Patent Description:
Generally, a laundry processing apparatus means all devices for managing clothing, such as washing, drying, and removing wrinkles, at home or at laundromat. For example, the laundry processing apparatus includes a washing machine for clothing, a drying machine for clothing, a washing machine having both drying and washing functions, a refresher for refreshing clothing, a steamer for removing wrinkles of clothing, and the like.

The clothing drying machine of the laundry processing apparatus includes a heat pump system. The clothing drying machine is configured to supply high temperature air to an object to be processed such as clothing and bed linen (hereinafter, which referred to as clothing) which are inserted into a processing space (drum or steamed space in which clothing hangs), through the operation of the heat pump system. Thus, moisture contained in the clothing to be processed is evaporated so that the clothing to be processed is dried.

The clothing drying machine may include an exhaust type drying machine and a condensation type drying machine that are classified according to the processing method of high temperature and humidity air escaping from a processing space after drying the clothing to be processed. The exhaust type drying machine is configured to discharge the high temperature and humidity air generated during drying operation directly to the outside of the drying machine. The condensation type drying machine is configured to condense moisture contained in the air through the heat exchange while circulating the high temperature and humidity air without discharging the high temperature and humidity air to the outside.

Meanwhile, <CIT> and US Patent No. <CIT> propose the laundry processing apparatus, wherein condensed water is generated while the high temperature and humidity air generated for drying heated air passes through an evaporator, which is a heat exchanger, and an air inlet portion of the evaporator is washed by using the generated condensed water or water supplied through a water pipe.

Accordingly, even when foreign matter such as lint generated from the clothing to be processed is collected on the air inlet portion (front surface) of the evaporator, the air inlet portion is periodically washed, thus the deterioration of heat exchange performance by the evaporator may be prevented.

In particular, since the method of washing the evaporator by itself using the generated condensed water (hereinafter, it is referred to as "self-washing") does not use a method of receiving water through the water pipe, the laundry processing apparatus can be installed anywhere indoors.

However, the self-washing type laundry processing apparatus according to the related art has a problem in that a front surface of the evaporator is not sufficiently washed. In order to increase the washing rate of the front surface of the evaporator, washing water (condensed water) should remove foreign matter such as lint while flowing downward in a direction of gravity along the front surface of the heat exchanger. However, the condensed water does not flow along the surface of the evaporator and flows into the evaporator, thus a lower portion of the front surface of the evaporator is not sufficiently washed.

The deviation of the washing water may be caused due to various reasons: (i) the condensed water spraying toward the surface of the evaporator flows into the evaporator by a blowing force of air blown toward the evaporator during the operational process of a heat pump; (ii) the surface tension of an outer surface of the evaporator is reduced due to a coating layer treated on the outer surface of the evaporator for waterproofing, so that the condensed water may penetrate into the evaporator; or (iii) the washing water may be introduced into the evaporator by the Coanda effect in which fluid formed near a surface of an object is attached to the surface of the object by difference in pressure.

Further, the amount of the condensed water generated in the operational process of the self-washing type laundry processing apparatus is in proportion to the amount of the clothing to be processed, so the cleaning flow rate of the condensed water is not constant. When the amount of the condensed water is large, at least part of the condensed water is discharged ahead of the surface of the evaporator, so that the flow rate flowing the surface of the evaporator may be sufficiently supplied even when the condensed water is discharged by deviating toward the evaporator due to the reasons described above. On the other hand, when the amount of the condensed water is small, the condensed water cannot be discharged ahead of the surface of the evaporator and penetrates into the inside of the evaporator thereby degrading the performance of washing the evaporator.

<CIT> discloses a laundry processing apparatus comprising a cabinet and a washing unit, the washing unit being configured to spray washing water on a front surface of the heat exchanger into which the exhaust air flows.

<CIT> discloses a laundry processing machine having a heat exchanger with a washing unit.

Accordingly, the present invention has been made keeping in mind the above problems occurring in the related art, and the present disclosure is intended to guide a discharge direction of condensed water (washing water) so that the discharge direction thereof directs ahead of a surface of a heat exchanger, thereby washing evenly to a lower side of the surface of the heat exchanger.

