Pre-dehumidification structure, refrigeration device and temperature control method of refrigeration device

Abstract

The application provides a pre-dehumidification structure, a refrigeration device and a temperature control method of the refrigeration device. The pre-dehumidification structure comprises a base body and a pre-dehumidification module. The base body is provided with a return air channel for connecting a refrigeration chamber and a freezing air duct. The base body is also provided with a hot-end air supply air duct. The pre-dehumidification module comprises a thermoelectric refrigeration piece, a cold-end heat sink, a hot-end heat sink and a fan. The cold-end heat sink is attached to the cold end of the thermoelectric refrigeration piece and is arranged in the return air channel. The hot-end heat sink is attached to the hot end of the thermoelectric refrigeration piece and is arranged in the hot-end air supply air duct. The fan is arranged in the hot-end air supply air duct and is used to suck the cold air of the freezing chamber into the hot-end air inlet, and then discharge the cold air from the hot-end air outlet into the refrigeration chamber after the cold air flows through the hot-end heat sink. The pre-dehumidification structure in the application uses the cold end of the thermoelectric refrigeration piece to condense and dehumidify the air returning to the freezing air duct, so that the moisture content of the air before entering the evaporator is significantly reduced, and the amount of frost on the surface of the evaporator is reduced at the source.

Description

Technical Field

[0001] This application relates to the technical field of refrigeration equipment, and in particular to a pre-dehumidification structure, refrigeration equipment, and a temperature control method for refrigeration equipment. Background Technology

[0002] Frost-free refrigerators have become the mainstream in the market due to their advantages such as frost-free operation and uniform temperature. However, frost inevitably forms on the evaporator surface during operation. When the frost layer accumulates to a certain thickness, it will seriously affect the heat exchange efficiency of the evaporator, leading to a decrease in cooling capacity and an increase in energy consumption. Therefore, regularly defrosting the evaporator is an essential and crucial step for frost-free refrigerators.

[0003] Currently, the mainstream defrosting methods in the industry are electric heating and hot gas defrosting. Electric heating relies on a defrosting heater located below the evaporator. When powered on, the surface heats up, and heat is transferred to the fins through radiation and natural convection, melting the frost layer from the outside in. Defrosting water is discharged along the guide channel, and the system stops heating once the evaporator temperature reaches the set value. Hot gas defrosting utilizes high-temperature gaseous refrigerant discharged from the compressor, which enters the evaporator in reverse through a bypass pipe. The refrigerant condenses and releases heat inside the finned tubes, melting the frost layer from the inside out. After defrosting, the bypass valve closes, and the system resumes the forward refrigeration cycle.

[0004] The two methods mentioned above alleviate the problem of evaporator frosting to some extent, but their solutions focus on "how to remove the frost after it forms," ​​without providing a feasible solution for how to actively intercept and remove water vapor before it reaches the evaporator. Summary of the Invention

[0005] This application provides a pre-dehumidification structure, a refrigeration device, and a temperature control method for the refrigeration device, which can solve the problem of reducing the amount of frost on the evaporator surface at the source.

[0006] In a first aspect, this application provides a pre-dehumidification structure applied to refrigeration equipment, which includes a freezer compartment, a refrigerator compartment, and a refrigeration air duct. The pre-dehumidification structure includes: The base is located between the freezer compartment and the refrigerator compartment; a return air duct connecting the refrigerator compartment and the freezer air duct is opened on the base; a hot end air supply duct is also opened on the base, the hot end air supply duct has a hot end air inlet and a hot end air outlet, the hot end air inlet is connected to the freezer compartment, and the hot end air outlet is connected to the refrigerator compartment. The pre-dehumidification module is located inside the substrate and includes: Thermoelectric cooling element, which has a cold end and a hot end; The cold end heat sink is attached to the cold end of the thermoelectric cooling chip and is located in the return air duct. The hot-end radiator is attached to the hot end of the thermoelectric cooling chip and is installed in the hot-end air supply duct. The fan is installed in the hot-end air supply duct to draw in the cold air from the freezer compartment through the hot-end air inlet, and after flowing through the hot-end radiator, it is discharged into the refrigerator compartment from the hot-end air outlet.

[0007] The beneficial effects of the pre-dehumidification structure provided in this application are as follows: By setting a pre-dehumidification structure between the freezer and refrigerator compartments, the cold end of the thermoelectric cooling element condenses and dehumidifies the air returning to the freezer duct, significantly reducing the moisture content of the air before it enters the evaporator, thereby reducing the amount of frost on the evaporator surface at the source. Compared to the passive defrosting approach in existing technologies that only focuses on "how to remove frost after it forms," ​​this application achieves active interception and removal of water vapor, effectively slowing down the rate of frost accumulation, extending the defrosting cycle, and reducing the defrosting frequency and corresponding energy consumption. In addition, the pre-dehumidification structure starts operating before the refrigerator compartment needs to be refrigerated. The low-temperature air (originating from the freezer compartment) discharged from its hot end outlet can pre-cool the refrigerator compartment. When the external heat load is low, this pre-cooling effect is sufficient to delay the compressor start-up, reducing the number of compressor start-ups and shutdowns and the number of refrigeration cycles of the freezer evaporator, further reducing the overall operating energy consumption of the refrigeration equipment.

[0008] In one possible design, the fan is a centrifugal fan; the hot-end airflow duct includes: The first part is located on one side of the return air duct and is connected to the hot end air outlet; the fan is installed in the first part. The second part is located on the side of the first part that is away from the return air duct and is connected to the hot end air inlet. The third part extends along the axial direction of the fan and communicates with the first and second parts respectively.

[0009] The above technical solution has the following advantages or beneficial effects: The centrifugal fan is located in the first section, and its radial airflow characteristics match those of the first section. This allows it to generate high static pressure within a limited space, overcoming duct resistance and ensuring smooth airflow through the hot-end radiator and stable discharge from the hot-end outlet. The second section is located on the side of the first section opposite to the return air channel and communicates with the hot-end inlet, used to introduce low-temperature air from the freezer compartment. The third section extends along the fan axis, connecting the first and second sections respectively, forming a complete airflow path from the hot-end inlet to the fan and then to the hot-end outlet. This three-section duct layout spatially separates the inlet section, fan drive section, and outlet section, avoiding short-circuiting of the inlet and outlet air. Simultaneously, it allows the fan, hot-end radiator, and duct structure to form a compact integrated unit, reducing the space occupied by the pre-dehumidification structure and improving the utilization rate of the cabinet space.

[0010] In one possible design approach, the cold-end heatsink includes: Mounting plate, which is attached to the cold end of the thermoelectric cooling element; The second fin is mounted on the mounting plate, and both the second fin and the mounting plate are located in the return air duct.

[0011] The above technical solution has the following advantages or beneficial effects: The mounting plate acts as a heat conduction bridge between the cold end of the thermoelectric cooling chip and the second fin, ensuring that the cooling capacity is efficiently transferred from the thermoelectric cooling chip to the second fin. The second fin increases the contact area between the cold end and the return air, enhancing the heat exchange efficiency of condensation and dehumidification, allowing water vapor in the return air to condense and precipitate quickly on the surface of the second fin. By placing the second fin and the mounting plate as a whole in the return air channel, the cold end radiator is directly exposed to the return airflow, resulting in rapid dehumidification response. Furthermore, condensate can flow downwards along the second fin under gravity and be collected and discharged, preventing water accumulation from affecting heat exchange performance.

