Laundry treating apparatus

Abstract

The laundry treating apparatus of the present invention is characterized by comprising: a heat pump having an evaporator, a compressor, a condenser, and an expansion valve, which applies heat to air circulating in a drum; and an air flow path forming a moving path to pass the air through the drum and circulate; the condenser comprising a plurality of condensing refrigerant tubes in which refrigerant flows, and a condensing fin conducting heat of the condensing refrigerant tubes; the evaporator comprising a plurality of evaporating refrigerant tubes in which refrigerant flows, and an evaporating fin conducting heat of the evaporating refrigerant; the condensing refrigerant tube comprising a plurality of passages for refrigerant flow; a cross-sectional area of each of the passages being smaller than a cross-sectional area of each of the evaporating refrigerant tubes; and a value of a sum of cross-sectional areas of the condensing refrigerant tubes divided by a sum of cross-sectional areas of the evaporating refrigerant tubes being 1.3 or less.

Description

Technical Field

[0001] The present invention relates to a heat exchanger that can further ensure heat exchange performance, increase heat exchange capacity, and improve power consumption, as well as a clothing treatment apparatus including the heat exchanger. Background Technology

[0002] Typically, a heat exchanger can be used as a condenser or evaporator in a refrigeration cycle device consisting of a compressor, condenser, expansion mechanism, and evaporator.

[0003] In addition, heat exchangers are installed in vehicles, refrigerators, clothing handling devices, etc., to allow refrigerant and air to exchange heat.

[0004] Typically, a laundry drying device dries laundry by blowing hot air generated by a heater into the drum to evaporate the moisture in the laundry.

[0005] Clothing handling devices can be classified into two types based on how they handle the humid air passing through the drum after drying laundry: venting-type clothing handling devices and condensation-type clothing handling devices.

[0006] The exhaust-type garment processing device discharges the humid air flowing out of the drum to the outside of the garment processing device. The condensing-type garment processing device does not discharge the humid air flowing out of the drum to the outside of the garment processing device. Instead, it circulates the humid air and cools it to below the dew point temperature through the condenser, thereby condensing the moisture contained in the humid air.

[0007] In condenser-type garment processing equipment, heated air flows into the drum after being heated by a heater before being supplied with condensed water from the condenser again. Here, because the humid air is cooled during the condensation process, heat energy is lost, thus requiring an additional heater or similar device to heat it to the temperature needed for drying.

[0008] Exhaust-type garment processing units also need to expel hot and humid air to the outside, allowing ambient air to flow in and be heated to the required temperature level by heaters or similar devices. In particular, as drying progresses, the humidity of the air discharged from the drum outlet decreases, so the heat from the discharged air is not used to dry the clothes in the drum, resulting in heat loss and reduced thermal efficiency.

[0009] Therefore, in recent years, clothing processing devices with heat pump cycles have emerged, which recover energy discharged from the drum and use it to heat the air flowing into the drum, thereby improving energy efficiency.

[0010] The condenser-type garment processing device of Patent Document 1 includes: a drum 1, into which the garment to be dried is placed; a circulation pipe 2, providing a flow path for air to circulate through the drum 1; a circulation fan 3, causing the circulating air to flow along the circulation pipe 2; and a heat pump cycle 4, having an evaporator 5 and a condenser 6 connected in series with the circulation pipe 2 for the air circulating along the circulation pipe 2 to pass through.

[0011] The heat pump cycle 4 may have: circulation piping forming a circulation path to allow refrigerant to circulate via the evaporator 5 and the condenser 6; and a compressor 7 and an expansion valve 8, which are disposed in the circulation piping between the evaporator 5 and the condenser 6.

[0012] The heat pump cycle 4, as described above, transfers the heat energy of the air passing through the drum 1 to the refrigerant through the evaporator 5, and then transfers the heat energy of the refrigerant to the air flowing into the drum 1 through the condenser 6.

[0013] Here, both the evaporator and condenser use ordinary heat exchangers, which have the disadvantages of reduced heat exchange efficiency and increased manufacturing cost and difficulty of the heat exchangers.

[0014] In the case of Patent Document 2, a manifold 20 on both sides, a plurality of pipes 30 connected to the manifold, and a plurality of fins 4 of the connecting pipe are disclosed.

[0015] In the case of Patent Document 2, although a microchannel heat exchanger is disclosed, the tubes are arranged in multiple rows. Therefore, in order to improve the heat exchange capacity, multiple manifolds and connecting pipes between the manifolds are required. However, when using multiple manifolds and connecting pipes, there is a problem that multiple additional structures are required, and the manufacturing process of connecting them is complex.

[0016] Existing technical documents

[0017] Patent documents

[0018] Patent Document 1: Korean Publication No. 2016-0069333

[0019] Patent Document 2: Korean Publication No. 2018-0040330 Summary of the Invention

[0020] The problem to be solved by the present invention is to provide a heat exchanger and a clothing treatment device including the heat exchanger, wherein the heat exchanger uses a microchannel type heat exchanger as a condenser of the clothing treatment device, thereby improving the heat exchange efficiency.

[0021] Another problem to be solved by the present invention is to provide a garment processing device that uses a multi-row microchannel type heat exchanger as the condenser of the garment processing device, thereby simplifying the manufacturing process and reducing manufacturing costs.

[0022] Another problem to be solved by the present invention is to provide a garment handling device that uses only two manifolds and flat tubes connecting them, as well as fins, thereby reducing the flow resistance of the refrigerant.

[0023] Another problem to be solved by the present invention is to provide a clothing treatment device that increases condensation heat and improves power consumption by using the size relationship between the flat tube, fins and curved sections.

[0024] Another problem to be solved by the present invention is to provide a clothing treatment device that balances the heat exchange between the condenser and the evaporator by adjusting the cross-sectional area of ​​the condenser tube and the cross-sectional area of ​​the evaporator tube, and can achieve stable operation by ensuring the subcooling and superheating of the cycle.

[0025] The subject matter of this invention is not limited to the subject matter mentioned above, and those skilled in the art can clearly understand other subject matters not mentioned from the following description.

[0026] The garment processing apparatus of the present invention is characterized by improving efficiency by adjusting the cross-sectional area of ​​the condenser tube and the cross-sectional area of ​​the evaporator tube.

[0027] Specifically, the present invention is characterized by comprising: a heat pump having an evaporator, a compressor, a condenser, and an expansion valve, for applying heat to air circulating in a drum; and an air flow path forming a movement path to allow the air to pass through and circulate in the drum; the condenser comprising: a plurality of condensing refrigerant tubes in which refrigerant flows; and condensing fins for conducting heat from the condensing refrigerant tubes; the evaporator comprising: a plurality of evaporating refrigerant tubes in which refrigerant flows; and evaporating fins for conducting heat from the evaporating refrigerant tubes; the condensing refrigerant tubes comprising a plurality of channels for refrigerant flow; the cross-sectional area of ​​each channel being smaller than the cross-sectional area of ​​each evaporating refrigerant tube; and the sum of the cross-sectional areas of the plurality of condensing refrigerant tubes divided by the sum of the cross-sectional areas of the plurality of evaporating refrigerant tubes having a value of 1.3 or less.

[0028] The sum of the cross-sectional areas of the plurality of condensing refrigerant tubes divided by the sum of the cross-sectional areas of the plurality of evaporating refrigerant tubes can be greater than 1.1 and less than 1.3.

[0029] The condenser refrigerant tube and the condenser fins may contain aluminum.

[0030] The evaporating refrigerant tube may contain aluminum.

[0031] The cross-section of the evaporating refrigerant tube can be circular, and the cross-section of the condensing refrigerant tube can be a shape in which the length in the direction parallel to the airflow direction is longer than the length in the direction intersecting the airflow direction.

[0032] The evaporative refrigerant tubes can be arranged in four to eight rows in the airflow direction, and two adjacent rows of evaporative refrigerant tubes can be located in a position that does not overlap in the airflow direction.

[0033] The distance between the evaporator and the condenser can be greater than the width of the evaporator in the direction of airflow.

[0034] The condenser may further include: a first manifold connected to one end of each of the condensing refrigerant tubes; and a second manifold connected to the other end of each of the condensing refrigerant tubes; each of the condensing refrigerant tubes may include a first flat portion, a second flat portion, and a curved portion located between the first flat portion and the second flat portion; at least a portion of the curved portion may include a curved shape.

[0035] The condenser fins may include: an inner portion located at a position that overlaps with the plurality of flat tubes when viewed in a first direction which is the extension direction of the first manifold; and an outer portion located at a position that does not overlap with the plurality of flat tubes when viewed in the first direction.

[0036] The curved section may include a first twisting segment, a second twisting segment, and a connecting segment between the first twisting segment and the second twisting segment.

