Refrigerator air circulation system and refrigerator

Abstract

The utility model discloses a refrigerator air circulation system and refrigerator, include: with the heat exchanger connection's air supply air duct, the heat exchanger is used for cooling the airflow of flowing into air supply air duct, air supply air duct is provided with first fan and second fan in the first direction along perpendicular to its extension direction side by side, first fan is connected with first chamber through first air duct, and the airflow of first fan exhaust is sent to first chamber through first air duct alone, second fan is connected with second chamber through second air duct, and the airflow of second fan exhaust is sent to second chamber through second air duct alone, wherein, the rotational speed of first fan is greater than second fan. First chamber can reach its set temperature threshold value faster like this, to make first fan and compressor stop working, and the start -stop of compressor is not influenced by the temperature of second chamber, thereby reduce the working time of compressor and first fan, reduced the starting rate of compressor, reach the purpose of reducing energy consumption.

Description

Technical Field

[0001] This utility model relates to the field of refrigeration technology, and in particular to a refrigerator air circulation system and a refrigerator. Background Technology

[0002] Traditional refrigerators typically use a single-fan, single-duct air circulation system. In this design, the freezer and refrigerator ducts are interconnected, sharing the same cold airflow. This means the compressor only stops working when both the refrigerator and freezer compartments reach their respective set temperature thresholds, increasing compressor operating time and thus energy consumption. Furthermore, the single-fan, single-duct design tends to result in a "jet-like" distribution of cold air. Due to the cumulative resistance along the duct, compartments closer to the duct reach their temperature thresholds faster, while those further away require more time, further increasing compressor operating time and energy consumption. Utility Model Content

[0003] This invention provides a refrigerator air circulation system and a refrigerator, which solves the problem of high energy consumption in existing air circulation systems.

[0004] The technical solution of this utility model is a refrigerator air circulation system, comprising:

[0005] An air supply duct connected to a heat exchanger, the heat exchanger being used to cool the airflow flowing into the air supply duct;

[0006] A first fan and a second fan are arranged side by side in the air supply duct along a first direction perpendicular to its extension direction.

[0007] The first fan is connected to the first room through the first air duct, and the airflow discharged by the first fan is delivered to the first room separately through the first air duct;

[0008] The second fan is connected to the second chamber through the second air duct, and the airflow discharged by the second fan is separately delivered to the second chamber through the second air duct;

[0009] The first fan rotates at a higher speed than the second fan.

[0010] Furthermore, the air intake surfaces of both the first fan and the second fan are configured as follows:

[0011] Within the dynamic range of the phase change heat transfer interface of the heat exchanger, it remains parallel to the average position of the phase change heat transfer interface.

[0012] Furthermore, the first air duct and the second air duct are completely independent and do not communicate with each other.

[0013] Furthermore, the air supply duct is provided with a front cover and a rear cover that fit together.

[0014] The front cover of the air duct is provided with a first mounting cavity along a first direction, and a first fan is matched and installed in the first mounting cavity.

[0015] The rear cover of the air duct is provided with a second mounting cavity corresponding to the first mounting cavity. The side of the second mounting cavity is provided with air suction holes at intervals. The second mounting cavity is matched with a second fan.

[0016] The first air duct is connected to the air supply duct through the air intake hole.

[0017] Furthermore, the center of the first mounting cavity and the center of the second mounting cavity are collinear, and the direction of the connecting line is parallel to the first direction.

[0018] Furthermore, a first air duct is formed between the front cover and the rear cover of the air duct that are fitted together.

[0019] Furthermore, when there are multiple first chambers, the front cover of the air duct is vertically provided with multiple sets of air inlet holes, each set of air inlet holes communicating with the corresponding first chamber.

[0020] Furthermore, the return air vent of the second chamber is connected to the heat exchanger through a return air duct. The end of the return air duct near the heat exchanger is provided with a honeycomb-shaped silica gel dehumidification structure. The silica gel dehumidification structure is provided with multiple airflow channels so that the airflow in the return air duct flows to the heat exchanger through the airflow channels.