[0012] In one possible design approach, the hot-end heatsink includes: A heat sink is attached to the hot end of a thermoelectric cooling chip. The heat sink is located in the first part and between the inner wall of the first part and the fan.

[0013] The above technical solution has the following advantages or beneficial effects: the heat sink directly receives the heat from the hot end of the thermoelectric cooling chip and diffuses it to the contact area with the airflow in the first part, ensuring that the heat from the hot end is removed in a timely and efficient manner, and maintaining the temperature difference between the hot and cold ends of the thermoelectric cooling chip.

[0014] In one possible design, the first part is shaped like a volute, with the outer contour of the heat sink resembling the inner wall of the first part.

[0015] The above technical solution has the following advantages or beneficial effects: The volute structure is a classic air duct form adapted for centrifugal fans. Its gradually expanding cross-sectional area along the circumference can effectively collect the radially discharged airflow of the fan and efficiently convert the kinetic energy of the airflow into static pressure, reducing eddy current losses and improving air delivery efficiency. The outer contour of the heat sink conforms to the inner wall of the volute, allowing the heat sink to obtain the maximum unfolded area within a limited space. At the same time, its curved shape fits the airflow streamline, reducing flow separation and resistance losses when the airflow flows around the heat sink, ensuring smooth airflow within the air duct. In addition, the conformal arrangement makes the flow channel gap between the heat sink and the inner wall of the first part uniform, avoiding uneven heat exchange caused by excessively high or low local wind speeds, and improving the overall uniformity and reliability of heat dissipation at the hot end.

[0016] In one possible design, a thermally conductive adhesive layer is applied between the hot end of the thermoelectric cooler and the heat sink, and between the cold end of the thermoelectric cooler and the mounting plate.

[0017] The above technical solution has the following advantages or beneficial effects: the thermally conductive adhesive layer fills the microscopic gap between the thermoelectric cooler and the heat sink, significantly reducing the contact thermal resistance and enabling heat to be efficiently transferred from the thermoelectric cooler to the heat sink and mounting plate, thus improving the heat transport efficiency of the hot and cold ends of the thermoelectric cooler. Simultaneously, the thermally conductive adhesive layer has a certain degree of elasticity and adhesion, which, while playing a thermal conductive role, can also buffer vibration and fix the relative position, improving the assembly reliability and long-term operational stability between the thermoelectric cooler and the heat sink, and avoiding the problem of increased contact thermal resistance due to mechanical loosening.

[0018] In one possible design, a mounting groove is provided on the base between the first part and the return air duct, and the thermoelectric cooling element is embedded in the mounting groove.

[0019] The above technical solution has the following advantages or beneficial effects: The mounting groove provides a precise positioning reference for the thermoelectric cooling element, ensuring the accurate position of the thermoelectric cooling element in the thickness direction, so that the cold end and the hot end accurately correspond to the return air channel and the first part respectively, ensuring the fitting accuracy of the heat sink at the cold and hot ends. The embedded structure allows the thermoelectric cooling element to be embedded inside the substrate, with both sides of the thermoelectric cooling element in the thickness direction adjacent to the return air channel and the hot end air supply channel respectively, achieving compact spatial isolation between the cold end and the hot end. This avoids direct thermal short circuits between the cold and hot ends, and minimizes the heat transfer path, improving the overall integration and structural compactness of the pre-dehumidification structure.

[0020] In one possible design, the cross-sectional area of ​​the second part gradually increases from the direction of the hot end air inlet; The area of ​​the hot end air outlet is 1 to 1.5 times the area of ​​the hot end air inlet.

[0021] The above technical solution has the following advantages or beneficial effects: From the second part to the hot-end air inlet, the cross-sectional area of ​​the second part gradually increases, forming a diffuser-type air inlet duct. This gradual diffuser structure causes the low-temperature air entering from the hot-end air inlet to gradually increase in velocity and gradually recover in static pressure as it flows towards the first part, reducing flow losses in the air inlet section. Simultaneously, it makes the airflow velocity distribution more uniform before entering the fan, which is beneficial for improving fan operating efficiency and reducing aerodynamic noise. The hot-end air outlet area is designed to be 1 to 1.5 times the area of ​​the hot-end air inlet, making the outlet area slightly larger than or equal to the inlet area. After the hot-end radiator heats the airflow (air volume expands), the outlet provides sufficient flow area, avoiding pressure increases within the duct and deterioration of fan operating conditions due to airflow obstruction. This ensures smooth air delivery and stable airflow, while also maintaining a moderate outlet airflow velocity to avoid direct airflow drying of food in the refrigerator compartment.

[0022] Secondly, this application also provides a refrigeration device, including the pre-dehumidification structure described in the first aspect.

[0023] Since the refrigeration equipment includes the pre-dehumidification structure mentioned in the first aspect, it also has the corresponding technical effect, which will not be elaborated here.

[0024] Thirdly, this application also provides a temperature control method for a refrigeration device, comprising: Obtain the actual temperature of the refrigerator compartment; When the actual temperature reaches the first threshold, the pre-dehumidification module is activated, the thermoelectric cooling chip is powered on, the fan rotates, and the cold air from the freezer compartment enters the hot-end air supply duct through the hot-end air inlet, flows through the hot-end radiator, and is discharged into the refrigerator compartment from the hot-end air outlet. The cold-end radiator condenses and dehumidifies the return air that enters the freezer air duct through the return air channel. When the actual temperature drops to the set temperature, the pre-dehumidification module stops operating; when the actual temperature continues to rise, the next step is initiated. When the actual temperature reaches the second threshold, the compressor and refrigeration fan are started. The second threshold is greater than the first threshold. During the compressor operation, the pre-dehumidification module runs continuously, and the cold end heat sink continuously condenses and dehumidifies the return air entering the refrigeration air duct through the return air channel. When the actual temperature drops to the set temperature, the compressor, refrigeration fan, and pre-dehumidification module are controlled to stop operating.