[0037] The radii of curvature of the first torsion section and the second torsion section may be larger than the radius of curvature of the connecting section.

[0038] When viewed in the first direction, the planar areas of the first torsion segment and the second torsion segment can be larger than the planar area of ​​the connecting segment.

[0039] One end of the first twisted section can be connected to the first flat portion; one end of the second twisted section can be connected to the second flat portion.

[0040] A portion of the first torsion section and the second torsion section may include a straight line shape.

[0041] The width of the first torsional section as observed in the first direction may decrease as it approaches the connecting section from the first flat portion.

[0042] The angle of inclination formed by the largest surface of the first torsion section and the largest surface of the first flat portion can increase as one approaches the connecting section from the first flat portion.

[0043] The angle of inclination formed by the largest surface of the second twisted section and the largest surface of the second flat portion can increase as one approaches the connecting section from the second flat portion.

[0044] The condenser fins may further include: a plurality of first fins located between first flat portions adjacent to each other in the first direction; and a plurality of second fins disposed between second flat portions adjacent to each other in the first direction; a portion of the first fins may protrude from the first flat portion toward the second flat portion, and a portion of the second fins may protrude from the second flat portion toward the first flat portion.

[0045] The first flat portion can be connected to the first manifold, and the second flat portion can be connected to the second manifold.

[0046] The width of the first fin can be greater than the width of the first flat portion, and the width of the second fin can be greater than the width of the second flat portion.

[0047] The garment processing device of the present invention has one or more of the following effects.

[0048] First, the present invention, by bending the middle part of a plurality of flat tubes arranged between two manifolds, arranges the flat tubes with a plurality of channels into multiple rows that intersect the direction of air movement, thereby making the connection between the manifold and the refrigerant pipe, as well as the manifold and the connecting pipe, easier to connect, simpler in structure, easier to manufacture, lower in manufacturing cost, and reduced in refrigerant flow resistance.

[0049] Secondly, according to the present invention, the portion of the flat tube that is bent does not have fins arranged between a plurality of flat tubes, thereby having the advantages of reducing manufacturing costs and making it easier to bend the flat tube.

[0050] Third, according to the present invention, when bending a flat tube, if bending is performed on a horizontal plane when the widest face of the flat tube is parallel to the horizontal direction, a single rod can be used to bend the vertically spaced flat tubes at once, thereby having the advantage of easily bending a rectangular flat tube by twisting the curved portion during bending.

[0051] Fourth, according to the present invention, for a condenser that requires a large amount of heat to reheat the air in the airflow path and supply it to the outer barrel, microchannels are used and configured in multiple rows, thereby having the advantages of easy temperature adjustment of the air supplied to the outer barrel, easy counterflow configuration, and improved heat exchange performance.

[0052] Fifth, according to the present invention, when condensers are arranged in multiple rows in a confined machine room, the pipes supplying refrigerant to the condensers and the pipes from which refrigerant flows out of the condensers are arranged in the same direction, and the refrigerant pipes of the evaporators are also arranged in the same direction as the condensers. Therefore, it has the advantage of minimizing the length of the refrigerant piping connecting the condensers and evaporators to the compressor and expansion valve, and reducing the increase in flow resistance caused by the refrigerant piping.

[0053] Sixth, according to the present invention, in the mechanical chamber of the garment processing device, a microchannel heat exchanger is used as a condenser and a finned tube heat exchanger is used as an evaporator. Since the evaporator requires less energy, a finned tube heat exchanger with low manufacturing cost is used. For the condenser, which requires a large amount of heat to reheat the air in the airflow path and supply it to the outer drum, a microchannel heat exchanger is used. Therefore, it has the advantages of improving heat exchange performance, reducing air supply resistance, and reducing manufacturing cost.

[0054] Seventh, according to the present invention, both the evaporator and the condenser are made of aluminum, thus having the advantages of improving the corrosion resistance of the airflow path of the garment treatment device with high moisture content, improving the reliability of the garment treatment device, and preventing galvanic corrosion caused by the mixing of copper and aluminum.

[0055] Eighth, according to the present invention, it has the advantages of being able to balance the heat exchange between the condenser and the evaporator by adjusting the cross-sectional area ratio of the refrigerant tubes of the evaporator and the condenser, and being able to operate stably by ensuring the subcooling and superheat of the cycle. Attached Figure Description

[0056] Figure 1 This is a schematic diagram illustrating the flow of air and refrigerant in a clothing handling apparatus according to an embodiment of the present invention.

[0057] Figure 2 This is a schematic diagram showing the configuration of a garment processing apparatus according to an embodiment of the present invention.

[0058] Figure 3 This is a diagram showing the mechanical chamber and airflow path of a garment processing apparatus according to an embodiment of the present invention.

[0059] Figure 4 It is shown Figure 3 Diagram of evaporator and condenser.

[0060] Figure 5 It is shown Figure 3 A 3D view of the condenser.

[0061] Figure 6 It is shown Figure 3 A top view of the condenser.

[0062] Figure 7 It is shown Figure 3 Front view of the condenser.

[0063] Figure 8 It is Figure 6 A magnified portion of the image.

[0064] Figure 9 yes Figure 3 A side view of the condenser.

[0065] Figure 10 yes Figure 3 Another side view of the condenser.

[0066] Figure 11 It is along Figure 8 A sectional view cut along line 11-11′.

[0067] Figure 12 It is Figure 11 A magnified image of a portion of the area.

[0068] Figure 13 yes Figure 11 A partial 3D view.

[0069] Figures 14 to 16 This is a diagram illustrating the manufacturing process of a heat exchanger according to an embodiment of the present invention.

[0070] Figure 17 It is along Figure 4 A sectional view cut along line 17-17′.

[0071] Figure 18 It is along Figure 4 A sectional view cut along the 18-18′ line.

[0072] Figure 19 This is a top view showing a condenser according to another embodiment of the present invention.

[0073] Figure 20 This is a top view showing a condenser according to another embodiment of the present invention.

[0074] Explanation of reference numerals in the attached figures

[0075] 150: Airflow path; 163: Compressor

[0076] 164: Expansion valve; 300: Evaporator

[0077] 400: Condenser Detailed Implementation

[0078] The advantages and features of the present invention, as well as the methods of implementing them, will become apparent upon reference to the accompanying drawings and the detailed description of the embodiments. However, the invention is not limited to the embodiments disclosed below and can be implemented in different ways. The embodiments are provided to fully disclose the contents of the invention and to fully inform those skilled in the art of the scope of the invention, which is defined only by the scope of the claims. Throughout the specification, the same reference numerals may refer to the same constituent elements.

[0079] As shown in the figure, terms such as "below," "below," "lower," "above," and "upper," used as relative terms relating to space, can be used to facilitate the description of the relationship between one constituent element and another. In addition to the directions shown in the figures, these relative terms relating to space should also be understood to include terms indicating different orientations of constituent elements during use or action. For example, if the constituent elements illustrated in the figures are inverted, a constituent element described as being "below" or "below" another constituent element can be placed "above" another constituent element. Therefore, the exemplary term "below" can include both "below" and "above." Constituent elements can be oriented in other directions; therefore, the relative terms relating to space can be interpreted according to orientation.

[0080] The terminology used in this specification is for illustrative purposes only and is not intended to limit the invention. In this specification, unless otherwise specified, singular expressions include plural expressions. The terms "comprises" and / or "comprising" as used in this specification do not imply that the referenced elements, steps, and / or actions exclude the presence or addition of more than one other element, step, and / or action.

[0081] Unless otherwise defined, all terms used in this specification (including scientific and technical terms) are to be used in the sense that is commonly understood by those skilled in the art. Furthermore, unless explicitly defined, terms as defined in commonly used dictionaries should not be interpreted ideally or excessively.

[0082] In the accompanying drawings, for ease of description and clarity, the thickness or dimensions of each component are exaggerated, omitted, or shown in a generalized manner. Furthermore, the dimensions or areas of each component do not perfectly reflect their actual dimensions or areas.

[0083] Furthermore, the angles and directions mentioned in the description of the structure of the embodiments are based on the figures shown. In the specification, when the reference points and positional relationships for angles are not explicitly mentioned in the description of the structure constituting the embodiments, please refer to the relevant figures.

[0084] The present invention will now be described in detail with reference to the accompanying drawings.

[0085] Figure 1 This is a schematic diagram illustrating the flow of air and refrigerant in a clothing handling apparatus according to an embodiment of the present invention. Figure 2 This is a schematic diagram showing the configuration of a garment processing apparatus according to an embodiment of the present invention.

[0086] Reference Figure 1 and Figure 2 The garment processing apparatus 100 of the present invention exemplifies a drum-type dryer, which may include a housing 110, a drum 130, a drive unit (not shown), a blower fan 170, and a heat pump 160, wherein the air of the drum 130 is connected to the heat pump 160 through an air flow path 150.

