Clothes drying device and washing-drying integrated machine

Abstract

A clothes drying device (10) and a washing-drying integrated machine. The clothes drying device (10) comprises a housing (100), a drum (200) and a heat pump system (300); the housing (100) is provided with an air duct (110); the drum (200) is provided with a drying cavity (210), the drying cavity (210) being communicated with the air duct (110) to form a circulating air path (120); the heat pump system (300) comprises a compressor (310), and a condenser (320), an evaporator (330) and an airflow driving member (340) which are arranged in the air duct (110), the airflow driving member (340) being used for driving airflow to circulate in the circulating air path (120); the condenser (320) has a condensation flow path (323), and the evaporator (330) has at least two independent evaporation flow paths (331), the number of evaporation flow paths (331) of the evaporator (330) being greater than the number of condensation flow paths (323) of the condenser (320); the at least two evaporation flow paths (331) are all communicated with the condenser (320); a refrigerant discharged from the compressor (310) first flows through the condensation flow path (323) and then flows through the at least two evaporation flow paths (331), thereby forming a refrigerant circulation loop (350).

Description

Clothes drying unit and washer-dryer combo

[0001] Related applications

[0002] This application claims priority to Chinese patent application No. 202520157531.5, filed on January 22, 2025, the entire contents of which are incorporated herein by reference. Technical Field

[0003] This application relates to the field of clothing drying technology, and in particular to a clothing drying device and a washer-dryer combo. Background Technology

[0004] In related technologies, clothes drying devices are used to dry items such as clothes, sheets, and curtains. Existing clothes drying devices have long drying times, affecting user experience. Traditional solutions improve drying efficiency by adding piping to the evaporator or condenser, but this increases the size of the heat pump, and the increased piping further increases flow resistance. In washer-dryer combos, which have both washing and drying structures, space is limited, and the heat pump system needs to improve drying efficiency within this confined space. Summary of the Invention

[0005] The main purpose of this application is to propose a clothes drying device and a washer-dryer combo machine, which aims to shorten the drying time of existing clothes drying devices.

[0006] To achieve the above objectives, the clothing drying apparatus proposed in this application includes:

[0007] The casing has air ducts;

[0008] The drum has a drying chamber, which is connected to the air duct to form a circulating air path;

[0009] A heat pump system includes a compressor and a condenser, an evaporator and an airflow drive unit disposed in the air duct, the airflow drive unit being used to drive airflow to circulate within the circulating air duct;

[0010] The condenser includes a condensing heat exchange tube, and the evaporator includes an evaporating heat exchange tube. The inner diameter of the evaporating heat exchange tube is larger than the inner diameter of the condensing heat exchange tube. The evaporating heat exchange tube has at least two independent evaporating flow paths, and at least two of the evaporating flow paths are connected to the condensing heat exchange tube. The refrigerant discharged from the compressor first flows through the condensing heat exchange tube, and then flows through the at least two evaporating flow paths to form a refrigerant circulation loop.

[0011] In one embodiment, the evaporation heat exchange tube includes a plurality of straight evaporation tubes and an evaporation bend connecting two adjacent straight evaporation tubes. The plurality of straight evaporation tubes are arranged in N rows along a first direction, where N is not less than 4.

[0012] And / or, the evaporator further includes a plurality of fins disposed on the evaporation heat exchange tube, the total length of the evaporation heat exchange tube being greater than 4 meters.

[0013] In one embodiment, the inner diameter of the evaporative heat exchange tube is not less than 7 mm and not more than 12 mm;

[0014] And / or, the inner diameter of the condenser heat exchange tube is not less than 5 mm and not more than 10 mm.

[0015] In one embodiment, the condenser heat exchange tube includes a plurality of condenser straight tubes and a condenser bend connecting two adjacent condenser straight tubes, and the evaporator heat exchange tube includes a plurality of evaporator straight tubes and an evaporator bend connecting two adjacent evaporator straight tubes; the inner diameter of the evaporator straight tube is larger than the inner diameter of the condenser straight tube.

[0016] And / or, the inner diameter of the evaporation bend is larger than the inner diameter of the condensation bend;

[0017] And / or, the plurality of condenser straight tubes and the plurality of evaporator straight tubes are all arranged to extend along a third direction, and the plurality of condenser straight tubes and the plurality of evaporator straight tubes are arranged in multiple rows along a first direction, the first direction being perpendicular to the third direction; the number of rows of condenser straight tubes in the condenser is less than or equal to the number of rows of evaporator straight tubes in the evaporator.

[0018] In one embodiment, along the first direction, the number of rows of condenser straight tubes in the condenser is the same as the number of rows of evaporator straight tubes in the evaporator; the plurality of condenser straight tubes and the plurality of evaporator straight tubes are arranged in multiple columns along the vertical direction, and the number of condenser straight tubes in each column is greater than the number of evaporator straight tubes in each column.

[0019] In one embodiment, the volume of the condenser is V1, the volume of the evaporator is V2, and the ratio of V1 to V2 is not less than 0.8 and not greater than 1.0.

[0020] And / or, in the direction from the windward side to the leeward side of the condenser, the width of the condenser is W1; in the direction from the windward side to the leeward side of the evaporator, the width of the evaporator is W2; the ratio of W1 to W2 is not less than 0.8 and not greater than 1.0.

[0021] In one embodiment, the operation phase of the clothes drying device includes a heating phase and a temperature stabilization phase, and the compressor includes a variable frequency compressor;

[0022] During the heating phase, the variable frequency compressor first increases the frequency and then decreases the frequency to a preset high frequency in order to enter the temperature stabilization phase.

[0023] During the temperature stabilization phase, the variable frequency compressor operates at the preset high frequency, which is not less than 70 Hz.

[0024] In one embodiment, the variable frequency compressor has an exhaust port connected to the refrigerant circulation loop, and during the temperature stabilization phase, the temperature of the refrigerant discharged from the exhaust port does not exceed 110 degrees Celsius.

[0025] In one embodiment, the condensing heat exchange tube has a condensing flow path, and the number of evaporating flow paths of the evaporating heat exchange tube is greater than the number of condensing flow paths of the condensing heat exchange tube. The refrigerant discharged from the compressor first flows through the condensing flow path and then flows through at least two of the evaporating flow paths to form the refrigerant circulation loop.

[0026] In one embodiment, one end of the evaporation flow path is a refrigerant inlet, and the other end of the evaporation flow path is a refrigerant outlet. At least two refrigerant inlets of the evaporation flow paths are located on the same side of the evaporator and are arranged adjacent to each other.

[0027] And / or, the refrigerant outlets of at least two of the evaporation flow paths are located on the same side of the evaporator and are arranged adjacent to each other.

[0028] In one embodiment, the evaporator further includes a distribution connector having at least three interconnected distribution channels; at least two refrigerant inlets of the evaporation flow paths are connected to the refrigerant circulation loop through one of the distribution connectors;

[0029] And / or, at least two of the refrigerant outlets of the evaporation flow paths are connected to the refrigerant circulation loop via one of the distribution connectors.

[0030] In one embodiment, the evaporator and the condenser are arranged sequentially along a first direction. The evaporation heat exchange tube includes a first branch tube and a second branch tube. The first branch tube has a first branch channel, and the second branch tube has a second branch channel. The first branch channel and the second branch channel are independent of each other and are respectively connected to one of the evaporation flow paths. The first branch tube and the second branch tube are arranged crosswise on the same side of the evaporator.

[0031] In one embodiment, the evaporation heat exchange tube further includes a plurality of evaporation pipes, which are arranged sequentially along the windward side to the leeward side of the evaporator. Each evaporation pipe includes a plurality of straight evaporation pipes and an evaporation bend connecting two adjacent straight evaporation pipes. The straight evaporation pipes extend in a third direction. The first branch pipe connects two evaporation pipes of one of the evaporation flow paths, and the second branch pipe connects two evaporation pipes of the other evaporation flow path.

[0032] And / or, the projection of the intersection point of the first and second branch pipes, which are arranged in a cross configuration, along the third direction falls on the center position of one side of the evaporator;

[0033] And / or, multiple evaporation straight tubes are arranged in multiple columns along the vertical direction, and two evaporation straight tubes in two adjacent columns are staggered in the vertical and horizontal directions.

[0034] In one embodiment, a plurality of the evaporation straight tubes are arranged in multiple columns along the vertical direction, and the number of the evaporation straight tubes in each column is even, so that the two evaporation flow paths are evenly distributed.

[0035] And / or, multiple rows of the evaporation straight tubes are arranged in an even number of rows along a first direction to allow the two evaporation flow paths to be evenly divided, wherein the first direction is perpendicular to the third direction.

[0036] In one embodiment, the refrigerant inlet of each evaporation flow path is located close to the first side, and the refrigerant outlet of each evaporation flow path is located close to the second side, with the first side and the second side being opposite to each other; the two evaporation flow paths are spaced apart in the vertical direction.

[0037] And / or, the two evaporation flow paths are spaced apart along the direction from the windward side to the leeward side of the evaporator.

[0038] This application also proposes a washer-dryer combo, including the clothing drying device described above.

[0039] In one embodiment, the washer-dryer combo includes a drying component and a washing component.