[0025] The beneficial effects of the temperature control method provided in this application are as follows: When the external heat load of the refrigeration equipment is small (such as at night, in winter, or when the door is opened infrequently), the temperature of the refrigerator compartment rises slowly. The pre-dehumidification structure starts operating before the refrigerator compartment needs to be refrigerated, and its hot-end air outlet continuously supplies low-temperature air into the refrigerator compartment. This pre-cooling effect is sufficient to offset the temperature rise in the refrigerator compartment, delaying or even avoiding the compressor starting. The number of compressor start-stop cycles is reduced, the number of refrigeration cycles of the evaporator is correspondingly reduced, and the overall energy consumption of the refrigeration equipment is reduced. When the external heat load is large (such as in summer, frequent door opening, or the placement of a large amount of hot food), the pre-cooling effect of the pre-dehumidification structure cannot completely offset the temperature rise in the refrigerator compartment. At this time, the compressor starts refrigeration normally, and the pre-dehumidification structure simultaneously performs the condensation dehumidification function. The moisture content of the return air entering the evaporator has been significantly reduced, the amount of frost on the evaporator is reduced, the subsequent defrosting heating time is shortened, and the defrosting energy consumption is reduced. Attached Figure Description

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

[0027] Figure 1 This is a schematic diagram of the refrigerator provided in an embodiment of this application; Figure 2 yes Figure 1 A diagram showing the refrigerator behind the hidden door; Figure 3 yes Figure 2 A diagram showing the refrigerator with the inner liner of the refrigerator compartment and the inner liner of the freezer compartment hidden. Figure 4 This is a schematic diagram of the pre-dehumidification structure provided in the embodiments of this application; Figure 5 yes Figure 4 A schematic diagram of the pre-dehumidification structure from another perspective; Figure 6 This is a cross-sectional view of the substrate provided in the embodiments of this application; Figure 7 This is a cross-sectional view of the substrate provided in an embodiment of this application from another perspective; Figure 8 This is a schematic diagram of the pre-dehumidification module provided in an embodiment of this application; Figure 9 This is a schematic diagram from another perspective of the pre-dehumidification module provided in the embodiments of this application; Figure 10 This is a cross-sectional view of the pre-dehumidification module provided in the embodiment of this application inside the substrate; Figure 11 This is a cross-sectional view of the pre-dehumidification structure provided in the embodiments of this application; Figure 12 This is a cross-sectional view from another perspective of the pre-dehumidification structure provided in the embodiments of this application; Figure 13 This is a flowchart of the refrigerator temperature control method provided in the embodiments of this application; Figure 14 This is a schematic diagram of the airflow inside the refrigerator under operating conditions. Figure 15 This is a schematic diagram of the airflow inside the refrigerator under operating condition two.

[0028] Figure label: 10. Substrate; 11. Return air duct; 12. Hot-end air supply duct; 121. Hot-end air inlet; 122. Hot-end air outlet; 123. First part; 124. Second part; 125. Third part; 13. Mounting slot; 20. Pre-dehumidification module; 21. Thermoelectric cooling chip; 22. Cold end heat sink; 221. Mounting plate; 222. Second fin; 23. Hot end heat sink; 231. Heat sink plate; 24. Fan; 100. Pre-dehumidification structure; 200. Box body; 201. Box door; 300. Refrigerator compartment; 301. Refrigerator inner liner; 400. Freezer compartment; 401. Inner liner of the freezer compartment; 500. Evaporator. Detailed Implementation

[0029] To make the objectives, technical solutions, and advantages of the embodiments of this application clearer, the technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0030] In the description of this application, "multiple" means at least two, such as two, three, etc., unless otherwise explicitly specified. In this application, unless otherwise explicitly specified and limited, the terms "installed," "connected," "linked," "fixed," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components, unless otherwise explicitly specified. Those skilled in the art can understand the specific meaning of the above terms in this application according to the specific circumstances.

[0031] In this application, unless otherwise expressly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature is in indirect contact with the second feature through an intermediate medium. Furthermore, "above," "on top of," and "over" the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0032] In the description of this application, it should be understood that the terms "inner," "outer," "upper," "bottom," "front," and "rear," etc., indicate the orientation or positional relationship (if any) based on the appendix. Figure 1 The orientations or positional relationships shown are for the purpose of facilitating and simplifying the description of this application, and are not intended to indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this application.

[0033] It should also be noted that in the embodiments of this application, the same reference numerals are used to represent the same component or part. For the same part in the embodiments of this application, the reference numerals may only be used to mark one part or component as an example. It should be understood that the reference numerals are also applicable to other identical parts or components.

[0034] Frost-free refrigerators have become the mainstream in the market due to their advantages such as frost-free operation and uniform temperature. However, frost inevitably forms on the evaporator surface during operation. When the frost layer accumulates to a certain thickness, it will seriously affect the heat exchange efficiency of the evaporator, leading to a decrease in cooling capacity and an increase in energy consumption. Therefore, regularly defrosting the evaporator is an essential and crucial step for frost-free refrigerators.

[0035] Currently, the mainstream defrosting methods in the industry are electric heating and hot gas defrosting. Electric heating relies on a defrosting heater located below the evaporator. When powered on, the surface heats up, and heat is transferred to the fins through radiation and natural convection, melting the frost layer from the outside in. Defrosting water is discharged along the guide channel, and the system stops heating once the evaporator temperature reaches the set value. Hot gas defrosting utilizes high-temperature gaseous refrigerant discharged from the compressor, which enters the evaporator in reverse through a bypass pipe. The refrigerant condenses and releases heat inside the finned tubes, melting the frost layer from the inside out. After defrosting, the bypass valve closes, and the system resumes the forward refrigeration cycle.

[0036] The two methods mentioned above alleviate the problem of evaporator frosting to some extent, but their solutions focus on "how to remove the frost after it forms," ​​without providing a feasible solution for how to actively intercept and remove water vapor before it reaches the evaporator.

[0037] In view of this, in order to solve the above-mentioned technical problems, this application provides a pre-dehumidification structure, a refrigeration device and a temperature control method for the refrigeration device. By setting a pre-dehumidification structure between the freezer and the refrigerator, the cold end of the thermoelectric cooling chip is used to condense and dehumidify the air flowing back to the refrigeration air duct, so that the moisture content of the air before entering the evaporator is significantly reduced, thereby reducing the amount of frost on the surface of the evaporator at the source.

[0038] To more conveniently illustrate the refrigeration equipment provided in the embodiments of this application, and as an example rather than a limitation, the technical solution of this application will be described in detail below using a refrigerator as an example. Optionally, the refrigeration equipment in this application can also be a freezer or other equipment with an air-cooling system.

[0039] Figure 1 This is a schematic diagram of a refrigerator provided in an embodiment of this application. Figure 2 yes Figure 1 The diagram shows the refrigerator behind the hidden door 201. Furthermore, for the convenience of the description of the embodiments below, an XYZ coordinate system is established for the refrigerator. Specifically, the width direction of the refrigerator is defined as the Y direction, the thickness direction as the X direction, and the height direction as the Z direction. The X, Y, and Z directions are perpendicular to each other.

[0040] like Figures 1-2As shown, this application embodiment first provides a refrigerator, which includes a cabinet 200 and a door 201.

[0041] The cabinet 200 is an integral insulated shell, consisting of an outer shell, an inner liner, and a polyurethane foam interlayer. Its main function is to thermally insulate the internal space from the external environment, reduce heat leakage load, and provide an installation reference for various functional components. The inner liner of the cabinet 200 is divided into two parts from left to right: the refrigerator inner liner 301 and the freezer inner liner 401. The refrigerator inner liner 301 forms the refrigerator compartment 300, and the freezer inner liner 401 forms the freezer compartment 400. The freezer compartment 400 maintains a temperature below freezing point and is used for long-term storage of meat, ice cream, and other foods requiring deep freezing. The refrigerator compartment 300 operates at a temperature close to but not below freezing point and is used for short-term preservation of perishable foods such as fruits and vegetables, beverages, and cooked foods.

