Washing and drying integrated machine

Abstract

The application discloses a washing and drying integrated machine, which comprises a box body, an outer cylinder, an inner cylinder, a condensing disc, a cooling device and a heating air duct. The condensing disc is provided with a heat superconducting channel, the heat superconducting channel has extremely high heat conductivity, can rapidly respond to heat change, can rapidly absorb heat in the wet and hot air entering the outer cylinder from the inner cylinder, so that the moisture in the wet and hot air is condensed into water, that is, the dehumidification efficiency of the product is improved, and the clothes can be rapidly dried; in addition, the channel wall of the heat superconducting channel is thin, on the one hand, the heat transfer time through the channel wall is shortened, the response speed of the heat superconducting channel to heat change is accelerated, and the heat conductivity of the heat superconducting channel is further improved, on the other hand, the thin channel wall can significantly reduce the thermal resistance in the heat transfer process, so that the heat exchange can be more smooth, and the heat conductivity of the heat superconducting channel is further improved.

Description

Technical Field

[0001] This application relates to the field of garment processing equipment technology, and in particular to a washer-dryer combo machine. Background Technology

[0002] With social progress and technological development, washer-dryer combos have become common household appliances. As living standards improve at a faster pace, people are using washer-dryer combos more frequently and have increasingly higher requirements for their drying performance.

[0003] In washer-dryer combos, the drying structure consists of a drying duct, a heating element, a fan, and a condenser. During operation, the heating element heats the air to create hot air. This hot air enters the drum, penetrates the clothes, and becomes humid air. This humid air exits the drum and is condensed into water by the condenser, then discharged. This cycle repeats multiple times to dry the clothes. The condenser's efficiency directly affects the efficiency with which the moisture in the humid air is condensed and discharged, thus affecting dehumidification efficiency. If the dehumidification efficiency is low, the hot air re-entering the drum will have a high moisture content, making it easier for the air to reach saturated vapor pressure, which is detrimental to the evaporation of moisture from the clothes and hinders rapid drying. Utility Model Content

[0004] To solve the above-mentioned technical problems, or at least partially solve them, this application provides the following technical solutions:

[0005] An embodiment of this application provides a washer-dryer combo, comprising: a housing with a clothing inlet on its front surface; an outer tub disposed within the housing, the outer tub having an opening on its front end opposite to the clothing inlet, and an air outlet on its rear wall; an inner tub disposed within the outer tub and rotatable within it; a condenser tray disposed on the rear wall of the outer tub and located between the inner tub and the outer tub, a cooling channel being formed between the condenser tray and the rear wall of the outer tub; and a cooling... The device includes a cooling system disposed on the outer cylinder and facing the inlet of the cooling channel, the cooling system being configured to supply a cooling medium to the condenser plate; and a heating air duct disposed on the outer surface of the outer cylinder and connecting the air outlet to the internal space of the inner cylinder; wherein the condenser plate includes two heat-conducting plates and a heat-absorbing medium, a closed thermal superconducting channel is formed between the two heat-conducting plates, the heat-absorbing medium is located within the thermal superconducting channel, and the thickness of the portion of the heat-conducting plate forming the thermal superconducting channel is less than the thickness of the other portions.

[0006] The washer-dryer provided in this application has a thermal superconducting channel in its condenser tray. This thermal superconducting channel has extremely high thermal conductivity and can respond rapidly to changes in heat. It can quickly absorb heat from the humid air entering the outer drum from the inner drum, causing the moisture in the humid air to condense into water, thus improving the dehumidification efficiency of the product and achieving rapid drying of clothes. In addition, because the channel wall of the thermal superconducting channel is relatively thin, on the one hand, the time for heat transfer through the channel wall is shortened, and the response speed of the thermal superconducting channel to changes in heat is accelerated, further improving the thermal conductivity of the thermal superconducting channel. On the other hand, the thinner channel wall can significantly reduce the thermal resistance during heat transfer, thereby enabling smoother heat exchange and further improving the thermal conductivity of the thermal superconducting channel.

[0007] In some embodiments, the cooling device includes a spray pipe inserted into the outer cylinder from the top of the outer cylinder, the spray pipe being configured to deliver coolant to the condenser pan.

[0008] In the above technical solution, liquid cooling is used to cool the condenser plate. Since liquid has a large specific heat capacity, it can quickly cool the condenser plate, thereby improving the heat exchange efficiency between the condenser plate and the humid air. At the same time, the coolant can also directly exchange heat with the humid air, condense and dehumidify the humid air, thereby improving the condensation efficiency and drying efficiency.

[0009] In some embodiments, the cooling channel is formed by a spaced arrangement between the condenser plate and the rear wall of the outer cylinder.

[0010] The above technical solution can form a cooling channel in a limited space without adding any complex structures or components, making the overall structure of the equipment more compact, saving space, and facilitating the miniaturization and integration of the equipment design.

[0011] In some embodiments, the thermal superconducting channel forms a protrusion on the outer surface of the condensing disk; on the side of the condensing disk near the rear wall of the outer cylinder, a plurality of intersecting protrusions form a cooling cavity on the outer surface of the condensing disk.