[0040] The clothing drying device of this application includes a shell, a drum, and a heat pump system. The shell has an air duct, the drum has a drying chamber, and the drying chamber is connected to the air duct to form a circulating air path. The heat pump system includes a compressor, a condenser, an evaporator, and an airflow drive component located in the air duct. Under the action of the airflow drive component, the air in the air duct is heated by the condenser and sent to the drying chamber to dry the clothes. The hot and humid air discharged from the drying chamber flows through the evaporator, which absorbs heat to turn the hot and humid air into dry, low-temperature air, and the water vapor in the hot and humid air is condensed into condensate and discharged. The dry, low-temperature air then flows through the condenser for circulation, thereby realizing the function of drying clothes. The condenser includes condensing heat exchange tubes, and the evaporator includes evaporating heat exchange tubes. The inner diameter of the evaporating heat exchange tubes is larger than that of the condensing heat exchange tubes. This improves the smoothness of refrigerant flow through the evaporator, reduces the flow resistance of the refrigerant, and thus reduces the pressure loss of the refrigerant flowing through the evaporator. This, in turn, increases the suction pressure at the compressor's suction port and reduces the discharge temperature at the compressor's discharge port, enabling the compressor to operate at high frequency for extended periods. Furthermore, compared to a single evaporation flow path, the evaporator in this application has at least two independent evaporation flow paths. The system has a strong dehumidification and cooling capacity for hot and humid air, which increases the dehumidification capacity of the evaporator. At least two independent evaporation flow paths can reduce the flow resistance of the refrigerant through the evaporator, thereby reducing the pressure loss of the refrigerant through the evaporator. This, in turn, increases the suction pressure at the compressor's suction port and reduces the discharge temperature at the compressor's discharge port, allowing the compressor to operate at a high frequency for a long time. In this way, while enhancing the dehumidification capacity of the clothes drying device, it can also prevent the compressor's discharge temperature from becoming too high and exceeding the acceptable range, thus requiring frequency reduction or shutdown. This can shorten the drying time of clothes. Attached Figure Description

[0041] 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 only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on the structures shown in these drawings without creative effort.

[0042] Figure 1 is a schematic diagram of the clothing drying device provided in this application;

[0043] Figure 2 is a partial structural schematic diagram of the clothes drying device provided in this application;

[0044] Figure 3 is a schematic diagram of part of the structure in Figure 2;

[0045] Figure 4 is a cross-sectional view of the structure in Figure 3;

[0046] Figure 5 is a schematic diagram of part of the structure in Figure 3;

[0047] Figure 6 is a schematic diagram of the structure in Figure 5 from another perspective;

[0048] Figure 7 is a schematic diagram of the evaporator in Figure 5 from another perspective;

[0049] Figure 8 is a schematic diagram of the first embodiment of the evaporator provided in this application;

[0050] Figure 9 is a schematic diagram of the second embodiment of the evaporator provided in this application;

[0051] Figure 10 is a schematic diagram of the third embodiment of the evaporator provided in this application;

[0052] Figure 11 is a schematic diagram of the fourth embodiment of the evaporator provided in this application;

[0053] Figure 12 is a schematic diagram of the fifth embodiment of the evaporator provided in this application;

[0054] Figure 13 is a schematic diagram of the condenser in Figure 5 from another perspective.

[0055] Reference numerals: 10. Clothes drying unit; 100. Shell; 110. Air duct; 120. Circulating air path; 200. Drum; 210. Drying chamber; 220. Air inlet; 230. Air outlet; 300. Heat pump system; 310. Compressor; 311. Exhaust port; 320. Condenser; 320a. Condensing heat exchange tube; 321. Condensing straight tube; 322. Condensing bend; 323. Condensing flow path; 330. Evaporator; 330a. Evaporating heat exchange tube; 331. Evaporating flow path; 332. Refrigerant inlet; 333. Refrigerant outlet; 334. Distribution connector; 335. First branch pipe; 336. Second branch pipe; 337. Evaporation pipe; 3371. Evaporating straight tube; 3372. Evaporating bend; 340. Airflow drive component; 350. Refrigerant circulation loop; 400. Drainage assembly; 500. Filter components.

[0056] The realization of the purpose, functional features and advantages of this application will be further explained in conjunction with the embodiments and with reference to the accompanying drawings. Detailed Implementation

[0057] 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 a part of the embodiments of this application, and not all of the embodiments. Based on the embodiments of this application, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of this application.

[0058] It should be noted that if the embodiments of this application involve directional indicators (such as up, down, left, right, front, back, etc.), the directional indicators are only used to explain the relative positional relationship and movement of the components in a specific posture. If the specific posture changes, the directional indicators will also change accordingly.

[0059] Furthermore, if the embodiments of this application involve descriptions such as "first" or "second," these descriptions are for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated. Therefore, a feature defined with "first" or "second" may explicitly or implicitly include at least one of those features. Additionally, the use of "and / or" or "and / or" throughout the text includes three parallel solutions. For example, "A and / or B" includes solution A, solution B, or a solution that simultaneously satisfies A and B. Furthermore, the technical solutions of the various embodiments can be combined with each other, but this must be based on the ability of those skilled in the art to implement them. When the combination of technical solutions is contradictory or impossible to implement, it should be considered that such a combination of technical solutions does not exist and is not within the scope of protection claimed in this application.

[0060] In related technologies, clothes drying devices are used to dry items such as clothes, sheets, and curtains. Existing clothes drying devices have long drying times, affecting user experience. Traditional solutions improve drying efficiency by adding piping to the evaporator or condenser, but this increases the size of the heat pump, and the increased piping further increases flow resistance. In washer-dryer combos, which have both washing and drying structures, space is limited, and the heat pump system needs to improve drying efficiency within this confined space.

[0061] Based on this, this application proposes a clothes drying device and a washer-dryer combo, which can shorten the drying time of clothes. The clothes drying device is used to dry items such as clothes, sheets, and curtains. The washer-dryer combo not only performs the function of washing clothes, but also dries them directly after washing, so users do not need to move clothes from the washing machine to the dryer; that is, the washer-dryer combo has both washing and drying functions.

[0062] Referring to Figures 1 to 6, in one embodiment of this application, the clothes drying device 10 includes a housing 100, a drum 200, and a heat pump system 300. The housing 100 has an air duct 110; the drum 200 has a drying chamber 210, which communicates with the air duct 110 to form a circulating air path 120; the heat pump system 300 includes a compressor 310 and a condenser 320, an evaporator 330, and an airflow drive 340 disposed in the air duct 110. The airflow drive 340 is used to drive airflow in the circulating air path 120. 0. Internal circulation; the condenser 320 includes a condensing heat exchange tube 320a, and the evaporator 330 includes an evaporating heat exchange tube 330a. The inner diameter of the evaporating heat exchange tube 330a is larger than the inner diameter of the condensing heat exchange tube 320a. The evaporating heat exchange tube 330a has at least two independent evaporating flow paths 331, and at least two evaporating flow paths 331 are connected to the condensing heat exchange tube 320a. The refrigerant discharged from the compressor 310 first flows through the condensing heat exchange tube 320a, and then flows through the at least two evaporating flow paths 331 to form a refrigerant circulation loop 350.

[0063] Figure 1 is a schematic diagram of the principle of the clothes drying device 10. Referring to Figure 1, the working principle of the clothes drying device 10 is as follows: The compressor 310 discharges refrigerant along the refrigerant circulation loop 350. The refrigerant releases heat through the condenser 320, absorbs heat through the evaporator 330, and then returns to the compressor 310. The airflow drive component 340 sends the air heated by the condenser 320 into the drum 200 to dry the clothes. The humid, hot air flowing out of the drum 200 then flows through the evaporator 330, where it transforms the humid, hot air from the drum 200 into dry, low-temperature air. The water vapor in the humid, hot air is condensed into condensate and discharged. The dry, low-temperature air is then reheated by the condenser 320, thus completing one cycle. The clothes drying device 10 continuously removes moisture through this cycle and discharges it as condensate, thereby achieving the function of drying clothes.

[0064] The drum 200 is rotatably housed within the housing 100. The heat pump system 300 is also housed within the housing 100. The condenser 320 and evaporator 330 are located below the drum 200 and spaced apart from it to prevent the drum 200 from impacting the heat pump system 300 during the washing and spin-drying process. The heat pump system 300 can also be detachably mounted from the housing 100 for easy disassembly, installation, maintenance, and replacement.

[0065] In one embodiment, the drum 200 has a drying chamber 210 and an air inlet 220 and an air outlet 230 communicating with the drying chamber 210. One end of the air duct 110 is connected to the air inlet 220, and the other end of the air duct 110 is connected to the air outlet 230. The airflow drive 340 is used to drive the airflow to flow sequentially through the condenser 320, the air inlet 220, the drying chamber 210, the air outlet 230, and the evaporator 330 to form a circulating air path 120.

[0066] In one embodiment, the airflow drive 340 can be a fan, but it can also be other components, which are not limited here. Furthermore, the clothes drying device 10 also includes a drainage assembly 400, which includes a drip tray for collecting condensate from the evaporator 330. The drainage assembly 400 may also include a drain pump for discharging the condensate collected in the drip tray.

[0067] In one embodiment, the clothes drying device 10 further includes a filter element 500 disposed in the circulating air passage 120 between the air outlet 230 of the drum 200 and the evaporator 330. The filter element 500 includes a filter screen for filtering impurities, such as lint, from the humid and hot air discharged from the air outlet 230.

[0068] The clothes drying device 10 includes a housing 100. When the external dimensions of the housing 100 are limited, such as when the external dimensions of the housing 100 cannot be changed and the existing external dimensions of the housing 100 need to be maintained, it is difficult to shorten the drying time of the clothes.