[0042] The front opening of the cabinet 200 is sealed by the door 201, which is hinged to the side wall of the cabinet 200 and can be opened and closed by rotating around a vertical axis. The door 201 has an embedded magnetic door seal that presses against the front face of the cabinet 200 to form a continuous sealing surface, blocking the exchange of hot and cold air. The cabinet 200 and the door 201 together form a complete thermal boundary, providing a stable thermal insulation environment for the refrigerator compartment 300 and the freezer compartment 400, ensuring the efficient operation of the refrigeration system and reducing energy consumption.

[0043] The refrigerator compartment 300 and the freezer compartment 400 can each be equipped with several horizontally arranged shelves to divide the internal space of the compartments into multiple independent storage areas, facilitating food classification and storage and improving space utilization. Each compartment also features pull-out drawers at the bottom, which slide smoothly along rails against the inner wall of the compartment, allowing for easy horizontal pulling and unpulling of items. Simultaneously, the drawers create a relatively sealed microenvironment between the drawers and the compartment walls, reducing cross-contamination of odors and slowing down moisture loss.

[0044] Continue as Figure 2 As shown, the interior of the housing 200 is further enclosed by partitions to form a refrigeration air duct. An evaporator 500 is installed within the refrigeration air duct. The evaporator 500 can be composed of pipes and first fins. The pipes are filled with refrigerant, and the first fins are located outside the pipes to dissipate the coldness of the refrigerant inside. It should be noted that... Figure 2 The partition used to enclose and form the refrigeration air duct is hidden in the middle, so that the evaporator 500 inside the refrigeration air duct is directly exposed to the outside for easy understanding.

[0045] Figure 3 yes Figure 2 The image shows a refrigerator with the inner liner 301 of the refrigerator compartment and the inner liner 401 of the freezer compartment concealed. Figure 3As shown, a pre-dehumidification structure 100 is provided between the freezer compartment 400 and the refrigerator compartment 300, specifically between the inner liner of the freezer compartment 401 and the inner liner of the refrigerator compartment 301. This pre-dehumidification structure 100 is used to dehumidify the air flowing back into the freezer air duct to alleviate the problem of frost formation on the evaporator 500. The pre-dehumidification structure 100 will be described in detail below.

[0046] Figure 4 This is a schematic diagram of the pre-dehumidification structure 100 provided in the embodiments of this application. Figure 5 yes Figure 4 A schematic diagram of the pre-dehumidification structure 100 from another perspective.

[0047] like Figures 4-5 As shown in the embodiment of this application, the pre-dehumidification structure 100 includes a base 10 and a pre-dehumidification module 20 embedded inside the base 10. The base 10 is the supporting and integrated skeleton of the pre-dehumidification structure 100. The base 10 forms the boundary of the air duct through solid walls, preventing air leakage between air ducts and into the inner liner of the housing 200, and ensuring the airtightness and controllability of the airflow of each air path.

[0048] Optionally, the material of the matrix 10 includes, but is not limited to, rigid polyurethane foam (PUR / PUF), polystyrene foam (PSF), extruded polystyrene foam (XPS), expanded polystyrene foam (EPS), polyethylene foam (PEF), expandable polyethylene foam (EPE), phenolic foam (PF), melamine foam (MF), etc.

[0049] The base 10 is located between the freezer compartment 400 and the refrigerator compartment 300. The base 10 has a return air channel 11 that connects the refrigerator compartment 300 and the freezer air duct. The return air channel 11 can connect the refrigerator compartment 300 and the freezer air duct. When the refrigerator compressor starts to cool, the air in the refrigerator compartment 300 flows into the freezer air duct through the return air channel 11. As mentioned earlier, an evaporator 500 is installed in the freezer air duct. The air coming from the refrigerator compartment 300 will be cooled by the first fin of the evaporator 500 when it flows through the evaporator 500.

[0050] Figure 6 This is a cross-sectional view of the base 10 provided in the embodiments of this application. Figure 7This is a cross-sectional view of the base 10 provided in the embodiments of this application from another perspective.

[0051] like Figures 6-7 As shown, a hot-end air supply duct 12 is also provided on the substrate 10. The hot-end air supply duct 12 has a hot-end air inlet 121 and a hot-end air outlet 122. The hot-end air inlet 121 is connected to the freezer compartment 400, and the hot-end air outlet 122 is connected to the refrigerator compartment 300.

[0052] Figure 8 This is a schematic diagram of the pre-dehumidification module 20 provided in the embodiments of this application. Figure 9 This is a schematic diagram from another perspective of the pre-dehumidification module 20 provided in the embodiments of this application. Figure 10 This is a cross-sectional view of the pre-dehumidification module 20 provided in the embodiment of this application inside the substrate 10.

[0053] like Figures 8-10 As shown, the pre-dehumidification module 20 includes a thermoelectric cooling chip 21, a cold-end heat sink 22, a hot-end heat sink 23, and a fan 24.

[0054] Thermoelectric cooler 21, also known as a semiconductor cooler or Peltier, uses an array of electrical couples composed of P-type and N-type semiconductor particles to achieve temperature difference conversion between the hot and cold ends by utilizing the direction of current. It has bidirectional cooling and heating functions, with a temperature difference range of -130℃ to 90℃. Thermoelectric cooler 21 requires no moving mechanical parts and features a compact structure, fast response, no vibration, and no working fluid leakage. Thermoelectric cooler 21 has a cold end and a hot end. These cold and hot ends can be understood as... Figure 10 The lower side of the thermoelectric cooling element 21 is the cold end, and the upper side of the thermoelectric cooling element 21 is the hot end.

[0055] The cold-end heat sink 22 is attached to the cold end of the thermoelectric cooling chip 21, that is... Figure 10 The lower side of the thermoelectric cooling plate 21. The cold end heat sink 22 is also disposed in the return air duct 11.

[0056] The hot-end heat sink 23 is attached to the hot end of the thermoelectric cooling chip 21, that is... Figure 10 The upper side of the thermoelectric cooling plate 21. The hot end heat sink 23 is also disposed in the hot end air supply duct 12.

[0057] The fan 24 is installed in the hot end air supply duct 12. The fan 24 is used to draw in the cold air of the freezer compartment 400 through the hot end air inlet 121, and after flowing through the hot end radiator 23, it is discharged into the refrigerator compartment 300 from the hot end air outlet 122.

[0058] The pre-dehumidification structure 100 in this embodiment of the application, by setting up a pre-dehumidification structure 100 between the freezer compartment 400 and the refrigerator compartment 300, utilizes the cold end of the thermoelectric cooling element 21 to condense and dehumidify the air returning to the freezer air duct, significantly reducing the moisture content of the air before entering the evaporator 500, thereby reducing the amount of frost on the surface of the evaporator 500 at the source. Compared with the passive defrosting approach in the prior art that only focuses on "how to remove frost after it forms", this application achieves active interception and removal of water vapor, effectively slowing down the rate of frost accumulation, extending the defrosting cycle, and reducing the defrosting frequency and corresponding energy consumption. In addition, the pre-dehumidification structure 100 starts operating before the refrigerator compartment 300 needs to be refrigerated. The low-temperature air (originating from the freezer compartment 400) discharged from its hot end air outlet 122 can pre-cool the refrigerator compartment 300. When the external heat load is small, this pre-cooling effect is sufficient to delay the start of the compressor, reduce the number of compressor start-stop times and the number of refrigeration times of the freezer evaporator 500, and further reduce the overall energy consumption of the refrigerator.

