Clothes drying device and washing and drying all-in-one machine

Abstract

The utility model discloses a clothes drying device and a washing and drying all-in-one machine. The clothes drying device comprises a shell, a roller and a heat pump system, the shell is provided with an air duct, the roller is provided with a drying cavity, and the drying cavity communicates with the air duct to form a circulating air path; the heat pump system comprises a compressor, a condenser, an evaporator and an airflow driving part, wherein the condenser, the evaporator and the airflow driving part are arranged in the air duct. The airflow driving part is used for driving airflow to circularly flow in the circulating air path. The condenser comprises a condensation heat exchange tube, the evaporator comprises an evaporation heat exchange tube, and the inner diameter of the evaporation heat exchange tube is larger than that of the condensation heat exchange tube; the evaporation heat exchange pipe is provided with at least two independent evaporation flow paths, the at least two evaporation flow paths are communicated with the condensation heat exchange pipe, and a refrigerant discharged by the compressor firstly flows through the condensation heat exchange pipe and then flows through the at least two evaporation flow paths to form a refrigerant circulation loop.

Description

TECHNICAL FIELD

[0001] The utility model relates to clothes drying technical field, especially a clothes drying device and washing and drying integrated machine. BACKGROUND

[0002] In the related art, the clothes drying device is used for drying clothes, bed sheets, curtains and other objects. The existing clothes drying device has a long drying time, which affects user experience. In the traditional scheme, the drying efficiency is improved by increasing the pipeline of the evaporator or the condenser, but this increases the size of the heat pump and further increases the flow resistance. In the washing and drying integrated device, there are both washing structures and drying structures, and the space is limited. The heat pump system needs to improve the drying efficiency in the limited space. SUMMARY

[0003] The main purpose of the utility model is to provide a clothes drying device and washing and drying integrated machine, which aims to shorten the drying time of the existing clothes drying device.

[0004] To achieve the above-mentioned purpose, the clothes drying device provided by the utility model comprises:

[0005] A shell has an air duct.

[0006] A drum has a drying cavity, and the drying cavity is in communication with the air duct to form a circulating air path.

[0007] A heat pump system comprises a compressor, a condenser, an evaporator and an airflow driving member arranged in the air duct. The airflow driving member is used to drive the airflow to circulate in the circulating air path.

[0008] The condenser comprises a condensation heat exchange pipe, the evaporator comprises an evaporation heat exchange pipe, the inner diameter of the evaporation heat exchange pipe is greater than that of the condensation heat exchange pipe, the evaporation heat exchange pipe has at least two independent evaporation flow paths, the at least two evaporation flow paths are in communication with the condensation heat exchange pipe, and the refrigerant discharged by the compressor first flows through the condensation heat exchange pipe and then flows through the at least two evaporation flow paths to form a refrigerant circulation loop.

[0009] In an embodiment, the evaporation heat exchange pipe comprises a plurality of evaporation straight pipes and an evaporation elbow pipe connecting adjacent two evaporation straight pipes, the plurality of evaporation straight pipes are arranged in N rows along a first direction, and N is not less than 4.

[0010] And / or, the evaporator further comprises a plurality of fins arranged on the evaporation heat exchange pipe, and the total length of the evaporation heat exchange pipe is greater than 4 meters.

[0011] In an embodiment, the inner diameter of the evaporation heat exchange pipe is not less than 7 mm and not greater than 12 mm.

[0012] And / or, the inner diameter of the condensing heat exchange pipe is not less than 5mm and not more than 10mm.

[0013] In an embodiment, the condensing heat exchange pipe comprises a plurality of condensing straight pipes and a plurality of condensing elbow pipes connecting adjacent two of the condensing straight pipes, and the evaporating heat exchange pipe comprises a plurality of evaporating straight pipes and a plurality of evaporating elbow pipes connecting adjacent two of the evaporating straight pipes; the inner diameter of the evaporating straight pipe is greater than the inner diameter of the condensing straight pipe.

[0014] And / or, the inner diameter of the evaporating elbow pipe is greater than the inner diameter of the condensing elbow pipe.

[0015] And / or, the plurality of condensing straight pipes and the plurality of evaporating straight pipes are arranged along a third direction, and the plurality of condensing straight pipes and the plurality of evaporating straight pipes are arranged in multiple rows along a first direction, the first direction being perpendicular to the third direction; the number of rows of the condensing straight pipes in the condenser is less than or equal to the number of rows of the evaporating straight pipes in the evaporator.

[0016] In an embodiment, along the first direction, the number of rows of the condensing straight pipes in the condenser is the same as the number of rows of the evaporating straight pipes in the evaporator; the plurality of condensing straight pipes and the plurality of evaporating straight pipes are arranged in multiple columns along an up-down direction, and the number of the condensing straight pipes in each column is greater than the number of the evaporating straight pipes in each column.

[0017] In an embodiment, the volume of the condenser is V1, and the volume of the evaporator is V2, and the ratio of the V1 to the V2 is not less than 0.8 and not more than 1.0.

[0018] And / or, in the direction from the windward surface to the leeward surface of the condenser, the width of the condenser is W1; in the direction from the windward surface to the leeward surface of the evaporator, the width of the evaporator is W2; the ratio of the W1 to the W2 is not less than 0.8 and not more than 1.0.

[0019] In an embodiment, the operation stage of the clothes drying device comprises a temperature rising stage and a temperature maintaining stage, and the compressor comprises a variable frequency compressor.

[0020] In the temperature rising stage, the variable frequency compressor first increases the frequency and then decreases the frequency to a preset high frequency to enter the temperature maintaining stage.

[0021] In the temperature maintaining stage, the variable frequency compressor operates at the preset high frequency, and the frequency of the preset high frequency is not less than 70Hz.

[0022] In an embodiment, the variable frequency compressor has an exhaust port, the exhaust port being communicated with the refrigerant circulation loop, and in the temperature maintaining stage, the temperature of the refrigerant discharged from the exhaust port is not higher than 110℃.

[0023] In an embodiment, the condensing heat exchange pipe has condensing flow paths, the number of the evaporation flow paths of the evaporation heat exchange pipe is greater than the number of the condensing flow paths of the condensing heat exchange pipe, and the refrigerant discharged by the compressor first flows through the condensing flow paths and then flows through at least two of the evaporation flow paths to form the refrigerant circulation loop.

[0024] In an embodiment, one end of the evaporation flow path is a refrigerant inlet, the other end of the evaporation flow path is a refrigerant outlet, and the refrigerant inlets of the at least two evaporation flow paths are arranged on the same side of the evaporator and are adjacent to each other.

[0025] In an embodiment, the refrigerant outlets of the at least two evaporation flow paths are arranged on the same side of the evaporator and are adjacent to each other.

[0026] In an embodiment, the evaporator further comprises a distribution joint having at least three distribution flow channels that are in communication with each other, the refrigerant inlets of the at least two evaporation flow paths are connected to the refrigerant circulation loop through one of the distribution joints.

[0027] In an embodiment, the refrigerant outlets of the at least two evaporation flow paths are connected to the refrigerant circulation loop through one of the distribution joints.

[0028] In an embodiment, the evaporator and the condenser are arranged in sequence along a first direction, the evaporation heat exchange pipe comprises a first shunt pipe and a second shunt pipe, the first shunt pipe has a first shunt passage, the second shunt pipe has a second shunt passage, the first shunt passage and the second shunt passage are independent of each other and are connected to one of the evaporation flow paths respectively, and the first shunt pipe and the second shunt pipe are arranged in a cross manner on the same side of the evaporator.

[0029] In an embodiment, the evaporation heat exchange pipe further comprises a plurality of evaporation pipe paths, the plurality of evaporation pipe paths are arranged in sequence along a direction from a windward side to a leeward side of the evaporator, each of the evaporation pipe paths comprises a plurality of evaporation straight pipes and evaporation elbow pipes connecting adjacent two of the evaporation straight pipes, and the evaporation straight pipes are arranged in extension along a third direction; the first shunt pipe is connected to two of the evaporation pipe paths of one of the evaporation flow paths, and the second shunt pipe is connected to two of the evaporation pipe paths of another of the evaporation flow paths.

[0030] In an embodiment, a projection of a cross point at which the first shunt pipe and the second shunt pipe are arranged in a cross manner along the third direction falls on a central position on one side of the evaporator.

[0031] In an embodiment, the plurality of evaporation straight pipes are arranged in multiple columns along an up-down direction, and two of the evaporation straight pipes in adjacent two columns are arranged in a staggered manner along the up-down direction and a left-right direction.

[0032] In an embodiment, the plurality of evaporation straight pipes are arranged in multiple columns along the up-down direction, and the number of the evaporation straight pipes in each column is even, so as to divide the two evaporation flow paths evenly.