[0021] Furthermore, a water receiving tray is provided below the silica gel dehumidification structure, which is used to collect water droplets that drip off after the silica gel dehumidification structure becomes saturated with moisture.

[0022] This utility model also proposes a refrigerator, including the refrigerator air circulation system described above.

[0023] Compared with the prior art, the present invention has at least the following beneficial effects:

[0024] This invention uses a first fan to draw cold air from the supply air duct and deliver it separately to the first room through the first air duct. A second fan draws cold air from the supply air duct and delivers it separately to the second room through the second air duct. Because the first fan rotates faster than the second fan, the first room reaches its set temperature threshold more quickly, causing the first fan and compressor to stop working. Simultaneously, the compressor's start-up and shutdown are unaffected by the temperature of the second room, thereby reducing the operating time of the compressor and the first fan, lowering the compressor's operating rate, and achieving the goal of reducing energy consumption. Attached Figure Description

[0025] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention pertains; the terminology used herein in the specification is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention; the terms "comprising" and "having," and any variations thereof, in the specification, claims, and accompanying drawings of this invention are intended to cover non-exclusive inclusion. The terms "first," "second," etc., in the specification, claims, or accompanying drawings of this invention are used to distinguish different objects and not to describe a particular order.

[0026] To more clearly illustrate the technical solutions in the embodiments of this utility model, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this utility model. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0027] Figure 1 This is a partial cross-sectional view of the refrigerator proposed in this utility model;

[0028] Figure 2 for Figure 1 An enlarged schematic diagram of reference numeral A in the attached figure;

[0029] Figure 3 This is a schematic diagram of the gas flow in the refrigerator air circulation system proposed in this utility model;

[0030] Figure 4 This is a partially exploded view of the refrigerator proposed in this utility model;

[0031] Figure 5 This is a partial internal schematic diagram of the refrigerator proposed in this utility model.

[0032] Figure label:

[0033] 10. Heat exchanger;

[0034] 20. Air supply duct; 201. Front cover of the duct; 202. Rear cover of the duct; 203. First mounting cavity; 204. Air intake hole; 205. Second mounting cavity; 206. Air inlet hole;

[0035] 30. First fan;

[0036] 40. Second fan

[0037] 50. First air duct;

[0038] 60. Second air duct;

[0039] 70. Return air duct;

[0040] 80. Silica gel dehumidification structure;

[0041] 90. Water tray. Detailed Implementation

[0042] To make the technical problem to be solved, the technical solution, and the beneficial effects of this utility model clearer, the present utility model will be further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the present utility model and are not intended to limit the present utility model. Therefore, a feature pointed out in this specification is used to describe one feature of one embodiment of the present utility model, and does not imply that every embodiment of the present utility model must have the described feature. Furthermore, it should be noted that this specification describes many features. Although certain features may be combined to illustrate possible system designs, these features may also be used in other combinations not explicitly stated. Therefore, unless otherwise stated, the described combinations are not intended to be limiting.

[0043] The principle and structure of this utility model will be described in detail below with reference to the accompanying drawings and embodiments.

[0044] Traditional refrigerators typically use a single-fan, single-duct air circulation system. In this design, the freezer and refrigerator ducts are interconnected, sharing the same cold air circulation. This means the compressor only stops working when both the refrigerator and freezer compartments reach their respective set temperature thresholds, increasing compressor operating time and thus energy consumption. Furthermore, the single-fan, single-duct design tends to result in a "jet-like" distribution of cold air. Due to the cumulative resistance along the duct, compartments closer to the duct reach their temperature thresholds faster, while compartments further away require more time, further increasing compressor operating time and energy consumption.

[0045] Therefore, in some embodiments, such as Figure 1 and Figure 3 As shown, this utility model proposes a low-energy refrigerator air circulation system, comprising:

[0046] An air supply duct 20 is connected to a heat exchanger 10, the heat exchanger 10 being used to cool the airflow flowing into the air supply duct 20;

[0047] The air supply duct 20 has a first fan 30 and a second fan 40 arranged side by side along a first direction perpendicular to its extension direction.