[0059] Furthermore, the pre-dehumidification structure 100 in this embodiment starts operating before the refrigerator compartment 300 needs air cooling. Its operating logic is also coordinated with the refrigerator's cooling cycle: when the external heat load is low, the pre-cooling effect generated by the pre-dehumidification structure 100 allows the low-temperature air supplied to the refrigerator compartment 300 to meet the temperature control requirements of the refrigerator compartment 300, thereby delaying or even avoiding compressor startup, reducing the number of compressor start-stop cycles, and reducing energy loss and mechanical wear caused by frequent compressor start-stop cycles; when the external heat load is high, the pre-dehumidification structure 100 simultaneously performs condensation dehumidification, reducing the moisture content of the return air, reducing frost formation on the evaporator 500, shortening the subsequent defrosting heating time, and reducing defrosting energy consumption. This coordinated control strategy enables the pre-dehumidification structure 100 to simultaneously possess the dual functions of pre-cooling energy saving and source dehumidification, achieving comprehensive optimization of refrigerator operating energy efficiency and defrosting performance.

[0060] Figure 11 This is a cross-sectional view of the pre-dehumidification structure 100 provided in the embodiments of this application. Figure 12 This is a cross-sectional view of the pre-dehumidification structure 100 provided in the embodiments of this application.

[0061] like Figures 11-12 As shown, and in combination Figure 6As shown, in some embodiments, the fan 24 is a centrifugal fan, and the hot-end air supply duct 12 includes a first portion 123, a second portion 124, and a third portion 125. The first portion 123 is located on one side of the return air duct 11 and communicates with the hot-end air outlet 122, and the fan 24 is disposed in the first portion 123. The second portion 124 is located on the side of the first portion 123 opposite to the return air duct 11 and communicates with the hot-end air inlet 121. The third portion 125 extends along the axial direction of the fan 24 and communicates with both the first portion 123 and the second portion 124.

[0062] The core working component of a centrifugal fan is the impeller, which consists of multiple blades arranged circumferentially. When the motor drives the impeller to rotate, the blades apply centrifugal force to the gas entering the center of the impeller (i.e., the axial air inlet). The gas accelerates radially outward within the blade channels, gaining kinetic and pressure energy, and is finally discharged at high speed from the radial air outlet at the outer edge of the impeller. A significant characteristic of centrifugal fans is that the airflow enters axially and exits radially, resulting in relatively high static pressure, making them particularly suitable for applications requiring overcoming duct resistance for air delivery.

[0063] In this embodiment, a centrifugal fan is disposed in the first part 123, and its radial airflow characteristics are matched with those of the first part 123. This allows it to generate high static pressure within a limited space, overcoming duct resistance and ensuring smooth airflow through the hot-end radiator 23 and stable discharge from the hot-end outlet 122. The second part 124 is located on the side of the first part 123 opposite to the return air channel 11 and communicates with the hot-end inlet 121, used to introduce low-temperature air into the freezer chamber 400. The third part 125 extends axially along the fan 24, connecting the first part 123 and the second part 124 respectively, forming a complete airflow path from the hot-end inlet 121 to the fan 24 and then to the hot-end outlet 122. This three-section duct layout spatially separates the inlet section, the fan 24 drive section, and the outlet section, avoiding short-circuiting of the inlet and outlet airflow. Simultaneously, it allows the fan 24, the hot-end radiator 23, and the duct structure to form a compact integrated unit, reducing the space occupied by the pre-dehumidification structure 100 and improving the space utilization of the cabinet 200.

[0064] Continue as Figure 9 As shown, in some embodiments, the cold end heat sink 22 includes a mounting plate 221 and a second fin 222. The mounting plate 221 is attached to the cold end of the thermoelectric cooling chip 21, and the second fin 222 is disposed on the mounting plate 221. Both the second fin 222 and the mounting plate 221 are disposed in the return air channel 11.

[0065] In this embodiment, the mounting plate 221 serves as a heat conduction bridge between the cold end of the thermoelectric cooling element 21 and the second fin 222, ensuring efficient transfer of cooling energy from the thermoelectric cooling element 21 to the second fin 222. The second fin 222 increases the contact area between the cold end and the return air, enhancing the heat exchange efficiency of condensation and dehumidification, allowing water vapor in the return air to condense and precipitate quickly on the surface of the second fin 222. By placing the second fin 222 and the mounting plate 221 as a whole in the return air channel 11, the cold end radiator 22 is directly exposed to the return airflow, resulting in rapid dehumidification response. Furthermore, condensate can flow downwards along the second fin 222 under gravity and be collected and discharged, preventing water accumulation from affecting heat exchange performance.

[0066] Optionally, the mounting plate 221 and the second fin 222 may be made of aluminum or aluminum alloys, or copper or copper alloys.

[0067] Continue as Figure 8 As shown, in some embodiments, the hot end heat sink 23 includes a heat sink 231, which is attached to the hot end of the thermoelectric cooling chip 21. The heat sink 231 is disposed in the first part 123 and is located between the inner wall of the first part 123 and the fan 24.

[0068] In this embodiment, the heat sink 231 directly receives the heat from the hot end of the thermoelectric cooler 21 and diffuses it to the contact area with the airflow in the first part 123, ensuring that the heat from the hot end is removed in a timely and efficient manner, and maintaining the temperature difference between the hot and cold ends of the thermoelectric cooler 21.

[0069] Continue as Figures 7-8 As shown, in some embodiments, the first part 123 is shaped like a volute, and the outer contour of the heat sink 231 is similar to the inner wall of the first part 123.

[0070] In this embodiment, the volute structure is a classic adaptable air duct form for centrifugal fans. Its gradually expanding cross-sectional area along the circumference can effectively collect the airflow radially discharged by the fan 24 and efficiently convert the kinetic energy of the airflow into static pressure, reducing eddy current losses and improving air delivery efficiency. The outer contour of the heat sink 231 conforms to the inner wall of the volute, allowing the heat sink 231 to obtain the maximum unfolded area within a limited space. At the same time, its curved shape fits the airflow streamline, reducing flow separation and resistance losses when the airflow flows around the heat sink 231, ensuring smooth airflow within the air duct. In addition, the conformal arrangement makes the flow channel gap between the heat sink 231 and the inner wall of the first part 123 uniform, avoiding uneven heat exchange caused by excessively high or low local wind speeds, and improving the overall uniformity and reliability of heat dissipation at the hot end.

[0071] In some embodiments, a thermally conductive adhesive layer is coated between the hot end of the thermoelectric cooler 21 and the heat sink 231, and between the cold end of the thermoelectric cooler 21 and the mounting plate 221.

