CLOTHING PROCESSING APPARATUS

Description

TECHNICAL FIELD

This disclosure relates to a heat exchanger capable of further securing heat exchange performance, increasing heat exchange volume, and improving power consumption, and a clothing processing apparatus including the same.

BACKGROUND

Heat exchanger can generally be used as a condenser or evaporator in a refrigeration cycle system which consists of a compressor, condenser, expansion device, and evaporator.

In addition, a heat exchanger is also installed in a vehicles, refrigerator, and clothing processing apparatus to exchange heat between refrigerant and air.

Generally, clothing processing apparatus is an apparatus that dries laundry by blowing hot air generated by a heater into a drum, and evaporating moisture contained in the laundry.

Clothing processing apparatus can be categorized into an exhaust type clothing processing apparatus and a condensation type clothing processing apparatus, depending on how the humid air passing through the drum is processed after drying the laundry.

The exhaust type clothing processing apparatus exhausts the humid air passing through the drum to the outside of the clothing processing apparatus. The condensation type clothing processing apparatus circulates the humid air passing through the drum while not exhausting the humid air to the outside of the clothing processing apparatus, cools the humid air at a dew point temperature or less through a condenser, and condenses the moisture contained in the humid air.

The condensation type clothing processing apparatus heats the condensed water from the condenser before re-supplying it to the drum, and then flows the heated air into the drum. Here, the humid air is cooled during the process of being condensed, causing a loss of heat energy in the air, so that a separate heater is required to heat air to the temperature required for drying.

The exhaust type clothing processing apparatus also need to discharge hot and humid air to the outside and bring in ambient air and heat it to the required temperature level through a heater. In particular, as the drying process progresses, the humidity of the air discharged from a drum outlet decreases, resulting in heat loss in the air that is not used for drying in the drum and is then discharged to the outside, thereby reducing thermal efficiency.

Therefore, in recent years, a clothing processing apparatus equipped with a heat pump cycle that can enhance energy efficiency by recovering the energy discharged from the drum and using it to heat the air flowing into the drum has been introduced.

The condensation type clothing processing apparatus of Patent Document 1 includes a drum 1 into which a drying target is loaded, a circulation duct 2 providing a path so that air circulates via the drum 1, a circulation fan 3 for allowing the circulating air to flow along the circulation duct 2, and a heat pump cycle 4 having an evaporator 5 and a condenser 6 installed in series in the circulation duct 2 so that the air circulating along the circulation duct 2 passes therethrough.

The heat pump cycle 4 may include a circulation pipe forming a circulation path so that refrigerant circulates via the evaporator 5 and the condenser 6, and a compressor 7 and an expansion valve 8 installed in the circulation pipe between the evaporator 5 and the condenser 6.

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

Here, both the evaporator and the condenser use a conventional heat exchanger, which reduces heat exchange efficiency and increases the manufacturing cost and difficulty of the heat exchanger.

Patent Document 2 discloses headers 20 on both sides, a plurality of tubes 30 connected to the header, and a plurality of fins 4 connecting the tubes.

Patent Document 2 discloses a microchannel heat exchanger, but in order to increase the heat exchange capacity by configuring tubes in multiple rows, it is required to have a structure such as multiple headers and a connecting pipe connecting them. However, the use of multiple headers and the connecting pipe connecting them requires additional configuration and complicates the manufacturing process of connecting them.

SUMMARY

The disclosure has been made in view of the above problems, and may provide a heat exchanger that uses a microchannel-type heat exchanger as a condenser for a clothing processing apparatus to improve heat exchange efficiency, and a clothing processing apparatus including the same.

The disclosure may further provide a clothing processing apparatus that uses a multi-row microchannel-type heat exchanger as a condenser for a clothing processing apparatus, while having a simple manufacturing process and reduced manufacturing costs.

The disclosure may further provide a clothing processing apparatus that reduces the flow resistance of refrigerant by using only two headers and a flat tube and a fin that connect them.

The disclosure may further provide a clothing processing apparatus that increases condensation heat and improves power consumption through the size relationship between a flat tube, a pin, and a curved section.

The disclosure may further provide a clothing can stably operate by processing apparatus that adjusting the cross-sectional area of the condenser tube and the cross-sectional area of the evaporator tube to balance the heat exchange volume between the condenser and the evaporator, and ensuring the supercooling degree and superheating degree of a cycle.

The problems of the present disclosure are not limited to the problems mentioned above, and other problems not mentioned will be clearly understood by those skilled in the art from the description below.

A clothing processing apparatus according to the present disclosure improves the efficiency by controlling the cross-sectional area of a tube of a condenser and the cross-sectional area of a tube of an evaporator.

Specifically, the present disclosure includes a heat pump which includes an evaporator, a compressor, a condenser, and an expansion valve, and applies heat to air circulating through a drum; and an air flow path forming a movement path so that the air circulates through the drum, in which the condenser includes: a plurality of condensation refrigerant tubes through which refrigerant flows; and a condensation fin for conducting heat from the condensation refrigerant tube, in which the evaporator includes: a plurality of evaporation refrigerant tubes through which refrigerant flows; and an evaporation fin for conducting heat from the evaporation refrigerant, in which the condensation refrigerant tube includes a plurality of channels through which refrigerant flows, in which each of the channels has a cross-sectional area smaller than a cross-sectional area of each of the evaporation refrigerant tubes, in which a sum of cross-sectional areas of the condensation refrigerant tubes divided by a sum of the cross-sectional areas of the evaporation refrigerant tubes is 1.3 or less.

The sum of the cross-sectional areas of the condensation refrigerant tubes divided by the sum of the cross-sectional areas of the evaporation refrigerant tubes is greater than 1.1 and less than or equal to 1.3.

The condensation refrigerant tube and the condensation fin include aluminum.

The evaporation refrigerant tube includes aluminum.

A cross-section of the evaporation refrigerant tube is circular, and a cross-section of the condensation refrigerant tube has a shape in which a length in a direction parallel to an air flow direction is greater than a length in a direction intersecting with the air flow direction.

The evaporation refrigerant tube is arranged in four to eight rows in an airflow direction, and evaporation refrigerant tubes in two adjacent rows are located so as not to overlap in the airflow direction.

A distance between the evaporator and the condenser is greater than a width of the evaporator in an airflow direction.

The condenser further includes: a first header connected to one end of each of the condensation refrigerant tubes; and a second header connected to the other end of each of the condensation refrigerant tubes. Each of the condensation 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, and at least a portion of the curved portion has a curved shape.

The condensation fin includes: an inner portion located to overlap with the plurality of flat tubes when viewed in a first direction which is an extension direction of the first header; and an outer portion located not to overlap with the plurality of flat tubes when viewed in the first direction.

The curved portion includes: a first twist section, a second twist section, and a connecting section between the first twist section and the second twist section.

A radius of curvature of the first twist section and the second twist section is greater than a radius of curvature of the connecting section.

When viewed in the first direction, a planar area of the first twist section and the second twist section is larger than a planar area of the connecting section.

One end of the first twist section is connected to the first flat portion, and one end of the second twist section is connected to the second flat portion.