[0033] And / or, the multiple columns of evaporation straight pipes are arranged in an even number of rows along a first direction, so as to divide the two evaporation flow paths evenly, and the first direction is perpendicular to the third direction.

[0034] In an embodiment, the refrigerant inlet of each evaporation flow path is arranged close to a first side, the refrigerant outlet of each evaporation flow path is arranged close to a second side, the first side is arranged opposite to the second side, and the two evaporation flow paths are arranged in the up-down direction.

[0035] And / or, the two evaporation flow paths are arranged in the direction from the windward side to the leeward side of the evaporator.

[0036] The utility model also proposes a washing and drying integrated machine, and the washing and drying integrated machine comprises the clothes drying device.

[0037] In an embodiment, the washing and drying integrated machine comprises a drying assembly and a washing assembly.

[0038] The clothes drying device comprises a shell, a roller and a heat pump system, the shell is provided with an air duct, the roller is provided with a drying cavity, the drying cavity and the air duct are communicated to form a circulating air path, the heat pump system comprises a compressor and a condenser, an evaporator and an airflow driving element arranged in the air duct, under the action of the airflow driving element, the air in the air duct is heated by the condenser and then sent into the drying cavity to dry the clothes, the wet and hot air discharged from the drying cavity flows through the evaporator, the evaporator absorbs heat to change the wet and hot air into dry and low-temperature air, and the water vapor in the wet and hot air is condensed into condensed water and discharged, and the dry and low-temperature air flows through the condenser again to realize the function of drying clothes. BRIEF DESCRIPTION OF DRAWINGS

[0039] In order to more clearly illustrate the technical solutions of the embodiments of the present application or the prior art, the following will briefly introduce the drawings needed to be used in the embodiments or the prior art description. Obviously, the drawings in the following description are only some embodiments of the present application, and for those skilled in the art, other drawings can also be obtained according to the structures shown in these drawings without creative labor.

[0040] Figure 1 The principle schematic diagram of the clothes drying device provided by the present application is shown in the figure.

[0041] Figure 2 The partial structure schematic diagram of the clothes drying device provided by the present application is shown in the figure.

[0042] Figure 3 The partial structure schematic diagram of the clothes drying device provided by the present application is shown in the figure. Figure 2

[0043] ​Figure 4 is a sectional view of the structure in Figure 3

[0044] Figure 5 is a schematic view of a partial structure in Figure 3

[0045] Figure 6 is a schematic view of another perspective of the structure in Figure 5

[0046] Figure 7 is a schematic view of another perspective of the evaporator in Figure 5

[0047] Figure 8 is a schematic view of a first embodiment of the evaporator provided in the present application;

[0048] Figure 9 is a schematic view of a second embodiment of the evaporator provided in the present application;

[0049] Figure 10 is a schematic view of a third embodiment of the evaporator provided in the present application;

[0050] Figure 11 is a schematic view of a fourth embodiment of the evaporator provided in the present application;

[0051] Figure 12 is a schematic view of a fifth embodiment of the evaporator provided in the present application;

[0052] Figure 13 is a schematic view of another perspective of the condenser in Figure 5

[0053] BRIEF DESCRIPTION OF THE DRAWINGS

[0054] 10, laundry drying apparatus;

[0055] 100, housing; 110, air duct; 120, circulating air path;

[0056] 200, drum; 210, drying cavity; 220, air inlet portion; 230, air outlet portion;

[0057] 300, heat pump system; 310, compressor; 311, exhaust port; 320, condenser; 320a, condensing heat exchange pipe; 321, condensing straight pipe; 322, condensing elbow pipe; 323, condensing flow path; 330, evaporator; 330a, evaporating heat exchange pipe; 331, evaporating flow path; 332, refrigerant inlet; 333, refrigerant outlet; 334, distribution joint; 335, first shunt pipe; 336, second shunt pipe; 337, evaporating pipe path; 3371, evaporating straight pipe; 3372, evaporating elbow pipe; 340, airflow driving member; 350, refrigerant circulation loop;​​​​​

[0058] 400, drainage assembly;

[0059] 500, filter.

[0060] The implementation, functional features and advantages of the utility model will be further described with reference to the drawings in combination with embodiments. DETAILED DESCRIPTION

[0061] The technical solutions in the embodiments of the utility model will be clearly and completely described below in combination with the drawings in the embodiments of the utility model. Obviously, the described embodiments are only part of the embodiments of the utility model, rather than all the embodiments. Based on the embodiments in the utility model, all other embodiments obtained by those skilled in the art without creative labor belong to the protection scope of the utility model.

[0062] It should be noted that if the embodiments of the utility model involve directional indications (such as up, down, left, right, front, back, etc.), the directional indications are only used to explain the relative position relationship, movement condition, etc. between components in a certain posture, and if the certain posture changes, the directional indications also change accordingly.

[0063] In addition, if the embodiments of the utility model involve descriptions such as "first", "second", etc., the descriptions of "first", "second", etc. are only for description purposes, and cannot be understood as indicating or implying the relative importance or implicitly indicating the number of indicated technical features. Therefore, the features limited by "first" and "second" can explicitly or implicitly include at least one feature. In addition, "and / or" or "and / or" appearing throughout the text means that the three parallel schemes are included, for example, "A and / or B" includes A scheme, or B scheme, or A and B simultaneously satisfy the scheme. In addition, the technical solutions of each embodiment can be combined with each other, but it must be based on the realization of ordinary skilled in the art, when the combination of technical solutions appears contradictory or unachievable, it should be considered that the combination of technical solutions does not exist, and is not within the protection scope required by the utility model.

[0064] In the related art, the clothes drying device is used for drying clothes, bed sheets, curtains and other objects. The existing clothes drying device has a long drying time, which affects user use. In the traditional scheme, the pipe of the evaporator or the condenser is increased to improve the drying efficiency, but the size of the heat pump is increased, and the increase of the pipe will further increase the flow resistance. In the washing and drying integrated device, there are washing structure and drying structure, and the space is limited, and the heat pump system needs to improve the drying efficiency in the limited space.

[0065] Based on this, the application provides a clothes drying device and a washing and drying integrated machine, which can shorten the drying time of clothes. The clothes drying device is used for drying clothes, bed sheets, curtains and the like. The washing and drying integrated machine can not only complete the function of washing clothes, but also directly performs drying after washing, so that the user does not need to move the clothes from the washing machine to the drying machine, that is, the washing and drying integrated machine has the functions of washing and drying.

[0066] Please refer to Figures 1 to 6 In an embodiment of the application, the clothes drying device 10 comprises a shell 100, a drum 200 and a heat pump system 300, the shell 100 has an air duct 110; the drum 200 has a drying cavity 210, the drying cavity 210 is communicated with the air duct 110 to form a circulating air path 120; the heat pump system 300 comprises a compressor 310, a condenser 320, an evaporator 330 and an airflow driving member 340 arranged in the air duct 110, the airflow driving member 340 is used for driving the airflow to circulate in the circulating air path 120; the condenser 320 comprises a condensing heat exchange pipe 320a, the evaporator 330 comprises an evaporating heat exchange pipe 330a, the inner diameter of the evaporating heat exchange pipe 330a is greater than the inner diameter of the condensing heat exchange pipe 320a; the evaporating heat exchange pipe 330a has at least two independent evaporating flow paths 331, the at least two evaporating flow paths 331 are communicated with the condensing heat exchange pipe 320a, the refrigerant discharged by the compressor 310 first flows through the condensing heat exchange pipe 320a, and then flows through the at least two evaporating flow paths 331 to form a refrigerant circulation loop 350.

[0067] Figure 1 The clothes drying device 10 is a schematic diagram of the principle, combined with 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, and then absorbs heat through the evaporator 330 to return to the compressor 310. The airflow driving member 340 sends the air heated by the condenser 320 into the drum 200 to dry the clothes, the wet and hot air flowing out of the drum 200 flows through the evaporator 330, the evaporator 330 changes the wet and hot air flowing out of the drum 200 into dry and low-temperature air, and the water vapor in the wet and hot air is condensed into condensed water and discharged, and the dry and low-temperature air is heated again through the condenser 320, so as to complete one cycle. The clothes drying device 10 continuously removes moisture through this cycle and discharges it in the form of condensed water, thereby realizing the function of drying clothes.

[0068] The drum 200 is rotatably arranged in the shell 100. The heat pump system 300 is arranged in the shell 100, the condenser 320 and the evaporator 330 are arranged below the drum 200 and are spaced apart from the drum 200, so as to avoid the drum 200 from colliding with the heat pump system 300 during the dehydration stage of washing clothes. The heat pump system 300 can also be arranged to be separable from the shell 100, so as to facilitate disassembly and maintenance and replacement in the later period.