[0012] In the above technical solution, the coolant can only flow out of the cooling chamber after it is full, which prolongs the contact time between the coolant and the condenser plate, allowing the coolant to exchange heat with the condenser plate and fully cool the condenser plate. This enables the condenser plate to continuously absorb heat from the humid air, thus effectively dehumidifying the humid air and ensuring the dehumidification efficiency of the product, thereby achieving rapid drying of clothing.

[0013] In some embodiments, the spray pipe is disposed toward the edge of the condenser plate; at the edge of the condenser plate, guide ramps are provided on both sides of the condenser plate, the guide ramps being configured to guide the coolant.

[0014] In the above technical solution, the two guide slopes allow the coolant to flow to the two sides of the condenser plate, increasing the contact area between the coolant and the condenser plate. More heat can be transferred from the condenser plate to the coolant through heat conduction, thereby more effectively reducing the temperature of the condenser plate and improving the cooling efficiency. This allows the condenser plate to continuously absorb heat from the humid air, thus enabling the condenser plate to effectively dehumidify the humid air, ensuring the dehumidification efficiency of the product and achieving rapid drying of clothing.

[0015] In some embodiments, the cooling device includes a cooling fan disposed on the outer surface of the outer cylinder, and the outlet of the cooling fan is connected to the cooling channel; wherein the cooling channel is isolated from the internal space of the outer cylinder, and the outlet of the cooling channel is disposed on the rear wall of the outer cylinder.

[0016] In the above technical solution, the cooling fan can start quickly and achieve a cooling effect. When the condenser plate needs cooling, the cooling fan turns on, and the air immediately begins to flow and carry away the heat. Therefore, it can respond more promptly to changes in the temperature of the condenser plate. Furthermore, the air-cooling method does not involve liquid media, eliminating safety hazards caused by liquid corrosion or electrical leakage. In addition, due to the extremely high thermal conductivity of the thermal superconducting channel, the condenser plate can transfer a significant amount of heat to the cooling air, thus improving the utilization rate of the cooling air, reducing its consumption, and consequently reducing the air volume supplied by the cooling fan, thereby reducing the power consumption of the cooling fan.

[0017] In some embodiments, on the side of the condensing plate near the rear wall of the outer cylinder, the thermal superconducting channel forms a protrusion on the outer surface of the condensing plate, and a rib is provided on the rear wall of the outer cylinder. The position of the rib corresponds to the position of the protrusion, and the rib, the protrusion, the condensing plate and the rear wall of the outer cylinder form the cooling channel.

[0018] In the above technical solution, the combination of ribs and protrusions makes the airflow boundary within the cooling channel more complex, generating more turbulence and vortices as the airflow passes through these structures. This additional airflow turbulence can further improve the heat exchange coefficient between the air and the condenser plate, promoting heat transfer and thus more effectively reducing the temperature of the condenser plate.

[0019] In some embodiments, an elastic seal is provided between the rib and the protrusion.

[0020] In the above technical solution, the elastic seal can fill the gap between the ribs and protrusions, preventing air leakage in the cooling channel. This helps maintain the stability of airflow and the consistency of pressure within the duct, ensuring the reliability of the cooling effect.

[0021] In some embodiments, the flow area at the outlet of the cooling channel is smaller than the flow area of ​​other parts of the cooling channel.

[0022] In the above technical solution, the speed at which the cooling medium flows out of the cooling channel is limited, thereby increasing the residence time of the cooling medium in the cooling channel. The longer residence time means that the cooling medium has more time to exchange heat with the condenser plate, which can fully cool the condenser plate and enable the condenser plate to continuously absorb heat from the humid air. This allows the condenser plate to effectively dehumidify the humid air, thus ensuring the dehumidification efficiency of the product and achieving rapid drying of clothing.

[0023] In some embodiments, a turbulence-disrupting structure is provided on the rear wall of the outer cylinder, the turbulence-disrupting structure being located within the cooling channel, and the turbulence-disrupting structure being configured to disrupt the flow direction of the cooling medium.

[0024] In the above technical solution, the turbulence structure can generate turbulence in the coolant, increase the contact frequency between the coolant and the condenser plate, thereby effectively improving the heat exchange efficiency and ensuring sufficient cooling of the condenser plate. Attached Figure Description

[0025] To more clearly illustrate the technical solutions in the embodiments of this application, 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 application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0026] Figure 1 This is a schematic diagram of the structure of a washer-dryer combo provided in some embodiments of this application;

[0027] Figure 2 for Figure 1 A partial structural schematic diagram of the first embodiment of the washer-dryer combo shown;

[0028] Figure 3 for Figure 2 A partial structural diagram of the structure shown;

[0029] Figure 4 for Figure 2 A cross-sectional view of the structure shown.