A portion of the first twist section and the second twist section has a linear shape.

A width of the first twist section, when viewed in the first direction, decreases from the first flat portion toward the connecting section.

An inclination angle formed by a largest surface of the first twist section and a largest surface of the first flat portion increases from the first flat portion toward the connecting section.

An inclination angle formed by a largest surface of the second twist section and a largest surface of the second flat portion increases from the second flat portion toward the connecting section.

The condensation fin further includes: a plurality of first fins located between the first flat portions that are adjacent to each other in the first direction; and a plurality of second fins located between the second flat portions that are adjacent to each other in the first direction. A portion of the first fin protrudes from the first flat portion toward the second flat portion, and a portion of the second fin protrudes from the second flat portion toward the first flat portion.

The first flat portion is connected to the first header, and the second flat portion is connected to the second header.

The width of the first fin may be greater than the width of the first flat portion, and the width of the second fin may be greater than the width of the second flat portion.

BRIEF DESCRIPTION OF THE DRAWINGS

The above and other objects, features and advantages of the present invention will be more apparent from the following detailed description in conjunction with the accompanying drawings, in which:

FIG. 1 is a schematic diagram illustrating the flow of air and refrigerant in a clothing processing apparatus according to an embodiment of the present disclosure;

FIG. 2 is a schematic diagram illustrating a configuration of a clothing processing apparatus according to an embodiment of the present disclosure;

FIG. 3 is a diagram illustrating a machine room and an air flow path portion of a clothing processing apparatus according to an embodiment of the present disclosure;

FIG. 4 is a diagram illustrating an evaporator and a condenser illustrated in FIG. 3;

FIG. 5 is a perspective view illustrating a condenser illustrated in FIG. 3;

FIG. 6 is a plan view illustrating the condenser illustrated in FIG. 3;

FIG. 7 is a front view illustrating the condenser illustrated in FIG. 3;

FIG. 8 is an enlarged view of a portion of FIG. 6;

FIG. 9 is one side view of the condenser illustrated in FIG. 3;

FIG. 10 is another side view of the condenser illustrated in FIG. 3;

FIG. 11 is a cross-sectional view taken along line 11-11′ of FIG. 8;

FIG. 12 is an enlarged view of a portion of FIG. 11;

FIG. 13 is a perspective view of a portion of FIG. 11;

FIGS. 14 to 16 are diagrams illustrating a manufacturing process of a heat exchanger according to an embodiment of the present disclosure;

FIG. 17 is a cross-sectional view taken along line 17-17′ of FIG. 4;

FIG. 18 is a cross-sectional view taken along line 18-18′ of FIG. 4;

FIG. 19 is a plan view illustrating a condenser according to another embodiment of the present disclosure; and

FIG. 20 is a plan view illustrating a condenser according to another embodiment of the present disclosure.

DETAILED DESCRIPTION

The advantages and features of the present disclosure, and methods for achieving them, will become clearer with reference to the embodiments described below in detail with the accompanying drawings. However, the present disclosure is not limited to the embodiments disclosed below and may be implemented in various different forms. These embodiments are provided solely to ensure the complete disclosure of the present disclosure and to fully convey the scope of the invention to those skilled in the art, and the present disclosure is defined solely by the scope of the claims. Like reference numerals designate like elements throughout the specification.

Spatially relative terms such as “below,” “beneath,” “lower,” “above,” and “upper” may be used to easily describe the relationship between one element and another, as illustrated in the drawings. Spatially relative terms should be understood to encompass different orientations of elements during use or operation, in addition to the orientations depicted in the drawings. For example, when a component depicted in a drawing is flipped, a component described as “below” or “beneath” another component may be located “above” the other component. Therefore, the exemplary term “below” may encompass both above and below directions. Components may also be oriented in other directions, and thus spatially relative terms may be interpreted based on their orientation.

The terminology used herein is for the purpose of describing embodiments and is not intended to limit the present disclosure. In this specification, singular forms also include plural forms unless specifically stated otherwise in the text. As used herein, the terms “comprises” and/or “comprising” do not exclude the presence or addition of one or more other components, steps, and/or operations.

Unless otherwise defined, all terms (including technical and scientific terms) used herein may have the same meaning as commonly understood by those skilled in the art to which this disclosure pertains. Furthermore, terms defined in commonly used dictionaries are not to be interpreted ideally or excessively unless explicitly defined otherwise.

In the drawings, the thickness and size of each component are exaggerated, omitted, or schematically illustrated for convenience and clarity of explanation. Furthermore, the size and area of each component do not entirely reflect the actual size or area.

Furthermore, angles and directions mentioned in the description of the structure of the embodiment are based on those described in the drawings. In the description of the structure forming the embodiment in the specification, if the reference point and positional relationship for angles are not clearly mentioned, refer to the relevant drawings.

The present disclosure will now be described in detail with reference to the attached drawings.

FIG. 1 is a schematic diagram illustrating the flow of air and refrigerant in a clothing processing apparatus according to an embodiment of the present disclosure, and FIG. 2 is a schematic diagram illustrating a configuration of a clothing processing apparatus according to an embodiment of the present disclosure.

Referring to FIGS. 1 and 2, a drum-type dryer exemplifies a clothing processing apparatus 100 according to the invention, and may include a cabinet 110, a drum 130, a driving unit (not shown), a blower fan 170, and a heat pump 160. Air from the drum 130 is connected to the heat pump 160 by an air path 150.

Here, the cabinet 110 may be provided with a door 112 configured to form the outer shape of a product and to load clothes into the front, and a base 114 on which the internal components of the clothing processing apparatus 100 are installed.

Meanwhile, the drum 130 may rotate around a rotation shaft disposed in a horizontal direction or inclined at a certain angle within the cabinet. Meanwhile, the drum 130 has a hollow cylindrical shape, and provides an accommodating space for drying clothes.

The drum 130 is formed in a cylindrical shape with open front and rear sides. The drum 130 is provided with a front support portion 132 at the front for rotatably supporting the drum 130. Furthermore, the drum 130 is provided with a rear support portion 133 at the rear for rotatably supporting the drum 130.

In addition, a front roller 142 and a rear roller 143 in the form of a roller may be additionally provided at the front and rear lower portions of the drum 130 for rotatably supporting the drum 130. That is, the front support portion 132 and the rear support portion 133 block the front and rear surfaces of the drum 130 to form a drying space for the drying target, while simultaneously supporting the front and rear ends of the drum 130.

Meanwhile, the front support portion 132 is formed with an inlet 132b for loading the drying target into the drum 130, and the inlet is selectively opened and closed by the door 112. Furthermore, an air outlet 132a to which an air path 150 described later is connected is located at the lower portion of the front support portion 132. The air outlet 132a is provided to communicate with a suction path 151 of the air path 150 described later.

Furthermore, the rear support portion 133 is formed with an air inlet 133a formed with a plurality of through holes to supply air to the drum 130. The air inlet 133a is provided to communicate with an exhaust path 152 of the air path 150 described later.