Another object of the present invention is to effectively wash the surface of the heat exchanger even when the amount of the condensed water (washing water) is not constant. The invention is specified by the independent claim.

In order to achieve the above objectives, according to one aspect of the present invention, there is provided a laundry processing apparatus. In the laundry processing apparatus, a washing unitis be provided in an installation space of a cabinet, which has the installation space therein and corresponds to an upper portion of the heat exchanger, to spray washing water to a front surface of the heat exchanger into which exhaust air flows. The washing unit has a guide end, the guide end protrudes from an end of a nozzle part toward a front guide part. The guide end guides the washing water toward the front surface of the heat exchanger, so that the washing water performs the washing evenly to a lower side of the front surface of the heat exchanger without being introduced into the heat exchanger.

In the present invention, the washing unit is provided in the installation space of the cabinet, which has the installation space therein and corresponds to the upper portion of the heat exchanger, to spray the washing water to the front surface of the heat exchanger into which the exhaust air may flow. Herein, the washing unit has: the nozzle part provided at the upper portion of the heat exchanger in the inclined direction to guide the washing water toward the heat exchanger; and the front guide part provided at an opposite side of the nozzle part while being spaced apart therefrom, with the front surface of the heat exchanger interposed between the nozzle part and the front guide part, to guide the washing water toward the front surface of the heat exchanger. A nozzle guide end protrudes from an end of the nozzle part, and the nozzle guide end guides the washing water to be sprayed at a predetermined angle ahead of the front surface of the heat exchanger, considering the tendency of the washing water to be deviated to the inside of the heat exchanger.

The guide end is the nozzle guide end protruding from the end of the nozzle part toward the front guide part, and a relative ratio (X/L) between a protruding length (X) of the nozzle guide end and a distance (L) between the nozzle guide end and the front guide part is set between <NUM> to <NUM> so that the optimum washing water spray angle (β°) may be obtained. Accordingly, the washing rate may be improved.

An inclined or curved spray surface that is continuously extended from the end of the nozzle part may be formed at an upper surface of the nozzle guide end. The spray surface may include: a first inclined surface protruding from the nozzle part; and a second inclined surface protruding from the first inclined surface and extended in a downward inclined direction toward a front of the heat exchanger than the first inclined surface. The inclined or curved front guide part may deliver smoothly the washing water toward the front guide part. Therefore, even when the flow rate of the washing water is reduced, the washing water may be prevented from being sprayed directly toward the front surface of the heat exchanger without passing through the front guide part.

The spray surface of the nozzle guide end through which the washing water may flow may be extended at a more gentle angle than an angle at which the nozzle part may be inclined at a downward inclined angle toward an outer surface of the heat exchanger, or may be extended in an upward inclined direction toward the front guide part. The spray surface may prevent the washing water from being sprayed directly toward the front surface of the heat exchanger without passing through the front guide part.

The nozzle part may be connected to an outlet of the water tube, and be arranged between a base extended toward the front of the heat exchanger while being inclined downward and a cover extended while being spaced upward from the base. The nozzle guide end may have a protruding shape from the nozzle part, thus the nozzle guide may be formed while using an existing shape of the nozzle part.

The base may include: a connection channel extended from the outlet of the water tube and having a height gradually lowered toward the front surface of the heat exchanger along a direction of gravity; and a discharge channel extended from the connection channel toward the front of the heat exchanger and having an inclined angle larger than an inclined angle of the connection channel. The nozzle guide end may protrude from an end of the discharge channel. Herein, the discharge channel may have a steeply inclined surface extended toward the front of the heat exchanger and having an inclined angle larger than the discharge channel. The steeply inclined surface may provide a steep slope to guide the flow rate of the washing water to be faster. The washing water with increased flow rate may be delivered fast toward the front guide part while passing through the spray surface.