[0069] In an embodiment, the drum 200 has a drying cavity 210, and an air inlet portion 220 and an air outlet portion 230 in communication with the drying cavity 210, one end of the air duct 110 is in communication with the air inlet portion 220, and the other end of the air duct 110 is in communication with the air outlet portion 230. The airflow driving member 340 is used to drive the airflow to flow through the condenser 320, the air inlet portion 220, the drying cavity 210, the air outlet portion 230 and the evaporator 330 in sequence to form the circulating air path 120.

[0070] In an embodiment, the airflow driving member 340 can be a fan, of course, it can also be other components, which are not limited here. In addition, the clothes drying device 10 also includes a drainage assembly 400, which includes a water collecting tray for collecting the condensed water condensed by the evaporator 330. Of course, the drainage assembly 400 can also include a drainage pump for discharging the condensed water collected by the water collecting tray.

[0071] In an embodiment, the clothes drying device 10 also includes a filter member 500, which is arranged in the circulating air path 120 between the air outlet portion 230 of the drum 200 and the evaporator 330. The filter member 500 includes a filter screen for filtering the lint and the like in the wet hot air discharged from the air outlet portion 230.

[0072] The clothes drying device 10 includes a housing 100, under the condition that the outer dimensions of the housing 100 are limited, for example, the outer dimensions of the product housing 100 cannot be changed, and it is necessary to maintain the existing outer dimensions of the housing 100, it is more difficult to shorten the drying time of the clothes at this time.

[0073] The condensing heat exchange pipe 320a is the pipe in the condenser 320 for the refrigerant to flow through, and the high-temperature and high-pressure refrigerant gas discharged by the compressor flows through the condensing heat exchange pipe 320a of the condenser 320 to release heat and condense into high-pressure liquid. In this process, the refrigerant releases heat to the surrounding environment.

[0074] The evaporating heat exchange pipe 330a is the pipe in the evaporator 330 for the refrigerant to flow through, and the high-pressure liquid refrigerant flows from the condenser into the throttling device, and after being depressurized, it flows into the evaporator. The evaporator is a component that absorbs heat of the refrigerant, and the low-pressure and low-temperature refrigerant flows out of the throttling device and into the evaporator, and is evaporated into low-pressure gas by absorbing heat, and then returns to the compressor.

[0075] Due to the size limitation of the shell 100, the total size of the condenser 320 and the evaporator 330 is limited, the evaporator 330 includes the evaporating heat exchange pipe 330a, and the area of the windward surface of the condenser 320 and the evaporator 330 in the shell 100 is small. Increasing the number of rows of the evaporating heat exchange pipe of the evaporator 330 will increase the thickness size of the evaporator 330, and also increase the air resistance in the air duct 110. Therefore, the scheme of increasing the number of rows of the evaporating heat exchange pipe of the evaporator 330 cannot meet the requirement of keeping the size of the shell 100 unchanged, and cannot solve the problem of shortening the drying time of clothes.

[0076] Therefore, the technical scheme of the present application limits the inner diameter of the evaporating heat exchange pipe 330a to be larger than the inner diameter of the condensing heat exchange pipe 320a, so as to improve the smoothness of the refrigerant flowing through the evaporator 330, reduce the flow resistance of the refrigerant flowing through the evaporator, thereby reducing the pressure loss of the refrigerant flowing through the evaporator, and further improving the suction pressure of the suction port of the compressor, reducing the exhaust temperature of the exhaust port of the compressor, so that the compressor can operate at high frequency for a long time. In addition, the evaporator 330 is provided with at least two independent evaporating flow paths 331, so as to increase the dehumidification amount of the evaporator and reduce the flow resistance of the refrigerant flowing through the evaporator. The evaporating flow path 331 can be two, three or more, and the specific number is not limited herein, as long as the evaporator 330 does not change the size of the existing shell 100.

[0077] The evaporator 330 has at least two independent evaporating flow paths 331, each of which can supply refrigerant. The arrangement of the at least two evaporating flow paths 331 is not limited, for example, the adjacent two evaporating flow paths 331 are arranged in the up-down direction; or the adjacent two evaporating flow paths 331 are arranged in the direction from the windward surface to the leeward surface of the evaporator 330, that is, the width direction of the evaporator 330.

[0078] When the evaporator has two evaporating flow paths, it has two refrigerant inlets for refrigerant inflow and two refrigerant outlets for refrigerant outflow, and the two evaporating flow paths are independent of each other, and the refrigerant in one evaporating flow path cannot flow into the other evaporating flow path. When the evaporator has multiple evaporating flow paths, it has multiple refrigerant inlets for refrigerant inflow and multiple refrigerant outlets for refrigerant outflow, and the multiple evaporating flow paths are independent of each other, and the refrigerant in any one of the multiple evaporating flow paths cannot flow into the other evaporating flow path.

[0079] As shown in FIG. 1, Figures 7 to 12 the refrigerant flows in the direction indicated by the arrow in the evaporator 330, Figures 7 to 12The evaporator 330 has two independent evaporation flow paths 331, in which the thick solid arrow represents the flow direction of the refrigerant in the pipeline located at the front side of the evaporator 330, and the thick dashed arrow represents the flow direction of the refrigerant in the pipeline located at the rear side of the evaporator 330.

[0080] Compared with only one evaporation flow path 331, the evaporator 330 in the present application has at least two independent evaporation flow paths 331, which have strong dehumidification and cooling capacity for the wet hot air, so as to increase the dehumidification amount of the evaporator 330, thereby shortening the drying time of the clothes.

[0081] The technical scheme of the present application sets the evaporator 330 to have at least two independent evaporation flow paths 331, compared with only one evaporation flow path 331, the two independent evaporation flow paths 331 can disperse the flow pressure of the refrigerant, that is, can 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, and further improving the suction pressure of the suction port of the compressor 310, reducing the exhaust temperature of the exhaust port 311 of the compressor 310, so that the compressor 310 can run at high frequency for a long time, avoiding the situation that the exhaust temperature of the compressor 310 exceeds the bearable range and needs to be reduced in frequency or stopped, thereby shortening the drying time of the clothes.

[0082] The clothes drying device 10 comprises a shell 100, a roller 200 and a heat pump system 300, the shell 100 is provided with an air duct 110, the roller 200 is provided with a drying cavity 210, the drying cavity 210 and the air duct 110 are communicated 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 element 340 arranged in the air duct 110, under the action of the airflow driving element 340, the air in the air duct 110 is heated by the condenser 320 and then sent into the drying cavity 210 to dry clothes, the wet and hot air discharged from the drying cavity 210 flows through the evaporator 330, the evaporator 330 absorbs heat to change the wet and hot air into dry and low-temperature air, and the water vapor in the wet and hot air is condensed into condensed water and discharged, and the dry and low-temperature air flows through the condenser 320 again to circulate, thereby realizing the function of drying clothes.

[0083] In an embodiment, the evaporating heat exchange pipe 330a comprises a plurality of evaporating straight pipes 3371 and a plurality of evaporating elbow pipes 3372 connecting two adjacent evaporating straight pipes 3371, the plurality of evaporating straight pipes 3371 are arranged in N rows along the first direction, and N is not less than 4. It can be understood that the number of rows of the plurality of evaporating straight pipes 3371 can be 4 rows, or 5 rows, or 6 rows, or other number of rows. By limiting the number of rows of the plurality of evaporating straight pipes 3371, it can be ensured that the evaporator 330 has sufficient volume, and the evaporating heat exchange pipe 330a has at least two independent evaporating flow paths 331, so that the refrigerant can flow smoothly through the evaporating heat exchange pipe 330a, thereby reducing the flow resistance of the refrigerant flowing through the evaporator, reducing the pressure loss of the refrigerant flowing through the evaporator, thereby increasing the suction pressure of the suction port of the compressor, reducing the exhaust temperature of the exhaust port of the compressor, and enabling the compressor to operate at a high frequency for a long time.

[0084] In an embodiment, the evaporator 330 further comprises a plurality of fins arranged on the evaporating heat exchange pipe 330a, and the total length of the evaporating heat exchange pipe 330a is greater than 4 meters. It can be understood that the total length of the evaporating heat exchange pipe 330a is the total length of the plurality of evaporating straight pipes 3371 and the plurality of evaporating elbow pipes 3372. The total length of the evaporating heat exchange pipe 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., which is not limited here. By limiting the total length of the evaporating heat exchange pipe 330a to be greater than 4 meters, it can be ensured that the evaporator 330 has strong dehumidification and cooling capacity for the wet and hot air when the refrigerant flows through the evaporator 330, thereby increasing the dehumidification amount of the evaporator; and the evaporator has at least two independent evaporating flow paths, which is beneficial to reduce the flow resistance of the refrigerant flowing through the evaporator, thereby reducing the pressure loss of the refrigerant flowing through the evaporator, thereby increasing the suction pressure of the suction port of the compressor, reducing the exhaust temperature of the exhaust port of the compressor, and enabling the compressor to operate at a high frequency for a long time, thereby avoiding the situation that the exhaust temperature of the compressor is too high to exceed the bearing range and needs to be reduced or stopped, so as to shorten the drying time of the clothes.