Here, in order to efficiently dry clothes which are a drying target, a lifter 131a may be further provided on the inner circumferential surface of the drum 130 to tumble the loaded clothes.

Furthermore, the driving unit provides rotational power by using a motor (not shown), the output shaft of the motor and the drum 130 are connected by a power transmission means such as a belt, and the rotational power of the motor is transmitted to the drum 130 to rotate the drum 130.

Furthermore, the air path 150 may be connected to the drum 130 to form a closed loop for air circulation. For example, the air path 150 may be formed in the form of a duct. A suction path 151 for air discharge is formed at the lower portion of the front support portion 132 of the drum 130, and an exhaust path 152 for air supply is formed at the rear support portion 133 of the drum 130.

Meanwhile, a blower fan 170 may be installed within the air path 150 extending from the suction path 151 to the evaporator 300 of the heat pump 160, or the air path 150 extending from the condenser 400 of the heat pump 160 to the exhaust path 152.

Here, the blower fan 170 may be driven by a separate fan motor, may energize air to pass through the inside of the drum 130, and may circulate air discharged from the drum 130 back into the drum 130.

In addition, a lint filter 162 (see FIG. 3) is installed in the suction path 151 to filter the lint in the circulating air. The lint filter 162 may capture the lint contained in the air as the air sucked into the suction path 151 from the drum 130 passes therethrough.

Therefore, clothing (also referred to as ‘fabric’) evaporates moisture by the hot air supplied into the drum 130, and the air passing through the drum 130 is discharged from the drum 130 containing the moisture evaporated from the clothing. The high-temperature and humid air discharged from the drum 130 moves along the air path 150, receives heat from the heat pump 160, is heated, and then is circulated to the drum 130.

Meanwhile, the heat pump 160 is configured to include an evaporator 300, a compressor 163, a condenser 400, and an expansion valve 164. The heat pump 160 may use a refrigerant as a working fluid. The refrigerant moves along a refrigerant pipe 165, and the refrigerant pipe 165 forms a closed loop for the circulation of the refrigerant. The evaporator 300, the compressor 163, the condenser 400, and the expansion valve 164 are connected by the refrigerant pipe 165, so that the refrigerant passes through the evaporator 300, the compressor 163, the condenser 400, and the expansion valve 164 in sequence.

Here, the evaporator 300 is installed in the air path 150 so as to be in communication with a drum outlet, and heat-exchanges the air discharged from the drum outlet with the refrigerant, thereby recovering the heat of the air discharged from the drum 130 without discharging it to the outside of the dryer.

In addition, the condenser 400 is installed in the air path 150 so as to be in communication with a drum inlet, and heat-exchanges the air passing through the evaporator 300 with the refrigerant, thereby dissipating the heat of the refrigerant absorbed in the evaporator 300 to the air flowing into the drum 130.

The compressor 163 compresses the refrigerant evaporated in the evaporator 300 to generate a high-temperature and high-pressure refrigerant, and moves the high-temperature and high-pressure refrigerant to the condenser 400 along the refrigerant pipe 165. The compressor 163 may be an inverter-type compressor 163 capable of varying the frequency to control the discharge amount of the refrigerant.

The expansion valve 164 is installed in the refrigerant pipe 165 extending from the condenser 400 to the evaporator 300, and expands the refrigerant condensed in the condenser 400 to generate a low-temperature and low-pressure refrigerant and transfers it to the evaporator 300.

According to such a configuration, in the refrigerant movement path, the refrigerant flows into the compressor 163 in a gaseous state and becomes high-temperature and high-pressure by compression by the compressor 163. The high-temperature and high-pressure refrigerant flows into the condenser 400 and changes from a gaseous state to a liquid state as the condenser 400 dissipates heat to the air.

Next, the liquid refrigerant flows into the expansion valve 164 and changes into low-temperature and low-pressure through the throttling process of the expansion valve 164 (or including a capillary tube, etc.). The low-temperature and low-pressure liquid refrigerant flows into the evaporator 300, so that the refrigerant is evaporated from a liquid state to a gaseous state as the evaporator 300 absorbs heat from the air.

As described above, the heat pump 160 repeatedly circulates the refrigerant in the order of the compressor 163, the condenser 400, the expansion valve 164, and the evaporator 300, thereby providing a heat source for the air circulated to the drum 130.

Meanwhile, the clothing processing apparatus 100 according to the present disclosure supplies pressurized air into the drum 130 separately from the circulating supply of heated air by the heat pump 160, thereby impacting the drying target inside the drum 130 and simultaneously changing the movement path of the heated air inside the drum 130.

That is, the drying target loaded into the drum 130 may contain various types of moisture depending on the material of the drying target and, by supplying pressure air, may remove the relatively large-sized moisture contained in the drying target from the drying target, or broken down into relatively small-sized moisture by crushing them, thereby accelerating the drying of the moisture by the heated air.

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 while drying the drying target inside the drum 130, and passes through the air path 150 and circulates the drum 130 and the heat pump 160.

In the case of such a movement path of heated air, the dryness of the drying target may be improved as the heated air comes in contact with the drying target over a larger area and for a longer period of time. Here, in the case of pressurized air supplied separately from the heated air, it is supplied at a higher pressure than the heated air through a different location and route than the heated air, thereby impacting the drying target and simultaneously changing the path along which the heated air moves within the drum 130 to accelerate the drying of moisture by the heated air.

Meanwhile, in order to supply pressurized air into the inside of the drum 130, a pressurized air generator 200 that generates pressurized air and a pressurized air nozzle 301 that sprays the pressurized air generated in the pressurized air generator 200 into the inside of the drum 130 may be provided.

Hereinafter, the arrangement of the evaporator 300 and the condenser 400 will be described in detail.

FIG. 3 is a diagram illustrating a machine room and an air flow path portion of a clothing processing apparatus according to an embodiment of the present disclosure, and FIG. 4 is a diagram illustrating the evaporator 300 and the condenser 400 illustrated in FIG. 3.

Referring to FIGS. 3 and 4, the evaporator 300 and the condenser 400 may be installed within the air path 150. The evaporator 300 may be connected to the drum outlet, and the condenser 400 may be connected to the drum inlet.

Meanwhile, the present disclosure may include a machine room 161 in which the compressor 163, the expansion valve, and the refrigerant pipe 165 are located. The machine room 161 may be located next to the air path 150.

The high-temperature and humid air discharged from the drum 130 has a higher temperature than the refrigerant in the evaporator 300. Therefore, as the air passes through the evaporator 300, its heat is removed by the refrigerant in the evaporator 300, and the air is condensed to generate condensate. Accordingly, the high-temperature and humid air is dehumidified by the evaporator 300, and the condensed condensate may be collected into a separate condensate tank (not shown) and drained.

Meanwhile, the heat source of the air absorbed in the evaporator 300 is transferred to the condenser 400 via the refrigerant. A compressor 163 may be located between the evaporator 300 and the condenser 400 to transfer the heat source from the evaporator 300 (low-heat source portion) to the condenser 400 (high-heat source portion).