[0048] The exhaust surface of the first fan 30 is connected to the first room (not shown, same throughout) through the first air duct 50, and the airflow discharged by the first fan 30 is separately delivered to the first room through the first air duct 50.

[0049] The exhaust surface of the second fan 40 is connected to the second chamber through the second air duct 60, and the airflow discharged by the second fan 40 is separately delivered to the second chamber (not shown, same throughout the text) through the second air duct 60;

[0050] The first fan 30 has a higher rotational speed than the second fan 40.

[0051] It should be noted that the first direction proposed in this embodiment is the X-axis direction, and the extension direction of the air supply duct 20 is the Z-axis direction. The first compartment is preferably a freezer compartment, and the second compartment is preferably a refrigerator compartment, with the first compartment located below the second compartment. The first fan 30 is preferably a high-speed centrifugal fan, the second fan 40 is preferably a low-speed centrifugal fan, and the heat exchanger 10 is preferably an evaporator. Temperature sensors are installed in both the first and second compartments to monitor the temperature of the corresponding compartments in real time.

[0052] The air supply duct 20 is vertically located at the top of the evaporator compartment (where the heat exchanger 10 is installed), forming an upper and lower stacked structure. In this way, the first fan 30 and the second fan 40 draw airflow, which passes through the heat exchanger 10 to form cold air before flowing into the air supply duct 20. Because the cold air has a high density, it can accelerate its flow in the air supply duct 20 with the help of gravity, reducing the power consumption of the first fan 30 and the second fan 40 in overcoming frictional resistance.

[0053] The refrigerator's air circulation system also includes a control unit, which is electrically connected to the first fan 30, the second fan 40, and a temperature sensor. The system also includes a compressor and a condenser to form a refrigeration cycle between the compressor, condenser, and heat exchanger 10.

[0054] Thus, when the refrigerator's air circulation system is first started, the control unit simultaneously activates the first fan 30 and the second fan 40. This causes the first and second fans 30 to draw airflow, which then flows through the heat exchanger 10 and into the air supply duct 20. As the airflow passes through the heat exchanger 10, it exchanges heat with the heat exchanger 10 to form cold air. At this time, the first fan 30 rotates at high speed, drawing more cold air from the air supply duct 20 and delivering it separately to the first compartment (e.g., through the first air duct 50). Figure 3 The first room receives refrigerated air from the air supply duct 20, which provides rapid cooling. The second fan 40 rotates at low speed, drawing a smaller amount of cold air from the air supply duct 20 and delivering it separately to the second room (e.g., through the second air duct 60). Figure 3The refrigerated air outlet in the first and second compartments maintains a constant refrigerated temperature, preventing cold air from concentrating in specific areas and achieving precise temperature control. This avoids frequent compressor starts and stops, reducing energy consumption. The control unit determines the on / off state of the corresponding fan based on the set temperature thresholds for both the first and second compartments. Specifically:

[0055] If the temperatures of the first and second chambers simultaneously reach their respective temperature thresholds, both the first fan 30 and the second fan 40 will stop working, and the compressor will also stop working.

[0056] If the temperature of the first chamber reaches the corresponding temperature threshold first, both the first fan 30 and the compressor stop working, while the second fan 40 continues to work. At this time, the low temperature of the heat exchanger 10 (equivalent to an evaporator, the same throughout) is used to meet the cooling requirements of the second chamber until the temperature of the second chamber reaches the corresponding temperature threshold, at which point the second fan 40 stops working. This reduces the working time of the first fan 30 and the compressor, thereby reducing energy consumption. Even if the compressor stops, the remaining cooling capacity of the heat exchanger 10 can still be continuously delivered to the second chamber through the second fan 40, maintaining the temperature of the second chamber at the set temperature, reducing the temperature difference in the second chamber, and achieving precise temperature control. The start and stop of the compressor are not affected by the temperature of the second chamber, thereby reducing the compressor's operating rate and reducing energy consumption.

[0057] If the temperature of the second chamber reaches the corresponding temperature threshold first, the second fan 40 stops working, while the first fan 30 and the compressor continue to work until the temperature of the first chamber reaches the corresponding temperature threshold, at which point the first fan 30 and the compressor can stop working. This reduces the working time of the second fan 40, thereby reducing energy consumption.