[0087] Here, the housing 110 forms the appearance of the product and may have: a door 112, provided at the front for inserting clothing; and a base 114, on which the internal structure of the clothing handling device 100 is disposed.

[0088] On the other hand, the drum 130 can rotate around a rotation axis disposed inside the chamber in a horizontal direction or at a predetermined angle. Furthermore, the drum 130 is a hollow cylindrical shape and provides a space for loading and drying clothing.

[0089] The roller 130 is formed in a cylindrical shape with openings at the front and rear. A front support portion 132 is provided at the front of the roller 130 to support the roller 130 in a rotatable manner. In addition, a rear support portion 133 is provided at the rear of the roller 130 to support the roller 130 in a rotatable manner.

[0090] Furthermore, a front roller 142 and a rear roller 143 can be additionally provided at the lower front and rear of the drum 130 to support the drum 130 in a rotatable roller form. That is, the front support part 132 and the rear support part 133 block the front and back of the drum 130 to form a drying space for the object to be dried, and at the same time serve to support the front and rear ends of the drum 130.

[0091] On the other hand, an inlet 132b for feeding the object to be dried into the drum 130 is formed in the front support portion 132, and the inlet is selectively opened and closed by a door 112. Additionally, an air outlet 132a connected to the air flow path 150 described later is provided at the lower part of the front support portion 132. The intake flow path 151 of the air flow path 150, described later, communicates with the air outlet 132a.

[0092] Furthermore, an air inlet 133a with a plurality of through holes is formed in the rear support portion 133 to supply air to the roller 130. The exhaust passage 152 of the air flow path 150, described later, is connected to the air inlet 133a.

[0093] In order to effectively dry the clothes that are to be dried, lifting ribs 131a for tumbling the clothes can also be provided on the inner circumferential surface of the drum 130.

[0094] In addition, the drive unit uses a motor (not shown) to provide rotational force. The output shaft of the motor and the roller 130 are connected by a power transmission mechanism such as a transmission belt. The rotational force of the motor is transmitted to the roller 130, which can make the roller 130 rotate.

[0095] Furthermore, the airflow path 150 can form a closed loop for air circulation by connecting it to the roller 130. For example, the airflow path 150 can be formed in the form of a pipe. An intake flow path 151 for discharging air is formed at the lower part of the front support portion 132 of the roller 130, and an exhaust flow path 152 for supplying air is formed at the rear support portion 133 of the roller 130.

[0096] On the other hand, the air supply fan 170 may be located inside the portion of the air flow path 150 that extends from the intake flow path 151 to the evaporator 300 of the heat pump 160, or inside the portion of the air flow path 150 that extends from the condenser 400 of the heat pump 160 to the exhaust flow path 152.

[0097] Here, the air supply fan 170 can be driven by an additional fan motor, which can apply power to the air to make it pass through the inside of the drum 130, so that the air discharged from the drum 130 can be circulated back into the drum 130.

[0098] Additionally, a lint filter 162 for filtering lint from the circulating air is provided in the intake flow path 151 (see reference). Figure 3 As air drawn into the suction flow path 151 by the roller 130 passes through the lint filter 162, the lint filter 162 can capture the lint contained in the air.

[0099] Therefore, the moisture in the clothing (also referred to as "fabric") evaporates due to the hot air supplied to the inside of the drum 130, and the air passing through the drum 130 is discharged from the drum 130 in a state containing the moisture evaporated from the clothing. The hot and humid air discharged from the drum 130 moves along the air flow path 150 and is heated by receiving heat from the heat pump 160 before circulating back into the drum 130.

[0100] On the other hand, the heat pump 160 includes an evaporator 300, a compressor 163, a condenser 400, and an expansion valve 164. The heat pump 160 can use a refrigerant as the working fluid. The refrigerant moves along a refrigerant piping 165, which forms a closed loop for refrigerant circulation. The evaporator 300, compressor 163, condenser 400, and expansion valve 164 are connected via the refrigerant piping 165, and the refrigerant passes sequentially through the evaporator 300, compressor 163, condenser 400, and expansion valve 164.

[0101] Here, the evaporator 300 is configured to communicate with the drum outlet in the air flow path 150, and recovers the heat of the air discharged from the drum 130 by exchanging heat with the refrigerant through the air discharged from the drum outlet, without discharging it to the outside of the dryer.

[0102] Furthermore, the condenser 400 is configured to communicate with the drum inlet in the air flow path 150, and by exchanging heat between the air passing through the evaporator 300 and the refrigerant, the heat absorbed by the refrigerant in the evaporator 300 is transferred to the air that will flow into the drum 130.

[0103] The compressor 163 produces a high-temperature, high-pressure refrigerant by compressing the refrigerant evaporated in the evaporator 300, and moves the high-temperature, high-pressure refrigerant along the refrigerant piping 165 to the condenser 400. The compressor 163 can be a variable frequency compressor 163 to control the amount of refrigerant discharged.

[0104] An expansion valve 164 is provided on a refrigerant pipe 165 extending from the condenser 400 to the evaporator 300, and produces a low-temperature, low-pressure refrigerant by expanding the refrigerant condensed in the condenser 400 and transferring it to the evaporator 300.

[0105] The movement path of the refrigerant as described above is explained. The refrigerant flows into the compressor 163 in a gaseous state and becomes a high-temperature and high-pressure state through compression by the compressor 163. The high-temperature and high-pressure refrigerant flows into the condenser 400 and releases heat to the air in the condenser 400, thereby changing from a gaseous state to a liquid state.

[0106] Next, the liquid refrigerant flows into the expansion valve 164 and is throttled by the expansion valve 164 (or including a capillary tube, etc.) to become a low-temperature and low-pressure state. The low-temperature and low-pressure liquid refrigerant flows into the evaporator 300 and absorbs heat from the air in the evaporator 300, thereby causing the refrigerant to evaporate from a liquid state to a gaseous state.

[0107] As described above, the heat pump 160 circulates the refrigerant repeatedly in the order of compressor 163, condenser 400, expansion valve 164, and evaporator 300, and provides a heat source to the air circulating to the drum 130.

[0108] On the other hand, the garment handling apparatus 100 of the present invention can supply pressurized air to the interior of the drum 130 separately from the circulating supply of heated air via the heat pump 160, thereby impacting the items to be dried inside the drum 130 while changing the movement path of the heated air inside the drum 130.

[0109] That is, the objects to be dried in the drum 130 may contain various forms of moisture depending on the material of the objects. By supplying pressurized air, the larger water molecules in the objects can be removed from the objects or broken into smaller water molecules, thereby allowing the moisture to be dried more quickly by heating the air.

[0110] Furthermore, the heated air supplied to the drum 130 moves from the air inlet 133a at the rear of the drum 130 to the air outlet 132a at the front of the drum 130, drying the objects inside the drum 130, and circulates between the drum 130 and the heat pump 160 through the air flow path 150. With this movement path of the heated air, the larger the contact area with the objects and the longer the contact time, the higher the degree of drying of the objects. Here, pressurized air supplied separately from the heated air can be supplied at a different location and along a different path with a higher pressure than the heated air, thereby impacting the objects while changing the path of the heated air within the drum 130, thus further accelerating the drying of moisture caused by the heated air.

[0111] On the other hand, in order to supply pressurized air to the inside of the roller 130, a pressurized air generating unit 200 may be provided to generate pressurized air; and a pressurized air nozzle 301 may be provided to inject the pressurized air generated by the pressurized air generating unit 200 into the inside of the roller 130.

[0112] The configuration of evaporator 300 and condenser 400 is described in detail below.

[0113] Figure 3 This is a diagram showing the mechanical chamber and airflow path portion of a garment handling apparatus according to an embodiment of the present invention. Figure 4 It is shown Figure 3 Diagram of evaporator 300 and condenser 400.

[0114] Reference Figure 3 and Figure 4 The evaporator 300 and condenser 400 can be located inside the airflow path 150. The evaporator 300 can be connected to the drum outlet, and the condenser 400 can be connected to the drum inlet.

[0115] On the other hand, the present invention may include a machine compartment 161, with a compressor 163, an expansion valve, and a refrigerant piping 165 located in the machine compartment 161. The machine compartment 161 may be configured adjacent to the airflow path 150.

[0116] Since the temperature of the hot and humid air discharged from the drum 130 is higher than the temperature of the refrigerant in the evaporator 300, the heat of the air is absorbed by the refrigerant in the evaporator 300 as it passes through the evaporator 300, causing the air to condense and produce condensate. Thus, the hot and humid air is dehumidified by the evaporator 300, and the condensate produced can be collected in an additional condensate tank (not shown) and discharged.