Meanwhile, the evaporator 300 may be a fin & tube type heat exchanger. The fin & tube type is a hollow tube having a plurality of flat fins attached thereto. The refrigerant flows along the inside of the tube, and air passes between the plurality of fins attached to the tube, so that the refrigerant and air can exchange heat with each other. Here, the fins are used to expand the heat exchange area between the air and the refrigerant.

For example, the evaporator 300 may include a plurality of evaporation refrigerant tubes 310 through which refrigerant flows, and an evaporation fin 320 that conducts heat from the evaporation refrigerant. The evaporator 300 may include an evaporation inlet pipe 391 that supplies refrigerant to the evaporation refrigerant tube 310, and an evaporative outlet pipe 392 through which refrigerant flows out from the evaporation refrigerant tube 310.

The evaporation refrigerant tube 310 and the evaporation fin 320 may include aluminum or an aluminum alloy. The evaporation inlet pipe 391 is connected to the expansion valve 164 and the evaporation refrigerant tube 310, and the evaporation outlet pipe 392 is connected to the compressor 163 and the evaporation refrigerant tube 310. The detailed structure of the evaporator 300 is described later in FIG. 18.

The condenser 400 may include a microchannel type heat exchanger. The condenser 400 includes a condensation refrigerant tube 410 including a plurality of channels 50a through which refrigerant flows, a condensation fin 420 for conducting heat of the condensation refrigerant tube 410, and a first header 431 and a second header 433 that are located at both ends of each condensation refrigerant tube 410. Hereinafter, the condensation fin 420 may be referred to as a fin, and the condensation refrigerant tube 421 may be referred to as a flat tube 410.

The condenser 400 may include a condensation inlet pipe 491 that supplies refrigerant to the flat tube 410, and a condensation outlet pipe 492 through which refrigerant flows out from the flat tube 410. The condensation inlet pipe 491 is connected to the compressor 163 and the flat tube 410, and the condensation outlet pipe 492 is connected to the expansion valve 164 and the flat tube 410. The condensation inlet pipe 491 may be used interchangeably as an inlet pipe, and the condensation outlet pipe 492 may be used interchangeably as an outlet pipe. The condensation inlet pipe 491 may be connected to the first header 431, and the condensation outlet pipe 492 may be connected to the second header 433.

The detailed structure of the condenser 400 is described later in FIGS. 5 to 9. When a microchannel type heat exchanger is used for the condenser 400, the temperature of the air passing through the condenser 400 may be increased in comparison with a case where a fin-tube heat exchanger is used, and the air may be heated to a target temperature in a much shorter heat exchange time. Therefore, when a microchannel type heat exchanger is used for the condenser 400, the drying efficiency of the clothing processing apparatus may be improved.

Here, the cross-sectional area of each channel 50a of the refrigerant tube of the condenser 400 is smaller than the cross-sectional area of the refrigerant tube of the evaporator 300. Since the evaporator 300 does not require a large heat exchange volume, it uses a fin-tube heat exchanger rather than a microchannel heat exchanger.

The air flowing in the air 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 arranged too close together, the condensate generated in the evaporator 300 flows into the condenser 400, thereby reducing the heat exchange efficiency of the condenser 400.

In order to prevent the condensate generated in the evaporator 300 from flowing into the condenser 400, the separation distance D1 between the evaporator 300 and the condenser 400 may be greater than the width W3 of the evaporator 300 in the air flow direction.

The width W3 of the evaporator 300 in the air flow direction may be greater than the width W4 of the condenser 400 in the air flow direction. The height H3 of the evaporator 300 may be less than the height H4 of the condenser 400.

Preferably, the separation distance D1 of the condenser 400 may be greater than the sum of the width W3 of the evaporator 300 in the air flow direction and the width W4 of the condenser 400 in the air flow direction.

More preferably, the separation distance D1 of the condenser 400 may be 100 mm to 250 mm.

If the separation distance D1 of the condenser 400 is greater than the sum of the width W3 of the evaporator 300 in the air flow direction and the width W4 of the condenser 400 in the air flow direction, condensate generated in the evaporator 300 by the air flow falls into a space between the condenser 400 and the evaporator 300.

The condensation inlet pipe 491 and the condensation outlet pipe 492 may be located in the same direction with respect to the flat tube 410. Specifically, the condensation inlet pipe 491 and the condensation outlet pipe 492 may extend from the flat tube 410 toward the machine room.

More specifically, if the air flow direction is defined as a front-rear direction FR, the condensation inlet pipe 491 and the condensation outlet pipe 492 extend to the right from the flat tube 410.

If the condensation inlet pipe 491 and the condensation outlet pipe 492 are located in the same direction with respect to the flat tube 410, the space for arranging the refrigerant pipe may be reduced, the length of the refrigerant pipe may be reduced, and sufficient space for the air flow path 150 may be secured.

The evaporation inlet pipe 391 and the evaporation outlet pipe 392 may be located in the same direction with respect to the evaporation refrigerant tube 310. Specifically, the evaporation inlet pipe 391 and the evaporation outlet pipe 392 may extend from the evaporation refrigerant tube 310 toward the machine room.

More specifically, the evaporation inlet pipe 391 and the evaporation outlet pipe 392 extend to the right from the evaporation refrigerant tube 310.

If the evaporation inlet pipe 391 and the evaporation outlet pipe 392 are located in the same direction with respect to the evaporation refrigerant tube 310, the space for arranging the refrigerant pipe may be reduced, the length of the refrigerant pipe may be reduced, and sufficient space for the air path 150 may be secured.

Preferably, the evaporation inlet pipe 391, the evaporation outlet pipe 392, the condensation inlet pipe 491, and the condensation outlet pipe 492 may extend in the same direction from the air path 150. The evaporation inlet pipe 391, the evaporation outlet pipe 392, the condensation inlet pipe 491, and the condensation outlet pipe 492 extend to the right from the air path 150.

Hereinafter, the structure of the condenser 400 will be described in detail. The condenser 400 includes the heat exchanger of the present disclosure. The description of the condenser 400 is the same as that of the heat exchanger.

FIG. 5 is a perspective view illustrating a condenser 400 illustrated in FIG. 3, FIG. 6 is a plan view illustrating the condenser 400 illustrated in FIG. 3, FIG. 7 is a front view illustrating the condenser 400 illustrated in FIG. 3, FIG. 8 is an enlarged view of a portion of FIG. 6, FIG. 9 is one side view of the condenser 400 illustrated in FIG. 3, and FIG. 10 is another side view of the condenser illustrated in FIG. 3.

Referring to FIGS. 5 to 10, the condenser 400 is a microchannel type heat exchanger. The condenser 400 is made of aluminum. The condenser 400 may have a plurality of flat tubes 50 located in the air flow direction. That is, the condenser 400 includes a plurality of flat tubes 50 stacked in an up-down direction intersecting with the air flow direction, and a first header 431 and a second header 433 at both ends of the plurality of flat tubes 50 in the horizontal direction, and the plurality of flat tubes 50 are bent in the middle so that the plurality of flat tubes 50 may form a plurality of rows along the air flow direction.