[0069] The condensing heat exchange tube 320a is the pipe through which the refrigerant flows in the condenser 320. When the high-temperature and high-pressure refrigerant gas discharged from the compressor flows through the condensing heat exchange tube 320a of the condenser 320, it releases heat and condenses into a high-pressure liquid. In this process, the refrigerant releases heat to the surrounding environment.

[0070] Evaporation heat exchange tube 330a is the pipeline through which the refrigerant flows in the evaporator 330. High-pressure liquid refrigerant enters the throttling device from the condenser, and after being depressurized, it flows into the evaporator. The evaporator is the part where the refrigerant absorbs heat. Low-pressure, low-temperature refrigerant comes out from the throttling device, enters the evaporator, and evaporates into low-pressure gas by absorbing heat, and then returns to the compressor.

[0071] Due to the limitations of the external dimensions of the housing 100, the total dimensions of the condenser 320 and the evaporator 330 are limited. The evaporator 330 includes evaporation heat exchange tubes 330a. The area of ​​the condenser 320 and the evaporator 330 on the windward side inside the housing 100 is small. Simply increasing the number of rows of evaporation heat exchange tubes will increase the thickness of the evaporator 330 and also increase the wind resistance in the air duct 110. Therefore, the solution of increasing the number of rows of evaporation heat exchange tubes in the evaporator 330 cannot meet the requirement of keeping the external dimensions of the housing 100 unchanged, nor can it solve the problem of shortening the clothes drying time.

[0072] Based on this, the technical solution of this application improves the smoothness of refrigerant flow through the evaporator 330 by limiting the inner diameter of the evaporator heat exchange tube 330a to be larger than the inner diameter of the condenser heat exchange tube 320a, thereby reducing the flow resistance of the refrigerant through the evaporator and reducing the pressure loss of the refrigerant through the evaporator. This, in turn, increases the suction pressure at the compressor's suction port and reduces the discharge temperature at the compressor's discharge port, enabling the compressor to operate at high frequency for a long time. Furthermore, the evaporator 330 is configured to have at least two independent evaporation flow paths 331 to increase the dehumidification capacity of the evaporator and reduce the flow resistance of the refrigerant through the evaporator. The evaporation flow paths 331 can be two, three, or more, etc., and are not specifically limited here. It is only necessary that the evaporator 330 has at least two independent evaporation flow paths 331 without changing the external dimensions of the existing shell 100.

[0073] The evaporator 330 has at least two independent evaporation flow paths 331, each of which can supply refrigerant. The arrangement of the at least two evaporation flow paths 331 is not limited. For example, two adjacent evaporation flow paths 331 are spaced apart in the vertical direction; or, two adjacent evaporation flow paths 331 are spaced apart in the direction from the windward side to the leeward side of the evaporator 330. The direction from the windward side to the leeward side of the evaporator 330 is the width direction of the evaporator 330.

[0074] When an evaporator has two evaporation paths, it has two refrigerant inlets for refrigerant to flow into and two refrigerant outlets for refrigerant to flow out. The two evaporation paths are independent of each other; refrigerant in one evaporation path cannot flow into the other. When an evaporator has multiple evaporation paths, it has multiple refrigerant inlets for refrigerant to flow into and multiple refrigerant outlets for refrigerant to flow out. The multiple evaporation paths are independent of each other; refrigerant in any one of the multiple evaporation paths cannot flow into the other.

[0075] As shown in Figures 7 to 12, the refrigerant flows in the evaporator 330 in the direction indicated by the arrow. Figures 7 to 12 show that the evaporator 330 has two independent evaporation flow paths 331. The thick solid arrow indicates the flow direction of the refrigerant in the pipe located on the front side of the evaporator 330, and the thick dashed arrow indicates the flow direction of the refrigerant in the pipe located on the rear side of the evaporator 330.

[0076] Compared to having only one evaporation flow path 331, the evaporator 330 in this application has at least two independent evaporation flow paths 331. The at least two independent evaporation flow paths 331 have a strong dehumidification and cooling capacity for hot and humid air, thereby increasing the dehumidification capacity of the evaporator 330 and thus shortening the drying time of clothes.

[0077] The technical solution of this application configures the evaporator 330 with at least two independent evaporation flow paths 331. Compared with only one evaporation flow path 331, two independent evaporation flow paths 331 can disperse the flow pressure of the refrigerant, that is, reduce the flow resistance of the refrigerant flowing through the evaporator 330, thereby reducing the pressure loss of the refrigerant flowing through the evaporator 330, thereby increasing the suction pressure of the compressor 310's suction port and reducing the discharge temperature of the compressor 310's discharge port 311. This allows the compressor 310 to operate at a high frequency for a long time, avoiding the situation where the discharge temperature of the compressor 310 exceeds the acceptable range and needs to be reduced in frequency or shut down. This can shorten the drying time of clothes.

[0078] The clothes drying device 10 of this application includes a housing 100, a drum 200, and a heat pump system 300. The housing 100 has an air duct 110, and the drum 200 has a drying chamber 210. The drying chamber 210 is connected to the air duct 110 to form a circulating air path 120. The heat pump system 300 includes a compressor 310 and a condenser 320, an evaporator 330, and an airflow drive component 340 disposed in the air duct 110. Under the action of the airflow drive component 340, the air in the air duct 110 is heated by the condenser 320 and sent to the drying chamber 210 to dry the clothes. The hot and humid air discharged from the drying chamber 210 flows through the evaporator 330. The evaporator 330 absorbs heat to turn the hot and humid air into dry, low-temperature air, and the water vapor in the hot and humid air is condensed into condensate and discharged. The dry, low-temperature air then flows through the condenser 320 for circulation, thereby realizing the function of drying clothes. The condenser 320 includes a condensing heat exchange tube 320a, and the evaporator 330 includes an evaporating heat exchange tube 330a. The inner diameter of the evaporating heat exchange tube 330a is larger than that of the condensing heat exchange tube 320a. This improves the smoothness of refrigerant flow through the evaporator 330, reduces the flow resistance of the refrigerant, and thus reduces the pressure loss of the refrigerant flowing through the evaporator 330. This, in turn, increases the suction pressure at the compressor's suction port and reduces the discharge temperature at the compressor's discharge port, enabling the compressor to operate at high frequency for extended periods. Furthermore, compared to a single evaporation flow path 331, the evaporator 330 in this application has at least two independent evaporation flow paths 331. The independent evaporation flow path 331 has a strong dehumidification and cooling capacity for hot and humid air, thereby increasing the dehumidification capacity of the evaporator 330. Moreover, at least two independent evaporation flow paths 331 can reduce the flow resistance of the refrigerant through the evaporator 330, thereby reducing the pressure loss of the refrigerant through the evaporator 330. This, in turn, increases the suction pressure at the suction port of the compressor 310 and reduces the discharge temperature at the discharge port 311 of the compressor 310, enabling the compressor 310 to operate at a high frequency for a long time. In this way, while enhancing the dehumidification capacity of the clothes drying device, it can also prevent the discharge temperature of the compressor 310 from becoming too high and exceeding the acceptable range, thus requiring frequency reduction or shutdown. This can shorten the drying time of clothes.

[0079] In one embodiment, the evaporator heat exchange tube 330a includes a plurality of straight evaporator tubes 3371 and an evaporator bend 3372 connecting two adjacent straight evaporator tubes 3371. The plurality of straight evaporator tubes 3371 are arranged in N rows along a first direction, where N is not less than 4. The number of rows of the plurality of straight evaporator tubes 3371 can be 4, 5, 6, or other numbers. By limiting the number of rows of the plurality of straight evaporator tubes 3371, it can be ensured that the evaporator 330 has sufficient volume, and that the evaporator heat exchange tube 330a has at least two independent evaporation flow paths 331, so that the refrigerant can flow smoothly through the evaporator heat exchange tube 330a, thereby reducing the flow resistance of the refrigerant through the evaporator, thereby reducing the pressure loss of the refrigerant through the evaporator, thereby increasing the suction pressure at the compressor suction port and reducing the discharge temperature at the compressor discharge port, so that the compressor can operate at high frequency for a long time.

[0080] In one embodiment, the evaporator 330 further includes multiple fins disposed on the evaporation heat exchange tube 330a, the total length of which is greater than 4 meters. The total length of the evaporation heat exchange tube 330a is the total length of the multiple straight evaporation tubes 3371 and the multiple bent evaporation tubes 3372. The total length of the evaporation heat exchange tube 330a is greater than 4 meters, for example, 4.1 meters, or 4.2 meters, or 4.3 meters, or 4.4 meters, or 4.5 meters, or 4.6 meters, or 4.7 meters, or 4.8 meters, or 4.9 meters, or 5.0 meters, or 5.1 meters, or 5.2 meters, or 5.3 meters, or 5.4 meters, or 5.5 meters, etc., and is not specifically limited here. By limiting the total length of the evaporator heat exchange tube 330a to more than 4 meters, it can be ensured that when the refrigerant flows through the evaporator 330, the evaporator 330 has a strong dehumidification and cooling capacity for the humid and hot air, thereby increasing the dehumidification capacity of the evaporator. In addition, the evaporator has at least two independent evaporation flow paths, which helps to reduce the flow resistance of the refrigerant flowing through the evaporator, thereby reducing the pressure loss of the refrigerant flowing through the evaporator. This, in turn, increases the suction pressure at the compressor's suction port and reduces the discharge temperature at the compressor's discharge port, allowing the compressor to operate at high frequency for a long time. This avoids the situation where the compressor's discharge temperature is too high and exceeds the acceptable range, requiring frequency reduction or shutdown. As a result, the drying time of clothes can be shortened.