[0085] In an embodiment, the inner diameter of the evaporating heat exchange pipe 330a is not less than 7 mm and not greater than 12 mm; and / or, the inner diameter of the condensing heat exchange pipe 320a is not less than 5 mm and not greater than 10 mm.

[0086] It can be understood that the inner diameter of the evaporation heat exchange pipe 330a can be 7 mm, or 7.5 mm, or 8.0 mm, or 8.5 mm, or 9.0 mm, or 9.5 mm, or 10.0 mm, or 10.5 mm, or 11.0 mm, or 11.5 mm, or 12.0 mm, etc., which is not limited here. The inner diameter of the condensation heat exchange pipe 320a can be 5 mm, or 5.5 mm, or 6.0 mm, or 6.5 mm, or 7.0 mm, or 7.5 mm, or 8.0 mm, or 8.5 mm, or 9.0 mm, or 9.5 mm, or 10.0 mm, etc., which is not limited here, as long as the inner diameter of the evaporation heat exchange pipe 330a is greater than that of the condensation heat exchange pipe 320a.

[0087] In an embodiment, the condensation heat exchange pipe 320a includes a plurality of condensation straight pipes 321 and a condensation elbow pipe 322 connecting adjacent two condensation straight pipes 321, and the evaporation heat exchange pipe 330a includes a plurality of evaporation straight pipes 3371 and an evaporation elbow pipe 3372 connecting adjacent two evaporation straight pipes 3371; the inner diameter of the evaporation straight pipe 3371 is greater than that of the condensation straight pipe 321; and / or, the inner diameter of the evaporation elbow pipe 3372 is greater than that of the condensation elbow pipe 322. In this way, the inner diameter of the evaporation heat exchange pipe 330a is ensured to be greater than that of the condensation heat exchange pipe 320a, which is conducive to improving the smoothness of the refrigerant flowing through the evaporator, reducing the flow resistance of the refrigerant flowing through the evaporator, thereby reducing the pressure loss of the refrigerant flowing through the evaporator, and further improving the suction pressure of the suction port of the compressor, reducing the exhaust temperature of the exhaust port of the compressor, so that the compressor can run at a high frequency for a long time. While enhancing the dehumidification capacity of the clothes drying device, it can also avoid the situation that the exhaust temperature of the compressor exceeds the bearable range and needs to be reduced or stopped, so as to shorten the drying time of the clothes.

[0088] In a conventional clothes dryer, in order to increase the heating capacity, the volume of the condenser 320 is set to be larger. However, in the case that the space in the shell 100 is limited, setting the volume of the condenser 320 to be larger will occupy the volume of the evaporator 330, so that the volume of the evaporator 330 is smaller, the dehumidification and cooling capacity of the evaporator 330 is poor, and the amount of water carried out of the drum 200 by the heat pump system 300 is greater than the dehumidification capacity of the evaporator 330, thereby reducing the dehumidification efficiency and affecting the drying time.

[0089] Therefore, in an embodiment, the volume of the condenser 320 is not greater than the volume of the evaporator 330. By limiting the volume of the condenser 320 to be not greater than the volume of the evaporator 330, the volume of the evaporator 330 is ensured to be large enough relative to the volume of the condenser 320, the heat exchange efficiency of the evaporator 330 is high, and the evaporator 330 has strong dehumidification and cooling capacity for the humid and hot air, so as to increase the dehumidification amount of the evaporator 330, thereby shortening the drying time of the clothes.

[0090] As can be seen from the foregoing, in the conventional clothes dryer, the volume of the condenser 320 is set to be large, the volume of the evaporator 330 in the conventional clothes dryer is smaller than the volume of the condenser 320, the dehumidification and cooling capacity of the evaporator 330 in the conventional clothes dryer is poor, and the drying time is affected.

[0091] Therefore, in an embodiment of the present 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.

[0092] It can be understood that 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, 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.

[0093] The sum of the volume V1 of the condenser 320 and the volume V2 of the evaporator 330 is V3. By limiting the ratio of the volume V1 of the condenser 320 to the volume V2 of the evaporator 330, the ratio of the volume V2 of the evaporator 330 to V3 is limited, that is, in the case that the sum of the volume V1 of the condenser 320 and the volume V2 of the evaporator 330 is constant, the embodiment limits the proportion of the volume V2 of the evaporator 330 in V3, so as to ensure that the evaporator 330 has sufficient size, thereby improving the dehumidification and cooling capacity of the evaporator 330.

[0094] The ratio of V1 to V2 is not less than 0.8 and not greater than 1.0, which means that the volume V1 of the condenser 320 is less than or equal to the volume V2 of the evaporator 330, so that the volume V2 of the evaporator 330 is large enough relative to the volume V1 of the condenser 320, and the evaporator 330 has sufficient dehumidification and cooling capacity.

[0095] Please refer to Figure 1 , the dehumidification capacity of the closed-loop heat pump system 300, and the wet capacity is:

[0096] The dehumidification capacity C = the humidity content G1 of the drum outlet air - the humidity content G2 of the evaporator outlet air;

[0097] The wet capacity D = the humidity content G1 of the drum outlet air - the humidity content G3 of the drum inlet air;

[0098] For the closed-loop heat pump system 300, the condenser 320 is an isohumid heating process, that is, the humidity content G2 of the evaporator outlet air = the humidity content G3 of the drum inlet air, that is, during the drying process, the dehumidification capacity and the wet capacity of the closed-loop heat pump system 300 are always in a dynamic balance process.

[0099] As can be seen from the above relationship, reducing the humidity content G2 of the evaporator outlet air can increase the dehumidification capacity and the wet capacity of the evaporator 330, that is, the dehumidification capacity and the wet capacity of the evaporator 330, and the humidity content G2 of the evaporator outlet air is proportional to the outlet air temperature of the evaporator 330.

[0100] Therefore, by limiting the ratio of the volume V1 of the condenser 320 to the volume V2 of the evaporator 330, the volume V2 of the evaporator 330 in V3 is limited, that is, under the condition that the total volume of the volume V1 of the condenser 320 and the volume V2 of the evaporator 330 is constant, by ensuring that the evaporator 330 has sufficient volume, compared with the conventional scheme, the volume of the evaporator 330 is increased, so that the outlet air temperature of the evaporator 330 is reduced, and the humidity content of the evaporator outlet air is reduced, so that the dehumidification capacity of the evaporator 330 is increased, thereby improving the dehumidification capacity and the wet capacity of the heat pump system 300, and speeding up the drying time of the clothes.

[0101] Please refer to Figure 5 and Figure 6 In an embodiment, in the direction from the windward surface to the leeward surface of the condenser 320, the width of the condenser 320 is W1; in the direction from the windward surface to the leeward surface of the evaporator 330, the width of the evaporator 330 is W2, and the ratio of W1 to W2 is not less than 0.8 and not greater than 1.0.

[0102] It can be understood that, as Figure 5As shown, the direction from the windward face to the leeward face of the evaporator 330 is the first direction, that is, 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.

[0103] The area of the windward face of the condenser 320 can be equal to the area of the windward face of the evaporator 330. Of course, the area of the windward face of the condenser 320 can also be different from the area of the windward face of the evaporator 330, which is not limited here.

[0104] In the present embodiment, the area of the windward face of the condenser 320 is equal to the area of the windward face of the evaporator 330, and the sum of the volume V1 of the condenser 320 and the volume V2 of 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, under the condition that the sum of the volume V1 of the condenser 320 and the volume V2 of the evaporator 330 is unchanged, the present embodiment limits the proportion of the volume V2 of the evaporator 330 in V3, to ensure that the evaporator 330 has sufficient size, thereby improving the dehumidification and cooling capacity of the evaporator 330.

[0105] The ratio of W1 to W2 is not less than 0.8 and not greater than 1.0, which means that the width W1 of the condenser 320 is less than or equal to the width W2 of the evaporator 330, so that the width W2 of the evaporator 330 is large enough relative to the width W1 of the condenser 320, that is, the volume V2 of the evaporator 330 is large enough, so that the evaporator 330 has sufficient dehumidification and cooling capacity.

[0106] In an 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. Wherein, the value of W1 is not limited, and can be 30 mm, or 32 mm, or 34 mm, or 36 mm, or 38 mm, or 40 mm, or 42 mm, or 44 mm, or 46 mm, or 48 mm, or 50 mm, or 52 mm, or 54 mm, or 56 mm, or 58 mm, or 60 mm, etc. The value of W2 is not limited, and can be 40 mm, or 42 mm, or 44 mm, or 46 mm, or 48 mm, or 50 mm, or 52 mm, or 54 mm, or 56 mm, or 58 mm, or 60 mm, etc.