[0117] On the other hand, the heat source of the air absorbed by the evaporator 300 can be moved to the condenser 400 by means of refrigerant. In order to move the heat source from the evaporator 300 (low heat source section) to the condenser 400 (high heat source section), the compressor 163 can also be located between the evaporator 300 and the condenser 400.

[0118] On the other hand, the evaporator 300 can be a finned tube type heat exchanger. A finned tube type is a hollow tube with multiple fins in the form of a flat plate. The refrigerant flows along the inside of the tube, and as air passes between the multiple fins attached to the tube, the refrigerant and air can exchange heat with each other. Here, the fins are used to increase the heat exchange area between the air and the refrigerant.

[0119] For example, evaporator 300 may include a plurality of refrigerant evaporation pipes 310 for refrigerant flow and evaporation fins 320 for conducting heat from the refrigerant. Evaporator 300 may include an evaporation inlet pipe 391 for supplying refrigerant to the refrigerant evaporation pipes 310 and an evaporation outlet pipe 392 for refrigerant to flow out of the refrigerant evaporation pipes 310.

[0120] The evaporator refrigerant tube 310 and the evaporator fins 320 may contain aluminum or an aluminum alloy.

[0121] The evaporator inlet pipe 391 is connected to the expansion valve 164 and the evaporator refrigerant pipe 310, and the evaporator outlet pipe 392 is connected to the compressor 163 and the evaporator refrigerant pipe 310. The specific structure of the evaporator 300 will be discussed later. Figure 18 Please provide an explanation.

[0122] The condenser 400 may include a microchannel type heat exchanger. The condenser 400 includes condensing refrigerant tubes 410 having a plurality of channels 50a for refrigerant flow, condensing fins 420 for conducting heat from the condensing refrigerant tubes 410, and a first manifold 431 and a second manifold 433 located at both ends of each condensing refrigerant tube 410. Hereinafter, the condensing fins 420 may also be referred to as fins, and the condensing refrigerant tubes 410 as flat tubes 410.

[0123] The condenser 400 may include: a condenser inlet pipe 491 that supplies refrigerant to the flat tube 410; and a condenser outlet pipe 492 that allows refrigerant to flow out of the flat tube 410. The condenser inlet pipe 491 is connected to the compressor 163 and the flat tube 410, and the condenser outlet pipe 492 is connected to the expansion valve 164 and the flat tube 410. The condenser inlet pipe 491 may be interchangeable with the inlet pipe, and the condenser outlet pipe 492 may be interchangeable with the outlet pipe. The condenser inlet pipe 491 may be connected to a first manifold 431, and the condenser outlet pipe 492 may be connected to a second manifold 433.

[0124] The specific structure of condenser 400 will refer to Figures 5 to 9 Please provide an explanation.

[0125] If the condenser 400 uses a microchannel type heat exchanger, the temperature of the air passing through the condenser 400 can be increased compared to using a finned tube heat exchanger, and the air can be heated to the target temperature in a significantly shorter heat exchange time. Therefore, if the condenser 400 uses a microchannel type heat exchanger, the drying efficiency of the garment handling device can be improved.

[0126] Here, the cross-sectional area of ​​each channel 50a of the refrigerant tube in the condenser 400 is smaller than that of the refrigerant tube in the evaporator 300. Since the evaporator 300 does not require a large heat exchange capacity, a finned tube heat exchanger is preferred over a microchannel heat exchanger.

[0127] Air flowing within the airflow path 150 exchanges heat with the evaporator 300 and then flows into the condenser 400. At this time, if the evaporator 300 and the condenser 400 are configured too close together, the condensate produced in the evaporator 300 will flow into the condenser 400, resulting in a decrease in the heat exchange efficiency of the condenser 400.

[0128] To prevent condensate generated in evaporator 300 from flowing into condenser 400, the distance D1 between evaporator 300 and condenser 400 can be greater than the width W3 in the airflow direction of evaporator 300.

[0129] The width W3 of the evaporator 300 in the airflow direction can be greater than the width W4 of the condenser 400 in the airflow direction. The height H3 of the evaporator 300 can be less than the height H4 of the condenser 400.

[0130] Preferably, the distance D1 between the evaporator 300 and the condenser 400 can be greater than the sum of the width W3 of the evaporator 300 in the airflow direction and the width W4 of the condenser 400 in the airflow direction.

[0131] More preferably, the distance D1 between the condenser 400 and the condenser 400 can be 100mm to 250mm.

[0132] If the distance D1 between the condenser 400 and the evaporator 300 is greater than the sum of the width W3 in the airflow direction of the evaporator 300 and the width W4 in the airflow direction of the condenser 400, then the condensate generated by the airflow in the evaporator 300 will fall into the space between the condenser 400 and the evaporator 300.

[0133] The condensate inlet pipe 491 and the condensate outlet pipe 492 can be located in the same direction relative to the flat pipe 410. Specifically, the condensate inlet pipe 491 and the condensate outlet pipe 492 can extend from the flat pipe 410 toward the machine room.

[0134] More specifically, if the direction of airflow is defined as the front-to-back direction, then the condenser inlet pipe 491 and the condenser outlet pipe 492 extend to the right from the flat pipe 410.

[0135] If the condenser inlet pipe 491 and the condenser outlet pipe 492 are in the same direction relative to the flat pipe 410, the space required for configuring the refrigerant pipe can be reduced, the length of the refrigerant pipe can be reduced, and sufficient space can be ensured for the air flow path 150.

[0136] The evaporator inlet pipe 391 and the evaporator outlet pipe 392 may be located in the same direction relative to the evaporator refrigerant pipe 310. Specifically, the evaporator inlet pipe 391 and the evaporator outlet pipe 392 may extend from the evaporator refrigerant pipe 310 toward the machine room.

[0137] More specifically, the evaporator inlet pipe 391 and the evaporator outlet pipe 392 extend to the right from the evaporator refrigerant pipe 310.

[0138] If the evaporator inlet pipe 391 and the evaporator outlet pipe 392 are in the same direction relative to the evaporator refrigerant pipe 310, the space required for configuring the refrigerant pipe can be reduced, the length of the refrigerant pipe can be reduced, and sufficient space can be ensured for the air flow path 150.

[0139] Preferably, the evaporator inlet pipe 391, the evaporator outlet pipe 392, the condenser inlet pipe 491, and the condenser outlet pipe 492 can extend from the air flow path 150 in the same direction. The evaporator inlet pipe 391, the evaporator outlet pipe 392, the condenser inlet pipe 491, and the condenser outlet pipe 492 extend from the air flow path 150 to the right.

[0140] The structure of the condenser 400 will now be described in detail. The condenser 400 includes the heat exchanger of the present invention. The description of the condenser 400 is the same as that of the heat exchanger.

[0141] Figure 5 It is shown Figure 3 A 3D view of the condenser 400. Figure 6 It is shown Figure 3 Top view of the condenser 400 Figure 7 It is shown Figure 3 Front view of condenser 400 Figure 8 It is Figure 6 A magnified portion of the image. Figure 9 yes Figure 3 A side view of the condenser 400. Figure 10 yes Figure 3 Another side view of the condenser 400.

[0142] Reference Figures 5 to 10 Condenser 400 is a microchannel type heat exchanger. Condenser 400 is made of aluminum.

[0143] In the condenser 400, a plurality of flat tubes 50 may be located in the airflow direction. That is, the condenser 400 may include a plurality of flat tubes 50 stacked in a vertical direction intersecting the airflow direction, a first manifold 431 and a second manifold 433 located at the horizontal ends of the plurality of flat tubes 50, and the plurality of flat tubes 50 bend in the middle, so that the plurality of flat tubes 50 form a plurality of columns along the airflow direction.

[0144] Specifically, the plurality of flat tubes 50 can be arranged in a first column, a second column, a third column, and a fourth column in the path of external air flow. External air can exchange heat with the fourth column for the first time, with the third column for the second time, with the second column for the third time, and finally with the first column.

[0145] The first manifold 431 and the second manifold 433 extend in a first direction. Specifically, the first manifold 431 and the second manifold 433 may extend in an upward direction. An inlet pipe 491 is connected to the first manifold 431 for refrigerant to flow in, and an outlet pipe 492 is connected to the second manifold 433.

[0146] The flat tube 50 may include an upper surface 51a and a lower surface 51b facing each other, and two side surfaces 51c and 51d connecting the two ends of the upper surface 51a and the lower surface 51b. The upper surface 51a and the lower surface 51b may have a larger area than the side surfaces 51c and 51d. Thus, the cross-sectional shape of the flat tube 50 may be a rectangle that is longer in the horizontal direction. Preferably, the upper surface 51a and the lower surface 51b may be configured to be parallel to the horizontal plane.