[0030] Figure 5 for Figure 2 A rear view schematic diagram of the structure shown;

[0031] Figure 6 for Figure 5 Schematic diagram of the cross-sectional structure along the AA direction;

[0032] Figure 7 for Figure 6 Enlarged structural diagram of section B in the middle;

[0033] Figure 8 for Figure 2 Another partial structural diagram of the structure shown;

[0034] Figure 9 for Figure 3 A schematic diagram of the condenser plate shown;

[0035] Figure 10 This is a cross-sectional structural schematic diagram of a first embodiment of the outer cylinder provided in some embodiments of this application;

[0036] Figure 11 This is a partial cross-sectional structural schematic diagram of an embodiment of the condenser plate provided in some embodiments of the application;

[0037] Figure 12 This is a partial cross-sectional view of a first embodiment of the condenser plate and outer cylinder provided in some embodiments of this application;

[0038] Figure 13 for Figure 1 A partial structural schematic diagram of the second embodiment of the washer-dryer shown;

[0039] Figure 14 for Figure 13 A partial structural diagram of the structure shown;

[0040] Figure 15 for Figure 13 A rear view schematic diagram of the structure shown;

[0041] Figure 16 for Figure 15 Schematic diagram of the cross-sectional structure along the CC direction;

[0042] Figure 17 for Figure 16 Enlarged structural diagram of section D in the middle;

[0043] Figure 18 This is a partial cross-sectional view of a second embodiment of the condenser plate and outer cylinder provided in some embodiments of this application;

[0044] Figure 19 A partial cross-sectional view of a third embodiment of the condenser plate and outer cylinder provided in some embodiments of this application;

[0045] Figure 20 A partial cross-sectional view of a fourth embodiment of the condenser plate and outer cylinder provided in some embodiments of this application;

[0046] Figure 21 A partial cross-sectional view of a fifth embodiment of the condenser plate and outer cylinder provided in some embodiments of this application;

[0047] Figure 22 This is a cross-sectional structural schematic diagram of a second embodiment of the outer cylinder provided in some embodiments of this application.

[0048] The attached figures are labeled as follows:

[0049] 10. Box body; 11. Box door; 12. Clothing storage opening;

[0050] 20. Outer cylinder; 21. Air outlet; 22. Rib; 30. Inner cylinder;

[0051] 40. Condensation plate; 41. Heat-conducting plate; 42. Heat-absorbing medium; 43. Thermal superconducting channel; 44. Guide slope; 45. Air vent; 46. Cooling chamber;

[0052] 51. Injection pipe; 52. Cooling fan;

[0053] 60. Heated air duct; 70. Turbulence structure;

[0054] 81. Heater; 82. Heating fan;

[0055] 91. Cooling channel; 911. Outlet; 92. Flow divider;

[0056] 100. Sealing components. Detailed Implementation

[0057] The present application will now be described in further detail with reference to the accompanying drawings and embodiments. Through these descriptions, the features and advantages of the present application will become clearer and more apparent.

[0058] Unless otherwise defined, all technical and scientific terms used in this application have the same meaning as commonly understood by one of ordinary skill in the art to which this application pertains; the terminology used in this application is for the purpose of describing particular embodiments only and is not intended to limit this application; the terms "comprising" and "having" and any variations thereof in the specification and the foregoing description of this application are intended to cover non-exclusive inclusion.

[0059] The term "embodiment" as used in this application means that a specific feature, structure, or characteristic described in connection with an embodiment may be included in at least one embodiment of this application. The appearance of this phrase in various places in the specification does not necessarily refer to the same embodiment, nor is it a separate or alternative embodiment mutually exclusive with other embodiments. It will be explicitly and implicitly understood by those skilled in the art that the embodiments described in this application can be combined with other embodiments.

[0060] The specific term "exemplary" used in this application means "serving as an example, embodiment, or illustration." Any embodiment illustrated as "exemplary" is not necessarily to be construed as superior or better than other embodiments. Although various aspects of embodiments are shown in the accompanying drawings, the drawings are not necessarily drawn to scale unless specifically indicated otherwise.

[0061] In the description of this application, the technical terms "upper", "lower", "inner", "outer", "front", "back", "left", "right", "top", "bottom", etc., indicate the orientation or positional relationship based on the orientation or positional relationship in the working state of this application. They are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this application.

[0062] In the description of this application, unless otherwise expressly specified and limited, the technical terms "installation," "connection," "joining," "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this application based on the specific circumstances.

[0063] In the description of this application, "multiple" means two or more (including two), unless otherwise expressly and specifically defined.

[0064] In the description of this application, the same reference numerals denote the same components, and for the sake of brevity, detailed descriptions of the same components are omitted in different embodiments. It should be understood that the thickness, length, and other dimensions of various components in the embodiments of this application shown in the drawings, as well as the overall thickness, length, and other dimensions of the integrated device, are merely illustrative and should not constitute any limitation on this application.

[0065] The technical solutions of the embodiments of this application are described in detail below with reference to the accompanying drawings. The technical features involved in the different embodiments of this application described below can be combined with each other as long as they do not conflict with each other.

[0066] like Figures 1 to 22 As shown, the washer-dryer combo provided in this application includes: a housing 10, an outer drum 20, an inner drum 30, a condenser tray 40, a cooling device, and a heating air duct 60.