[0107] Referring to Figure 4 In an embodiment, the evaporator 330 and the condenser 320 are arranged side by side in the first direction, and the width between the windward surface of the evaporator 330 and the leeward surface of the condenser 320 along the first direction is W3; along the second direction, the width of the shell 100 is W4, and the first direction intersects the second direction; the ratio of W3 to W4 is not less than 0.1 and not greater than 0.25. By such arrangement, the ratio of the sum of the width of the evaporator 330 and the width of the condenser 320 to the width of the shell 100 is between 0.1 and 0.25, and the specific value of the ratio of W3 to W4 is not limited, for example, but not limited to: 0.1, or 0.15, or 0.2, or 0.25, etc. In the case of determining 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 within the range of the foregoing embodiment, so as to ensure that the width W2 of the evaporator 330 is large enough, thereby ensuring that the evaporator 330 has sufficient size, and further improving the dehumidification and cooling capacity of the evaporator 330.

[0108] Referring to Figures 5 to 7 In an embodiment, the condensing heat exchange pipe 320a includes a plurality of condensing straight pipes 321 and a condensing elbow pipe 322 connecting adjacent two condensing straight pipes 321, and the evaporating heat exchange pipe 330a includes a plurality of evaporating straight pipes 3371 and an evaporating elbow pipe 3372 connecting adjacent two evaporating straight pipes 3371; the plurality of condensing straight pipes 321 and the plurality of evaporating straight pipes 3371 are arranged along the third direction, and the plurality of condensing straight pipes 321 and the plurality of evaporating straight pipes 3371 are arranged in multiple rows along the first direction, and the first direction is perpendicular to the third direction; the number of rows of the condensing straight pipes 321 in the condenser 320 is less than or equal to the number of rows of the evaporating straight pipes 3371 in the evaporator 330.

[0109] It can be understood that the evaporator 330 and the condenser 320 can also include heat exchange fins. The number of rows of the condensing straight tubes 321 in the condenser 320 can be 3 rows, or 4 rows, or 5 rows, or other rows. The number of rows of the evaporating straight tubes 3371 in the evaporator 330 can be 4 rows, or 5 rows, or other rows. It is only required that the number of rows of the condensing straight tubes 321 in the condenser 320 is not greater than the number of rows of the evaporating straight tubes 3371 in the evaporator 330.

[0110] By limiting the number of rows of the condensing straight tubes 321 in the condenser 320 to be less than or equal to the number of rows of the evaporating straight tubes 3371 in the evaporator 330, it is equivalent to limiting the width of the condenser 320 to be less than or equal to the width of the evaporator 330, so that the width of the evaporator 330 is large enough relative to the width of the condenser 320, that is, the volume of the evaporator 330 is large enough, so that the evaporator 330 has sufficient dehumidification and cooling capacity.

[0111] In an embodiment, along the first direction, the number of rows of the condensing straight tubes 321 in the condenser 320 is the same as the number of rows of the evaporating straight tubes 3371 in the evaporator 330; the plurality of condensing straight tubes 321 and the plurality of evaporating straight tubes 3371 are arranged in multiple columns along the up-down direction, and the number of condensing straight tubes 321 in each column is greater than the number of evaporating straight tubes 3371 in each column. As shown in Figure 5 and Figure 6 As shown in the figures, the number of rows of the condensing straight tubes 321 in the condenser 320 is 4 rows, and the number of rows of the evaporating straight tubes 3371 in the evaporator 330 is 4 rows, at this time the number of rows of the condensing straight tubes 321 in the condenser 320 is equal to the number of rows of the evaporating straight tubes 3371 in the evaporator 330; the number of condensing straight tubes 321 in each column is 9, and the number of evaporating straight tubes 3371 in each column is 6, at this time the number of condensing straight tubes 321 in each column is greater than the number of evaporating straight tubes 3371 in each column, to ensure that the evaporator 330 has at least two independent evaporating flow paths 331; and at this time the volume V1 of the condenser 320 is less than or equal to the volume V2 of the evaporator 330. In this way, the total volume of the volume of the condenser 320 and the volume of the evaporator 330 on a certain basis can ensure that the evaporator 330 has sufficient volume, that is, it ensures that the evaporator 330 has sufficient size, thereby improving the dehumidification and cooling capacity of the evaporator 330.

[0112] In an embodiment, the width W1 of the condenser 320 is 40 mm, and the width W2 of the evaporator 330 is 48 mm. In this way, the width W1 of the condenser 320 is less than the width W2 of the evaporator 330, so that the width of the evaporator 330 is large enough relative to the width of the condenser 320, that is, the volume of the evaporator 330 is large enough, so that the evaporator 330 has sufficient dehumidification and cooling capacity.

[0113] In an embodiment, the width W1 of the condenser 320 is 40 mm, the number of rows of the condensing straight tubes 321 in the condenser 320 is 4 rows, and the width of each row of the condensing straight tubes 321 is 10 mm; the width W2 of the evaporator 330 is 48 mm, the number of rows of the evaporating straight tubes 3371 in the evaporator 330 is 4 rows, and the width of each row of the evaporating straight tubes 3371 is 12 mm. In this way, the width of each row of the evaporating straight tubes 3371 is greater than the width of each row of the condensing straight tubes 321, and the width of the evaporator 330 is greater than the width of the condenser 320. In this way, under the same conditions in the length direction and the height direction, that is, the total volume of the volume of the condenser 320 and the volume of the evaporator 330 is on a certain basis, the evaporator 330 can have sufficient volume, that is, the evaporator 330 can have sufficient size, thereby improving the dehumidification and cooling capacity of the evaporator 330.

[0114] In an embodiment, the tube wall thickness of the condensing heat exchange tube 320a and the evaporating heat exchange tube 330a is the same, and the outer diameter of the evaporating straight tube 3371 is greater than the outer diameter of the condensing straight tube 321. In order to improve the uniformity of heat exchange, the distance between two adjacent straight tubes in the condenser 320 and the evaporator 330 is the same. In this way, the width of the condenser 320 is limited to be less than the width of the evaporator 330. As known from the foregoing, the width of the evaporator 330 is large enough, that is, the volume of the evaporator 330 is large enough, so that the evaporator 330 has sufficient dehumidification and cooling capacity.

[0115] In an embodiment, the plurality of condensing straight tubes 321 and the plurality of evaporating straight tubes 3371 are arranged in the third direction. The third direction is perpendicular to the first direction. In this way, the uniformity of air flowing through the condenser 320 and the evaporator 330 for heat exchange is improved.

[0116] In an embodiment, the operating stage of the clothes drying device 10 includes a temperature rising stage and a temperature stabilizing stage, and the compressor 310 includes a variable frequency compressor 310. In the temperature rising stage, the variable frequency compressor 310 first increases the frequency and then decreases the frequency to a preset high frequency to enter the temperature stabilizing stage. In the temperature stabilizing stage, the variable frequency compressor 310 operates at the preset high frequency, and the frequency of the preset high frequency is not less than 70 Hz.

[0117] It can be understood that the heat pump system 300 adopts the variable frequency compressor 310, and the clothes drying device 10 is provided 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.

[0118] In the fast drying mode, the compressor 310 needs to run at a safety protection temperature (a condenser 320 temperature T1 and a compressor 310 exhaust temperature T2 described later), and the drying stage of the fast drying mode includes a pre-stage temperature rising stage and a post-stage temperature stabilizing stage. In the pre-stage temperature rising stage, the compressor 310 runs at a highest running frequency, which can be 100 Hz or other values. When the temperature sensor detects that the safety protection temperature exceeds the limit, the controller of the clothes drying device 10 controls the compressor 310 to reduce the running frequency until the temperature is within the safety protection temperature. Then, the compressor 310 enters the post-stage temperature stabilizing stage at a preset high frequency, and the variable frequency compressor 310 runs stably at the preset high frequency in the temperature stabilizing stage.

[0119] In this embodiment, in the temperature stabilizing stage, the variable frequency compressor 310 runs at a preset high frequency, and the frequency of the preset high frequency is not less than 70 Hz. In this way, the frequency of the compressor 310 in the temperature stabilizing stage is increased, that is, the refrigeration and heating capacity of the compressor 310 is increased, which is beneficial to improve the drying efficiency of the clothes and thus shorten the drying time of the clothes. The frequency of the preset high frequency can be 70 Hz, or 72 Hz, or 74 Hz, or 76 Hz, or 78 Hz, or 80 Hz, or 82 Hz, or 84 Hz, or 85 Hz, or 86 Hz, or 87 Hz, or 88 Hz, or 89 Hz, or 90 Hz, etc.