[0147] Each flat tube 50 may include a first flat portion 551, a second flat portion 552, and a curved portion 500 located between the first flat portion 551 and the second flat portion 552.

[0148] Each flat tube 50 may include a third flat portion 553, a fourth flat portion 554, and a plurality of curved portions 500 located between the first flat portion 551 and the second flat portion 552.

[0149] Here, the first flat portion 551, the second flat portion 552, the third flat portion 553, and the fourth flat portion 554 can be unbent regions. The first flat portion 551, the second flat portion 552, the third flat portion 553, and the fourth flat portion 554 can extend parallel to the horizontal direction. The first flat portion 551, the second flat portion 552, the third flat portion 553, and the fourth flat portion 554 can be arranged parallel to each other.

[0150] The first flat portion 551, the second flat portion 552, the third flat portion 553, and the fourth flat portion 554 can define the columns of the aforementioned flat tube 50.

[0151] The first flat portion 551, the second flat portion 552, the third flat portion 553, and the fourth flat portion 554 may be located in a position that overlaps in the airflow direction. Specifically, the first flat portion 551, the second flat portion 552, the third flat portion 553, and the fourth flat portion 554 are located in a position that overlaps in the front-back direction.

[0152] The third flat portion 553 can be configured to be closer to the first flat portion 551 than the second flat portion 552, and the fourth flat portion 554 can be configured to be closer to the second flat portion 552 than the first flat portion 551.

[0153] The curved portion 500 is a bent section of the flat tube 50, and the curved portion 500 may be located between the first flat portion 551 and the second flat portion 552. The curved portion 500 may connect one end of the first flat portion 551 and one end of the second flat portion 552. At least a portion of the curved portion 500 may include a curved shape.

[0154] Of course, a plurality of curved portions 500 can be located between the first flat portion 551 and the second flat portion 552.

[0155] Specifically, such as Figure 6 As shown, between the first manifold 431 and the second manifold 433, there are three curved sections 500, a first flat section 551, a second flat section 552, a third flat section 553, and a fourth flat section 554, so that the flat tubes 50 can be arranged in four rows. At this time, the curved sections 500 can be arranged alternately from left to right as they approach from the front to the rear.

[0156] The curved portion 500 may include a first curved portion 511 connecting the first flat portion 551 and the third flat portion 553, a second curved portion 512 connecting the third flat portion 553 and the fourth flat portion 554, and a third curved portion 513 connecting the fourth flat portion 554 and the second flat portion 552.

[0157] A plurality of fins 60 may be disposed in a region of adjacent flat tubes 50. Specifically, the plurality of fins 60 may include a first fin 641 disposed between adjacent first flat portions 551, a second fin 642 disposed between adjacent second flat portions 552, a third fin 643 disposed between adjacent third flat portions 553, and a fourth fin 644 disposed between adjacent fourth flat portions 554.

[0158] Specifically, the refrigerant pipe 50 at the top is defined as the first refrigerant pipe 50, 51, and the refrigerant pipe 50 located below the first refrigerant pipe 50, 51 is defined as the second refrigerant pipe 50, 52. The nth refrigerant pipe and the nth fin 60 can be defined in this way. The first fin 60, 61 can be arranged between the first flat portion 551 of the first refrigerant pipe 50, 51 and the first flat portion 551 of the second refrigerant pipe 50, 52, and the first fin 60, 61 can also be arranged between the second flat portion 552 of the first refrigerant pipe 50, 51 and the second flat portion 552 of the second refrigerant pipe 50, 52.

[0159] The plurality of fins 60 are not arranged between the curved portions 500 of the adjacent flat tubes 50. Because the plurality of fins 60 are not arranged between the curved portions 500, space for twisting when the flat tubes 50 are bent can be ensured. The detailed structure of the fins 60 will be described later.

[0160] A portion of the first fin 641 may protrude from the first flat portion 551 toward the second flat portion 552. That is, a portion of the first fin 641 may be located in a position that does not overlap with the first flat portion 551 when viewed from above. The width of the first fin 641 may be greater than the width of the first flat portion 551. A portion of the first fin 641 may protrude further downward than the first flat portion 551.

[0161] A portion of the second fin 642 may protrude from the second flat portion 552 toward the first flat portion 551. That is, a portion of the second fin 642 may be located in a position that does not overlap with the second flat portion 552 when viewed from above. The width of the second fin 642 may be greater than the width of the second flat portion 552. A portion of the second fin 642 may protrude upwards more than the second flat portion 552.

[0162] A portion of the third fin 643 may protrude from the third flat portion 553 toward the first flat portion 551. That is, a portion of the third fin 643 may be located in a position that does not overlap with the third flat portion 553 when viewed from above. The width of the third fin 643 may be greater than the width of the third flat portion 553. A portion of the third fin 643 may protrude upwards more than the third flat portion 553.

[0163] A portion of the fourth fin 644 may protrude from the fourth flat portion 554 toward the second flat portion 552. That is, a portion of the fourth fin 644 may be located in a position that does not overlap with the fourth flat portion 554 when viewed from above. The width of the fourth fin 644 may be greater than the width of the fourth flat portion 554. A portion of the fourth fin 644 may protrude further downward than the fourth flat portion 554.

[0164] As described above, if the fins protrude from the flat tube toward the adjacent flat sections, it has the advantage of reducing the risk of fin breakage when bending the flat tube with the curved section as the center, and can solve the problem of difficulty in drainage due to the surface tension of water between the fins.

[0165] The following is a detailed explanation of the structure of the curved section 500.

[0166] In particular, refer to Figures 7 to 9 The curved section 500 may include a first torsion section 533, a second torsion section 534, and a connecting section 540.

[0167] The curved portion 500 is the portion that is located between the first flat portion 551 and the second flat portion 552 and is curved.

[0168] The curved portion 500 may be a portion in which one end of the first flat portion 551 and the second flat portion 552 are connected to each other in the longitudinal direction and bent (see reference). Figure 8 ).

[0169] The curved portion 500 may be a portion in which one end of the first flat portion 551 and the third flat portion 553 are connected to each other in the longitudinal direction and bent. The curved portion 500 may be a portion in which one end of the third flat portion 553 and the fourth flat portion 554 are connected to each other in the longitudinal direction and bent.

[0170] The following description is based on the curved portion 500 that connects the first flat portion 551 and the third flat portion 553, but this description can also be directly applied to the curved portion 500 that connects other flat portions.

[0171] To bend multiple flat tubes 50 at once using a single rod, bending can be performed around a bending axis C2 parallel to the vertical direction. However, when bending around the bending axis C2, which is parallel to the vertical direction, the upper surface 51a and lower surface 51b of the wide surface of the flat tube 50 are parallel to the horizontal direction. Therefore, there is a problem that one side of the flat tube 50 may deform significantly during bending, leading to breakage.

[0172] Therefore, the curved portion 500 can be bent around the bending axis C2, which is parallel to the vertical direction, but the curved portion 500 is twisted relative to the first flat portion 551 and the third flat portion 553, so that the upper surface 51a and the lower surface 51b of the curved portion 500 are mainly deformed, thereby reducing the stress generated when the flat tube 50 is bent.

[0173] Here, torsion can refer to the upper surface 51a of the first flat portion 551 and the upper surface of the curved portion 500 being at an angle to each other.

[0174] One end of the first torsion section 533 is connected to the first flat portion 551, and the other end of the first torsion section 533 is connected to the connecting section 540. One end of the second torsion section 534 is connected to the third flat portion 553, and the other end of the second torsion section 534 is connected to the connecting section 540.

[0175] The first torsion section 533 and the second torsion section 534 are areas in which the flat tube 50 is torsioned to increase the deformation of the connecting section 540.

[0176] A portion of the first torsion segment 533 and the second torsion segment 534 may include a straight line shape. Specifically, the portion of the first torsion segment 533 near the first flat portion 551 may be a straight line shape, and the portion of the second torsion segment 534 near the third flat portion 553 may be a straight line shape.

[0177] Specifically, the first torsional section 533 may include a first outer edge 535 and a first inner edge 537. The first outer edge 535 is configured to be further away from the bending axis C2 than the first inner edge 537. The first outer edge 535 may be connected to one side surface 51d of the first flat portion 551, and the first inner edge 537 may be connected to the other side surface 51c of the first flat portion 551.

[0178] The first torsion section 533 may include an upper surface connecting the upper end of the first outer edge 535 and the upper end of the first inner edge 537, and a lower surface connecting the lower end of the first outer edge 535 and the lower end of the first inner edge 537.

[0179] A portion of the first inner edge 537 is a straight line, and another portion of the first inner edge 537 is a curved line. A portion of the first outer edge 535 is a straight line, and another portion of the first outer edge 535 is a curved line.