[0072] In this embodiment, the thermally conductive adhesive layer fills the microscopic gap between the thermoelectric cooler 21 and the heat sink, significantly reducing the contact thermal resistance. This allows heat to be efficiently transferred from the thermoelectric cooler 21 to the heat sink 231 and the mounting plate 221, improving the heat transport efficiency of the hot and cold ends of the thermoelectric cooler 21. Simultaneously, the thermally conductive adhesive layer possesses a certain degree of elasticity and adhesion, serving both a thermal conductivity function and the ability to buffer vibrations and fix relative positions. This improves the assembly reliability and long-term operational stability between the thermoelectric cooler 21 and the heat sink, preventing increased contact thermal resistance due to mechanical loosening.

[0073] Alternatively, the thermally conductive adhesive layer can be made of thermally conductive silicone pads, thermally conductive gels, thermally conductive grease, etc.

[0074] Continue as Figure 7 and Figure 10 As shown, in some embodiments, a mounting groove 13 is provided on the base 10 between the first part 123 and the return air channel 11, and the thermoelectric cooling chip 21 is embedded in the mounting groove 13.

[0075] In this embodiment, the mounting groove 13 provides a precise positioning reference for the thermoelectric cooling chip 21, ensuring the accurate position of the thermoelectric cooling chip 21 in the thickness direction, so that the cold end and the hot end accurately correspond to the return air channel 11 and the first part 123 respectively, ensuring the fitting accuracy of the heat sink 23 at the cold and hot ends. The embedded structure allows the thermoelectric cooling chip 21 to be embedded inside the substrate 10. The two sides of the thermoelectric cooling chip 21 in the thickness direction are adjacent to the return air channel 11 and the hot end air supply channel 12 respectively, realizing the compact spatial isolation between the cold end and the hot end. This avoids direct thermal short circuit between the cold and hot ends and minimizes the heat transfer path, improving the overall integration and structural compactness of the pre-dehumidification structure 100.

[0076] Continue as Figure 5 As shown, in some embodiments, the cross-sectional area of ​​the second portion 124 gradually increases from the direction of the second portion 124 to the hot end air inlet 121, or it can be understood that the second portion 124 is flared. The area of ​​the hot end air outlet 122 is 1 to 1.5 times the area of ​​the hot end air inlet 121.

[0077] In this embodiment, from the direction of the second part 124 to the hot-end air inlet 121, the cross-sectional area of ​​the second part 124 gradually increases, forming a diffuser-type air inlet duct. This gradual diffuser structure causes the low-temperature air entering from the hot-end air inlet 121 to gradually increase in velocity and gradually recover in static pressure as it flows towards the first part 123, reducing flow loss in the air inlet section. At the same time, it makes the airflow velocity distribution more uniform before entering the fan 24, which is beneficial to improving the operating efficiency of the fan 24 and reducing aerodynamic noise. The area of ​​the hot-end air outlet 122 is designed to be 1 to 1.5 times the area of ​​the hot-end air inlet 121, so that the outlet area is slightly larger than or equal to the inlet area. After the hot-end radiator 23 heats the airflow (air volume expands), the outlet provides sufficient flow area, avoiding the increase in pressure in the duct and the deterioration of the fan 24's operating condition due to obstructed airflow. This ensures smooth air delivery and stable airflow, while also keeping the outlet airflow velocity moderate, avoiding direct blowing and drying of food in the refrigerator compartment 300.

[0078] Continue as Figures 11-12 As shown, the working principle of the fan 24 in the pre-dehumidification structure 100 is described below.

[0079] I. Air Intake Stage. When fan 24 starts rotating, a negative pressure is generated at the center of the impeller, and the cold air from the freezer compartment 400 is drawn into the second part 124 through the hot end air inlet 121. In the second part 124 of the gradual diffusion structure, the airflow velocity gradually increases and the static pressure gradually recovers, distributing at a relatively uniform speed as it enters the third part 125. The third part 125 extends along the axial direction of fan 24, guiding the airflow to the axial air inlet of the centrifugal fan, achieving smooth axial intake.

[0080] II. Pressurization Stage. After the airflow enters the centrifugal fan, the impeller, composed of multiple circumferentially arranged blades, applies centrifugal force to the gas. The gas accelerates radially outward within the blade channels, gaining kinetic and pressure energy, and is finally discharged at high speed from the radial outlet at the outer edge of the impeller. The high-speed airflow discharged radially from the impeller directly enters the first section 123. The volute structure gradually expands its cross-section along the rotation direction of the fan 24, effectively collecting the circumferential airflow discharged from the impeller and efficiently converting the kinetic energy of the airflow into static pressure, forming a stable high-pressure outlet. The heat sink 231 is located between the inner wall of the first section 123 and the fan 24, and its outer contour conforms to the inner wall of the volute. The airflow discharged radially from the fan 24 first flows over the surface of the heat sink 231. The conformal arrangement ensures a uniform flow channel gap between the heat sink 231 and the inner wall of the first section 123, allowing for smooth airflow and reducing flow separation and resistance loss. Simultaneously, it maximizes the unfolded area of ​​the heat sink 231 within a limited space, enhancing heat transfer uniformity. A thermally conductive adhesive layer is coated between the hot end of the thermoelectric cooler 21 and the heat sink 231 to ensure efficient heat transfer from the hot end of the thermoelectric cooler 21 to the heat sink 231. When the airflow passes through the heat sink 231, it effectively removes the heat from the hot end of the thermoelectric cooler 21, maintains the temperature difference between the hot and cold ends of the thermoelectric cooler 21, and ensures that the cold end has a stable condensation and dehumidification capability.

[0081] III. Air Supply Stage. The airflow heated by the heat sink 231 is discharged into the refrigerator compartment 300 from the hot end air outlet 122. The area of ​​the hot end air outlet 122 is 1 to 1.5 times the area of ​​the hot end air inlet 121, providing sufficient flow area for the airflow that expands in volume after being heated by the heat sink 231, avoiding pressure rise in the air duct and deterioration of the fan 24's operating condition, and ensuring smooth air supply and stable air volume.

[0082] The control logic of the pre-dehumidification structure 100 of the refrigerator in this application will be described in detail below.

[0083] Figure 13 This is a flowchart of a refrigerator temperature control method provided in an embodiment of this application.

[0084] like Figure 13 As shown in the figure, this application embodiment also provides a temperature control method for a refrigerator, which includes the following steps.

[0085] Step 101: Obtain the actual temperature of the refrigerator compartment 300.

[0086] Step 102: When the actual temperature reaches the first threshold, the pre-dehumidification module 20 is activated, the thermoelectric cooling chip 21 is powered on, the fan 24 rotates, and the cold air from the freezer compartment 400 enters the hot-end air supply duct 12 through the hot-end air inlet 121, flows through the hot-end radiator 23, and is discharged into the refrigerator compartment 300 from the hot-end air outlet 122. The cold-end radiator 22 condenses and dehumidifies the return air that enters the freezer air duct through the return air channel 11.

[0087] Step 103: When the actual temperature drops to the set temperature, control the pre-dehumidification module 20 to stop operating; when the actual temperature continues to rise, proceed to step 104.