[0081] In one embodiment, the inner diameter of the evaporation heat exchange tube 330a is not less than 7 mm and not more than 12 mm; and / or, the inner diameter of the condensation heat exchange tube 320a is not less than 5 mm and not more than 10 mm.

[0082] The inner diameter of the evaporator heat exchanger tube 330a can be 7mm, 7.5mm, 8.0mm, 8.5mm, 9.0mm, 9.5mm, 10.0mm, 10.5mm, 11.0mm, 11.5mm, or 12.0mm, etc., and is not specifically limited here. The inner diameter of the condenser heat exchanger tube 320a can be 5mm, 5.5mm, 6.0mm, 6.5mm, 7.0mm, 7.5mm, 8.0mm, 8.5mm, 9.0mm, 9.5mm, or 10.0mm, etc., and is not specifically limited here, only requiring that the inner diameter of the evaporator heat exchanger tube 330a is larger than the inner diameter of the condenser heat exchanger tube 320a.

[0083] In one embodiment, the condenser heat exchanger tube 320a includes a plurality of condenser straight tubes 321 and a condenser bend 322 connecting two adjacent condenser straight tubes 321, and the evaporator heat exchanger tube 330a includes a plurality of evaporator straight tubes 3371 and an evaporator bend 3372 connecting two adjacent evaporator straight tubes 3371; the inner diameter of the evaporator straight tube 3371 is larger than the inner diameter of the condenser straight tube 321; and / or, the inner diameter of the evaporator bend 3372 is larger than the inner diameter of the condenser bend 322. This configuration ensures that the inner diameter of the evaporator heat exchange tube 330a is larger than that of the condenser heat exchange tube 320a. This improves the smoothness of the refrigerant flow through the evaporator, reduces the flow resistance of the refrigerant, and thus reduces the pressure loss of the refrigerant flowing through the evaporator. This, in turn, increases the suction pressure at the compressor's suction port and reduces the discharge temperature at the compressor's discharge port, allowing the compressor to operate at a high frequency for a longer period of time. While enhancing the dehumidification capacity of the clothes drying device, it also prevents the compressor's discharge temperature from exceeding the acceptable range and requiring frequency reduction or shutdown, thereby shortening the drying time of clothes.

[0084] In conventional dryers, the condenser 320 is made larger to increase heating capacity. However, given the limited space within the casing 100, making the condenser 320 larger will reduce the volume of the evaporator 330, resulting in a smaller evaporator 330 with poor dehumidification and cooling capacity. The amount of water carried out by the heat pump system 300 from the drum 200 is greater than the dehumidification capacity of the evaporator 330, thus reducing dehumidification efficiency and affecting drying time.

[0085] Based on this, in one embodiment, the volume of the condenser 320 is not greater than the volume of the evaporator 330. The technical solution of this application limits the volume of the condenser 320 to be no greater than the volume of the evaporator 330. With the sum of the volumes of the condenser 320 and the evaporator 330 limited, the volume of the condenser 320 is limited to be less than or equal to the volume of the evaporator 330. This ensures that the volume of the evaporator 330 is sufficiently large relative to the volume of the condenser 320, resulting in high heat exchange efficiency and strong dehumidification and cooling capacity for humid and hot air. This increases the dehumidification capacity of the evaporator 330, thereby shortening the drying time of clothes.

[0086] As can be seen from the foregoing, in conventional dryers, the condenser 320 has a relatively large volume, while the evaporator 330 in conventional dryers has a smaller volume than the condenser 320. Consequently, the evaporator 330 in conventional dryers has poor dehumidification and cooling capabilities, which affects the drying time.

[0087] Based on this, in one embodiment of this application, the volume of the condenser 320 is V1, the volume of the evaporator 330 is V2, and the ratio of V1 to V2 is not less than 0.8 and not greater than 1.0.

[0088] The specific value of the ratio of the volume V1 of the condenser 320 to the volume V2 of the evaporator 330 is not limited, but can be, for example but not limited to: 0.8, or 0.81, or 0.82, or 0.83, or 0.84, or 0.85, or 0.86, or 0.87, or 0.88, or 0.89, or 0.90, or 0.91, or 0.92, or 0.93, or 0.94, or 0.95, or 0.96, or 0.97, or 0.98, or 0.99, or 1.0, etc.

[0089] The sum of the volume V1 of the condenser 320 and the volume V2 of the evaporator 330 is V3. This solution limits the ratio of the volume V1 of the condenser 320 to the volume V2 of the evaporator 330, which is equivalent to limiting the ratio of the volume V2 to V3 of the evaporator 330. That is, when the sum of the volume V1 of the condenser 320 and the volume V2 of the evaporator 330 remains unchanged, this embodiment ensures that the evaporator 330 has sufficient size by limiting the proportion of the volume V2 of the evaporator 330 in V3, thereby improving the dehumidification and cooling capacity of the evaporator 330.

[0090] The ratio of V1 to V2 is not less than 0.8 and not greater than 1.0, indicating that the volume V1 of the condenser 320 is less than or equal to the volume V2 of the evaporator 330. This makes the volume V2 of the evaporator 330 sufficiently large relative to the volume V1 of the condenser 320, and the evaporator 330 has sufficient dehumidification and cooling capacity.

[0091] Please refer to Figure 1. The dehumidification and moisture carrying capacity of the closed-loop heat pump system 300 are as follows:

[0092] Dehumidification capacity C = Moisture content of air discharged from the drum G1 - Moisture content of air discharged from the evaporator G2;

[0093] Moisture content D = Moisture content of air discharged from the drum G1 - Moisture content of air entering the drum G3;

[0094] For the closed-loop heat pump system 300, the condenser 320 is a constant humidity heating process, that is, the moisture content G2 of the evaporator outlet air is equal to the moisture content G3 of the drum inlet air. In other words, during the drying process, the dehumidification capacity and moisture carrying capacity of the closed-loop heat pump system 300 are always in a dynamic equilibrium process.

[0095] As can be seen from the above relationship, reducing the moisture content G2 of the evaporator outlet air can increase the dehumidification and moisture carrying capacity of the evaporator 330, that is, improve the dehumidification and moisture carrying capacity of the evaporator 330. The moisture content G2 of the evaporator outlet air is directly proportional to the outlet air temperature of the evaporator 330.

[0096] Therefore, by limiting the ratio of the volume V1 of the condenser 320 to the volume V2 of the evaporator 330, this embodiment effectively limits the proportion of the volume V2 of the evaporator 330 in V3. In other words, while keeping the total volume of the sum of the volumes V1 and V2 of the condenser 320 and the evaporator 330 constant, this embodiment increases the volume of the evaporator 330 compared to conventional solutions by ensuring that the evaporator 330 has sufficient volume. This reduces the outlet air temperature of the evaporator 330, thereby reducing the moisture content of the outlet air and increasing the dehumidification capacity of the evaporator 330. This improves the dehumidification and moisture-carrying capacity of the heat pump system 300 and speeds up the drying time of clothes.

[0097] Please refer to Figures 5 and 6. In one embodiment, the width of the condenser 320 is W1 in the direction from the windward side to the leeward side; the width of the evaporator 330 is W2 in the direction from the windward side to the leeward side, and the ratio of W1 to W2 is not less than 0.8 and not greater than 1.0.

[0098] As shown in Figure 5, the direction from the windward side to the leeward side of the evaporator 330 is the first direction. That is to say, in the first direction, the specific value of the ratio of the width W1 of the condenser 320 to the width W2 of the evaporator 330 is not limited, for example but not limited to: 0.8, or 0.81, or 0.82, or 0.83, or 0.84, or 0.85, or 0.86, or 0.87, or 0.88, or 0.89, or 0.90, or 0.91, or 0.92, or 0.93, or 0.94, or 0.95, or 0.96, or 0.97, or 0.98, or 0.99, or 1.0, etc.

[0099] The area of ​​the windward side of the condenser 320 can be equal to the area of ​​the windward side of the evaporator 330. Of course, the area of ​​the windward side of the condenser 320 can also be different from the area of ​​the windward side of the evaporator 330; this is not limited here.

[0100] In this embodiment, the area of ​​the windward side of the condenser 320 is equal to the area of ​​the windward side of the evaporator 330, and the sum of the volumes V1 and V2 of the condenser 320 and the evaporator 330 is V3. By limiting the ratio of the width W1 of the condenser 320 to the width W2 of the evaporator 330, it is equivalent to limiting the ratio of the volume V1 of the condenser 320 to the volume V2 of the evaporator 330, and also equivalent to limiting the ratio of the volume V2 to V3 of the evaporator 330. That is, while the sum of the volumes V1 and V2 of the condenser 320 and the evaporator 330 remains unchanged, this embodiment ensures that the evaporator 330 has sufficient size by limiting the proportion of the volume V2 of the evaporator 330 in V3, thereby improving the dehumidification and cooling capacity of the evaporator 330.

[0101] The ratio of W1 to W2 is not less than 0.8 and not greater than 1.0, indicating that the width W1 of the condenser 320 is less than or equal to the width W2 of the evaporator 330. This makes the width W2 of the evaporator 330 sufficiently large relative to the width W1 of the condenser 320, that is, the volume V2 of the evaporator 330 is sufficiently large, so that the evaporator 330 has sufficient dehumidification and cooling capacity.