Specifically, the plurality of flat tubes 50 are arranged in a first row, a second row, a third row, and a fourth row on a path along which external air flows, and the external air may be heat-exchanged firstly with the fourth row, secondarily with the third row, thirdly with the second row, and finally with the first row.

The first header 431 and the second header 433 extend in the first direction. Specifically, the first header 431 and the second header 433 may extend upward. The inlet pipe 491 is connected to the first header 431 to allow refrigerant to flow in, and the outlet pipe 492 is connected to the second header 433.

The flat tube 50 may include an upper surface 51a and a lower surface 51b that face each other, and both side surfaces 51c, 51d connecting both 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 both side surfaces 51c, 51d. Therefore, the cross-sectional shape of the flat tube 50 may be an elongated rectangle in a horizontal direction. Preferably, the upper surface 51a and the lower surface 51b may be arranged parallel to a horizontal plane.

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.

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

Here, the first flat portion 551, the second flat portion 552, the third flat portion 553, and the fourth flat portion 554 may be a non-bending area. The first flat portion 551, the second flat portion 552, the third flat portion 553, and the fourth flat portion 554 may extend parallel to a horizontal direction. The first flat portion 551, the second flat portion 552, the third flat portion 553, and the fourth flat portion 554 may be arranged parallel to each other.

Each row of the above-described flat tube 50 may be defined by the first flat portion 551, the second flat portion 552, the third flat portion 553, and the fourth flat portion 554.

The first flat portion 551, the second flat portion 552, the third flat portion 553, and the fourth flat portion 554 may be located to overlap with each other 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 may be located to overlap with each other in the front-rear direction.

The third flat portion 553 may be located closer to the first flat portion 551 than the second flat portion 552, and the fourth flat portion 554 may be located closer to the second flat portion 552 than the first flat portion 551.

The curved portion 500 is a portion where the flat tube 50 is bent. 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.

Obviously, a plurality of curved portions 500 may be located between the first flat portion 551 and the second flat portion 552.

Specifically, as illustrated in FIG. 6, the flat tube 50 may form four rows by including three curved portions 500, the first flat portion 551, the second flat portion 552, the third flat portion 553, and the fourth flat portion 554, at between the first header 431 and the second header 433. At this time, each curved portion 500 may be alternately arranged left and right from the front to the rear.

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.

A plurality of fins 60 may be arranged in an area of the flat tube 50 adjacent to each other. Specifically, the plurality of fins 60 may include a first fin 641 arranged between adjacent first flat portions 551, a second fin 642 arranged between adjacent second flat portions 552, a third fin 643 arranged between adjacent third flat portions 553, and a fourth fin 644 arranged between adjacent fourth flat portions 554.

Specifically, the refrigerant tube 50 located at the uppermost end is defined as a first refrigerant tube 50, 51, the refrigerant tube 50 located below the first refrigerant tube 50, 51 is defined as a second refrigerant tube 50, 52, and in this manner, a n-th refrigerant tube and a n-th end fin 60 may be defined.

A first end fin 60, 61 may be arranged between the first flat portion 551 of the first refrigerant tube 50, 51 and the first flat portion 551 of the second refrigerant tube 50, 52, and the first end fin 60, 61 may be arranged between the second flat portion 552 of the first refrigerant tube 50, 51 and the second flat portion 552 of the second refrigerant tube 50, 52.

The plurality of fins 60 are not arranged between the curved portions 500 of the flat tubes 50 that are adjacent to each other. Since the plurality of fins 60 are not arranged between the curved portions 500, a space where the flat tube 50 is twisted while being bent may be secured. The detailed structure of the fin 60 will be described later.

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 so as not to 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 downward than the first flat portion 551.

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 so as not to 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 upward than the second flat portion 552.

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 so as not to 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 upward than the third flat portion 553.

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 so as not to 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 downward than the fourth flat portion 554.

As described above, if the fin protrudes from the flat tube toward adjacent flat portions, the risk of fin breakage when bending the flat tube around the curved portion is reduced, and the problem that it is difficult to drain due to surface tension of water between the fins may be resolved.

Hereinafter, the structure of the curved portion 500 will be described in detail.

In particular, referring to FIGS. 7 to 9, the curved portion 500 may include a first twist section 533, a second twist section 534, and a connecting section 540.

The curved portion 500 is a portion that is located between the first flat portion 551 and the second flat portion 552, and is bent.

The curved portion 500 is a portion that connects the longitudinal ends of the first flat portion 551 and the second flat portion 552, and is bent (see FIG. 18).

The curved portion 500 is a portion that connects the longitudinal ends of the first flat portion 551 and the third flat portion 553. The curved portion 500 is a portion that connects the longitudinal ends of the third flat portion 553 and the fourth flat portion 554, and is bent

Hereinafter, the curved portion 500 connecting the first flat portion 551 and the third flat portion 553 will be mainly described, but this description can be applied to the curved portion 500 connecting other flat portions.

A plurality of flat tubes 50 may be bent about a bending axis C2 parallel to the up-down direction so as to be bent at once by using a single rod. However, when bending is performed with the bending axis C2 parallel to the up-down direction as a center axis, since the upper surface 51a, which is the wide surface of the flat tube 50, and the lower surface 51b are parallel to the horizontal direction, there is a problem in that one surface of the flat tube 50 is greatly deformed and damaged during bending.

Accordingly, the curved portion 500 is bent with the bending axis C2 parallel to the up-down direction as a center axis, but the curved portion 500 is twisted with respect 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 is mainly deformed, thereby reducing the stress generated during the bending of the flat tube 50.

Here, the term “twisted” may mean that the first flat portion 551, the upper surface 51a, and the upper surface of the curved portion 500 are deformed at an angle to each other.

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

The first twist section 533 and the second twist section 534 are an area where the flat tube 50 is twisted to increase the deformation of the connecting section 540.

A portion of the first twist section 533 and the second twist section 534 may have a linear shape. Specifically, a portion of the first twist section 533 closer to the first flat portion 551 may have a linear shape, and a portion of the second twist section 534 closer to the third flat portion 553 may have a linear shape.

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

The first twist section 533 may include an upper surface connecting the upper end of the first outer edge 535 to the upper end of the first inner edge 537, and a lower surface connecting the lower end of the first outer edge 535 to the lower end of the first inner edge 537.

A portion of the first inner edge 537 has a linear shape, and another portion of the first inner edge 537 has a curved shape. A portion of the first outer edge 535 has a linear shape, and another portion of the first outer edge 535 has a curved shape.

A portion of the first inner edge 537 adjacent to the first flat portion 551 has a linear shape, and another portion of the first inner edge 537 adjacent to the connecting section 540 has a curved shape. A portion of the first outer edge 535 adjacent to the first flat portion 551 has a linear shape, and another portion of the first outer edge 535 adjacent to the connecting section 540 has a curved shape.

The length of the first outer edge 535 is longer than that of the first inner edge 537. In the first outer edge 535, the length of the curved shape may be longer than that of the linear shape, and in the first inner edge 537, the length of the linear shape may be longer than that of the curved shape.