[0088] Step 104: When the actual temperature reaches the second threshold, control the compressor and the refrigeration fan to start, wherein the second threshold is greater than the first threshold; during the operation of the compressor, the pre-dehumidification module 20 continues to operate, and the cold end heat sink 22 continuously condenses and dehumidifies the return air entering the refrigeration air duct through the return air channel 11.

[0089] Step 105: When the actual temperature drops to the set temperature, control the compressor, refrigeration fan and pre-dehumidification module 20 to stop running.

[0090] To facilitate understanding of the refrigerator temperature control method provided in this application embodiment, the following simulates the specific working conditions of the refrigerator and uses specific temperature values ​​as examples to introduce the temperature control method.

[0091] First, assuming the refrigerator compartment 300 is set to a temperature of T=4℃, the pre-dehumidification module 20 is set to a first threshold of T+1=5℃ and a second threshold of T+2=6℃.

[0092] Operating condition 1, low heat load condition: the pre-dehumidification module 20 can meet the temperature control requirements by operating independently. The specific working process is as follows.

[0093] Step 1: The temperature sensor in the refrigerator compartment 300 continuously acquires the actual temperature of the refrigerator compartment 300. As external heat load slowly intrudes, the actual temperature of the refrigerator compartment 300 gradually rises.

[0094] Step two: When the actual temperature reaches the first threshold T+1=5℃, the control system determines that the pre-dehumidification module 20 needs to be activated. The pre-dehumidification module 20 is activated, the thermoelectric cooling element 21 is powered on and the fan 24 rotates.

[0095] Hot-end air supply path: Low-temperature air (approximately -18°C) from the freezer compartment 400 enters the hot-end air supply duct 12 through the hot-end air inlet 121, flows through the hot-end radiator 23, and is then discharged into the refrigerator compartment 300 from the hot-end air outlet 122. This low-temperature air pre-cools the refrigerator compartment 300 and simultaneously removes heat from the hot end of the thermoelectric cooling element 21, maintaining the temperature difference between the hot and cold ends of the thermoelectric cooling element 21.

[0096] Cold end dehumidification path: The cold end radiator 22 condenses and dehumidifies the return air entering the refrigeration air duct through the return air channel 11. At this stage, the compressor has not yet started, the airflow in the return air channel 11 is weak, and the pre-dehumidification module 20 performs preliminary dehumidification on natural convection or residual airflow.

[0097] Because the external heat load is small, the low-temperature air discharged from the pre-dehumidification module 20 (heated by the hot end radiator 23 to a temperature of about -10°C, which is still far below the temperature of the refrigerator compartment 300) is sufficient to offset the heat load intrusion, and the actual temperature of the refrigerator compartment 300 no longer continues to rise.

[0098] Step 3: As the pre-dehumidification module 20 continues to operate, the actual temperature of the refrigerator compartment 300 begins to decrease. When the temperature sensor detects that the actual temperature has dropped to the set temperature T=4℃, the control system controls the pre-dehumidification module 20 to stop operating. The thermoelectric cooling element 21 is de-energized, the fan 24 stops, and the system enters standby mode.

[0099] Figure 14 This is a schematic diagram of the airflow inside the refrigerator under operating conditions. Figure 14 Solid arrows indicate airflow direction with lower moisture content, while hollow arrows indicate airflow direction with higher moisture content. For example... Figure 14 As shown, under operating condition one, the fan 24 draws air from the freezer compartment 400 into the refrigerator compartment 300 through the hot end air inlet 121, the hot end air supply duct 12, and the hot end air outlet 122. As the air pressure inside the refrigerator compartment 300 increases, the humid air inside the refrigerator compartment 300 flows to the freezer air duct through the return air duct 11. During this process, the humid air is condensed and dehumidified by the cold end radiator 22 in the return air duct 11.

[0100] The technical effect of operating condition one, namely the effect of low heat load operating condition: the compressor is not started throughout the process, and only the pre-dehumidification module 20 completes the temperature control by operating at low power consumption. The number of compressor start-stop times is zero, the energy consumption is significantly reduced, and the moisture content of the return air is pre-dehumidified to a certain extent.

[0101] Operating condition 2, high heat load condition, the pre-dehumidification module 20 works in conjunction with the compressor, and the specific working process is as follows.

[0102] Step 1: The temperature sensor in the refrigerator compartment 300 continuously acquires the actual temperature of the refrigerator compartment 300.

[0103] Step 2: When the actual temperature reaches the first threshold T+1=5℃, the pre-dehumidification module 20 is activated, the thermoelectric cooling chip 21 is powered on and the fan 24 rotates to perform the pre-cooling and pre-dehumidification functions.

[0104] Step 3: Due to the high external heat load (such as high summer temperatures, frequent door opening, or the placement of a large amount of hot food), the pre-cooling effect of the pre-dehumidification module 20 is insufficient to completely offset the heat load intrusion, and the actual temperature of the refrigerator compartment 300 continues to rise.

[0105] Step four: When the actual temperature reaches the second threshold T+2=6℃, the control system determines that the compressor needs to be started. The compressor starts cooling, the damper connecting the freezer compartment 400 to the refrigerator compartment 300 opens, and the refrigeration fan starts running, blowing cold air into the refrigerator compartment 300. At this time, the pre-dehumidification module 20 continues to operate, forming a collaborative working mode with the compressor.

[0106] The evaporator 500 deeply cools the return air in the refrigeration duct, providing the main cooling capacity for the refrigerator compartment 300. The cold-end radiator 22 continuously condenses and dehumidifies the return air entering the refrigeration duct through the return air channel 11. Due to the operation of the refrigeration fan, the airflow in the return air channel 11 is enhanced, increasing the dehumidification load of the cold-end radiator 22 and significantly improving the dehumidification effect. The moisture content of the return air entering the evaporator 500 has been significantly reduced, and the amount of frost on the surface of the first fin of the evaporator 500 has been greatly reduced. During compressor operation, the temperature in the refrigeration duct is even lower, and the air temperature entering the hot-end supply air channel 12 through the hot-end air inlet 121 is also lower. The hot-end heat dissipation conditions are optimized, the temperature difference between the hot and cold ends of the thermoelectric cooling element 21 increases, and the cold-end dehumidification efficiency is further improved.

[0107] Step 5: As the compressor and pre-dehumidification module 20 operate in tandem, the actual temperature of the refrigerator compartment 300 decreases. When the temperature sensor detects that the actual temperature has dropped to the set temperature T=4℃, the control system controls the compressor and pre-dehumidification module 20 to stop operating synchronously. The refrigeration fan stops, the damper closes, and the system enters standby mode.

[0108] Figure 15 This is a schematic diagram of the airflow inside the refrigerator under operating condition two. Among them, Figure 15 Solid arrows indicate airflow direction with lower moisture content, while hollow arrows indicate airflow direction with higher moisture content. For example... Figure 15 As shown, under operating condition two, the compressor and refrigeration fan start. The airflow in the freezer compartment 400 flows through the refrigeration air duct to the evaporator 500. After being cooled by the evaporator 500, it flows to the upper part of the cabinet 200, then passes through the air damper of the refrigerator compartment 300 and enters the refrigerator compartment 300. Afterward, it enters the freezer air duct through the return air duct 11. At the same time, the pre-dehumidification module 20 operates synchronously. When the humid air inside the refrigerator compartment 300 passes through the return air duct 11, the humid air is condensed and dehumidified by the cold end radiator 22. In addition, the pre-dehumidification module 20 also draws some of the gas from the freezer compartment 400 into the refrigerator compartment 300.