[0102] In one embodiment, the width W1 of the condenser 320 ranges from 30 mm to 60 mm; and / or, the width W2 of the evaporator 330 ranges from 40 mm to 60 mm. The value of W1 is not limited and can be 30 mm, 32 mm, 34 mm, 36 mm, 38 mm, 40 mm, 42 mm, 44 mm, 46 mm, 48 mm, 50 mm, 52 mm, 54 mm, 56 mm, 58 mm, or 60 mm, etc. The value of W2 is not limited and can be 40 mm, 42 mm, 44 mm, 46 mm, 48 mm, 50 mm, 52 mm, 54 mm, 56 mm, 58 mm, or 60 mm, etc.

[0103] Referring to Figure 4, in one embodiment, the evaporator 330 and the condenser 320 are arranged side by side in a first direction. Along the first direction, the width between the windward side of the evaporator 330 and the leeward side of the condenser 320 is W3. Along the second direction, the width of the casing 100 is W4. The first and second directions intersect. The ratio of W3 to W4 is not less than 0.1 and not greater than 0.25. This arrangement limits the ratio of the sum of the widths of the evaporator 330 and the condenser 320 to the width of the casing 100 to between 0.1 and 0.25. The specific value of the ratio of W3 to W4 is not limited, but can be, for example, but not limited to, 0.1, 0.15, 0.2, or 0.25, etc. Given the total width of the evaporator 330 and the condenser 320, the ratio of the width W1 of the condenser 320 to the width W2 of the evaporator 330 is limited to the range of the aforementioned embodiments to ensure that the width W2 of the evaporator 330 is large enough, thereby ensuring that the evaporator 330 has sufficient size and thus improving the dehumidification and cooling capacity of the evaporator 330.

[0104] Please refer to Figures 5 to 7. In one embodiment, the condenser heat exchanger tube 320a includes a plurality of condenser straight tubes 321 and a condenser bend 322 connecting two adjacent condenser straight tubes 321. The evaporator heat exchanger tube 330a includes a plurality of evaporator straight tubes 3371 and an evaporator bend 3372 connecting two adjacent evaporator straight tubes 3371. The plurality of condenser straight tubes 321 and the plurality of evaporator straight tubes 3371 are all arranged along a third direction. The plurality of condenser straight tubes 321 and the plurality of evaporator straight tubes 3371 are all arranged in multiple rows along a first direction, which is perpendicular to the third direction. The number of rows of condenser straight tubes 321 in the condenser 320 is less than or equal to the number of rows of evaporator straight tubes 3371 in the evaporator 330.

[0105] The evaporator 330 and condenser 320 may also include heat exchange fins. The number of rows of condenser straight tubes 321 in the condenser 320 can be 3, 4, 5, or other numbers. The number of rows of evaporator straight tubes 3371 in the evaporator 330 can be 4, 5, or other numbers. It is only necessary that the number of rows of condenser straight tubes 321 in the condenser 320 is not greater than the number of rows of evaporator straight tubes 3371 in the evaporator 330.

[0106] By limiting the number of rows of condenser straight tubes 321 in condenser 320 to be less than or equal to the number of rows of evaporator straight tubes 3371 in evaporator 330, it is equivalent to limiting the width of condenser 320 to be less than or equal to the width of evaporator 330. This makes the width of evaporator 330 sufficiently large relative to the width of condenser 320, meaning the volume of evaporator 330 is sufficiently large, thus giving evaporator 330 sufficient dehumidification and cooling capacity.

[0107] In one embodiment, along the first direction, the number of rows of condenser straight tubes 321 in the condenser 320 is the same as the number of rows of evaporator straight tubes 3371 in the evaporator 330; the multiple condenser straight tubes 321 and the multiple evaporator straight tubes 3371 are arranged in multiple columns along the vertical direction, and the number of condenser straight tubes 321 in each column is greater than the number of evaporator straight tubes 3371 in each column. As shown in Figures 5 and 6, the condenser 320 has 4 rows of condensing straight tubes 321, and the evaporator 330 has 4 rows of evaporating straight tubes 3371. In this configuration, the number of rows of condensing straight tubes 321 in the condenser 320 is equal to the number of rows of evaporating straight tubes 3371 in the evaporator 330. Each row contains 9 condensing straight tubes 321 and 6 evaporating straight tubes 3371, ensuring that the evaporator 330 has at least two independent evaporation flow paths 331. Furthermore, the volume V1 of the condenser 320 is less than or equal to the volume V2 of the evaporator 330. This configuration ensures that the total volume of the condenser 320 and the evaporator 330, within a certain range, guarantees sufficient volume for the evaporator 330, thus improving its dehumidification and cooling capacity.

[0108] In one embodiment, the width W1 of the condenser 320 is 40 mm, and the width W2 of the evaporator 330 is 48 mm. This arrangement, where the width W1 of the condenser 320 is smaller than the width W2 of the evaporator 330, ensures that the width of the evaporator 330 is sufficiently large relative to the width of the condenser 320, resulting in a sufficiently large volume and adequate dehumidification and cooling capacity.

[0109] In one embodiment, the condenser 320 has a width W1 of 40 mm, and the condenser 320 has four rows of condenser straight tubes 321, each row of which has a width of 10 mm. The evaporator 330 has a width W2 of 48 mm, and the evaporator 330 has four rows of evaporator straight tubes 3371, each row of which has a width of 12 mm. This arrangement ensures that the width of each row of evaporator straight tubes 3371 is greater than the width of each row of condenser straight tubes 321, and the width of the evaporator 330 is greater than the width of the condenser 320. This ensures that, under the same length and height conditions, the total volume of the condenser 320 and the evaporator 330 is within a certain range, guaranteeing that the evaporator 330 has sufficient volume and dimensions, thereby improving its dehumidification and cooling capacity.

[0110] In one embodiment, the condenser heat exchange tube 320a and the evaporator heat exchange tube 330a have the same wall thickness, and the outer diameter of the evaporator straight tube 3371 is larger than the outer diameter of the condenser straight tube 321. To ensure uniform heat exchange, the distance between two adjacent straight tubes in the condenser 320 and evaporator 330 is the same. This effectively limits the width of the condenser 320 to be smaller than the width of the evaporator 330. As mentioned above, this makes the width of the evaporator 330 sufficiently large, i.e., the volume of the evaporator 330 sufficiently large, giving the evaporator 330 sufficient dehumidification and cooling capacity.

[0111] In one embodiment, multiple condenser straight tubes 321 and multiple evaporator straight tubes 3371 are all arranged along a third direction, which is perpendicular to the first direction. This arrangement helps to improve the uniformity of heat exchange as air flows through the condenser 320 and evaporator 330.

[0112] In one embodiment, the operation phase of the clothes drying device 10 includes a heating phase and a temperature stabilization phase. The compressor 310 includes a variable frequency compressor 310. In the heating phase, the variable frequency compressor 310 first increases the frequency and then decreases the frequency to a preset high frequency to enter the temperature stabilization phase. In the temperature stabilization phase, the variable frequency compressor 310 operates at a preset high frequency, and the frequency of the preset high frequency is not less than 70 Hz.

[0113] The heat pump system 300 uses a variable frequency compressor 310, and the clothes drying device 10 is equipped with a fast drying mode and an energy-saving mode. In the energy-saving mode, the compressor 310 operates at a low frequency to reduce the energy consumption of the compressor 310.

[0114] In fast drying mode, compressor 310 needs to operate at a safe protection temperature (the intermediate cooling temperature T1 on condenser 320, and the discharge temperature T2 of compressor 310, described later). The drying stage of fast drying mode includes an initial heating stage and a later temperature stabilization stage. During the initial heating stage, compressor 310 operates at its highest operating frequency, which can be 100 Hz or other values. When the temperature sensor detects that the safe protection temperature has exceeded the limit, the controller of the clothes drying device 10 will control compressor 310 to reduce its operating frequency until the temperature is within the safe protection temperature. Then, compressor 310 enters the temperature stabilization stage at a preset high frequency, and the variable frequency compressor 310 operates stably at the preset high frequency during the temperature stabilization stage.

[0115] In this embodiment, during the temperature stabilization phase, the variable frequency compressor 310 operates at a preset high frequency, which is no less than 70 Hz. This setting increases the frequency of the compressor 310 during the temperature stabilization phase, thereby increasing the cooling and heating capacity of the compressor 310. This is beneficial for improving the drying efficiency of clothes, thus shortening the drying time. The preset high frequency can be 70 Hz, 72 Hz, 74 Hz, 76 Hz, 78 Hz, 80 Hz, 82 Hz, 84 Hz, 85 Hz, 86 Hz, 87 Hz, 88 Hz, 89 Hz, or 90 Hz, etc.

[0116] In one embodiment, the variable frequency compressor 310 has an exhaust port 311 connected to the refrigerant circulation loop 350. During the temperature stabilization phase, the temperature of the refrigerant discharged from the exhaust port 311 does not exceed 110 degrees Celsius. This configuration ensures that the exhaust temperature of the compressor 310 is limited to no more than 110 degrees Celsius during the temperature stabilization phase. This keeps the exhaust temperature of the compressor 310 below a safe protection temperature, allowing it to operate at high frequency for extended periods. This prevents the exhaust temperature from exceeding the acceptable range, thus avoiding the need for frequency reduction or shutdown, and consequently shortens the drying time for clothes.

[0117] In one embodiment, during the temperature stabilization phase, the temperature of the airflow blown out of the leeward side of the evaporator 330 in the circulating air path 120 does not exceed 20 degrees Celsius. This setting ensures that the moisture content G2 of the evaporator outlet air is relatively small. Since the dehumidification capacity C = moisture content G1 of the drum outlet air - moisture content G2 of the evaporator outlet air, the smaller G2 value results in a larger dehumidification capacity C. This ensures that the evaporator 330 has good dehumidification and moisture-carrying capacity, thus improving the dehumidification and moisture-carrying capabilities of the evaporator 330.