[0058] Therefore, this utility model uses a first fan 30 to draw cold air from the supply air duct 20 and deliver it separately to the first room through the first air duct 50, and a second fan 40 to draw cold air from the supply air duct 20 and deliver it separately to the second room through the second air duct 60. At this time, because the rotation speed of the first fan 30 is greater than that of the second fan 40, the first room can reach its set temperature threshold more quickly, so that the first fan 30 and the compressor stop working. At the same time, the start and stop of the compressor is not affected by the temperature of the second room, thereby reducing the working time of the compressor and the first fan 30, thereby reducing the compressor's operating rate and achieving the purpose of reducing energy consumption.

[0059] Furthermore, a first fan 30 and a second fan 40 are arranged side by side along the first direction inside the air supply duct 20, which reduces the space occupied by the air circulation system.

[0060] Moreover, compared with the traditional technology that uses multiple evaporators for independent temperature control, this utility model can achieve precise temperature control with just one heat exchanger 10, which is simpler in structure and lower in cost.

[0061] Compared to the single-fan, single-duct design of traditional air circulation systems, where the fan operates at a constant speed and the airflow distribution depends entirely on the duct size and airflow path, making precise temperature control of the rooms difficult, this invention uses a first fan 30 and a second fan 40 to form two independent air circulation systems that do not interfere with each other. When the first room requires cooling, the first fan 30 operates; when the second room requires cooling, the second fan 40 operates, reducing the compressor's operating rate and thus facilitating precise temperature control of both rooms and reducing energy consumption.

[0062] In some embodiments, the air intake surfaces of both the first fan 30 and the second fan 40 are configured as follows:

[0063] Within the dynamic range of the phase change heat transfer interface of the heat exchanger 10, it remains parallel to the average position of the phase change heat transfer interface.

[0064] It should be noted that the phase change heat transfer interface proposed in this embodiment is equivalent to the evaporation surface of the evaporator. Furthermore, the extension direction of the air supply duct 20 is parallel to the arrangement plane of the heat exchanger 10, thereby ensuring that the airflow direction within the air supply duct 20 is perpendicular to the fin gaps. The airflow penetrates the fin gaps perpendicularly, increasing the contact area and time between the airflow and the fins, and improving the refrigerant's heat absorption efficiency.

[0065] In contrast to traditional air circulation systems, which draw and deliver air from the front with the air intake surface perpendicular to the average position of the evaporation surface, resulting in high-speed airflow through the fin gaps of the evaporator (typically >3m / s) and creating a strongly mixed airflow field, this embodiment maintains the air intake surfaces of the first fan 30 and the second fan 40 parallel to the average position of the phase change heat transfer interface. This makes the air intake surfaces of the first fan 30 and the second fan 40 perpendicular to the corresponding fan blades, forming a laminar air lake. The cold air naturally sinks due to the density difference, thereby improving the air intake efficiency of the first fan 30 and the second fan 40, enhancing the heat exchange efficiency, reducing the cold loss of the heat exchanger 10, and improving the refrigeration efficiency of the refrigerator air circulation system.

[0066] In some embodiments, the first air duct 50 and the second air duct 60 are completely independent and do not communicate with each other.

[0067] It should be noted that the first air duct 50 is located on one side of the first fan 30 along the first direction, and the second air duct 60 is located above the second fan 40.

[0068] In this way, the first fan 30 can distribute more cooling capacity to the first room through the first air duct 50, so that the first room can be cooled quickly. Since the second room requires less cooling capacity than the first room, the second fan 40 distributes less cooling capacity to the second room through the first air duct 50. In this way, the first room can reach the set temperature threshold faster than the second room, thereby reducing the working time of the compressor and the first fan 30 and achieving the purpose of reducing energy consumption.

[0069] In some embodiments, to ensure that both the first fan 30 and the second fan 40 can draw cold air from the air supply duct 20, such as Figure 2 and Figures 4-5 As shown, the air supply duct 20 is provided with a front cover 201 and a rear cover 202 that cover each other.