The nozzle guide end may be in a position retracted from the front surface of the heat exchanger based on a direction of moving the washing water and be spaced upward from an upper surface of the heat exchanger, the end of the front guide part may be spaced apart from the front surface of the heat exchanger and be in a position lower than the upper surface of the heat exchanger. Whereby, the washing water discharged from the nozzle part may be smoothly supplied to the front surface of the heat exchanger without interference with the heat exchanger, and the washing water may be prevented from being sprayed to the upper surface of the heat exchanger.

The nozzle guide end may be in a relatively higher position than the end of the front guide part based on the direction of gravity. The nozzle guide end at the relatively high position may supply the washing water to the end of the front guide part at the relatively low position, so that the supply of the washing water may be stable.

When a distance (D2) in which the nozzle guide end is retracted from the front surface of the heat exchanger is between <NUM> to <NUM> and a height (H2) in which the nozzle guide end is spaced upward from the upper surface of the heat exchanger is between <NUM> to <NUM>, a length (X) in which the nozzle guide end protrudes toward the front guide part may be between <NUM> to <NUM>. The washing rate may be improved by the protruding length.

The washing water discharged from the washing unit may be discharged through between the nozzle guide end and the front guide part, and the spray angle (β) formed in a direction away from the front surface of the heat exchanger based on the direction of gravity may be between <NUM>° to <NUM>°, and the internal angle (α) formed between the upper surface of the nozzle guide end and the outer surface of the discharge channel may be between <NUM>° to <NUM>°.

The nozzle guide end may be extended in a left to right width direction of the nozzle part. A plurality of nozzle guide ends that are spaced apart from each other may be arranged in the discharge channel of the nozzle part in a left to right direction of the discharge channel, and falling spaces that are open in the direction of gravity may be formed between the nozzle guide ends. The falling space may prevent all of the washing water from being sprayed forward of the heat exchanger when the flow rate of the washing water is fast.

A length (X1) in which the nozzle guide end may protrude toward the front guide part or a thickness (Y1) of the nozzle guide end may be configured to be different from each other.

The installation space may have a base cover that covers at least a part of the upper portion of the heat exchanger, the base cover may be configured by assembling a front cover and a rear cover to each other, and the front guide part may be provided at a lower surface of the front cover and the nozzle part may be provided at a lower surface of the rear cover.

As described above, the laundry processing apparatus according to the present disclosure has the following effects.

The condensed water generated during operation of a heat pump system in the laundry processing apparatus is used as washing water for the heat exchanger (evaporator). The washing unit of the present disclosure sprays the washing water (the condensed water) in a front direction of the heat exchanger where foreign matter such as lint is collected. Considering the tendency of the washing water to deviate into the heat exchanger, the washing unit guides a direction of the washing water so that the washing water is sprayed forward at a predetermined angle than a front surface of the heat exchanger. Accordingly, the washing water does not flow into the inside of the heat exchanger, and washes to the lower side of the front surface of the heat exchanger evenly, and as a result, the washing efficiency of the washing unit can be improved.

In the present disclosure, the washing direction of the washing water is set by the nozzle part spraying the condensed water and the front guide part facing the nozzle part, with the front surface of the heat exchanger interposed between the nozzle part and the front guide part. The guide end protrudes from at least one of the nozzle part and the front guide part. The guide end can guide the washing water to flow onto the front surface of the evaporator constituting the heat exchanger, thereby minimizing unwashed sections in the heat exchanger.

In the guide end constituting the present disclosure, the nozzle guide end formed at the nozzle part can prevent maximally the sprayed washing water from being sprayed directly toward the front surface of the heat exchanger without passing through the front guide part.

Further, the spray angle (β°) of the washing water and the washing rate associated thereto vary in response to the relative ratio (X/L) between the protruding length (X) of the nozzle guide end and the separate distance (L) between the nozzle guide end and the front guide part. In the present disclosure, as the optimum relative ratio is set, the washing rate can be improved.