[0109] The technical effects of operating condition 2, namely the effects of high heat load operating condition: During compressor operation, the pre-dehumidification module 20 continuously condenses and dehumidifies the return air, reducing frost formation on the evaporator 500 from the source; the defrosting cycle is extended, and defrosting energy consumption is reduced; the heat exchange efficiency of the evaporator 500 is maintained at a high level for a longer period of time, and the overall energy efficiency of the system is improved.

[0110] In summary, the temperature control method provided in this application embodiment allows for a slow temperature rise in the refrigerator compartment 300 when the external heat load is low (e.g., at night, in winter, or with low door opening frequency). The pre-dehumidification structure 100 starts operating before the refrigerator compartment 300 needs air cooling, continuously supplying low-temperature air to the refrigerator compartment 300 through its hot-end air outlet 122. This pre-cooling effect is sufficient to offset the temperature rise in the refrigerator compartment 300, delaying or even preventing the compressor from starting. With fewer compressor start-stop cycles, the refrigeration cycles of the freezer evaporator 500 are correspondingly reduced, lowering the overall energy consumption of the refrigerator. When the external heat load is high (e.g., in summer, with frequent door opening, or with a large amount of hot food placed inside), the pre-cooling effect of the pre-dehumidification structure 100 cannot completely offset the temperature rise in the refrigerator compartment 300. In this case, the compressor starts cooling normally, and the pre-dehumidification structure 100 simultaneously performs condensation dehumidification. The moisture content of the return air entering the evaporator 500 is significantly reduced, the amount of frost on the evaporator 500 is reduced, the subsequent defrosting heating time is shortened, and defrosting energy consumption is reduced.

[0111] The above description is merely a specific embodiment of this application, but the scope of protection of this application is not limited thereto. Any variations or substitutions that can be easily conceived by those skilled in the art within the scope of the technology disclosed in this application should be included within the scope of protection of this application. Therefore, the scope of protection of this application should be determined by the scope of the claims.

Claims

1. A pre-dehumidification structure, characterized in that, Applied to refrigeration equipment, the refrigeration equipment is provided with a freezer compartment (400), a refrigerator compartment (300), and a refrigeration air duct, the pre-dehumidification structure (100) includes: A base (10) is disposed between the freezer compartment (400) and the refrigerator compartment (300); a return air channel (11) is provided on the base (10) to connect the refrigerator compartment (300) and the freezer air duct; a hot end air supply duct (12) is also provided on the base (10), the hot end air supply duct (12) has a hot end air inlet (121) and a hot end air outlet (122), the hot end air inlet (121) is connected to the freezer compartment (400), and the hot end air outlet (122) is connected to the refrigerator compartment (300); A pre-dehumidification module (20) is disposed inside the substrate (10), and the pre-dehumidification module (20) includes: Thermoelectric cooling element (21) has a cold end and a hot end; A cold-end heat sink (22) is attached to the cold end of the thermoelectric cooling chip (21), and the cold-end heat sink (22) is disposed in the return air channel (11); A hot-end radiator (23) is attached to the hot end of the thermoelectric cooling chip (21), and the hot-end radiator (23) is disposed in the hot-end air supply duct (12); A fan (24) is installed in the hot end air supply duct (12) to draw in the cold air from the freezer (400) through the hot end air inlet (121), and after flowing through the hot end radiator (23), it is discharged into the refrigerator (300) from the hot end air outlet (122).

2. The pre-dehumidification structure according to claim 1, characterized in that, The fan (24) is a centrifugal fan; the hot-end air supply duct (12) includes: The first part (123) is located on one side of the return air duct (11) and is connected to the hot end air outlet (122); the fan (24) is disposed in the first part (123); The second part (124) is located on the side of the first part (123) opposite to the return air channel (11) and is connected to the hot end air inlet (121); The third part (125) extends along the axial direction of the fan (24) and communicates with the first part (123) and the second part (124), respectively.

3. The pre-dehumidification structure according to claim 2, characterized in that, The cold-end heat sink (22) includes: Mounting plate (221) is attached to the cold end of the thermoelectric cooling chip (21); The second fin (222) is disposed on the mounting plate (221), and both the second fin (222) and the mounting plate (221) are disposed in the return air duct (11).

4. The pre-dehumidification structure according to claim 3, characterized in that, The hot-end heat sink (23) includes: A heat sink (231) is attached to the hot end of the thermoelectric cooling chip (21). The heat sink (231) is disposed in the first part (123) and is located between the inner wall of the first part (123) and the fan (24).

5. The pre-dehumidification structure according to claim 4, characterized in that, The first part (123) has a volute structure, and the outer contour of the heat sink (231) is similar to the inner wall of the first part (123).

6. The pre-dehumidification structure according to claim 4 or 5, characterized in that, A thermally conductive adhesive layer is applied between the hot end of the thermoelectric cooling chip (21) and the heat sink (231), and between the cold end of the thermoelectric cooling chip (21) and the mounting plate (221).

7. The pre-dehumidification structure according to any one of claims 2-5, characterized in that, An installation groove (13) is provided on the substrate (10) between the first part (123) and the return air channel (11), and the thermoelectric cooling chip (21) is embedded in the installation groove (13).

8. The pre-dehumidification structure according to any one of claims 2-5, characterized in that, From the second part (124) to the hot end air inlet (121), the cross-sectional area of ​​the second part (124) gradually increases; The area of ​​the hot end air outlet (122) is 1 to 1.5 times the area of ​​the hot end air inlet (121).

9. A refrigeration device, characterized in that, Includes the pre-dehumidification structure (100) as described in any one of claims 1-8.

10. A temperature control method for a refrigeration device, characterized in that, Applied to the refrigeration equipment as described in claim 9, comprising: Obtain the actual temperature of the refrigerator compartment (300); When the actual temperature reaches the first threshold, the pre-dehumidification module (20) is activated, the thermoelectric cooling chip (21) is powered on, the fan (24) rotates, and the cold air from the freezer (400) enters the hot-end air supply duct (12) through the hot-end air inlet (121), flows through the hot-end radiator (23), and is discharged into the refrigerator (300) from the hot-end air outlet (122). The cold-end radiator (22) condenses and dehumidifies the return air that enters the freezer duct through the return air channel (11). When the actual temperature drops to the set temperature, the pre-dehumidification module (20) is controlled to stop operating; when the actual temperature continues to rise, the next step is initiated. When the actual temperature reaches the second threshold, the compressor and the refrigeration fan are started, wherein the second threshold is greater than the first threshold; during the operation of the compressor, the pre-dehumidification module (20) continues to operate, and the cold end heat sink (22) continuously condenses and dehumidifies the return air entering the refrigeration air duct through the return air channel (11); When the actual temperature drops to the set temperature, the compressor, the refrigeration fan, and the pre-dehumidification module (20) are controlled to stop operating.

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