[0067] like Figures 1 to 7 As shown, the front surface of the housing 10 has a clothing inlet 12. Specifically, the housing 10 typically adopts a rectangular hollow structure. As the outer shell of the washer-dryer combo, its shape can be designed as needed. The internal space of the housing 10 provides installation space for components such as the outer drum 20 and inner drum 30. The clothing inlet 12 on the front surface of the housing 10 connects to the installation space inside the housing 10. A door 11 is located on the front side of the housing 10, which is used to open and close the clothing inlet 12 on the front side of the housing 10, thereby opening and closing the installation space inside.

[0068] like Figures 1 to 7 As shown, the outer drum 20 is disposed inside the housing 10. The front face of the outer drum 20 has an opening opposite to the clothing inlet 12, and the rear wall of the outer drum 20 has an air outlet 21. Specifically, the outer drum 20 is disposed within the installation space of the housing 10 and is relatively fixed inside the housing 10. The outer drum 20 is a shell structure with an opening, the opening of which faces the clothing inlet 12 on the front side of the housing 10. The outer drum 20 is constructed to hold washing water; that is, the internal space of the outer drum 20 can be used to hold washing liquid.

[0069] like Figures 1 to 7 , Figures 13 to 17 As shown, the inner drum 30 is disposed inside the outer drum 20 and can rotate within the outer drum 20. Specifically, the inner drum 30 is rotatably disposed within the internal space of the outer drum 20, and a clothes handling chamber is formed within the inner drum 30 for holding clothes to be washed. The opening of the inner drum 30 is directly opposite the opening of the outer drum 20, that is, the front opening of the clothes handling chamber is directly opposite the opening of the outer drum 20 and the clothes inlet 12. Therefore, clothes can sequentially enter the clothes handling chamber from the clothes inlet 12 of the housing 10, the opening of the outer drum 20, and the opening of the inner drum 30; the outer drum 20 and the inner drum 30 are arranged coaxially inside and outside. Holes are provided on the outer wall of the inner drum 30, allowing water from the outer drum 20 to enter the inner drum 30 through these holes to wash the clothes in the clothes handling chamber of the inner drum 30. Simultaneously, during clothes drying, air from the clothes handling chamber of the inner drum 30 can also enter the internal space of the outer drum 20 through these holes.

[0070] like Figures 1 to 7 , Figures 13 to 17As shown, the condenser plate 40 is disposed on the rear wall of the outer cylinder 20 and located between the inner cylinder 30 and the outer cylinder 20. A cooling channel is provided between the condenser plate and the rear wall of the outer cylinder. Specifically, the condenser plate 40 has a shielding area, which shields the air outlet 21. The air outlet 21 is located on the upper part of the rear wall of the outer cylinder 20. The position of the shielding area is adapted to the position of the air outlet 21. An air passage hole 45 is formed on the shielding area, which connects the air outlet 21 and the space of the condenser plate 40 near the opening of the outer cylinder 20, so that air can pass through the air passage hole 45 and enter the heating channel from the air outlet 21.

[0071] like Figures 1 to 7 , Figures 13 to 17 As shown, the cooling device is installed on the outer cylinder and faces the inlet of the cooling channel. The cooling device is configured to deliver a cooling medium (including coolant and cooling air) to the condenser plate.

[0072] Heating air duct 60 is set on the outer surface of outer cylinder 20 and connects air outlet 21 with the internal space of inner cylinder 30.

[0073] Among them, such as Figure 11 , Figure 12 , Figures 18 to 21 As shown, the condenser plate 40 includes two heat-conducting plates 41 (the material of the heat-conducting plates 41 should be a material with good thermal conductivity; specifically, the material of the heat-conducting plates 41 can be at least one of stainless steel, copper, copper alloy, aluminum, aluminum alloy, titanium, and titanium alloy) and a heat-absorbing medium 42 (the heat-absorbing medium 42 is a gas-liquid mixture with a low boiling point (<20℃). When the condenser plate 40 encounters humid and hot air (the temperature of humid and hot air is generally between 20 and 65℃, and the humidity is between 40%), the liquid heat-absorbing medium 42 can quickly absorb heat and turn into a gaseous state). A closed thermal superconducting channel 43 is formed between the two heat-conducting plates 41. The heat-absorbing medium 42 is located inside the thermal superconducting channel 43. The thickness of the part of the heat-conducting plate 41 that forms the thermal superconducting channel 43 is less than the thickness of other parts.

[0074] The washer-dryer provided in this application, when hot and humid air flows through the condenser plate 40, because the superheated heat pipe covers the entire surface of the condenser plate 40 and the superheated heat pipe has the characteristics of high heat transfer rate and high heat transfer density, the condenser plate 40 can respond quickly to changes in heat, so that the heat is quickly and evenly distributed on the entire condenser plate 40, increasing the temperature difference between the condenser plate 40 and the air and the effective heat transfer area, greatly improving the heat dissipation capacity and heat exchange efficiency of the condenser plate 40, and can quickly absorb the heat in the hot and humid air, so that the moisture in the hot and humid air condenses into water, thereby improving the dehumidification efficiency of the product and achieving rapid drying of clothes.