[0120] In an embodiment, the variable frequency compressor 310 has an exhaust port 311 which is communicated with the refrigerant circulation loop 350. In the temperature stabilizing stage, the temperature of the refrigerant discharged from the exhaust port 311 is not higher than 110 degrees Celsius. In this way, when the compressor 310 runs in the temperature stabilizing stage, the exhaust temperature of the compressor 310 is limited to not higher than 110 degrees Celsius, so that the exhaust temperature of the compressor 310 is below the safety protection temperature, and the compressor 310 can run at a high frequency for a long time, avoiding the situation that the exhaust temperature of the compressor 310 exceeds the bearable range and needs to be reduced or stopped, so that the drying time of the clothes can be shortened.

[0121] In an embodiment, in the temperature stabilizing stage, the temperature of the air flow blown out from the leeward side of the evaporator 330 in the circulating air path 120 is not higher than 20 degrees Celsius. In this way, the value of the humidity content G2 of the evaporator outflow is small. As can be seen from the dehumidification amount C = the drum outflow humidity content G1 - the evaporator outflow humidity content G2, the value of G2 is small, so that the value of the dehumidification amount C is large, so as to ensure that the evaporator 330 has good dehumidification amount and wet amount, that is, the dehumidification capacity and wet capacity of the evaporator 330 are improved.

[0122] Please refer to Figures 6 to 8 In an embodiment,

[0123] The condensing heat exchange pipe 320a has a condensing flow path 323 (as shown in Figure 13 The number of the evaporation flow paths 331 of the evaporation heat exchange pipe 330a is greater than the number of the condensing flow paths 323 of the condensing heat exchange pipe 320a. The refrigerant discharged by the compressor 310 first flows through the condensing flow paths 323 and then flows through at least two evaporation flow paths 331 to form the refrigerant circulation loop 350.

[0124] It can be understood that the evaporation flow paths 331 can be two, three, or more. The condenser 320 has the condensing flow paths 323, and the number of the evaporation flow paths 331 of the evaporator 330 is greater than the number of the condensing flow paths 323 of the condenser 320. For example, when the number of the evaporation flow paths 331 of the evaporator 330 is two, the number of the condensing flow paths 323 of the condenser 320 is one. For another example, when the number of the evaporation flow paths 331 of the evaporator 330 is three, the number of the condensing flow paths 323 of the condenser 320 is one or two. For another example, when the number of the evaporation flow paths 331 of the evaporator 330 is four, the number of the condensing flow paths 323 of the condenser 320 is one, two, or three. That is, only the number of the evaporation flow paths 331 of the evaporator 330 needs to be greater than the number of the condensing flow paths 323 of the condenser 320. In this way, the dehumidification capacity of the clothes drying device can be enhanced, and the exhaust temperature of the compressor can be prevented from being too high to exceed the tolerable range, thereby shortening the drying time of the clothes.

[0125] The condensing flow path 323 is a path for the refrigerant to flow through the condenser 320. When the high-temperature and high-pressure refrigerant gas discharged by the compressor flows through the condensing flow path 323 of the condenser 320, the refrigerant gas is condensed into high-pressure liquid by releasing heat. In this process, the refrigerant releases heat to the surrounding environment.

[0126] In an embodiment, the condenser 320 has one condensing flow path 323, which has one refrigerant inlet for the refrigerant to flow in and one refrigerant outlet for the refrigerant to flow out. When the condenser has two condensing flow paths, it has two refrigerant inlets for the refrigerant to flow in and two refrigerant outlets for the refrigerant to flow out. The two condensing flow paths are independent of each other, and the 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 the refrigerant to flow in and multiple refrigerant outlets for the refrigerant to flow out. The multiple condensing flow paths are independent of each other, and the refrigerant in any one condensing flow path cannot flow into the other condensing flow path.

[0127] 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.

[0128] 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.

[0129] 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.

[0130] like Figure 13 As shown, the refrigerant flows in the direction indicated by the arrow in the condenser 320. Figure 13 The diagram illustrates that the condenser 320 has a condensation flow path 323, where 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.

[0131] like Figures 7 to 12 As shown, the refrigerant flows in the evaporator 330 in the direction indicated by the arrow. Figures 7 to 12 The diagram 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 on the front side of the evaporator 330, and the thick dashed arrows indicate the flow direction of the refrigerant in the pipe located on the rear side of the evaporator 330.

[0132] 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.

[0133] The heat pump system 300 comprises a compressor 310, a condenser 320 and an evaporator 330, and the compressor 310 can be a variable frequency compressor 310. In order to protect the safety of the heat pump system 300, it is usually necessary to detect the temperature of the key components of the heat pump system 300, for example, a temperature sensor is arranged at the middle position of the pipeline of the condenser 320, when the temperature of the condenser 320 exceeds the upper limit temperature T1 (T1 is 80 degrees Celsius) corresponding to the saturated condensing pressure of the compressor 310, the compressor 310 needs to be reduced in frequency or stopped to protect the compressor 310 and ensure the reliability of the compressor 310. For another example, a temperature sensor is arranged on the exhaust pipe of the compressor 310, when the exhaust temperature of the compressor 310 exceeds the upper limit temperature T2 (T2 is 110 degrees Celsius) of the safe temperature that the compressor 310 can withstand, the compressor 310 needs to be reduced in frequency or stopped to protect the compressor 310 and ensure the reliability of the compressor 310. For another example, when the heat pump system 300 operates at different ambient temperatures, the cold medium temperature T1 on the condenser 320 (the cold medium temperature represents the temperature of the condenser 320 at a predetermined position), the exhaust temperature T2 of the compressor 310, needs to be always lower than the corresponding safe temperature for protection. When the system detects that T1 or T2 is greater than or equal to the safe temperature, the compressor 310 needs to reduce its operating frequency or even stop to ensure that the cold medium temperature T1 on the condenser 320 and the exhaust 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.

[0134] The technical solution of the present application sets the evaporator 330 to have at least two independent evaporation flow paths 331, and the number of the evaporation flow paths 331 of the evaporator 330 is greater than the number of the condensation flow paths 323 of the condenser 320, so that while enhancing the dehumidification capacity of the clothes drying device, the situation that the exhaust temperature of the compressor 310 is too high to exceed the bearable range and needs to be reduced in frequency or stopped can be avoided, and thus the drying time of the clothes can be shortened.

[0135] Please refer to Figure 8 In an embodiment, one end of the evaporation flow path 331 is a refrigerant inlet 332, the other end of the evaporation flow path 331 is a refrigerant outlet 333, the refrigerant inlets 332 of the at least two evaporation flow paths 331 are arranged on the same side of the evaporator 330 and adjacent to each other; and / or, the refrigerant outlets 333 of the at least two evaporation flow paths 331 are arranged on the same side of the evaporator 330 and adjacent to each other.

[0136] It can be understood that the specific position of the refrigerant inlet 332 of the at least two evaporation flow paths 331 is not limited, and the specific position of the refrigerant outlet 333 of the at least two evaporation flow paths 331 is not limited. By arranging the two refrigerant inlets 332 on the same side and adjacent to each other, the length of the connecting pipeline is shortened, the pipeline arrangement is facilitated, the evaporator 330 is easy to manufacture and assemble, and the production cost is reduced. Similarly, by arranging the two refrigerant outlets 333 on the same side and adjacent to each other, the length of the connecting pipeline is shortened, the pipeline arrangement is facilitated, the evaporator 330 is easy to manufacture and assemble, and the production cost is reduced.

[0137] Please refer to Figures 5 to 7 In an embodiment, the evaporator 330 further comprises a distribution joint 334, the distribution joint 334 has at least three distribution flow channels in communication with each other; the refrigerant inlets 332 of the at least two evaporation flow paths 331 are connected to the refrigerant circulation loop 350 through one distribution joint 334; and / or, the refrigerant outlets 333 of the at least two evaporation flow paths 331 are connected to the refrigerant circulation loop 350 through one distribution joint 334.

[0138] It can be understood that for the refrigerant inlets 332 of the two evaporation flow paths 331, one of the distribution flow channels of the distribution joint 334 is connected to the refrigerant circulation loop 350, and the other two distribution flow channels of the distribution joint 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 of the distribution flow channels of the distribution joint 334 is connected to the refrigerant circulation loop 350, and the other two distribution flow channels of the distribution joint 334 are respectively connected to the two refrigerant outlets 333 of the two evaporation flow paths 331. Exemplarily, the distribution joint 334 is a multi-way pipe, and in this scheme, the distribution joint 334 is a three-way pipe. By using the distribution joint 334 for connection, the number of pipes is reduced, the pipe layout of the evaporator 330 is simplified, the production cost is reduced, and the efficiency of the refrigerant flowing through the at least two evaporation flow paths 331 is improved. In addition, by assembling the distribution joint 334 at the position of the refrigerant inlet 332 of the two evaporation flow paths 331, the structure of the original compressor refrigerant outlet pipeline can be unchanged, that is, the refrigerant inlet 332 of the evaporator 330 is directly connected to the original compressor refrigerant outlet pipeline through one distribution joint 334, so that the assembly is more simple.