Further, in the present disclosure, the spray surface through which the washing water flows is formed in the inclined surface or the curved surface at the upper surface of the nozzle guide end. Since the inclined or curved spray surface can smoothly deliver the washing water toward the front guide part, even when the flow rate of the washing water is reduced, it is possible to prevent the washing water from being sprayed directly toward the front surface of the heat exchanger without passing through the front guide part. Accordingly, even when the amount of the washing water (the condensed water) is not constant, the washing unit can wash the front surface of the heat exchanger evenly and can always provide a high washing rate regardless of a usage pattern of a user.

Further, the nozzle guide end may be formed at the base cover in which the washing unit is installed, and may be formed at a boundary portion between a moving side die and a slide core in a mold for forming the base cover. The boundary portion between the moving side die and the slide core has a parting line, thus the boundary portion is an error-prone portion in the manufacturing process. As the boundary portion is changed into a protruding shape rather than a flat surface or a curved surface, the influence of the error caused during the manufacturing process can be reduced and the product reliability can be increased.

Further, the nozzle guide end constituting the present disclosure includes a plurality of nozzle guide ends, and the falling space which is open along the direction of gravity is provided between the nozzle guide ends, so that part of the washing water can be guided to fall in the direction of gravity to face the front surface of the heat exchanger. The falling space prevents all of the washing water from being sprayed forward of the heat exchanger when the flow rate of the washing water is fast. Accordingly, even when the flow rate of the washing water is not constant, the heat exchanger washing rate above a predetermined level can be maintained.

Further, the nozzle part and the front guide part positioned in the washing unit of the present disclosure can be installed at two components (front cover and rear cover) constituting the base cover, respectively. In this case, a relative distance between the nozzle part and the front guide part may vary depending on manufacturing tolerances or assembly tolerances of the two components. However, in the present disclosure, the nozzle guide end protrudes to extend the flow path toward the front guide part, thus some errors can be compensated. Accordingly, the reliability of the washing operation using the washing unit can be improved.

Further, in the guide ends of the present disclosure, the front guide end formed at the front guide part protrudes in a falling direction of the washing water to guide the sprayed washing water in a perpendicular direction. Whereby, it is possible to maximally prevent the washing water from being directly sprayed toward the front surface of the heat exchanger, and to further reduce the unwashed sections in the heat exchanger.

The spray angle (β°) of the washing water and the washing rate associated thereto vary in response to a relative ratio between the protruding length (H1) of the front guide end and the separate distance (L) between the nozzle guide end and the front guide part. In the present disclosure, as the optimum relative ratio is set, the washing rate can be improved.

Further, in the present disclosure, the nozzle guide end and the front guide end have forms protruding from the nozzle part and the front guide part, so that the nozzle guide end and the front guide end can be molded while using existing forms of the nozzle part and the front guide part. Accordingly, manufacturing facilities for molding the washing unit can have high compatibility and manufacturing can be easy.

Hereinbelow, some embodiments of the present disclosure will be described in detail with reference to exemplary drawings. Like reference numerals are used to identify like elements throughout different drawings. Further, in the following description, when it is decided that the detailed description of known function or configuration related to the invention makes the subject matter of the present disclosure unclear, the detailed description is omitted.

The present disclosure relates to a laundry processing apparatus and includes a heat pump system. The present disclosure is configured to repeat an operation in which high temperature and dry air supplied from the heat pump system performs heat processing for clothing or bed linen to be processed and then humid air containing moisture while drying clothing to be processed is supplied to the heat pump system again and circulated. In the process, foreign matter such as lint is collected in an air inlet part formed in a front surface (<NUM>, referring to <FIG>) of an evaporator <NUM> that is a heat exchanger constituting the heat pump system. The foreign matter is washed away using condensed water generated during an operational process of the heat pump system. A structure and a method of washing using the condensed water will be described in detail below.

Hereinbelow, a clothing drying machine is described as an example of the laundry processing apparatus, and the present disclosure can be applied to various laundry processing apparatus including the heat pump system, such as a washing machine for drying, a washing machine for both drying and washing, in addition to the clothing drying machine, a refresher for refreshing clothing, and a steamer removing wrinkles of the clothing.