[0180] The portion of the first inner edge 537 adjacent to the first flat portion 551 is straight, while another portion of the first inner edge 537 adjacent to the connecting section 540 is curved. The portion of the first outer edge 535 adjacent to the first flat portion 551 is straight, while another portion of the first outer edge 535 adjacent to the connecting section 540 is curved.

[0181] The length of the first outer edge 535 is longer than the length of the first inner edge 537. In the first outer edge 535, the length of the curved shape can be longer than the length of the straight shape, and in the first inner edge 537, the length of the straight shape can be longer than the length of the curved shape.

[0182] The width of the first torsional section 533 when viewed in the vertical direction decreases as it approaches the connecting section 540 from the first flat portion 551.

[0183] The angle of inclination formed by the largest surface of the first torsion section 533 and the largest surface of the first flat portion 551 can increase as the first flat portion 551 approaches the connecting section 540. The angle of inclination A1 formed by the upper surface 51a of the first torsion section 533 and the upper surface of the first flat portion 551 can increase as the first flat portion 551 approaches the connecting section 540.

[0184] The height of the first torsion section 533 can increase as it approaches the connecting section 540 from the first flat section 551.

[0185] The second torsion section 534 can be configured symmetrically with respect to the first torsion section 533, based on the connecting section 540.

[0186] Specifically, the second torsional section 534 may include a second outer edge 536 and a second inner edge 538. The second outer edge 536 is configured to be further away from the bending axis C2 than the second inner edge 538. The second outer edge 536 may be connected to one side surface of the third flat portion 553, and the second inner edge 538 may be connected to the other side surface of the third flat portion 553.

[0187] The second torsional section 534 may include an upper surface connecting the upper end of the second outer edge 536 and the upper end of the second inner edge 538, and a lower surface connecting the lower end of the second outer edge 536 and the lower end of the second inner edge 538.

[0188] A portion of the second inner edge 538 is a straight line, and another portion of the second inner edge 538 is a curved line. A portion of the second outer edge 536 is a straight line, and another portion of the second outer edge 536 is a curved line.

[0189] The portion of the second inner edge 538 adjacent to the third flat portion 553 is straight, while another portion of the second inner edge 538 adjacent to the connecting section 540 is curved. The portion of the second outer edge 536 adjacent to the third flat portion 553 is straight, while another portion of the second outer edge 536 adjacent to the connecting section 540 is curved.

[0190] The length of the second outer edge 536 is longer than the length of the second inner edge 538. In the second outer edge 536, the length of the curved shape can be longer than the length of the straight shape, and in the second inner edge 538, the length of the straight shape can be longer than the length of the curved shape.

[0191] The width of the second torsional section 534 when viewed in the vertical direction decreases as it approaches the connecting section 540 from the third flat section 553.

[0192] The angle of inclination formed by the largest surface of the second torsion section 534 and the largest surface of the third flat portion 553 can increase as the third flat portion 553 approaches the connecting section 540. The angle of inclination A1 formed by the upper surface 51a of the second torsion section 534 and the upper surface 51a of the third flat portion 553 can increase as the third flat portion 553 approaches the connecting section 540.

[0193] The height of the second torsional section 534 can increase as it approaches the connecting section 540 from the third flat section 553.

[0194] The connecting section 540 is located between the first torsion section 533 and the second torsion section 534. One end of the connecting section 540 is connected to the first torsion section 533, and the other end of the connecting section 540 is connected to the second torsion section 534.

[0195] The connecting section 540 includes a short edge 541 and a long edge 542 that is longer than the short edge 541. The long edge 542 is located further away from the bending axis C2 than the short edge 541.

[0196] The rear end of the long edge 542 is connected to the first outer edge 535 of the first twist segment 533, and the front end of the long edge 542 is connected to the second outer edge 536 of the second twist segment 534. The rear end of the short edge 541 is connected to the first inner edge 537 of the first twist segment 533, and the front end of the short edge 541 is connected to the second inner edge 538 of the second twist segment 534.

[0197] The radius of curvature of the longer edge 542 is larger than that of the shorter edge 541. The shorter edge 541 can be located at a higher position than the longer edge 542.

[0198] The connecting section 540 includes a first horizontal end 543 connected to the first torsion section 533 and a second horizontal end 544 connected to the second torsion section 534. The first horizontal end 543 is the rear end of the connecting section 540, and the second horizontal end 544 is the front end of the connecting section 540.

[0199] The tilt angle A2 formed by the largest surface of the connecting section 540 and the largest surface of the first flat portion 551 is the largest between the first horizontal end 543 and the second horizontal end 544, and the smallest between the first horizontal end 543 and the second horizontal end 544.

[0200] The angle of inclination formed by the largest surface of the connecting section 540 and the upper surface 51a of the first flat portion 551 is the largest between the first horizontal end 543 and the second horizontal end 544, and the smallest between the first horizontal end 543 and the second horizontal end 544.

[0201] The tilt angle A2 formed by the largest surface of the connecting section 540 and the upper surface 51a of the first flat portion 551 can be larger than the tilt angle A1 formed by the first torsion section 533 and the upper surface 51a of the first flat portion 551 and the tilt angle formed by the second torsion section 534 and the upper surface 51a of the first flat portion 551.

[0202] Preferably, the tilt angle A2 formed by the largest surface of the connecting section 540 and the upper surface 51a of the first flat portion 551 can be less than 90 degrees and greater than 80 degrees.

[0203] The radius of curvature of a portion of the first torsion segment 533 and the second torsion segment 534 may be larger than the radius of curvature R2 of the connecting segment 540. The radius of curvature R2 of the connecting segment 540 may be the average of the radii of curvature of the long edge 542 and the short edge 541.

[0204] The radius of curvature R1 of the first outer edge 535 of the first torsion section 533 and the second outer edge 536 of the second torsion section 534 can be larger than the radius of curvature of the long edge 542 and the short edge 541 of the connecting section 540.

[0205] A portion of the curved portion 500 of any one flat tube 50 may be located at a position where the curved portion 500 of another flat tube 50 configured adjacent to any one flat tube 50 overlaps in the horizontal direction.

[0206] Any short edge 541 of the plurality of flat tubes 50 can be located at a position that overlaps with any adjacent long edge 542. The long edge 542 of the first flat tube 50 is located at a position that overlaps with the short edge 541 of the second flat tube 50 in the horizontal direction.

[0207] When viewed from above in the first direction, the planar areas of the first torsion section 533 and the second torsion section 534 can be larger than the planar area of ​​the connecting section 540.

[0208] The uppermost flat tube 51 in the flat tube 50 can omit the curved portion 500, consisting only of the first flat portion 551 and the third flat portion 553. The first flat portion 551 and the third flat portion 553 of the uppermost flat tube 51 in the flat tube 50 can have an upper curved portion 59. The upper curved portion 59 is formed by bending one end of the first flat portion 551 and the third flat portion 553 in one direction. One end of the first flat portion 551 and the third flat portion 553 in the upper curved portion 59 can be bent downwards.

[0209] The lowermost flat tube 50 may omit the curved portion 500, consisting only of a first flat portion 551 and a third flat portion 553. The first flat portion 551 and the third flat portion 553 at the lowermost end of the flat tube 50 may have a lower curved portion 58. The lower curved portion 58 is formed by bending one end of the first flat portion 551 and the third flat portion 553 in one direction. In the lower curved portion 58, one end of the first flat portion 551 and the third flat portion 553 may be bent upwards.

[0210] The reason for needing the upper curved part 59 and the lower curved part 58 is to solve the problem that the curved part 500 cannot stand upright when the heat exchanger is configured upright because it interferes with the bottom or the ceiling of the machine room.

[0211] Furthermore, when the lower part 500 is filled with water due to the lower curved portion 58, the curved portion 500 will not be submerged, thus protecting the curved portion 500 from corrosion. Additionally, if the curved portion 500 bends upwards and protrudes, it will not be submerged, thus again protecting the curved portion 500 from corrosion.

[0212] The length J2 of the curved portion 500 can be the same as or greater than the height J1 of the curved portion 500. This is because if the length J2 of the curved portion 500 is smaller than the height J1 of the curved portion 500, the excessively abrupt bending over a shorter distance would increase the stress on the curved portion 500.

[0213] The width W2 of fin 60 can be larger than the width W1 of flat tube 50. This is because, as will be explained later, drainage is easier.

[0214] The length J2 of the curved section 500 divided by the height J1 of the curved section 500 satisfies the following relationship 1.

[0215] <Relation 1>

[0216]

[0217] Here, H1 is the height of fin 60, and H2 is the height of flat tube 50.

[0218] The structure of fin 60 will be described in detail below.