[0075] In addition, because the channel wall of the thermal superconducting channel 43 is relatively thin, on the one hand, the thin channel wall can shorten the heat transfer time, that is, heat can be transferred quickly through the thin channel wall, enabling the thermal superconducting channel 43 to respond more quickly to temperature changes, and further improving the thermal conductivity of the thermal superconducting channel 43; on the other hand, the thinner channel wall means that the resistance encountered by heat during the transfer process is smaller, allowing heat to be transferred through the channel wall more quickly and efficiently, thereby enabling smoother heat exchange, reducing the accumulation of heat on the channel wall, and further improving the thermal conductivity of the thermal superconducting channel 43.

[0076] Those skilled in the art will understand that, in addition to the above-described structure, washer-dryer combos also include heating components disposed within the heating duct 60, which will not be listed here. In one embodiment of this application, the heating components include a heater 81 and a heating fan 82. The heater 81 heats the air dehumidified by the condenser plate 40, generating high-temperature air within the heating duct 60. The heating fan 82 provides airflow, allowing the high-temperature air within the heating duct 60 to enter the garment processing chamber of the inner drum 30, drying the garments within.

[0077] like Figures 1 to 8 As shown, the drying process of the washer-dryer combo is as follows: The heating element heats the air and allows the hot air to enter the inner drum 30. The hot air passes through the clothes in the inner drum 30, causing the moisture on the clothes to evaporate. The air in the inner drum 30 becomes humid and hot air, which then enters the outer drum 20. The humid and hot air rises in the outer drum 20 and passes through the air outlet 21 into the heating air duct 60. During its upward movement, the condenser plate 40 quickly condenses the moisture in the humid and hot air to form condensate, turning the humid and hot air into dry and cold air. The condensate is drained through the drain outlet below the condenser plate 40 to the bottom of the outer drum 20, and the water in the outer drum 20 is drained away through the drainage device. The dry and cold air is heated by the heating element and re-enters the clothes in the inner drum 30, thus repeating the cycle to dry the clothes.

[0078] like Figure 7 and Figure 17 As shown, in one embodiment of this application, there are multiple cooling channels 91, and a flow divider 92 is provided between the condensation plate 40 and the rear wall of the outer cylinder 20. The multiple cooling channels 91 are all connected to the flow divider 92, and the location of the flow divider 92 corresponds to the location of the cooling device.

[0079] The distribution chamber 92 allows the cooling medium to undergo pressure equalization within the chamber before entering each cooling channel 91. This avoids uneven distribution of cooling medium flow caused by excessive pressure differences at the inlet of cooling channels 91 at different locations; that is, the distribution chamber 92 can evenly distribute the cooling medium from the cooling device into each cooling channel 91. Regardless of the location of the cooling channel 91, a relatively consistent cooling medium flow rate can be obtained, ensuring uniform cooling of all areas of the condenser plate 40, avoiding local overheating or undercooling, and improving the consistency and stability of the cooling effect. In addition, the flow of the cooling medium in the distribution chamber 92 is relatively smooth. When the cooling medium enters the cooling channel 91 from the distribution chamber 92, the flow resistance is reduced due to the expansion and buffering effect of the channel compared to the cooling medium entering the cooling channel 91 directly. This helps to reduce system energy consumption, improve the circulation efficiency of the cooling medium, and make the entire cooling process more energy-efficient and effective.

[0080] like Figure 10 As shown, in one embodiment of this application, a turbulence structure 70 is provided on the rear wall of the outer cylinder 20. The turbulence structure 70 is located in the cooling channel 91 and is configured to disrupt the flow direction of the cooling medium.

[0081] The turbulence structure 70 can generate turbulence in the coolant in the cooling channel. That is, the turbulence structure 70 makes the flow path of the cooling medium in the cooling channel more tortuous and complex, increasing the contact frequency between the cooling medium and the condenser plate 40, thereby effectively improving the heat exchange efficiency and ensuring sufficient cooling of the condenser plate 40. This helps more moisture in the hot and humid air to condense into water droplets on the condenser plate 40, so as to ensure that the condenser plate 40 can fully dehumidify the hot and humid air.

[0082] In one embodiment of this application, the flow area at the outlet of the cooling channel is smaller than the flow area of ​​other parts of the cooling channel (flow area refers to the cross-sectional area when fluid passes through a pipe or channel), that is, the flow area at the outlet of the cooling channel is smaller than the flow area at the inlet of the cooling channel.

[0083] A large inlet allows the cooling medium to enter the channel quickly, increasing the inflow rate. Conversely, a small outlet restricts the outflow rate, causing the accumulation rate of the cooling medium within the channel to exceed its outflow rate. This results in a longer residence time for the cooling medium to reach the outlet and flow out, allowing for more heat exchange with the condenser plate. This ensures the condenser plate can continuously absorb heat from the humid air, effectively dehumidifying the air and guaranteeing efficient dehumidification for rapid drying of clothing. Furthermore, the slow outflow of the cooling medium ensures more even distribution around the condenser plate, preventing uneven cooling and guaranteeing consistent cooling performance across all parts of the condenser plate.