The width of the first twist section 533 as viewed in the up-down direction decreases from the first flat portion 551 to the connecting section 540.

The inclination angle formed by the largest surface of the first twist section 533 and the largest surface of the first flat portion 551 may increase from the first flat portion 551 to the connecting section 540. The inclination angle A1 formed by the upper surface 51a of the first twist section 533 and the upper surface of the first flat portion 551 may increase from the first flat portion 551 to the connecting section 540.

The height of the first twist section 533 may increase from the first flat portion 551 to the connecting section 540.

The second twist section 534 may be arranged symmetrically with the first twist section 533 with respect to the connecting section 540.

Specifically, the second twist section 534 may include a second outer edge 536 and a second inner edge 538. The second outer edge 536 is arranged further from the bending axis C2 than the second inner edge 538. The second outer edge 536 may be connected to one surface of the third flat portion 553, and the second inner edge 538 may be connected to the other surface of the third flat portion 553.

The second twist 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.

A portion of the second inner edge 538 has a linear shape, and another portion of the second inner edge 538 has a curved shape. A portion of the second outer edge 536 has a linear shape, and another portion of the second outer edge 536 has a curved shape.

A portion of the second inner edge 538 adjacent to the third flat portion 553 has a linear shape, and another portion of the second inner edge 538 adjacent to the connecting section 540 has a curved shape. A portion of the second outer edge 536 adjacent to the third flat portion 553 has a linear shape, and another portion of the second outer edge 536 adjacent to the connecting section 540 has a curved shape.

The length of the second outer edge 536 is longer than that of the second inner edge 538. The length of the curved shape of the second outer edge 536 may be greater than that of the linear shape, and the length of the linear shape of the second inner edge 538 may be greater than that of the curved shape.

The width of the second twist section 534 as viewed in the up-down direction decreases from the third flat portion 553 to the connecting section 540.

The inclination angle: formed by the largest surface of the second twist section 534 and the largest surface of the third flat portion 553 may increase from the third flat portion 553 to the connecting section 540. The inclination angle A1 formed by the upper surface 51a of the second twist section 534 and the upper surface 51a of the third flat portion 553 may increase from the third flat portion 553 to the connecting section 540.

The height of the second twist section 534 may increase from the third flat portion 553 to the connecting section 540.

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

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 from the bending axis C2 than the short edge 541.

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

The radius of curvature of the long edge 542 is greater than the radius of curvature of the short edge 541. The short edge 541 may be located higher than the long edge 542.

The connecting section 540 includes a first horizontal end 543 connected to the first twist section 533 and a second horizontal end 544 connected to the second twist 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.

The inclination angle A2 formed by the largest surface of the connecting section 540 and the largest surface of the first flat portion 551 becomes maximum at between the first horizontal end 543 and the second horizontal end 544, and becomes minimum at between the first horizontal end 543 and the second horizontal end 544.

The inclination angle formed by the largest surface of the connecting section 540 and the upper surface 51a of the first flat portion 551 becomes maximum at between the first horizontal end 543 and the second horizontal end 544, and becomes minimum at the first horizontal end 543 and the second horizontal end 544.

The inclination angle A2 formed by the largest surface of the connecting section 540 and the upper surface 51a of the first flat portion 551 may be greater than the inclination angle A1 formed by the first twist section 533 and the upper surface 51a of the first flat portion 551 and the inclination angle formed by the second twist section 534 and the upper surface 51a of the first flat portion 551.

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

The radius of curvature of partial area of the first twist section 533 and the second twist section 534 may be greater than the radius of curvature R2 of the connecting section 540. The radius of curvature R2 of the connecting section 540 may be an average value of the radii of curvature of the long edge 542 and the short edge 541.

The radius of curvature R1 of the first outer edge 535 of the first twist section 533 and the second outer edge 536 of the second twist section 534 may be greater than the radius of curvature of the long edge 542 and the radius of curvature of the short edge 541 of the connecting section 540.

A portion of the curved portion 500 of one flat tube 50 may be located to overlap with the curved portion 500 of another flat tube 50 arranged to be adjacent to the one flat tube 50 in a horizontal direction.

The short edge 541 of one of the plurality of flat tubes 50 may be located to overlap with another long edge 542 adjacent to one flat tube 50. The long edge 542 of the first flat tube 50 is located to overlap with the short edge 541 of the second flat tube 50 in a horizontal direction.

When viewed from above, i.e., viewed in a first direction, the planar area of the first twist section 533 and the second twist section 534 may be larger than the planar area of the connecting section 540.

The flat tube 51 located at the uppermost end of the flat tube 50 may omit the curved portion 500, and may only have the first flat portion 551 and the third flat portion 553. An upper bent portion 59 may be formed in the first flat portion 551 and the third flat portion 553 of the flat tube 51 located at the uppermost end of the flat tubes 50. The upper bent portion 59 is formed by bending one end of the first flat portion 551 and the third flat portion 553 in one direction. The upper bent portion 59 may be formed by bending one end of the first flat portion 551 and the third flat portion 553 downward.

The flat tube 50 located at the lowest end of the flat tube 50 may omit the curved portion 500, and may have only the first flat portion 551 and the third flat portion 553. A lower bent portion 58 may be formed in the first flat portion 551 and the third flat portion 553 of the flat tube 50 located at the lowest end of the flat tube 50. The lower bent portion 58 is formed by bending one end of the first flat portion 551 and the third flat portion 553 in one direction. The lower bent portion 58 may be formed by bending one end of the first flat portion 551 and the third flat portion 553 upward.

The reason why the upper bent portion 59 and the lower bent portion 58 are necessary is to solve the problem that when the heat exchanger is placed upright, the curved portion 500 interferes with the floor or the ceiling of the machine room and cannot stand upright.

Furthermore, when water fills the lower portion due to the lower bent portion 58, the curved portion 500 is protected from corrosion as the curved portion 500 is not submerged. Furthermore, when the curved portion 500 protrudes upward, it is bent, so that the curved portion 500 is not submerged, thereby protecting the curved portion 500 from corrosion.

The length J2 of the curved portion 500 may be equal to or greater than the height J1 of the curved portion 500. This is because, if the length J2 of the curved portion 500 is shorter than the height J1 of the curved portion 500, bending occurs too abruptly over a short distance, thereby increasing stress in the curved portion 500.

The width W2 of the fin 60 may be greater than the width W1 of the flat tube 50. This facilitates drainage, as described below.

The value obtained by dividing the length J2 of the curved portion 500 by the height J1 of the curved portion 500 satisfies the following Equation 1.

W ⁢ 1 W ⁢ 2 × H ⁢ 2 < J ⁢ 2 J ⁢ 1 < W ⁢ 1 W ⁢ 2 × H ⁢ 1 < Equation ⁢ 1 >

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

The structure of the fin 60 will be described in detail below.

FIG. 11 is a cross-sectional view taken along line 11-11′ of FIG. 8, FIG. 12 is an enlarged view of a partial area of FIG. 11, and FIG. 13 is a partial front view of FIG. 11.