[0219] Figure 11 It is along Figure 8 A sectional view cut along line 11-11′. Figure 12 It is Figure 11 A magnified image of a portion of the area. Figure 13 yes Figure 11 A partial front view.

[0220] Reference Figures 11 to 13 The plurality of fins 60 includes: an inner portion 610 which is located at a position that overlaps with the plurality of flat tubes 50 when viewed in a first direction which is the extension direction of the first manifold 431; and an outer portion 620 which is located at a position that does not overlap with the plurality of flat tubes 50 when viewed in the first direction.

[0221] A portion of the fin 60 protrudes outward from the flat tube 50, thereby suppressing water inflow from the outside and allowing water condensed in the space between the fins 60 to be easily discharged to the outside.

[0222] In addition, a portion of the fin 60 protrudes outward from the flat tube 50, and the lower end of the outward protrusion extends downward, thereby suppressing water flowing in from the outside and making it easy for water condensed in the space between the fins 60 to be discharged to the outside.

[0223] The inner portion 610 connects adjacent flat tubes 50. The upper end of the inner portion 610 is connected to the lower end of the flat tube 50 located above the inner portion 610, and the lower end of the inner portion 610 is connected to the upper end of the flat tube 50 located below the inner portion 610.

[0224] The internal portion 610 is located at a position that overlaps with the flat tube 50 in the vertical direction.

[0225] Specifically, the outer portion 620 is connected to the rear end of the inner portion 610 and is located further rearward than the inner portion 610. The flat tube 50 is not positioned below or above the outer portion 620.

[0226] The longitudinal length of the inner portion 610 can be longer than that of the outer portion 620. This is because if the inner portion 610 is shorter than the outer portion 620, the area for heat exchange with the flat tube 50 will be reduced. Heat from the flat tube 50 is transferred from the inner portion 610 to the fins 60. Even if water flows in from the outer portion 620, the surface tension is less than gravity because the lower part of the outer portion 620 is not blocked by the tube, causing the water to fall.

[0227] Water in the space between the fins 60 in the inner part 610 diffuses horizontally due to surface tension. A portion of the diffused water falls downward from the outer part 620. Water in the inner part 610 moves towards the outer part 620 due to surface tension and viscosity. Water that has moved to the outer part 620 falls again due to gravity. Therefore, it has the advantage of easily draining water condensed in the space between the fins 60 to the outside.

[0228] The front-to-back width of the outer portion 620 can be smaller than the spacing between adjacent flat tubes 50. This is because if the front-to-back width of the outer portion 620 is larger than the spacing between adjacent tubes, the heat exchange area is reduced, leading to a decrease in heat exchange efficiency and no improvement in the ability to suppress water inflow.

[0229] The outer part 620 is located in a position that does not overlap with the flat tube 50 in the front-back direction.

[0230] The inner portion 610 is located at a position where at least a portion of it overlaps with at least one of the flat tubes 50 in the front-rear direction. Specifically, at least a portion of the inner portion 610 may overlap with the flat tube 50 located below the fin 60 where the inner portion 610 is located in the front-rear direction.

[0231] The fin 60 can be formed by bending a plurality of bodies in a zigzag pattern. For example, the fin 60 may include: a plurality of first bodies 611, 621 extending in the vertical direction; a plurality of second bodies 613, 623 extending in the vertical direction and located between the plurality of first bodies 611, 621; upper bodies 615, 625 connecting the upper ends of adjacent first bodies 611, 621 and the upper ends of second bodies 613, 623; and lower body 617 connecting the lower ends of adjacent first bodies 611, 621 and the lower ends of second bodies 613, 623.

[0232] Of course, according to the embodiments, the first body 611, 621 and the second body 613, 623 may also be tilted relative to the vertical direction.

[0233] The first entities 611 and 621 and the second entities 613 and 623 can be configured to face each other and be parallel to each other.

[0234] The upper main bodies 615 and 625 are connected to the lower ends of the upper flat tube 50 of the adjacent flat tubes 50, and the lower main body 617 is connected to the upper ends of the lower flat tube 50 of the adjacent flat tubes 50.

[0235] A portion 615 of the upper main body of the first fin 60, 61 is connected to the lower end of the first flat tube 50, 51, and a portion 617 of the lower main body of the first fin 60, 61 is connected to the upper end of the second flat tube 50, 52.

[0236] The upper main bodies 615 and 625 are located in a position that does not overlap with the lower main body 617 in the vertical direction. The upper main bodies 615 and 625 and the lower main body 617 alternate in the left-right direction.

[0237] The first main body 611, 621, the second main body 613, 623, the upper main body 615, 625, and the lower main body 617 extend in a direction intersecting the length direction of the flat tube 50. Specifically, the first main body 611, 621, the second main body 613, 623, the upper main body 615, 625, and the lower main body 617 extend in a front-rear direction.

[0238] The first entities 611 and 621 and the second entities 613 and 623 can define the surfaces that intersect with the left and right directions.

[0239] The first bodies 611 and 621 may include a first inner body 611 located in the inner portion 610 and a first outer body 621 located in the outer portion 620. The second bodies 613 and 623 may include a second inner body 613 located in the inner portion 610 and a second outer body 623 located in the outer portion 620. The upper bodies 615 and 625 may include an upper inner body 615 located in the inner portion 610 and an upper outer body 625 located in the outer portion 620. The lower body 617 may include a lower inner body 617 located in the inner portion 610.

[0240] That is, the internal part 610 may include a first internal body 611, a second internal body 613, an upper internal body 615, and a lower internal body 617, and the external part 620 may include a first external body 621, a second external body 623, and an upper external body 625.

[0241] A first inner body 611 extends vertically, and a second inner body 613 extends vertically and is located between the plurality of first inner bodies 611. The fins 60 may include a plurality of through-holes formed by penetrating a portion of the inner portion 610 and a plurality of louvers 651 covering a portion of the through-holes. The through-holes and louvers may be formed in the first inner body 611 and / or the second inner body 613.

[0242] The upper inner body 615 is connected to the upper ends of the first inner body 611 and the second inner body 613 that are adjacent to each other, and is connected to any one of the plurality of flat tubes 50.

[0243] The lower inner body 617 is connected to the lower ends of the first inner body 611 and the second inner body 613, which are adjacent to each other, and is connected to another flat tube 50 among the plurality of flat tubes 50.

[0244] The upper internal main body 615 is located in a position that does not overlap with the lower internal main body 617 in the vertical direction. The upper internal main body 615 and the lower internal main body 617 are arranged alternately in the left-right direction.

[0245] Of course, in other embodiments where the first inner body 611 and the second inner body 613 are inclined relative to the vertical direction, the center of the upper inner body 615 is located at a position that does not overlap with the center of the lower inner body 617 in the vertical direction.

[0246] The first outer body 621 extends vertically and is connected to the first inner body 611. The rear end of the first outer body 621 is connected to the rear end of the first inner body 611.

[0247] The second outer body 623 extends vertically, is located between the plurality of first outer bodies 621, and is connected to the second inner body 613. The rear end of the second outer body 623 is connected to the rear end of the second inner body 613.

[0248] The upper outer body 625 is connected to the upper ends of the first outer body 621 and the second outer body 623, which are adjacent to each other. The upper outer body 625 is not in contact with the flat tube 50. The upper outer body 625 is connected to the upper inner body 615.

[0249] The following is a detailed description of a method for manufacturing an evaporator according to an embodiment of the present invention.

[0250] Figures 14 to 16 This is a diagram illustrating the manufacturing process of a heat exchanger according to an embodiment of the present invention.

[0251] Reference Figure 14 Prepare a plurality of straight flat tubes 50, and connect a first manifold 431 and a second manifold 433 to both ends of the plurality of flat tubes 50. Arrange fins 60 between the first flat portions 531 of adjacent flat tubes 50 and between the second flat portions 532 of adjacent flat tubes 50.

[0252] Reference Figure 15 Place the bending rod 700 against the curved section 500 and bend the flat tube 50.

[0253] Reference Figure 16 If the first flat portion 531 and the second flat portion 532 are almost parallel, then the bent rod 700 is removed.

[0254] Figure 17 It is along Figure 4 A sectional view cut along line 17-17′. Figure 18 It is along Figure 4 A sectional view cut along the 18-18′ line.

[0255] Reference Figure 17 and Figure 18 The present invention has a refrigerant tube cross-sectional area ratio of the evaporator and the condenser, which can balance the heat exchange between the condenser and the evaporator and achieve stable operation by ensuring the subcooling and superheat of the cycle.

[0256] The cross-sectional area of ​​each channel of the condensing refrigerant pipe 410 is smaller than the cross-sectional area of ​​each evaporating refrigerant pipe 310. The sum of the cross-sectional areas of the condensing refrigerant pipes 410 divided by the sum of the cross-sectional areas of the evaporating refrigerant pipes 310 can be less than 1.3.