[0118] Please refer to Figures 6 to 8. In one embodiment,

[0119] The condensing heat exchanger tube 320a has a condensing flow path 323 (as shown in Figure 13). The number of evaporating flow paths 331 of the evaporating heat exchanger tube 330a is greater than the number of condensing flow paths 323 of the condensing heat exchanger tube 320a. The refrigerant discharged from the compressor 310 first flows through the condensing flow path 323, and then flows through at least two evaporating flow paths 331 to form a refrigerant circulation loop 350.

[0120] The evaporation flow path 331 can have two, three, or more paths, etc. The condenser 320 has a condensation flow path 323. The number of evaporation flow paths 331 in the evaporator 330 is greater than the number of condensation flow paths 323 in the condenser 320. For example, when the number of evaporation flow paths 331 in the evaporator 330 is two, the number of condensation flow paths 323 in the condenser 320 is one; for another example, when the number of evaporation flow paths 331 in the evaporator 330 is three, the number of condensation flow paths 323 in the condenser 320 is one or two; for yet another example, when the number of evaporation flow paths 331 in the evaporator 330 is four, the number of condensation flow paths 323 in the condenser 320 is one, two, or three. In other words, the number of evaporation flow paths 331 in the evaporator 330 only needs to be greater than the number of condensation flow paths 323 in the condenser 320. This is beneficial to enhance the dehumidification capacity of the clothes drying device while avoiding the situation where the compressor exhaust temperature is too high and exceeds the acceptable range, requiring frequency reduction or shutdown, thereby shortening the drying time of clothes.

[0121] The condensing flow path 323 is the path through which the refrigerant flows in the condenser 320. When the high-temperature and high-pressure refrigerant gas discharged from the compressor flows through the condensing flow path 323 of the condenser 320, it releases heat and condenses into a high-pressure liquid. During this process, the refrigerant releases heat into the surrounding environment.

[0122] In one embodiment, the condenser 320 has one condensing flow path 323, which has a refrigerant inlet for refrigerant inflow and a refrigerant outlet for refrigerant outflow. When the condenser has two condensing flow paths, it has two refrigerant inlets for refrigerant inflow and two refrigerant outlets for refrigerant outflow. The two condensing flow paths are independent of each other, and refrigerant in one condensing flow path cannot flow into the other condensing flow path. When the condenser has multiple condensing flow paths, it has multiple refrigerant inlets for refrigerant inflow and multiple refrigerant outlets for refrigerant outflow. The multiple condensing flow paths are independent of each other, and refrigerant in any one of the multiple condensing flow paths cannot flow into the other condensing flow path.

[0123] Similarly, evaporation path 331 is the path through which the refrigerant flows in evaporator 330. High-pressure liquid refrigerant enters the throttling device from the condenser, and after being depressurized, it flows into the evaporator. The evaporator is the part where the refrigerant absorbs heat. Low-pressure, low-temperature refrigerant comes out from the throttling device, enters the evaporator, and evaporates into low-pressure gas by absorbing heat, and then returns to the compressor.

[0124] The evaporator 330 has at least two independent evaporation flow paths 331, each of which can supply refrigerant. The arrangement of the at least two evaporation flow paths 331 is not limited. For example, two adjacent evaporation flow paths 331 are spaced apart in the vertical direction; or, two adjacent evaporation flow paths 331 are spaced apart in the direction from the windward side to the leeward side of the evaporator 330. The direction from the windward side to the leeward side of the evaporator 330 is the width direction of the evaporator 330.

[0125] When an evaporator has two evaporation paths, it has two refrigerant inlets for refrigerant to flow into and two refrigerant outlets for refrigerant to flow out. The two evaporation paths are independent of each other; refrigerant in one evaporation path cannot flow into the other. When an evaporator has multiple evaporation paths, it has multiple refrigerant inlets for refrigerant to flow into and multiple refrigerant outlets for refrigerant to flow out. The multiple evaporation paths are independent of each other; refrigerant in any one of the multiple evaporation paths cannot flow into the other.

[0126] As shown in Figure 13, the refrigerant flows in the condenser 320 in the direction indicated by the arrow. Figure 13 shows that the condenser 320 has a condensation flow path 323. The thick solid arrow indicates the flow direction of the refrigerant in the pipe located on the front side of the condenser 320, and the thick dashed arrow indicates the flow direction of the refrigerant in the pipe located on the rear side of the condenser 320.

[0127] As shown in Figures 7 to 12, the refrigerant flows in the evaporator 330 in the direction indicated by the arrow. Figures 7 to 12 show that the evaporator 330 has two independent evaporation flow paths 331. The thick solid arrow indicates the flow direction of the refrigerant in the pipe located on the front side of the evaporator 330, and the thick dashed arrow indicates the flow direction of the refrigerant in the pipe located on the rear side of the evaporator 330.

[0128] Compared to having only one evaporation flow path 331, the evaporator 330 in this application has at least two independent evaporation flow paths 331. The at least two independent evaporation flow paths 331 have a strong dehumidification and cooling capacity for hot and humid air, thereby increasing the dehumidification capacity of the evaporator 330 and thus shortening the drying time of clothes.

[0129] The heat pump system 300 includes a compressor 310, a condenser 320, and an evaporator 330. The compressor 310 can be a variable frequency compressor. To protect the safety of the heat pump system 300, it is usually necessary to monitor the temperature of its critical components. For example, a temperature sensor can be installed in the middle of the condenser 320's piping. When the temperature of the condenser 320 exceeds the upper limit temperature T1 (80 degrees Celsius) corresponding to the saturation condensation pressure of the compressor 310, the compressor 310 needs to reduce its frequency or shut down to protect itself and ensure its reliability. Similarly, a temperature sensor can be installed on the compressor 310's exhaust pipe. When the exhaust temperature of the compressor 310 exceeds the upper limit temperature T2 (110 degrees Celsius) of the compressor 310's safe operating temperature, the compressor 310 needs to reduce its frequency or shut down to protect itself and ensure its reliability. For example, when the heat pump system 300 operates under different ambient temperatures, the intermediate cooling temperature T1 on the condenser 320 (the intermediate cooling temperature represents the temperature of the condenser 320 at a preset position) and the discharge temperature T2 of the compressor 310 must always be lower than their corresponding protected safe temperatures. When the system detects that T1 or T2 is greater than or equal to its safe temperature, the compressor 310 needs to reduce its operating frequency or even shut down to ensure that the intermediate cooling temperature T1 on the condenser 320 and the discharge temperature T2 of the compressor 310 are always lower than the safe protection temperature, thereby ensuring the reliable operation of the heat pump system 300.

[0130] The technical solution of this application sets the evaporator 330 to have at least two independent evaporation flow paths 331, and the number of evaporation flow paths 331 of the evaporator 330 is greater than the number of condensation flow paths 323 of the condenser 320. This enhances the dehumidification capacity of the clothes drying device while preventing the exhaust temperature of the compressor 310 from being too high and exceeding the acceptable range, thus requiring frequency reduction or shutdown. This shortens the drying time of clothes.

[0131] Referring to Figure 8, in one embodiment, one end of the evaporation flow path 331 is a refrigerant inlet 332, and the other end of the evaporation flow path 331 is a refrigerant outlet 333. The refrigerant inlets 332 of at least two evaporation flow paths 331 are located on the same side of the evaporator 330 and are arranged adjacent to each other; and / or, the refrigerant outlets 333 of at least two evaporation flow paths 331 are located on the same side of the evaporator 330 and are arranged adjacent to each other.

[0132] The specific locations of the refrigerant inlets 332 of at least two evaporation flow paths 331 are not limited, nor are the specific locations of the refrigerant outlets 333 of at least two evaporation flow paths 331. By placing the two refrigerant inlets 332 on the same side and adjacent to each other, it is beneficial to shorten the length of the connecting pipes, facilitate pipe layout, make the evaporator 330 easier to manufacture and assemble, and reduce production costs. Similarly, by placing the two refrigerant outlets 333 on the same side and adjacent to each other, it is beneficial to shorten the length of the connecting pipes, facilitate pipe layout, make the evaporator 330 easier to manufacture and assemble, and reduce production costs.

[0133] Referring to Figures 5 to 7, in one embodiment, the evaporator 330 further includes a distribution connector 334 having at least three interconnected distribution channels; the refrigerant inlets 332 of at least two evaporation flow paths 331 are connected to the refrigerant circulation loop 350 through a distribution connector 334; and / or, the refrigerant outlets 333 of at least two evaporation flow paths 331 are connected to the refrigerant circulation loop 350 through a distribution connector 334.

[0134] For the refrigerant inlets 332 of the two evaporation flow paths 331, one branch channel of the distribution connector 334 is connected to the refrigerant circulation loop 350, and the other two branch channels of the distribution connector 334 are respectively connected to the two refrigerant inlets 332 of the two evaporation flow paths 331. For the refrigerant outlets 333 of the two evaporation flow paths 331, one branch channel of the distribution connector 334 is connected to the refrigerant circulation loop 350, and the other two branch channels of the distribution connector 334 are respectively connected to the two refrigerant outlets 333 of the two evaporation flow paths 331. Exemplarily, the distribution connector 334 is a multi-way pipe; in this solution, the distribution connector 334 is a tee pipe. By using the distribution connector 334 for connection, it is beneficial to reduce the number of pipes, simplify the piping layout of the evaporator 330, reduce production costs, and improve the efficiency of refrigerant flow through at least two evaporation flow paths 331. In addition, by installing a distribution connector 334 at the refrigerant inlet 332 position of the two evaporation flow paths 331, the original structure of the compressor refrigerant outlet pipeline can be maintained. That is, the refrigerant inlet 332 of the evaporator 330 can be directly connected to the original compressor refrigerant outlet pipeline through a distribution connector 334, making the assembly simpler.