Referring to FIGS. 11 to 13, a plurality of fins 60 include an inner portion 610 located to overlap with a plurality of flat tubes 50 when viewed in a first direction which is the extension direction of the first header 431, and an outer portion 620 located not to overlap with a plurality of flat tubes 50 when viewed in the first direction.

A portion of the fin 60 protrudes to the outside of the flat tube 50, thereby preventing water from flowing in from the outside, and allowing water collected in a space between the fins 60 to be easily discharged to the outside.

In addition, the fin 60 partially protrudes to the outside of the flat tube 50, and the protruding lower end extends downward, thereby preventing water from flowing in from the outside, and allowing water collected in a space between the fins 60 to be easily discharged to the outside.

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.

The inner portion 610 is located to overlap with the flat tube 50 in the up-down direction.

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

The length of the inner portion 610 in the front-rear direction may be longer than the length of the outer portion 620 in the front-rear direction. This is because if the length of the inner portion 610 becomes shorter than that of the outer portion 620, the area for heat exchange with the flat tube 50 decreases.

Even if the heat of the flat tube 50 is transferred to the fin 60 in the inner portion 610 and external water flows into from the outer portion 620, the lower side of the outer portion 620 is not blocked by the tube, so that the surface tension becomes weaker than gravity, thereby causing the water to fall.

Water located in the space between the fins 60 in the inner portion 610 spreads out in a horizontal direction due to surface tension. Some of the spread water falls downward in the outer portion 620. The water in the inner portion 610 moves to the outer portion 620 due to surface tension and viscosity. The water moved to the outer portion 620 falls again due to gravity. Therefore, there is an advantage in that the water collected in the space between the fins 60 may be easily discharged to the outside.

The front-rear width of the outer portion 620 may be smaller than the distance between adjacent flat tubes 50. This is because if the front-rear width of the outer portion 620 is larger than the distance between adjacent tubes, the heat exchange area is reduced, so that the heat exchange efficiency is decreased and the ability of suppressing water inflow is not enhanced.

The outer portion 620 is located so as not to overlap with the flat tube 50 in the front-rear direction.

At least a portion of the inner portion 610 is located so as to overlap with 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 on which the inner portion 610 located is in the front-rear direction.

The fin 60 may 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 up-down direction, a plurality of second bodies 613, 623 that extend in the up-down direction and are located between the plurality of first bodies 611, 621, an upper body 615, 625 connecting the upper end of the first body 611, 621 and the upper end of the second body 613, 623 that are adjacent to each other, and a lower body 617 connecting the lower end of the first body 611, 621 and the lower end of the second body 613, 623 that are adjacent to each other.

Obviously, in some embodiment, the first body 611, 621 and the second body 613, 623 may have an inclination with respect to the up-down direction.

The first body 611, 621 and the second body 613, 623 are arranged to face each other, and may be arranged parallel to each other.

The upper body 615, 625 is connected to the lower end of the flat tube 50 located at the upper portion among the adjacent flat tubes 50, and the lower body 617 is connected to the upper end of the flat tube 50 located at the upper portion among the adjacent flat tubes 50.

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

The upper body 615, 625 is located so as not to overlap with the lower body 617 in a vertical direction. The upper body 615, 625 and the lower body 617 are located alternately in the left-right direction.

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

The first body 611, 621 and the second body 613, 623 may define a surface intersecting with the left-right direction.

The first body 611, 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 body 613, 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 body 615, 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.

That is, the inner portion 610 may include a first inner body 611, a second inner body 613, an upper inner body 615, and a lower inner body 617, and the outer portion 620 may include a first outer body 621, a second outer body 623, and an upper outer body 625.

The first inner body 611 extends in an up-down direction, and the second inner body 613 extends in an up-down direction, and is located between a plurality of first inner bodies 611.

The fin 60 may include a plurality of penetration portions formed by penetrating a portion of the inner portion 610, and a plurality of louvers 651 covering a portion of the penetration portion.

The penetration portion and the louver may be formed in the first inner body 611 or/and the second inner body 613.

The upper inner body 615 connects the upper end of the first inner body 611 and the upper end of the second inner body 613 that are adjacent to each other, and is in contact with one flat tube 50 among the plurality of flat tubes 50.

The lower inner body 617 connects the lower end of the first inner body 611 and the lower end of the second inner body 613 that are adjacent to each other, and is in contact with another flat tube 50 among the plurality of flat tubes 50.

The upper inner body 615 is located so as not to overlap with the lower inner body 617 in the vertical direction. The upper inner body 615 and the lower inner body 617 are alternately arranged in the left-right direction.

Obviously, in another embodiment where the first inner body 611 and the second inner body 613 are inclined with respect to the vertical direction, the center of the upper inner body 615 is located so as not to overlap with the center of the lower inner body 617 in the vertical direction.

The first outer body 621 extends in the up-down direction, and is connected to the first inner body 611. The first outer body 621 is connected to the rear end of the first inner body 611.

The second outer body 623 extends in the up-down direction, is located between a plurality of first outer bodies 621, and is connected to the second inner body 613. The second outer body 623 is connected to the rear end of the second inner body 613.

The upper outer body 625 connects the upper end of the first outer body 621 and the upper end of the second outer body 623 that are adjacent to each other. The upper outer body 625 does not come into contact with the flat tube 50. The upper outer body 625 is connected to the upper inner body 615.

Hereinafter, a method for manufacturing an evaporator according to an embodiment of the present disclosure will be described in detail.

FIGS. 14 to 16 are diagrams illustrating a manufacturing process of a heat exchanger according to an embodiment of the present disclosure.

Referring to FIG. 14, a plurality of flat tubes 50 having a linear shape are prepared, and a first header 431 and a second header 433 are connected to both ends of the plurality of flat tubes 50. Fins 60 are arranged between the first flat portions 531 of the flat tubes 50 that are adjacent to each other and between the second flat portions 532 of the flat tubes 50 that are adjacent to each other.

Referring to FIG. 15, the flat tube 50 is bent by placing a bending pole 700 against the curved portion 500.

Referring to FIG. 16, when the first flat portion 531 and the second flat portion 532 become nearly parallel, the bending pole 700 is removed.

FIG. 17 is a cross-sectional view taken along line 17-17′ of FIG. 4, and FIG. 18 is a cross-sectional view taken along line 18-18′ of FIG. 4.

Referring to FIGS. 17 and 18, the present disclosure has a cross-sectional area ratio of refrigerant tubes in the evaporator and condenser which enables stable operation by balancing heat exchange volume between the condenser and the evaporator and ensuring the supercooling degree and superheating degree of a cycle.

The cross-sectional area of each channel of the condensation refrigerant tube 410 is smaller than the cross-sectional area of each evaporation refrigerant tube 310. The value obtained by dividing the sum of the cross-sectional areas the condensation of refrigerant tubes 410 by the sum of the cross-sectional areas of the evaporation refrigerant tubes 310 may be 1.3 or less.