[0257] Preferably, the sum of the cross-sectional areas of the condensing refrigerant pipes 410 divided by the sum of the cross-sectional areas of the evaporating refrigerant pipes 310 can be greater than 1.1 and less than 1.3. This is because when the sum of the cross-sectional areas of the condensing refrigerant pipes 410 divided by the sum of the cross-sectional areas of the evaporating refrigerant pipes 310 is less than 1.1, subcooling and superheating cannot be sufficiently ensured; when the sum of the cross-sectional areas of the condensing refrigerant pipes 410 divided by the sum of the cross-sectional areas of the evaporating refrigerant pipes 310 exceeds 1.3, subcooling and superheating cannot be sufficiently ensured either.

[0258] Here, the cross-sectional area of ​​the condenser refrigerant pipe 410 refers to the cross-sectional area of ​​the condenser refrigerant pipe 410 cut in a direction parallel to the airflow direction. Specifically, the cross-sectional area of ​​the condenser refrigerant pipe 410 is the total cross-sectional area occupied by the condenser refrigerant pipe 410 within the cross-sectional area cut by planes parallel to the front-back and up-down directions.

[0259] More specifically, the total cross-sectional area of ​​the condenser refrigerant pipe 410 can be the total cross-sectional area of ​​the first flat portion 531 and the second flat portion 532 in the cross-section.

[0260] Here, the cross-sectional area of ​​the evaporating refrigerant tube 310 refers to the cross-sectional area of ​​the evaporating refrigerant tube 310 cut in a direction parallel to the airflow direction. Specifically, the cross-sectional area of ​​the evaporating refrigerant tube 310 is the total cross-sectional area occupied by the evaporating refrigerant tube 310 within the cross-sectional area of ​​the evaporator cut in a plane parallel to the front-back direction and the up-down direction.

[0261] The cross-section of the evaporating refrigerant pipe 310 can be circular, and the length of the condensing refrigerant pipe 410 in the direction parallel to the airflow direction can be longer than the length in the direction intersecting the airflow direction. That is, in the cross-section of the condensing refrigerant pipe 410, the length in the front-to-back direction can be longer than the length in the up-down direction.

[0262] The evaporative refrigerant tubes 310 can be arranged in four to eight rows in the airflow direction. The evaporative refrigerant tubes 310 are spaced apart in the front-to-back direction and arranged in four to eight rows.

[0263] The evaporative refrigerant pipes 310 can be defined from the front as the first column 311, the second column 312, the third column 313, and the fourth column 314.

[0264] Two adjacent rows of evaporative refrigerant tubes 310 can be positioned in a non-overlapping manner in the airflow direction. Specifically, the evaporative refrigerant tubes 310 of the first row 311 and the second row 312 are configured to not overlap in the front-to-back direction.

[0265] Figure 19 This is a top view showing a condenser 400′ according to another embodiment of the present invention.

[0266] Reference Figure 19 In another embodiment (second embodiment) of the present invention, the condenser 400' and Figure 6 Compared with the embodiment (first embodiment), the difference is that the third flat portion 553 and the fourth flat portion 554 are omitted, and the curved portion 500 connects one end of the first flat portion 551 and the second flat portion 552.

[0267] Unless otherwise specified in the second embodiment, the parts thereof shall be regarded as the same as those in the first embodiment.

[0268] Each flat tube 50 may include a first flat portion 551, a second flat portion 552, and a curved portion 500 located between the first flat portion 551 and the second flat portion 552.

[0269] The first manifold 431 is connected to the first flat portion 551, and the second manifold 433 is connected to the second flat portion 552.

[0270] A portion of the first fin 641 may protrude from the first flat portion 551 toward the second flat portion 552. That is, a portion of the first fin 641 may be located in a position that does not overlap with the first flat portion 551 when viewed from above. The width of the first fin 641 may be greater than the width of the first flat portion 551. A portion of the first fin 641 may protrude further downward than the first flat portion 551.

[0271] A portion of the second fin 642 may protrude from the second flat portion 552 toward the first flat portion 551. That is, a portion of the second fin 642 may be located in a position that does not overlap with the second flat portion 552 when viewed from above. The width of the second fin 642 may be greater than the width of the second flat portion 552. A portion of the second fin 642 may protrude upwards more than the second flat portion 552.

[0272] Figure 20 This is a top view of a condenser 400″ according to another embodiment of the present invention.

[0273] Reference Figure 20 In another embodiment (third embodiment) of the present invention, the condenser 400″ and Figure 6 The difference between this embodiment (the first embodiment) and the previous embodiment lies in the structure of the third fin 643 and the fourth fin 644.

[0274] Unless otherwise specified in the third embodiment, the parts thereof shall be regarded as the same as those in the first embodiment.

[0275] When viewed from the first direction (upper part), the third fin 643 may not be exposed to the outside of the third flat portion 553.

[0276] That is, when viewed from above, the third fin 643 can completely overlap with the third flat portion 553, and the width of the third fin 643 can be less than or equal to the width of the third flat portion 553.

[0277] When viewed from the first direction (upper part), the fourth fin 644 may not be exposed to the outside of the fourth flat portion 554.

[0278] When viewed from above, the fourth fin 644 can completely overlap with the fourth flat portion 554, and the width of the fourth fin 644 can be less than or equal to the width of the fourth flat portion 554.

[0279] The embodiments of the present invention have been described above with reference to the accompanying drawings. However, the present invention is not limited to the above embodiments and can be manufactured in various different forms. Those skilled in the art will understand that it can be implemented in other specific forms without departing from the technical concept of the present invention or changing the essential features. Therefore, it should be understood that the embodiments described above are exemplary and not limiting.

Claims

1. A garment processing device, wherein, include: A heat pump, consisting of an evaporator, compressor, condenser, and expansion valve, applies heat to air circulating in a drum. as well as An airflow path is formed to allow the air to pass through and circulate in the roller; The condenser includes: A plurality of condensing refrigerant tubes, in which refrigerant flows; and The condenser fins conduct heat from the condenser refrigerant tube. The evaporator includes: A plurality of refrigerant evaporation tubes, in which refrigerant flows; and Evaporation fins conduct heat from the evaporating refrigerant tube; The condenser refrigerant pipe includes a plurality of channels for refrigerant flow; The cross-sectional area of ​​each of the channels is smaller than the cross-sectional area of ​​each of the evaporating refrigerant tubes; The sum of the cross-sectional areas of the plurality of said condensing refrigerant tubes divided by the sum of the cross-sectional areas of the plurality of said evaporating refrigerant tubes is 1.3 or less.

2. The garment processing apparatus according to claim 1, wherein, The sum of the cross-sectional areas of the plurality of said condenser refrigerant tubes divided by the sum of the cross-sectional areas of the plurality of said evaporator refrigerant tubes is greater than 1.1 and less than 1.

3.

3. The garment processing apparatus according to claim 1, wherein, At least one of the condenser refrigerant tube, the condenser fins, and the evaporator refrigerant tube comprises aluminum.

4. The garment processing apparatus according to claim 1, wherein, The distance between the evaporator and the condenser is greater than the width of the evaporator in the direction of airflow.

5. The garment processing apparatus according to claim 1, wherein, The condenser also includes: The first manifold is connected to one end of each of the aforementioned condenser refrigerant pipes; and The second manifold is connected to the other end of each of the aforementioned condenser refrigerant pipes; Each of the condenser refrigerant tubes includes a first flat portion, a second flat portion, and a curved portion located between the first flat portion and the second flat portion; At least a portion of the curved section includes a curved shape.

6. The garment processing apparatus according to claim 5, wherein, The condenser fins include: The internal portion is located at the position where it overlaps with the plurality of the condensing refrigerant pipes when viewed in a first direction that is the extension direction of the first manifold; and The external portion is located at a position that does not overlap with the plurality of the condenser refrigerant tubes when viewed in the first direction.

7. The garment processing apparatus according to claim 6, wherein, The curved section includes a first twisting segment, a second twisting segment, and a connecting segment between the first twisting segment and the second twisting segment.

8. The garment processing apparatus according to claim 7, wherein, The radii of curvature of the first torsion section and the second torsion section are larger than the radii of curvature of the connecting section.

9. The garment processing apparatus according to claim 7, wherein, When viewed in the first direction, the planar areas of the first torsion section and the second torsion section are larger than the planar area of ​​the connecting section.

10. The garment processing apparatus according to claim 7, wherein, One end of the first twisted section is connected to the first flattened portion; One end of the second twisted section is connected to the second flat portion; A portion of the first torsion section and the second torsion section includes a straight line shape.

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