[0070] The air duct front cover 201 is provided with a first mounting cavity 203 along the first direction, and a first fan 30 is matched and installed in the first mounting cavity 203;

[0071] The air duct rear cover 202 is provided with a second mounting cavity 205 corresponding to the first mounting cavity 203. The second mounting cavity 205 is provided with air suction holes 204 at intervals on its side. The second mounting cavity 205 is fitted with a second fan 40.

[0072] The first air duct 50 is connected to the air supply duct 20 through the air intake hole 204.

[0073] It should be noted that the air intake hole 204 is located below the second mounting cavity 205, so that the cold air in the air supply duct 20 can be simultaneously drawn by the first fan 30 and the second fan 40. Furthermore, the second air duct 60 communicates with the air supply duct 20 through the second mounting cavity 205.

[0074] In this way, the first fan 30 can directly draw cold air from the supply air duct 20, and the second fan 40 draws cold air from the supply air duct 20 through the air intake hole 204, thereby splitting the cold air in the supply air duct 20 into two streams, which flow to the first air duct 50 and the second air duct 60 respectively, forming two independent air circulation systems that do not interfere with each other. When the first room has a cooling demand, the first fan 30 works; when the second room has a cooling demand, the second fan 40 works, reducing the compressor's operating rate, which is conducive to precise control of the temperature of the first and second rooms and reduces energy consumption.

[0075] In a further embodiment, the center of the first mounting cavity 203 and the center of the second mounting cavity 205 are collinear, and the direction of the connecting line is parallel to the first direction.

[0076] By setting the first fan 30 and the second fan 40 in this way, the length of the air supply duct 20 extending along the first direction can be reduced, thereby reducing the space occupied by the air circulation system.

[0077] Specifically, such as Figure 1 and Figure 4 As shown, a first air duct 50 is formed between the front cover 201 and the rear cover 202 of the air duct that are fitted together.

[0078] This design does not significantly increase the thickness of the first air duct 50, making the structure of the first air duct 50 more compact and improving the overall volume ratio of the refrigerator.

[0079] Among them, such as Figures 4-5 As shown, when there are multiple first chambers, the front cover 201 of the air duct is vertically provided with multiple sets of air inlet holes 206, and each set of air inlet holes 206 communicates with the corresponding first chamber.

[0080] It should be noted that multiple sets of air inlets 206 at the same height along the second direction (equivalent to the Y-axis direction) of the duct front cover 201 supply cooling to the same first chamber. Of course, each set of air inlets 206 can also supply cooling to different first chambers, which is not limited here.

[0081] In this way, the cold air drawn by the first fan 30 from the air supply duct 20 can be simultaneously delivered to different first rooms through the air inlet 206 to ensure the cooling needs of multiple first rooms.

[0082] Of course, multiple second rooms can be provided, so that the cold air drawn by the second fan 40 from the air supply duct 20 can be delivered to different second rooms through the second air duct 60.

[0083] In some embodiments, such as Figure 1 As shown, the return air vent of the second chamber is connected to the heat exchanger 10 through a return air duct 70. The end of the return air duct 70 near the heat exchanger 10 is provided with a honeycomb-shaped silica gel dehumidification structure 80. The silica gel dehumidification structure 80 is provided with multiple airflow channels so that the airflow in the return air duct 70 flows to the heat exchanger 10 through the airflow channels.

[0084] Understandably, one end of the return air duct 70 is connected to the return air inlet of the second chamber, and the other end of the return air duct 70 is directly connected to the evaporator cavity (i.e., the sealed space that houses the heat exchanger 10), so as to realize the circulation and recovery of cold air. Of course, the airflow in the first chamber will also be connected to the evaporator cavity through the refrigeration return air duct. In this way, through the heat exchange in the evaporator cavity, the return gas is cooled again and re-enters the refrigeration cycle, ensuring the temperature stability of the first and second chambers.