[0084] like Figure 11 , Figure 12 , Figures 18 to 21 As shown, in one embodiment of this application, at least one of the two heat-conducting plates 41 is provided with a groove, and the groove and the plate surface of the other heat-conducting plate 41 form a thermal superconducting channel 43. When one of the two heat-conducting plates 41 is provided with a groove, the groove on one heat-conducting plate 41 and the plate surface of the other heat-conducting plate 41 form a thermal superconducting channel 43; when both heat-conducting plates 41 are provided with grooves, the grooves on the two heat-conducting plates 41 form a thermal superconducting channel 43 (the groove wall is the plate surface of the heat-conducting plate 41). In a specific embodiment of this application, the thermal superconducting channel 43 is formed by a blow-blowing process (the condensing plate 40 can be in a double-sided blow-blowing form, or the condensing plate 40 can be in a single-sided blow-blowing form). The thermal superconducting channel 43 formed by the blow-blowing process forms a protrusion corresponding to the thermal superconducting channel 43 on the outer surface of the heat-conducting plate 41, and at the same time forms a corresponding groove on the inner surface of the heat-conducting plate 41.

[0085] The above structure creates protrusions on the outer surface of one or two heat-conducting plates 41. These protrusions increase the contact area between the hot and humid air and the condenser plate 40, thereby effectively improving the heat exchange efficiency and ensuring that the condenser plate 40 fully dehumidifies the hot and humid air.

[0086] Several embodiments of the cooling device are described below with reference to the accompanying drawings.

[0087] Example 1

[0088] like Figures 1 to 12 As shown, the cooling device includes a spray pipe 51, which is inserted into the outer cylinder 20 from the top and is positioned toward the condenser plate 40. The spray pipe 51 is configured to deliver coolant to the condenser plate 40.

[0089] The condenser plate 40 is cooled by liquid cooling. Since liquid has a large specific heat capacity, it can quickly cool down the condenser plate 40, thereby improving the heat exchange efficiency between the condenser plate 40 and the humid air. At the same time, the coolant can also directly exchange heat with the humid air to condense and dehumidify the humid air, thereby improving the condensation efficiency and drying efficiency.

[0090] In addition, since the thermal superconducting channel 43 has extremely high thermal conductivity, the condenser plate 40 can transfer a large amount of heat to the coolant, which improves the utilization rate of the coolant and reduces the consumption of coolant.

[0091] like Figure 12 As shown, in one embodiment of this application, the condenser plate 40 and the rear wall of the outer cylinder 20 are spaced apart to form a cooling channel 91.

[0092] The cooling channel 91 constructed as described above can form a cooling channel 91 in a limited space without the need to add additional complex structures or components, making the overall structure of the equipment more compact, saving space, and facilitating the miniaturization and integrated design of the equipment.

[0093] like Figure 9 As shown, in one embodiment of this application, the thermal superconducting channel 43 forms a protrusion on the outer surface of the condensation disk 40.

[0094] On the side of the condenser plate 40 near the rear wall of the outer cylinder 20, multiple intersecting protrusions form a cooling cavity 46 on the outer surface of the condenser plate 40.

[0095] The coolant flows within the cooling channel 91 and the cooling chamber 46, forming a complex flow path that allows for heat exchange with the condenser plate 40 from different angles. In the cooling channel 91, the coolant carries away heat from the sides of the condenser plate 40. Upon entering the cooling chamber 46, it cools from the inside, achieving multi-angle, all-around cooling. This results in a more uniform temperature distribution on the condenser plate 40, preventing localized overheating. Furthermore, the coolant can only flow out of the cooling chamber 46 after it is completely filled, extending the contact time between the coolant and the condenser plate 40. This allows for heat exchange, ensuring thorough cooling of the condenser plate 40 and enabling it to continuously absorb heat from the humid air. This effectively dehumidifies the air, ensuring high dehumidification efficiency and enabling rapid drying of clothing.

[0096] In one embodiment of this application, a protrusion is formed on the outer surface of the condenser plate in the thermal superconducting channel. The protrusion and the rear wall of the outer cylinder form a cooling channel, and the spray pipe is configured to deliver coolant to the cooling channel. The protrusion may be continuous or discontinuous.

[0097] The protrusions increase the surface area of ​​the condenser plate, thereby increasing the contact area between the condenser plate and the coolant. This allows the coolant to absorb heat from the condenser plate more effectively, improving cooling efficiency and reducing the condenser plate temperature more efficiently. This also helps to cool and condense more humid air into water droplets, enabling the condenser plate to effectively dehumidify the humid air and ensure efficient dehumidification of the product, thus achieving rapid drying of clothing. Furthermore, the protrusions can form cooling channels with relatively complex shapes and flow fields, making the flow of coolant within these channels more complex and turbulent, thereby enhancing the turbulence of the coolant. Turbulence can break the boundary layer formed by the coolant on the surface of the condenser plate, reducing thermal resistance, increasing the heat transfer coefficient, and further optimizing the cooling effect.

[0098] like Figure 11 As shown, in one embodiment of this application, the spray pipe 51 is positioned toward the edge of the condenser plate 40.

[0099] At the edge of the condenser plate 40, guide slopes 44 are provided on both sides of the condenser plate 40, and the guide slopes 44 are configured to guide the coolant.