[0139] Please refer to Figures 5 to 7In an embodiment, the evaporator 330 and the condenser 320 are arranged in sequence along the first direction, the evaporating heat exchange pipe 330a comprises a first shunt pipe 335 and a second shunt pipe 336, the first shunt pipe 335 has a first shunt passage, the second shunt pipe 336 has a second shunt passage, the first shunt passage and the second shunt passage are independent of each other and respectively communicate with a evaporating flow path 331, and the first shunt pipe 335 and the second shunt pipe 336 are arranged in cross on the same side of the evaporator 330.

[0140] It can be understood that, as shown in Figure 7 , the refrigerant flows in the evaporator 330 along the direction indicated by the arrow, Figure 7 , the evaporator 330 has two independent evaporating flow paths 331, wherein the thick solid line arrow indicates the flow direction of the refrigerant in the pipe located at the front side of the evaporator 330, and the thick dashed line arrow indicates the flow direction of the refrigerant in the pipe located at the back side of the evaporator 330. The refrigerant inlets 332 of the two evaporating flow paths 331 are connected by a distribution joint 334, and the refrigerant outlets 333 of the two evaporating flow paths 331 are connected by a distribution joint 334.

[0141] Figure 7 The first shunt pipe 335 and the second shunt pipe 336 in the evaporator 330 are arranged in cross on the same side, that is, one of the first shunt pipe 335 and the second shunt pipe 336 is arranged in front of the other, and one of the first shunt passage and the second shunt passage is located in front of the other. In this embodiment, the first shunt pipe 335 is arranged in front of the second shunt pipe 336, so that the flow direction and path of the refrigerant are changed when the refrigerant flows through the first shunt passage and the second shunt passage in the evaporator 330, avoiding the problem of too fast or too slow local flow rate, and ensuring that the refrigerant can be uniformly heat exchanged in the evaporator 330, thereby improving the influence of the temperature difference between the upper and lower two evaporating flow paths 331 in the evaporator 330 on the reversing performance.

[0142] In an embodiment, the evaporating heat exchange pipe 330a further comprises a plurality of evaporating pipes 337 arranged in sequence along the direction from the windward side to the leeward side of the evaporator 330, each evaporating pipe 337 comprises a plurality of evaporating straight pipes 3371 and an evaporating elbow pipe 3372 connecting adjacent two evaporating straight pipes 3371, and the evaporating straight pipe 3371 is arranged in the third direction; the first shunt pipe 335 connects two evaporating pipes 337 of one of the evaporating flow paths 331, and the second shunt pipe 336 connects two evaporating pipes 337 of the other of the evaporating flow paths 331.

[0143] It can be understood that, as shown in Figure 7 and Figure 8As shown, the evaporator 330 has two independent evaporation flow paths 331, the first distribution pipe 335 connects two evaporation pipelines 337 of one of the evaporation flow paths 331 to form a communication flow channel; and the second distribution pipe 336 connects two evaporation pipelines 337 of the other of the evaporation flow paths 331 to form a communication flow channel.

[0144] In an embodiment, the first distribution pipe 335 and the second distribution pipe 336 are arranged in a cross shape, and the projection of the intersection point of the cross shape along the third direction falls on the central position of one side of the evaporator. In this way, the overall structure of the evaporator 330 is regular, which is conducive to ensuring that the refrigerant can be uniformly heat-exchanged in the evaporator 330, thereby improving the influence of the temperature difference between the two evaporation flow paths 331 on the reversing performance.

[0145] Please refer to Figure 5 and Figure 6 In an embodiment, the plurality of evaporation straight pipes 3371 are arranged in multiple columns along the up-down direction, and two evaporation straight pipes 3371 in adjacent two columns are arranged in a staggered manner along the up-down direction and the left-right direction. It can be understood that, in Figure 5 and Figure 6 , one evaporation pipeline 337 includes three evaporation straight pipes 3371 and two evaporation elbow pipes 3372, and the three evaporation straight pipes 3371 are connected to form a communication flow channel through the two evaporation elbow pipes 3372, thereby ensuring the continuity of the refrigerant flow. And two evaporation straight pipes 3371 in adjacent two columns are arranged in a staggered manner along the up-down direction and the left-right direction, that is, adjacent two evaporation straight pipes 3371 have a height difference along the up-down direction and the left-right direction, so that the installation space can be saved, and the space utilization rate of the evaporator 330 is high.

[0146] In an embodiment, the evaporation flow path 331 is repeatedly folded and arranged along the up-down direction and the front-rear direction. In this way, not only the length of the evaporation flow path 331 can be increased, but also the space occupied by the evaporation flow path 331 can be effectively reduced, and the contact area with the air can be increased, thereby improving the heat exchange effect. In addition, by repeatedly folding and arranging, the vibration and noise of the pipeline of the evaporation flow path 331 caused by the flow of the refrigerant can be reduced.

[0147] In an embodiment, the refrigerant inlet 332 of each evaporation flow path 331 is arranged close to the first side, the refrigerant outlet 333 of each evaporation flow path 331 is arranged close to the second side, the first side and the second side are arranged opposite to each other; the two evaporation flow paths 331 are arranged in a spaced manner along the up-down direction; and / or, the two evaporation flow paths 331 are arranged in a spaced manner along the direction from the windward side to the leeward side of the evaporator 330.

[0148] It can be understood that, as Figure 9 , Figure 10 and Figure 11As shown, the two evaporation flow paths 331 are spaced apart in the vertical direction; as Figure 12 As shown, the two evaporation flow paths 331 are arranged at intervals along the windward side to the leeward side of the evaporator 330.

[0149] exist Figures 8 to 10 In the process, the refrigerant inlets 332 of the two evaporation flow paths 331 are both located close to the first side, and the refrigerant outlets 333 of the two evaporation flow paths 331 are both 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.

[0150] 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.

[0151] 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.

[0152] like Figures 8 to 10 As shown, 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 diagram 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 even 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.

[0153] like Figure 11 and Figure 12As shown, the multiple columns of the evaporation straight pipes 3371 are arranged in an even number of rows in the first direction for even division of the two evaporation flow paths 331. In this arrangement, the evaporator 330 adopts a longitudinal pipe arrangement, and in the figure, there are a total of 4 rows, and each of the two evaporation flow paths 331 includes 12 evaporation straight pipes 3371, wherein one evaporation flow path 331 uses the evaporation straight pipes 3371 in the first row and the third row to form a flow path, and the other evaporation flow path 331 uses the evaporation straight pipes 3371 in the second row and the fourth row to form a flow path, so that the pipe arrangement of the evaporator 330 is regular, and the refrigerant can be uniformly distributed in the evaporator 330, which helps to ensure that the air fully contacts all the heat exchange surfaces, thereby improving the heat exchange efficiency.

[0154] The utility model also proposes a washing and drying integrated machine, the washing and drying integrated machine includes clothes drying device 10 as described above, the specific structure of clothes drying device 10 refers to the above embodiment, because the washing and drying integrated machine adopts all the technical schemes of the above all embodiments, therefore at least has all the beneficial effects brought by the technical scheme of the above embodiment, here will not repeat.

[0155] In an embodiment, the washing and drying integrated machine includes a drying assembly and a washing assembly. The washing and drying integrated machine integrates the washing and drying processes in the same device, so that the clothes can be directly dried after washing without transferring the wet clothes to another dryer or drying. Among them, the main function of the washing assembly is to clean the clothes, including but not limited to cleaning, decontamination and rinsing steps. The washing assembly includes a drum for stirring the clothes to improve the cleaning effect. The washing assembly can also include a motor and a drive system for driving the drum to rotate. The washing assembly can also include a water pump and a water pipe system for water injection and drainage to ensure water level control, sewage discharge and rinsing during the washing process. The washing assembly can also include a detergent box or a dispensing system for placing laundry detergent, laundry detergent, fabric softener and other washing and care products. The drying assembly can include the aforementioned shell 100, drum 200 and heat pump system 300, and the drying assembly is used to dry the washed clothes to make the clothes not wet.

[0156] The washing and drying all-in-one machine comprises a washing assembly and a drying assembly, the washing assembly comprises a water inlet system, a drainage system, a liquid inlet system, a damping system and the like, and the drying assembly comprises a heat pump system, a drying channel assembly and the like. The washing and drying all-in-one machine needs to place the washing assembly and the drying assembly in a limited space, so that the installation space of the heat pump system is severely limited, and in addition, the space is also limited, so that the air duct flow in the washing and drying all-in-one machine is small, and the air volume is small. That is, the overall performance of the heat pump in the washing and drying all-in-one machine is limited by the installation space and the air duct flow, and the overall performance of the heat pump is low, so it is necessary to further improve the drying performance under the premise of limited space and limited air volume. The traditional evaporator and condenser are penetrated by a single refrigerant pipe through multiple bending, and the number of refrigerant pipe arrangements in the thickness direction or the height direction of the evaporator or the condenser is generally increased. This method inevitably increases the size of the evaporator or the condenser in the thickness direction or the height direction, that is, the volume of the evaporator or the condenser is increased. In the washing and drying all-in-one machine, the space is limited, and the above-mentioned method cannot be used. In addition, if the efficiency of the condenser is greatly improved, the temperature near the compressor will be too high, which will affect the operation of the compressor.