[0085] Furthermore, the silica gel dehumidification structure 80 extends radially along the end of the return air duct 70 and completely covers the corresponding radial cross-section. The silica gel dehumidification structure 80 is made of silica gel, a porous adsorbent material whose internal micropores provide a large specific surface area, enabling it to adsorb water vapor molecules from the air through van der Waals forces and hydrogen bonds. When the silica gel reaches its adsorption limit, the adsorption rate equals the desorption rate, forming a dynamic equilibrium state. At this point, the silica gel cannot absorb further moisture, i.e., it is saturated. In a saturated state, if the ambient humidity remains high or if it is not regenerated in time, water molecules on the silica gel surface will begin to desorb (backflow) due to the disruption of the adsorption equilibrium. Due to the porous structure of silica gel, the desorbed water may condense into liquid water and flow downwards along the silica gel surface or pores under gravity.

[0086] Thus, because the second compartment (equivalent to the refrigerator compartment) is opened more frequently during daily use, the airflow returning from the second compartment to the return air duct 70 (such as...) Figure 3 The refrigerated return air contains a lot of moisture, so a silica gel dehumidification structure 80 is installed at the end of the return air duct 70 to reduce the humidity of the airflow in the return air duct 70, thereby reducing the amount of frost on the heat exchanger 10, shortening the working time of the defrosting heater, increasing the defrosting interval, improving the cooling efficiency of the heat exchanger 10, reducing the compressor start-stop ratio, and achieving the goal of reducing energy consumption.

[0087] Furthermore, by setting multiple airflow channels within the silica gel dehumidification structure 80, it can ensure that the return airflow in the return air duct 70 can smoothly pass through the airflow channels and reach the evaporator cavity after passing through the silica gel dehumidification structure 80, thereby achieving the purpose of ventilation and return air; and when the return airflow flows into the airflow channel, the silica gel dehumidification structure 80 can dehumidify the return airflow.

[0088] In some embodiments, such as Figure 1 As shown, a water receiving tray 90 is provided below the silica gel dehumidification structure 80. The water receiving tray 90 is used to collect water droplets that drip from the silica gel dehumidification structure 80 after it has absorbed enough moisture.

[0089] It should be noted that the water receiving tray 90 is located directly below the heat exchanger 10. This is because defrosting water is generated when the heat exchanger 10 defrosts. At this time, a pipe is set directly below the silica gel dehumidification structure 80 in the water receiving tray 90 so that the water droplets dripping after the silica gel dehumidification structure 80 is saturated with moisture can flow into the water receiving tray 90 through the pipe. Then, the water collected in the water receiving tray 90 is directed into the evaporation plate, and the evaporation plate heats and vaporizes the introduced water before discharging it.

[0090] In other embodiments (not shown in the figures), a water receiving tray structure is provided directly below the silica gel dehumidification structure 80 and directly below the heat exchanger 10, and the two water receiving tray structures are connected by a pipe. The vertical height of the water receiving tray structure directly below the silica gel dehumidification structure 80 is greater than that of the water receiving tray structure directly below the heat exchanger 10.

[0091] In some embodiments, the present invention also provides a refrigerator including the refrigerator air circulation system described above.

[0092] In this way, when the refrigerator is turned on for the first time, the refrigerator's air circulation system starts up. Then, the control unit simultaneously starts the first fan 30 and the second fan 40 to draw in the cold air formed by heat exchange in the air duct 20 after heat exchange in the heat exchanger 10. At this time, the first fan 30 rotates at high speed, drawing more cold air from the air duct 20 and delivering it separately to the first compartment through the first air duct 50 to meet the rapid cooling needs of the first compartment. The second fan 40 rotates at low speed, drawing less cold air from the air duct 20 and delivering it separately to the second compartment through the second air duct 60 to maintain a constant refrigeration temperature in the second compartment, thereby avoiding the concentration of cold air in a specific area and achieving precise temperature control. At this time, because the speed of the first fan 30 is greater than that of the second fan 40, the first compartment can reach its set temperature threshold more quickly, so that the compressor and the first fan 30 stop working. At the same time, the start and stop of the compressor are not affected by the temperature of the second compartment, thereby reducing the working time of the compressor and the first fan 30, reducing the compressor's operating rate, and achieving the purpose of reducing energy consumption.