[0100] The two guide ramps 44 direct the coolant flow to both sides of the condenser plate 40, increasing the contact area between the coolant and the condenser plate 40. A larger cooling area means more heat can be transferred from the condenser plate 40 to the coolant through thermal conduction, thus more effectively reducing the temperature of the condenser plate 40, improving cooling efficiency, and enhancing the condensation effect on hot and humid air. Furthermore, the coolant flowing on both sides helps to create a more uniform temperature distribution on the condenser plate 40. This avoids the large temperature gradient that can occur with cooling only one side, resulting in a more even overall temperature distribution on the condenser plate 40, reducing thermal stress caused by temperature differences, and extending the service life of the condenser plate 40.

[0101] Example 2

[0102] like Figure 1 , Figures 13 to 22 As shown, the cooling device includes a cooling fan 52, which is disposed on the outer surface of the outer cylinder 20, and the outlet of the cooling fan 52 is connected to the cooling channel 91.

[0103] The cooling channel 91 is isolated from the internal space of the outer cylinder 20, and the outlet 911 of the cooling channel 91 is located on the rear wall of the outer cylinder 20.

[0104] The cooling fan 52 can start quickly and achieve a cooling effect. When the condenser plate 40 needs to be cooled, the cooling fan 52 is turned on, and the air immediately begins to flow and carry away the heat. Therefore, it can respond to the temperature change of the condenser plate 40 more promptly. Moreover, the air cooling method does not involve liquid media, so there are no safety hazards caused by liquid corrosion, leakage, etc.

[0105] In addition, since the thermal superconducting channel 43 has extremely high thermal conductivity, the condenser plate 40 can transfer a large amount of heat to the cooling air, which improves the utilization rate of the cooling air, reduces the consumption of cooling air, and reduces the air volume of the cooling fan 52, thereby reducing the power consumption of the cooling fan 52.

[0106] like Figure 18 As shown, in one embodiment of this application, a thermal superconducting channel 43 forms a protrusion on the outer surface of the condensing plate 40 near the rear wall of the outer cylinder 20, and the protrusion, the condensing plate 40 and the rear wall of the outer cylinder 20 form a cooling channel 91.

[0107] By utilizing the space on the outer surface of the condenser plate 40 to form protrusions and cooling channels, no additional space is needed to arrange the cooling channels 91, making the entire condensation system more compact. This compact design helps reduce the size of the equipment and improves space utilization, making it particularly suitable for applications with limited space.

[0108] In addition, the thermal superconducting channel 43 forms a protrusion on the outer surface of the condensing plate 40. The protrusion increases the area of ​​the outer surface of the condensing plate 40, thereby increasing the contact area between the condensing plate 40 and the cooling air. This allows the cooling air to absorb the heat of the condensing plate 40 more fully, thereby improving the cooling efficiency and reducing the temperature of the condensing plate 40 more effectively.

[0109] like Figure 19 As shown, in one embodiment of this application, a raised rib 22 is provided on the rear wall of the outer cylinder 20. The position of the raised rib 22 corresponds to the position of the protrusion. The raised rib 22, the protrusion, the condensation plate 40, and the rear wall of the outer cylinder 20 form a cooling channel 91. Specifically, the raised rib 22 and the protrusion can be continuous or discontinuous. When the raised rib 22 and the protrusion are continuous, the fitting relationship between the raised rib 22 and the protrusion is that their ends abut against each other; when the raised rib 22 and the protrusion are discontinuous, the fitting relationship between the raised rib 22 and the protrusion is that they are inserted into each other.

[0110] The different combinations of ribs 22 and protrusions make the airflow boundary within the cooling channel 91 more complex, generating more turbulence and vortices as the airflow passes through these structures. This additional airflow turbulence can further improve the heat exchange coefficient between the air and the condenser plate 40 and the rear wall of the outer cylinder 20, promoting heat transfer and thus more effectively reducing the temperature of the condenser plate 40.

[0111] In addition, the ribs 22 can enhance the structural strength of the rear wall of the outer cylinder 20, making it more able to withstand the pressure generated by the air flow in the cooling channel 91 and various stresses during equipment operation, reducing the possibility of deformation of the outer cylinder 20 and improving the stability and reliability of the entire equipment.

[0112] like Figure 20As shown, in one embodiment of this application, an elastic seal 100 is provided between the rib 22 and the protrusion.

[0113] The resilient seal 100 tightly fills the gap between the rib 22 and the protrusion, preventing air from leaking out of the cooling channel 91. This helps maintain air pressure and airflow velocity within the duct, ensuring that cooling air flows along the designed path, thereby improving cooling efficiency and ensuring that the condenser plate 40 is adequately cooled.

[0114] like Figure 21 As shown, in one embodiment of this application, a raised rib 22 is provided on the rear wall of the outer cylinder 20, and the raised rib 22, the condensation plate 40, and the rear wall of the outer cylinder 20 form a cooling channel 91. In a specific embodiment of this application, an elastic seal 100 is provided between the raised rib 22 and the rear wall of the outer cylinder 20.