[0157] In the washing and drying all-in-one machine, the above-mentioned laundry drying equipment can improve the dehumidification efficiency in a limited space to further improve the drying performance, and in the case of using a variable frequency compressor, the safe temperature of the compressor is ensured, so that the compressor will not enter the stage of high frequency and unable to run.

[0158] The above-mentioned is only an exemplary embodiment of the present application, and does not limit the patent range of the present application, and any equivalent structural transformation or direct / indirect application in other related technical fields under the technical concept of the present application is included in the patent protection range of the present application.

Claims

1. A laundry drying apparatus, characterized by, The laundry drying device comprises: a housing having an air duct; a drum having a drying cavity, the drying cavity being in communication with the air duct to form a circulating air path; a heat pump system comprising a compressor and a condenser, an evaporator and an airflow driving member arranged in the air duct, the airflow driving member being configured to drive the airflow to circulate in the circulating air path; the condenser comprises a condensing heat exchange pipe, the evaporator comprises an evaporating heat exchange pipe, the inner diameter of the evaporating heat exchange pipe is greater than the inner diameter of the condensing heat exchange pipe; the evaporating heat exchange pipe has at least two independent evaporating flow paths, each of the at least two independent evaporating flow paths is in communication with the condensing heat exchange pipe, and the refrigerant discharged by the compressor flows through the condensing heat exchange pipe and then flows through the at least two independent evaporating flow paths to form a refrigerant circulation loop.

2. The clothes drying apparatus of claim 1, wherein, The evaporating heat exchange pipe comprises a plurality of evaporating straight pipes and a plurality of evaporating elbow pipes connecting adjacent two evaporating straight pipes, the plurality of evaporating straight pipes are arranged in N rows along a first direction, and N is not less than 4. And / or, the evaporator further comprises a plurality of fins arranged on the evaporating heat exchange pipe, and the total length of the evaporating heat exchange pipe is greater than 4 meters.

3. The clothes drying device as described in claim 2, characterized in that, The inner diameter of the evaporating heat exchange pipe is not less than 7 mm and not greater than 12 mm. And / or, the inner diameter of the condensing heat exchange pipe is not less than 5 mm and not greater than 10 mm.

4. The clothes drying apparatus of claim 1, wherein the air flow guide is formed of a material having a thermal conductivity lower than that of the air flow guide. The condensing heat exchange pipe comprises a plurality of condensing straight pipes and a plurality of condensing elbow pipes connecting adjacent two condensing straight pipes, and the evaporating heat exchange pipe comprises a plurality of evaporating straight pipes and a plurality of evaporating elbow pipes connecting adjacent two evaporating straight pipes; the inner diameter of the evaporating straight pipe is greater than the inner diameter of the condensing straight pipe. And / or, the inner diameter of the evaporating elbow pipe is greater than the inner diameter of the condensing elbow pipe. And / or, the plurality of condensing straight pipes and the plurality of evaporating straight pipes are arranged in a third direction, the plurality of condensing straight pipes and the plurality of evaporating straight pipes are arranged in a plurality of rows along a first direction, and the first direction is perpendicular to the third direction; the number of rows of the condensing straight pipes in the condenser is less than or equal to the number of rows of the evaporating straight pipes in the evaporator.

5. The clothes drying device as described in claim 4, characterized in that, Along the first direction, the number of rows of the condensing straight pipes in the condenser is the same as the number of rows of the evaporating straight pipes in the evaporator; the plurality of condensing straight pipes and the plurality of evaporating straight pipes are arranged in a plurality of columns along an up-down direction, the number of condensing straight pipes in each column is greater than the number of evaporating straight pipes in each column.

6. The clothes drying apparatus of 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 surface to the leeward surface of the condenser, the width of the condenser is W1. In the direction from the windward surface to the leeward surface of the evaporator, the width of the evaporator is W2, and the ratio of W1 to W2 is not less than 0.8 and not greater than 1.

0.

7. The clothes drying apparatus of claim 1, wherein the air flow guide is formed of a material having a thermal conductivity lower than that of the air flow guide. The operating stage of the laundry drying device comprises a temperature rising stage and a temperature maintaining stage, and the compressor comprises a variable frequency compressor; In the temperature rising stage, the variable frequency compressor first increases the frequency and then decreases the frequency to a preset high frequency to enter the temperature maintaining stage; In the temperature maintaining stage, the variable frequency compressor operates at the preset high frequency, and the frequency of the preset high frequency is not less than 70 Hz.

8. The clothes drying apparatus as described in claim 7, characterized in that, The variable frequency compressor has an exhaust port which is communicated with the refrigerant circulation loop, and the temperature of the refrigerant exhausted from the exhaust port is not higher than 110 DEG C in the temperature stabilizing stage.

9. The laundry drying apparatus as claimed in any one of claims 1 to 8, wherein, The condensing heat exchange pipe has condensing flow paths, the number of the evaporation flow paths of the evaporation heat exchange pipe is greater than the number of the condensing flow paths of the condensing heat exchange pipe, and the refrigerant exhausted from the compressor flows through the condensing flow paths and then flows through at least two evaporation flow paths to form the refrigerant circulation loop.

10. The clothes drying apparatus of claim 9, wherein the air flow guide is formed of a material having a thermal conductivity lower than that of the air flow guide of the first clothes drying apparatus. One end of the evaporation flow path is a refrigerant inlet, and the other end of the evaporation flow path is a refrigerant outlet, and the refrigerant inlets of the at least two evaporation flow paths are arranged on the same side of the evaporator and are arranged adjacently. And / or, the refrigerant outlets of the at least two evaporation flow paths are arranged on the same side of the evaporator and are arranged adjacently.

11. The clothes drying apparatus as described in claim 10, characterized in that, The evaporator further comprises a distribution joint having at least three distribution flow channels which are communicated with each other, and the refrigerant inlets of the at least two evaporation flow paths are communicated with the refrigerant circulation loop through one distribution joint. And / or, the refrigerant outlets of the at least two evaporation flow paths are communicated with the refrigerant circulation loop through one distribution joint.

12. The clothes drying apparatus of claim 9, wherein the air flow guide is formed of a material having a thermal conductivity lower than that of the air flow guide. The evaporator and the condenser are arranged in sequence along a first direction, the evaporation heat exchange pipe comprises a first shunt pipe and a second shunt pipe, the first shunt pipe has a first shunt passage, the second shunt pipe has a second shunt passage, the first shunt passage and the second shunt passage are independent of each other and are respectively communicated with one evaporation flow path, and the first shunt pipe and the second shunt pipe are arranged in a cross manner on the same side of the evaporator.

13. The clothes drying apparatus of claim 12, wherein, The evaporation heat exchange pipe further comprises a plurality of evaporation pipe routes, the plurality of evaporation pipe routes are arranged in sequence along a direction from a windward side to a leeward side of the evaporator, each evaporation pipe route comprises a plurality of evaporation straight pipes and evaporation elbow pipes connecting adjacent two evaporation straight pipes, and the evaporation straight pipes are arranged in extension along a third direction. And / or, a projection of a cross point at which the first shunt pipe and the second shunt pipe are arranged in a cross manner falls on a central position on one side of the evaporator along the third direction. And / or, the plurality of evaporation straight pipes are arranged in multiple columns along an up-down direction, and two evaporation straight pipes in adjacent two columns are arranged in a staggered manner along the up-down direction and a left-right direction.

14. The clothes drying apparatus as described in claim 13, characterized in that, The plurality of evaporation straight pipes are arranged in multiple columns along the up-down direction, and the number of the evaporation straight pipes in each column is even, so as to divide two evaporation flow paths evenly. And / or, the multiple columns of evaporation straight pipes are arranged in an even number of rows along a first direction, so as to divide two evaporation flow paths evenly, and the first direction is perpendicular to the third direction.

15. The clothes drying apparatus of claim 9, wherein the air flow guide is formed of a material having a thermal conductivity lower than that of the air flow guide of the first clothes drying apparatus. The refrigerant inlets of the two evaporation flow paths are arranged in a staggered manner along the up-down direction. And / or, the two evaporation flow paths are arranged in a staggered manner along a direction from a windward side to a leeward side of the evaporator.

16. A washer-dryer, characterized in that, The laundry drying device according to any one of claims 1 to 15.

17. The washer-dryer according to claim 16, characterized in that, The washing and drying integrated machine comprises a drying assembly and a washing assembly.

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