[0093] Furthermore, a first fan 30 and a second fan 40 are arranged side by side along the first direction inside the air supply duct 20. This arrangement can reduce the space occupied by the air circulation system and meet the requirements of thin-walled refrigerators.

[0094] Obviously, the embodiments described above are only some embodiments of this utility model, not all embodiments. The accompanying drawings show preferred embodiments of this utility model, but do not limit the patent scope of this utility model. This utility model can be implemented in many different forms; rather, the purpose of providing these embodiments is to provide a more thorough and comprehensive understanding of the disclosure of this utility model. Although this utility model has been described in detail with reference to the foregoing embodiments, those skilled in the art can still modify the technical solutions described in the foregoing specific embodiments, or make equivalent substitutions for some of the technical features. Any equivalent structures made using the content of this utility model specification and drawings, directly or indirectly applied to other related technical fields, are similarly within the patent protection scope of this utility model.

Claims

1. A refrigerator air circulation system, characterized in that, include: An air supply duct (20) is connected to a heat exchanger (10), the heat exchanger (10) being used to cool the airflow flowing into the air supply duct (20); The air supply duct (20) is provided with a first fan (30) and a second fan (40) arranged side by side along a first direction perpendicular to its extension direction; The first fan (30) is connected to the first room through the first air duct (50), and the airflow discharged by the first fan (30) is separately delivered to the first room through the first air duct (50); The second fan (40) is connected to the second chamber through the second air duct (60), and the airflow discharged by the second fan (40) is separately delivered to the second chamber through the second air duct (60); The first fan (30) has a higher rotational speed than the second fan (40).

2. The refrigerator air circulation system according to claim 1, characterized in that, The suction surfaces of both the first fan (30) and the second fan (40) are configured as follows: Within the dynamic range of the phase change heat transfer interface of the heat exchanger (10), it remains parallel to the average position of the phase change heat transfer interface.

3. The refrigerator air circulation system according to claim 1, characterized in that, The first air duct (50) and the second air duct (60) are completely independent and do not communicate with each other.

4. The refrigerator air circulation system according to claim 1, characterized in that, The air supply duct (20) is provided with a front cover (201) and a rear cover (202) that cover each other; The air duct front cover (201) is provided with a first mounting cavity (203), and a first fan (30) is matched and installed in the first mounting cavity (203); The air duct rear cover (202) is provided with a second mounting cavity (205) corresponding to the first mounting cavity (203). The second mounting cavity (205) is provided with suction holes (204) at intervals on its side. The second mounting cavity (205) is fitted with a second fan (40). The first air duct (50) is connected to the air supply duct (20) through the air intake hole (204).

5. The refrigerator air circulation system according to claim 4, characterized in that, The center of the first mounting cavity (203) and the center of the second mounting cavity (205) are collinear, and the direction of the connecting line is parallel to the first direction.

6. The refrigerator air circulation system according to claim 4, characterized in that, A first air duct (50) is formed between the front cover (201) and the rear cover (202) of the air duct that are fitted together.

7. The refrigerator air circulation system according to claim 4, characterized in that, When there are multiple first chambers, the front cover (201) of the air duct is vertically provided with multiple sets of air inlet holes (206), and each set of air inlet holes (206) communicates with the corresponding first chamber.

8. The refrigerator air circulation system according to claim 1, characterized in that, The return air vent of the second chamber is connected to the heat exchanger (10) through a return air duct (70). The end of the return air duct (70) near the heat exchanger (10) is provided with a honeycomb-shaped silica gel dehumidification structure (80). The silica gel dehumidification structure (80) is provided with multiple airflow channels so that the airflow in the return air duct (70) flows to the heat exchanger (10) through the airflow channels.

9. The refrigerator air circulation system according to claim 8, characterized in that, A water receiving tray (90) is provided below the silica gel dehumidification structure (80), and the water receiving tray (90) is used to collect water droplets that drip after the silica gel dehumidification structure (80) is saturated with water.

10. A refrigerator, characterized in that, Includes the refrigerator air circulation system according to any one of claims 1 to 9.

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