[0115] By utilizing the rear wall of the outer cylinder 20 and the protruding ribs 22 to form a cooling channel 91 with the condensation plate 40, no additional space is needed to set up a separate cooling channel 91 structure, thus achieving a compact design. This design effectively integrates heat dissipation functions within a limited space, improves space utilization, and makes the overall structure of the equipment simpler and more compact.

[0116] In addition, the raised rib 22 acts as a reinforcing rib on the rear wall of the outer cylinder 20. It can improve the structural strength and rigidity of the rear wall of the outer cylinder 20, making it better able to withstand changes in air pressure within the cooling channel 91 and various stresses generated during equipment operation, reducing the possibility of deformation of the outer cylinder 20 and extending the service life of the equipment.

[0117] In one embodiment of this application, there is one cooling channel, which is spirally arranged between the condenser plate and the outer cylinder.

[0118] The spiral-shaped cooling channel ensures that the cooling air is evenly distributed across the entire circumference of the condenser plate during flow, preventing uneven cooling. The cooling air flows gradually along the spiral channel, sequentially cooling each part of the condenser plate, resulting in a more uniform temperature distribution. This reduces deformation and damage caused by localized overheating or undercooling, extending the lifespan of the condenser plate. Furthermore, the spiral cooling channel maximizes the cooling path within a limited space, fully utilizing the annular space between the condenser plate and the outer cylinder, increasing the contact length between the cooling air and the condenser plate, thereby improving cooling efficiency and achieving better cooling performance in a smaller space.

[0119] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of this application, and not to limit them. Although this application has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some or all of the technical features therein. These modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the scope of the technical solutions of the embodiments of this application, and they should all be covered within the scope of the claims and specification of this application. In particular, as long as there is no structural conflict, the various technical features mentioned in the embodiments can be combined in any way. This application is not limited to the specific embodiments disclosed herein, but includes all technical solutions falling within the scope of the claims.

Claims

1. A washer-dryer combo machine, characterized in that, The washer-dryer combo includes: The box body has a clothing loading port on its front surface; The outer tube is disposed inside the box. The front end face of the outer tube is provided with a tube opening that is arranged opposite to the clothing loading port. The rear wall of the outer tube is provided with an air outlet. An inner cylinder is disposed inside the outer cylinder and is rotatable within the outer cylinder; A condenser plate is disposed on the rear wall of the outer cylinder and located between the inner cylinder and the outer cylinder. A cooling channel is provided between the condenser plate and the rear wall of the outer cylinder. A cooling device, disposed on the outer cylinder and facing the inlet of the cooling channel, is configured to supply a cooling medium to the condensation pan; and A heating air duct is disposed on the outer surface of the outer cylinder and connects the air outlet with the internal space of the inner cylinder; The condensation plate includes two heat-conducting plates and a heat-absorbing medium. A closed thermal superconducting channel is formed between the two heat-conducting plates. The heat-absorbing medium is located inside the thermal superconducting channel. The thickness of the portion of the heat-conducting plate that forms the thermal superconducting channel is less than the thickness of the other portions.

2. The washer-dryer combo machine according to claim 1, characterized in that, The cooling device includes a spray pipe inserted into the outer cylinder from the top of the outer cylinder, the spray pipe being configured to deliver coolant to the condenser pan.

3. The washer-dryer combo machine according to claim 2, characterized in that, The cooling channel is formed by the condenser plate and the rear wall of the outer cylinder spaced apart.

4. The washer-dryer combo machine according to claim 3, characterized in that, The thermal superconducting channel forms a protrusion on the outer surface of the condensation disk; On the side of the condenser plate near the rear wall of the outer cylinder, a plurality of intersecting protrusions form a cooling cavity on the outer surface of the condenser plate.

5. The washer-dryer combo machine according to claim 2, characterized in that, The spray pipe is positioned toward the edge of the condensation plate; At the edge of the condenser, guide ramps are provided on both sides of the condenser, and the guide ramps are configured to guide the coolant.

6. The washer-dryer combo machine according to claim 1, characterized in that, The cooling device includes a cooling fan, which is disposed on the outer surface of the outer cylinder and the outlet of the cooling fan is connected to the cooling channel. The cooling channel is isolated from the internal space of the outer cylinder, and the outlet of the cooling channel is located on the rear wall of the outer cylinder.

7. The washer-dryer combo machine according to claim 6, characterized in that, On the side of the condensing plate near the rear wall of the outer cylinder, the thermal superconducting channel forms a protrusion on the outer surface of the condensing plate. The rear wall of the outer cylinder is provided with a rib, the position of which corresponds to the position of the protrusion. The rib, the protrusion, the condensing plate, and the rear wall of the outer cylinder form the cooling channel.

8. The washer-dryer combo machine according to claim 7, characterized in that, An elastic seal is provided between the rib and the protrusion.

9. The washer-dryer combo machine according to any one of claims 1 to 8, characterized in that, The flow area at the outlet of the cooling channel is smaller than the flow area of ​​other parts of the cooling channel.

10. The washer-dryer combo machine according to any one of claims 1 to 8, characterized in that, A turbulence-disrupting structure is provided on the rear wall of the outer cylinder. The turbulence-disrupting structure is located within the cooling channel and is configured to disrupt the flow direction of the cooling medium.

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