[0135] Please refer to Figures 5 to 7. In one embodiment, the evaporator 330 and the condenser 320 are arranged sequentially along a first direction. The evaporation heat exchange tube 330a includes a first branch tube 335 and a second branch tube 336. The first branch tube 335 has a first branch channel, and the second branch tube 336 has a second branch channel. The first branch channel and the second branch channel are independent of each other and are respectively connected to an evaporation flow path 331. The first branch tube 335 and the second branch tube 336 are arranged crosswise on the same side of the evaporator 330.

[0136] As shown in Figure 7, the refrigerant flows in the evaporator 330 in the direction indicated by the arrow. Figure 7 illustrates that the evaporator 330 has two independent evaporation flow paths 331. The thick solid arrows indicate the flow direction of the refrigerant in the pipe located at the front of the evaporator 330, and the thick dashed arrows indicate the flow direction of the refrigerant in the pipe located at the rear of the evaporator 330. The refrigerant inlets 332 of the two evaporation flow paths 331 are connected by a distribution connector 334, and the refrigerant outlets 333 of the two evaporation flow paths 331 are connected by a distribution connector 334.

[0137] In Figure 7, the first branch pipe 335 and the second branch pipe 336 are arranged in a crisscross pattern on the same side of the evaporator 330, meaning that one of the first branch pipe 335 and the second branch pipe 336 is located in front of the other, and one of the first branch channel and the second branch channel is located in front of the other. Specifically, in this design, the first branch pipe 335 is located in front of the second branch pipe 336, which changes the flow direction and path of the refrigerant as it flows through the first branch channel and the second branch channel in the evaporator 330. This avoids the problem of excessively fast or slow local flow velocities, ensuring that the refrigerant can exchange heat evenly in the evaporator 330, thereby improving the effect of the temperature difference between the upper and lower parts of the two evaporation flow paths 331 in the evaporator 330 on the reversing performance.

[0138] In one embodiment, the evaporation heat exchange tube 330a further includes a plurality of evaporation pipes 337, which are arranged sequentially along the windward side to the leeward side of the evaporator 330. Each evaporation pipe 337 includes a plurality of evaporation straight pipes 3371 and an evaporation bend 3372 connecting two adjacent evaporation straight pipes 3371. The evaporation straight pipes 3371 extend in a third direction. A first branch pipe 335 connects two evaporation pipes 337 of one of the evaporation flow paths 331, and a second branch pipe 336 connects two evaporation pipes 337 of the other evaporation flow path 331.

[0139] As shown in Figures 7 and 8, the evaporator 330 has two independent evaporation flow paths 331. The first branch pipe 335 connects the two evaporation pipes 337 of one of the evaporation flow paths 331 to form a connecting flow channel; the second branch pipe 336 connects the two evaporation pipes 337 of the other evaporation flow path 331 to form a connecting flow channel.

[0140] In one embodiment, the intersection of the first branch pipe 335 and the second branch pipe 336 is arranged in a cross configuration, and the projection of this intersection along a third direction falls on the center of one side of the evaporator. This arrangement makes the overall structure of the evaporator 330 regular, which helps to ensure that the refrigerant can exchange heat evenly in the evaporator 330, thereby improving the effect of the temperature difference between the upper and lower parts of the two evaporation flow paths 331 in the evaporator 330 on the reversing performance.

[0141] Referring to Figures 5 and 6, in one embodiment, multiple straight evaporator tubes 3371 are arranged in multiple rows along the vertical direction, with two straight evaporator tubes 3371 in adjacent rows staggered in both the vertical and horizontal directions. In Figures 5 and 6, one evaporator pipe 337 includes three straight evaporator tubes 3371 and two evaporator bends 3372. The three straight evaporator tubes 3371 are connected by the two bends to form a continuous flow channel, thus ensuring the continuity of refrigerant flow. Furthermore, the staggered arrangement of two straight evaporator tubes 3371 in adjacent rows, meaning that adjacent straight evaporator tubes 3371 have a height difference in both the vertical and horizontal directions, saves installation space and achieves high space utilization of the evaporator 330.

[0142] In one embodiment, the evaporation flow path 331 is repeatedly zigzagged in both the vertical and horizontal directions. This arrangement not only increases the length of the evaporation flow path 331 but also effectively reduces the space it occupies and increases the contact area with air, thereby improving heat exchange efficiency. Furthermore, the repeated zigzagged arrangement helps reduce vibration and noise generated by the refrigerant flow in the evaporation flow path 331.

[0143] In one embodiment, the refrigerant inlet 332 of each evaporation flow path 331 is located close to the first side, and the refrigerant outlet 333 of each evaporation flow path 331 is located close to the second side, with the first side and the second side being opposite to each other; the two evaporation flow paths 331 are spaced apart in the vertical direction; and / or, the two evaporation flow paths 331 are spaced apart in the direction from the windward side to the leeward side of the evaporator 330.

[0144] As shown in Figures 9, 10 and 11, the two evaporation flow paths 331 are arranged at intervals along the vertical direction; as shown in Figure 12, the two evaporation flow paths 331 are arranged at intervals along the direction from the windward side to the leeward side of the evaporator 330.

[0145] In Figures 8 to 10, the refrigerant inlets 332 of both evaporation flow paths 331 are located close to the first side, and the refrigerant outlets 333 of both evaporation flow paths 331 are located close to the second side. The refrigerant flowing into the evaporator 330 is diverted through the two evaporation flow paths 331, which increases the heat exchange with the humid air and improves the dehumidification and cooling capacity of the humid air, thereby increasing the dehumidification capacity of the evaporator 330.

[0146] Furthermore, the two independent evaporation flow paths 331 can reduce the resistance caused by the excessive length of the evaporation flow path 331, reduce the flow resistance of the refrigerant flowing through the evaporator 330, thereby reducing the pressure loss of the refrigerant flowing through the evaporator 330, thereby increasing the suction pressure of the compressor 310's suction port and reducing the discharge temperature of the compressor 310's discharge port 311. This allows the compressor 310 to operate at a high frequency for a long time, avoiding the situation where the discharge temperature of the compressor 310 exceeds the acceptable range and needs to be reduced in frequency or shut down. This can shorten the drying time of clothes.

[0147] In one embodiment, the evaporator 330 includes a plurality of straight evaporation tubes 3371 and an evaporation bend 3372 connecting two adjacent straight evaporation tubes 3371. The straight evaporation tubes 3371 extend along a third direction, and the plurality of straight evaporation tubes 3371 are arranged in multiple columns along the vertical direction. The number of straight evaporation tubes 3371 in each column is even, so that the two evaporation flow paths 331 are evenly distributed. And / or, the multiple columns of straight evaporation tubes 3371 are arranged in an even number of rows along a first direction, so that the two evaporation flow paths 331 are evenly distributed.

[0148] As shown in Figures 8 to 10, multiple straight evaporator tubes 3371 are arranged in multiple rows along the vertical direction, with an even number of straight evaporator tubes 3371 in each row to ensure even distribution between the two evaporation flow paths 331. This arrangement means the evaporator 330 uses a horizontal tube arrangement. Each row in the figures has 6 straight evaporator tubes 3371, for a total of 4 rows. Each of the two evaporation flow paths 331 includes 12 straight evaporator tubes 3371. This ensures a regular tube arrangement in the evaporator 330, allowing for uniform distribution of the refrigerant within the evaporator 330. This helps ensure sufficient contact between air and all heat exchange surfaces, thereby improving heat exchange efficiency.

[0149] As shown in Figures 11 and 12, multiple rows of straight evaporator tubes 3371 are arranged in even-numbered rows along the first direction to evenly distribute the refrigerant among the two evaporation flow paths 331. This arrangement means the evaporator 330 uses a longitudinal tube arrangement, with a total of four rows shown in the figures. Each of the two evaporation flow paths 331 includes 12 straight evaporator tubes 3371. One evaporation flow path 331 utilizes the first and third rows of straight evaporator tubes 3371 to form its flow path, while the other evaporation flow path 331 utilizes the second and fourth rows of straight evaporator tubes 3371. This ensures a regular tube arrangement in the evaporator 330, allowing for uniform distribution of the refrigerant and helping to ensure sufficient contact between air and all heat exchange surfaces, thereby improving heat exchange efficiency.

[0150] This application also proposes a washer-dryer combo, which includes the clothes drying device 10 as described above. The specific structure of the clothes drying device 10 is as described in the above embodiments. Since this washer-dryer combo adopts all the technical solutions of all the above embodiments, it has at least all the beneficial effects brought about by the technical solutions of the above embodiments, which will not be described in detail here.

[0151] In one embodiment, the washer-dryer combo includes a drying component and a washing component. The washer-dryer combo integrates the washing and drying processes into a single device, allowing clothes to be dried directly after washing without needing to transfer wet clothes to another dryer or air dry them. The washing component's primary function is to clean the clothes, including but not limited to cleaning, stain removal, and rinsing steps. The washing component includes a drum for agitating the clothes, thereby improving the washing effect. The washing component may also include a motor and drive system for driving the drum's rotation. The washing component may also include a water pump and water pipe system for water injection and drainage, ensuring water level control, wastewater discharge, and rinsing during the washing process. The washing component may also include a detergent dispenser or dispensing system for adding laundry detergent, washing powder, fabric softener, and other washing and care products. The drying component may include the aforementioned housing 100, drum 200, and heat pump system 300. The drying component is used to dry the washed clothes, removing any dampness.

