaust air passage (11), and the flow guide component (1) isolating the second exhaust air passage (11) from the air inlet of the fresh air passage (4).

2. The fresh air system of claim 1, wherein, At least part of a surface of the flow guide component (1) is provided with a first heat insulation material configured to hinder heat transfer from the second exhaust air passage (11) to an outside of the flow guide component (1).

3. The fresh air system of claim 2, wherein, The air chamber body (7) is arranged at one side of the condenser (10) along a first direction (z), the air inlet of the fresh air passage (4) is arranged at one side of the air chamber body (7) close to the flow guide component (1) along the first direction (z), the air inlet of the fresh air passage (4) and the flow guide component (1) are arranged in a staggered manner along the first direction (z) and keep a first distance, and the air inlet of the fresh air passage (4) and the flow guide component (1) are arranged in a staggered manner along a second direction (y) perpendicular to the first direction (z) and the air outlet direction of the condenser (10) and keep a second distance.

4. The fresh air system of claim 2, wherein, An outer contour of the air outlet of the condenser (10) coincides with an outer contour of a flow passage cross section of the second exhaust air passage (11) in a projection of the flow passage cross section.

5. The fresh air system of claim 1, wherein, The air inlet (14) is arranged at a region of a side wall of the first exhaust air passage (8) opposite to the second air outlet (13).

6. The fresh air system of claim 1, wherein, At least part of a wall surface of the air chamber is provided with a second heat insulation material configured to hinder heat transfer from the air chamber to the target area (A).

7. The fresh air system of claim 1, wherein, ​ 8. The fresh air system according to any one of claims 1 to 7, wherein, 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 rotating 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, wherein, The third temperature detection device (18) is configured to detect the temperature Te of an external environment in which the fresh air system is located, so as to adjust the rotating 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, wherein, The first pressure detection device (19) is configured to detect the gas pressure of the fresh air channel (4), and the second pressure detection device (20) is configured to detect the gas pressure of the first exhaust channel (8), so as to adjust the rotating speed F1 of the fresh air fan (3) according to the difference ΔP between the gas pressure of the fresh air channel (4) and the gas pressure of the first exhaust channel (8).

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

12. A refrigeration appliance characterized in that, The storage compartment; And The fresh air system according to any one of claims 1 to 11, wherein the internal space of the storage compartment is the target area (A). 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), the rotating speed F2 of the exhaust fan (9) is adjusted, so as to adjust the exhaust speed of the gas in the gas compartment.

13. A control method of a fresh air system according to any one of claims 1 to 11, characterized by, 14. The control method of the fresh air system according to claim 13, wherein, If the humidity RHr of the compartment body (7) is greater than a 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), the rotating speed F2 of the exhaust fan (9) is increased by a first preset rotating speed value ΔF21; and / or If the humidity RHr of the compartment body (7) is less than or equal to the first preset humidity value RH1, and the change rate of the temperature Tc of the condenser (10) is greater than a preset change rate value r0, the rotating speed F2 of the exhaust fan (9) is increased by a second preset rotating speed value ΔF22; and / or ​ ​ 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 change rate of the temperature Tc of the condenser (10) is greater than a preset change rate value r0, the rotation speed F2 of the exhaust fan (9) is increased by a second preset rotation speed value AF22. The first preset rotation speed value AF21 is greater than the second preset rotation speed value AF22.

15. The control method of the fresh air system according to claim 14, characterized in that, The first preset rotation speed value AF21 is determined according to the humidity RHr of the compartment body (7) and the change rate of the temperature Tc of the condenser (10), and / or the second preset rotation speed value AF22 is determined according to the change rate of the temperature Tc of the condenser (10).

16. The control method of the fresh air system according to claim 15, characterized in that, AF21 = b1 x (RHr - RH1) + c1 x (dTc / dt - r0), wherein b1 represents a first proportional coefficient, c1 represents a second proportional coefficient, dTc / dt represents the derivative of the temperature Tc of the condenser (10) with respect to time t; and / or AF22 = c2 x (dTc / dt - r0), wherein c2 represents a third proportional coefficient, dTc / dt represents the derivative of the temperature Tc of the condenser (10) with respect to time t.

17. The control method of a fresh air system according to any one of claims 13 to 16, wherein If the temperature Te of the external environment in which the fresh air system is located is less than a preset temperature value T0, the rotation speed F1 of the fresh air fan (3) is increased.

18. The control method of a fresh air system according to any one of claims 13 to 16, wherein, In response to the increase of the rotation speed F2 of the exhaust fan (9), the rotation speed F1 of the fresh air fan (3) is increased by a third preset rotation speed value AF11 according to the difference AP between the gas pressure of the fresh air channel (4) and the gas pressure of the first exhaust channel (8) and the increase AF2 of the rotation speed F2 of the exhaust fan (9).

19. The control method of the fresh air system according to claim 18, wherein, AF11 = d1 x AP x AF2, wherein d1 represents a fourth proportional coefficient.

20. The control method of a fresh air system according to any one of claims 13 to 16, wherein, If the humidity RHe of the external environment in which the fresh air system is located is less than a second preset humidity value RH2, the rotation speed F2 of the exhaust fan (9) is no longer increased, and the rotation speed F1 of the fresh air fan (3) remains unchanged.

21. A computer readable storage medium having stored thereon a computer program which, when executed by a processor, implements the control method of the fresh air system according to any one of claims 13 to 20.

22. A control device characterized by comprising: comprising: a memory; and a processor coupled to the memory, the processor being configured to execute the control method as claimed in any one of claims 13 to 20 based on instructions stored in the memory.

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