Preferably, the value obtained by dividing the sum of the cross-sectional areas of the condensation refrigerant tubes 410 by the sum of the cross-sectional areas of the evaporation refrigerant tubes 310 may be greater than 1.1 and less than or equal to 1.3. If the value obtained by dividing the sum of the cross-sectional areas of the condensation refrigerant tubes 410 by the sum of the cross-sectional areas of the evaporation refrigerant tubes 310 is 1.1 or less, the degree of supercooling and superheating cannot be sufficiently secured. In addition, even if the value obtained by dividing the sum of the cross-sectional areas of the condensation refrigerant tubes 410 by the sum of the cross-sectional areas of the evaporation refrigerant tubes 310 exceeds 1.3, the degree of supercooling and superheating cannot be sufficiently secured.

Here, the cross-sectional area of the condensation refrigerant tube 410 refers to a cross-sectional area obtained by cutting the condensation refrigerant tube 410 in a direction parallel to the air flow direction. Specifically, the cross-sectional area of the condensation refrigerant tube 410 is a total cross-sectional area occupied by the condensation refrigerant tube 410 in a cross-sectional area of the condenser cut by a plane parallel to the front-rear direction and the up-down direction.

More specifically, the total cross-sectional area of the condensation refrigerant tube 410 may be the total cross-sectional area of the first flat portion 531 and the second flat portion 532, in the cross-section.

Here, the cross-sectional area of the evaporation refrigerant tube 310 refers to the cross-sectional area of the evaporation refrigerant tube 310 cut along a direction parallel to the air flow direction. Specifically, the cross-sectional area of the evaporation refrigerant tube 310 is the total cross-sectional area occupied by the evaporation refrigerant tube 310 in a cross-sectional area of the evaporator cut by a plane parallel to the front-rear direction and the up-down direction.

The cross-section of the evaporation refrigerant tube 310 is circular, and the cross-section of the condensation refrigerant tube 410 may have a length parallel to the airflow direction that is greater than a length intersecting with the airflow direction. That is, the cross-section of the condensation refrigerant tube 410 may have a length in the front-rear direction that is greater than a length in the up-down direction.

The evaporation refrigerant tube 310 may be arranged in four to eight rows in the airflow direction. The evaporation refrigerant tubes 310 are arranged in four to eight rows spaced apart from each other in the front-rear direction.

The evaporation refrigerant tube 310 may be defined as a first row 311, a second row 312, a third row 313, and a fourth row 314 from the front.

Two adjacent rows of evaporation refrigerant tubes 310 may be located so as not to overlap in the airflow direction. Specifically, the evaporation refrigerant tubes 310 of the first row 311 and the second row 312 are arranged so as not to overlap in the front-rear direction.

FIG. 19 is a plan view illustrating a condenser 400′ according to another embodiment of the present disclosure.

Referring to FIG. 19, the condenser 400′ according to another embodiment (a second embodiment) of the present disclosure differs from the embodiment of FIG. 6 (a first embodiment) in that the third flat portion 553 and the fourth flat portion 554 are omitted, and one ends of the first flat portion 551 and the second flat portion 552 are connected by the curved portion 500.

Hereinafter, unless specifically described, the second embodiment is considered to be identical to the first embodiment.

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. The first header 431 is connected to the first flat portion 551, and the second header 433 is connected to the second flat portion 552.

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 so as not to 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 downward from the first flat portion 551.

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 so as not to 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 upward from the second flat portion 552.

FIG. 20 is a plan view illustrating a condenser 400″ according to another embodiment of the present disclosure.

Referring to FIG. 20, the condenser 400″ according to another embodiment (a third embodiment) of the present disclosure differs from the embodiment of FIG. 6 (the first embodiment) in the structures of the third fin 643 and the fourth fin 644.

Hereinafter, any portion of the third embodiment that is not specifically described will be considered identical to the first embodiment.

The third fin 643 may not be exposed to the outside of the third flat portion 553 when viewed in a first direction (from above).

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

The fourth fin 644 may not be exposed to the outside of the fourth flat portion 554 when viewed in the first direction (from above).

The fourth fin 644 may completely overlap with the fourth flat portion 554 when viewed from above, and the width of the fourth fin 644 may be less than or equal to the width of the fourth flat portion 554.

The clothing processing apparatus of the present disclosure has one or more of the following effects.

First, the present disclosure bends the middle of a plurality of flat tubes arranged between two headers, and forms a multi-row arrangement of flat tubes with multiple channels to intersect with the direction of air movement, thereby facilitating a connection between the header and the refrigerant tube and between the header and the connecting pipe, simplifying the structure, facilitating manufacturing, reducing manufacturing costs, and reducing the flow resistance of refrigerant.

Second, the present disclosure can reduce manufacturing costs and facilitating bending of flat tubes by not arranging fins disposed between multiple flat tubes at the bending portion of the flat tubes.

Third, when bending the flat tube, if the flat tube is bent on the horizontal surface, when the widest surface of the flat tube is parallel to the horizontal direction, the present disclosure can bend flat tubes spaced apart in a vertical direction at one time by using a single rod, thereby being able to easily bend a flat tube having a longitudinal shape by twisting the curved portion when bending.

Fourth, the present disclosure forms multi-row condenser which require a large amount of heat so as to reheat air within the air path and supply it to the tub by using microchannels, so that it is easy to control the temperature of the air supplied to the tub, and it is easy to configure the counterflow, thereby enhancing heat exchange performance.

Fifth, when arranging condensers in multiple rows, within a machine room with limited space, the present disclosure can minimize the length of the refrigerant pipe connecting the condenser and evaporator and the compressor and the expansion valve, and reduce the increase in flow resistance caused by the refrigerant pipe, by arranging all of the pipe supplying the refrigerant to the condenser and the pipe through which the refrigerant flows out from the condenser in the same direction, and also arranging the refrigerant pipe of the evaporator in the same direction as the condenser.

Sixth, the present disclosure utilizes a microchannel heat exchanger as the condenser, utilizes a fin-tube heat exchanger as the evaporator in the machine room of a clothing processing apparatus, utilizes a fin-tube heat exchanger having a low manufacturing cost as the evaporator requires relatively little energy, and utilizes a microchannel heat exchanger as the condenser which requires a large amount of heat to reheat the air in the air path and supply it to the tub, thereby improving heat exchange performance, reducing airflow resistance, and lowering manufacturing costs.

Seventh, the present disclosure forms both an evaporator and a condenser made of aluminum, thereby enhancing corrosion resistance in the airflow of a clothing processing apparatus with high moisture content, enhancing the reliability of the clothing processing apparatus, and preventing galvanic corrosion caused by the combined use of copper and aluminum.

Eighth, the present disclosure adjusts the cross-sectional area ratio of the refrigerant tubes in the evaporator and the condenser to balance the heat exchange volume between the condenser and the evaporator, and is able to perform a stable operation by ensuring the degrees of supercooling and superheating of a cycle.

While the embodiments of the present disclosure have been described above with reference to the attached drawings, the present disclosure is not limited to the above embodiments and may be manufactured in various different forms. Those skilled in the art will understand that the present disclosure may be implemented in other specific forms without altering the technical concept or essential features of the present disclosure. Therefore, the embodiments described above should be understood as illustrative in all respects and not restrictive.