[0152] A washer-dryer combo includes a washing unit and a drying unit. The washing unit includes a water inlet system, a drainage system, a liquid inlet system, and a shock absorption system, while the drying unit includes a heat pump system and a drying tunnel assembly. Washer-dryer combos require a limited space to house both the washing and drying units, severely restricting the installation space for the heat pump system. Furthermore, the limited space also results in a smaller airflow rate and air volume within the duct. In other words, the overall performance of the heat pump in a washer-dryer combo is limited by the installation space and airflow rate, leading to lower overall performance. Therefore, it is necessary to further improve drying performance within the constraints of limited space and airflow. Traditionally, evaporators and condensers consist of a single refrigerant pipe that is bent multiple times. This is typically achieved by increasing the number of refrigerant pipes in the thickness or height direction of the evaporator or condenser. This method inevitably increases the dimensions of the evaporator or condenser in these directions, thus increasing their volume. However, this method is not feasible in washer-dryer combos due to space constraints. Additionally, significantly increasing the condenser efficiency would cause excessively high temperatures near the compressor, affecting its operation.

[0153] In the embodiment of the above-mentioned clothes drying equipment used in the washer-dryer combo, the dehumidification efficiency can be improved in a limited space, thereby further improving the drying performance. Moreover, with the use of a variable frequency compressor, the safe temperature of the compressor is guaranteed, so that the compressor will not enter the stage where it cannot operate at high frequency.

[0154] The above description is merely an exemplary embodiment of this application and does not limit the patent scope of this application. Any equivalent structural transformations made based on the technical concept of this application and the contents of the specification and drawings of this application, or direct / indirect applications in other related technical fields, are included within the patent protection scope of this application.

Claims

1. A clothes drying device, wherein, The clothes drying device includes: The casing has air ducts; The drum has a drying chamber, which is connected to the air duct to form a circulating air path; A heat pump system includes a compressor and a condenser, an evaporator and an airflow drive unit disposed in the air duct, the airflow drive unit being used to drive airflow to circulate within the circulating air duct; The condenser includes a condensing heat exchange tube, and the evaporator includes an evaporating heat exchange tube. The inner diameter of the evaporating heat exchange tube is larger than the inner diameter of the condensing heat exchange tube. The evaporating heat exchange tube has at least two independent evaporating flow paths, and at least two of the evaporating flow paths are connected to the condensing heat exchange tube. The refrigerant discharged from the compressor first flows through the condensing heat exchange tube, and then flows through the at least two evaporating flow paths to form a refrigerant circulation loop.

2. The clothes drying apparatus as described in claim 1, wherein, The evaporation heat exchange tube includes multiple straight evaporation tubes and an evaporation bend connecting two adjacent straight evaporation tubes. The multiple straight evaporation tubes are arranged in N rows along a first direction, and N is not less than 4. And / or, the evaporator further includes a plurality of fins disposed on the evaporation heat exchange tube, the total length of the evaporation heat exchange tube being greater than 4 meters.

3. The clothes drying apparatus as described in claim 2, wherein, The inner diameter of the evaporative heat exchange tube is not less than 7 mm and not more than 12 mm; And / or, the inner diameter of the condenser heat exchange tube is not less than 5 mm and not more than 10 mm.

4. The clothes drying apparatus as described in claim 1, wherein, The condensing heat exchange tube includes multiple condensing straight tubes and a condensing bend connecting two adjacent condensing straight tubes; the evaporating heat exchange tube includes multiple evaporating straight tubes and an evaporating bend connecting two adjacent evaporating straight tubes; the inner diameter of the evaporating straight tube is larger than the inner diameter of the condensing straight tube. And / or, the inner diameter of the evaporation bend is larger than the inner diameter of the condensation bend; And / or, the plurality of condenser straight tubes and the plurality of evaporator straight tubes are all arranged to extend along a third direction, and the plurality of condenser straight tubes and the plurality of evaporator straight tubes are arranged in multiple rows along a first direction, the first direction being perpendicular to the third direction; the number of rows of condenser straight tubes in the condenser is less than or equal to the number of rows of evaporator straight tubes in the evaporator.

5. The clothes drying apparatus as described in claim 4, wherein, Along the first direction, the number of rows of condenser straight tubes in the condenser is the same as the number of rows of evaporator straight tubes in the evaporator; the multiple condenser straight tubes and the multiple evaporator straight tubes are arranged in multiple columns along the vertical direction, and the number of condenser straight tubes in each column is greater than the number of evaporator straight tubes in each column.

6. The clothes drying apparatus as described in claim 1, wherein, The volume of the condenser is V1, the volume of the evaporator is V2, and the ratio of V1 to V2 is not less than 0.8 and not greater than 1.

0. And / or, in the direction from the windward side to the leeward side of the condenser, the width of the condenser is W1; The width of the evaporator is W2 in the direction from the windward side to the leeward side; the ratio of W1 to W2 is not less than 0.8 and not greater than 1.

0.

7. The clothes drying apparatus as described in claim 1, wherein, The operation of the clothes drying device includes a heating stage and a temperature stabilization stage, and the compressor includes a variable frequency compressor. During the heating phase, the variable frequency compressor first increases the frequency and then decreases the frequency to a preset high frequency in order to enter the temperature stabilization phase. During the temperature stabilization phase, the variable frequency compressor operates at the preset high frequency, which is not less than 70 Hz.

8. The clothes drying apparatus as described in claim 7, wherein, The variable frequency compressor has an exhaust port connected to the refrigerant circulation loop. During the temperature stabilization phase, the temperature of the refrigerant discharged from the exhaust port does not exceed 110 degrees Celsius.

9. The clothes drying apparatus according to any one of claims 1 to 8, wherein, The condensing heat exchange tube has a condensing flow path, and the number of evaporating flow paths of the evaporating heat exchange tube is greater than the number of condensing flow paths of the condensing heat exchange tube. The refrigerant discharged from the compressor first flows through the condensing flow path, and then flows through at least two of the evaporating flow paths to form the refrigerant circulation loop.

10. The clothes drying apparatus as described in claim 9, wherein, One end of the evaporation flow path is a refrigerant inlet, and the other end of the evaporation flow path is a refrigerant outlet. At least two refrigerant inlets of the evaporation flow paths are located on the same side of the evaporator and are arranged adjacent to each other. And / or, the refrigerant outlets of at least two of the evaporation flow paths are located on the same side of the evaporator and are arranged adjacent to each other.

11. The clothes drying apparatus as claimed in claim 10, wherein, The evaporator further includes a distribution connector having at least three interconnected distribution channels; at least two of the refrigerant inlets of the evaporation flow paths are connected to the refrigerant circulation loop through one of the distribution connectors. And / or, at least two of the refrigerant outlets of the evaporation flow paths are connected to the refrigerant circulation loop via one of the distribution connectors.

12. The clothes drying apparatus as described in claim 9, wherein, The evaporator and the condenser are arranged sequentially along a first direction. The evaporation heat exchange tube includes a first branch tube and a second branch tube. The first branch tube has a first branch channel, and the second branch tube has a second branch channel. The first branch channel and the second branch channel are independent of each other and are respectively connected to one of the evaporation flow paths. The first branch tube and the second branch tube are arranged crosswise on the same side of the evaporator.

13. The clothes drying apparatus as described in claim 12, wherein, The evaporation heat exchange tube also includes multiple evaporation pipes, which are arranged sequentially along the windward side to the leeward side of the evaporator. Each evaporation pipe includes multiple straight evaporation pipes and an evaporation bend connecting two adjacent straight evaporation pipes. The straight evaporation pipes extend in a third direction. The first branch pipe connects two evaporation pipes in one of the evaporation flow paths, and the second branch pipe connects two evaporation pipes in the other evaporation flow path. And / or, the projection of the intersection point of the first and second branch pipes, which are arranged in a cross configuration, along the third direction falls on the center position of one side of the evaporator; And / or, multiple evaporation straight tubes are arranged in multiple columns along the vertical direction, and two evaporation straight tubes in two adjacent columns are staggered in the vertical and horizontal directions.

14. The clothes drying apparatus as described in claim 13, wherein, Multiple evaporation straight tubes are arranged in multiple columns along the vertical direction, and the number of evaporation straight tubes in each column is even, so that the two evaporation flow paths can be evenly distributed. And / or, multiple rows of the evaporation straight tubes are arranged in an even number of rows along a first direction to allow the two evaporation flow paths to be evenly divided, wherein the first direction is perpendicular to the third direction.

15. The clothes drying apparatus as described in claim 9, wherein, The refrigerant inlet of each evaporation flow path is located close to the first side, and the refrigerant outlet of each evaporation flow path is located close to the second side. The first side and the second side are arranged opposite to each other. The two evaporation flow paths are spaced apart in the vertical direction. And / or, the two evaporation flow paths are spaced apart along the direction from the windward side to the leeward side of the evaporator.

16. A washer-dryer combo, wherein, The washer-dryer combo includes a clothing drying device as described in any one of claims 1 to 15.

17. The washer-dryer combo as described in claim 16, wherein, The washer-dryer combo includes a drying component and a washing component.

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