<FIG> depicts a configuration of the laundry processing apparatus according to an embodiment of the present disclosure and external structures such as a cabinet <NUM> are indicated by dotted lines for showing an internal structures. <FIG> depicts a lower structure including the heat pump system of <FIG>. <FIG> depicts an exploded states of components shown in <FIG>.

As shown in the drawings, the laundry processing apparatus according to the embodiment of the present disclosure includes the cabinet <NUM>, a drum <NUM>, the heat pump system, a circulation fan <NUM>, the washing unit (C), a drainage tank <NUM>, and a controller <NUM>. In the components, partial components constituting the heat pump system are installed at a lower portion of the laundry processing apparatus while being distributed, and the washing unit (C) constitutes a part of the lower structure and is not needed to be a separate structure.

Describing the components sequentially, the cabinet <NUM> makes an exterior of the laundry processing apparatus. The cabinet <NUM> is formed in a container body in which an empty installation space is arranged, and multiple components may be assembled to constitute one cabinet <NUM>, and the installation space may be partitioned into several spaces. In the embodiment, the cabinet <NUM> is formed of a metal material, but may be formed of various materials including synthetic resin. Further, the cabinet <NUM> has an exterior shape of an approximately hexahedral structure in the embodiment, but the exterior shape thereof may be variously modified.

The cabinet <NUM> has a door <NUM> at a front surface thereof, and an entrance <NUM> for the clothing to be processed is arranged inside the door <NUM>. The entrance <NUM> for the clothing to be processed is exposed outward when the door <NUM> is opened, so that the clothing to be processed may be inserted into an interior space of the drum <NUM>. In the embodiment, at least a part of the door <NUM> is formed of a transparent or translucent material so that the interior space of the drum <NUM> is visible. The door <NUM> is opened and closed using a hinge, but a folding method or a sliding method may be applied thereto.

A lower frame <NUM> is arranged at a lower portion of the cabinet <NUM>. The lower frame <NUM> has an approximately square frame shape and is positioned in a bottom side of the installation space of the cabinet <NUM>. Various components including the heat pump system are installed in the lower frame <NUM>. The lower frame <NUM> provides an installation part in which the various components are installed and allows air after completing heat processing process to flow through an upper space of the lower frame <NUM>.

As shown in <FIG> and <FIG>, the lower frame <NUM> has a drum motor installation part <NUM>. The drum motor installation part <NUM> is a space in which a drum motor <NUM> to be described below is installed and has a downward depressed shape. A compressor installation part <NUM> is positioned at a position adjacent to the drum motor installation part <NUM>, and a compressor <NUM> to be described below is installed therein. The drum motor installation part <NUM> and the compressor installation part <NUM> are respectively positioned at opposite sides to the heat exchanger and a circulation flow path (H) based on a condensed water collecting part <NUM>.

The lower frame <NUM> has the condensed water collecting part <NUM>. The condensed water collecting part <NUM> is connected with the circulation flow path (H), which will be described below, to recover the condensed water generated from the heat exchanger. More precisely, the condensed water that has fallen to a bottom of the circulation flow path (H) is collected in the condensed water collecting part <NUM>. Therefore, the condensed water collecting part <NUM> has the shape depressed toward the bottom. The condensed water collecting part <NUM> is provided with a water pump <NUM> which will be described below. The water pump <NUM> may deliver the condensed water collected in the condensed water collecting part <NUM> to the drainage tank <NUM>, and supply the condensed water in the drainage tank <NUM> to the washing unit (C) side. In <FIG>, a water cover <NUM> provided at a bottom of a heat exchange space <NUM>, and the water cover <NUM> may be omitted when the evaporator <NUM> that is the heat exchanger and a condenser <NUM> are spaced apart from the bottom of heat exchange space <NUM>.

Referring to <FIG>, an input and output panel <NUM> is installed at a front surface or an upper surface of the laundry processing apparatus. In the embodiment, the input and output panel <NUM> is installed at a position adjacent to the drainage tank <NUM>. The input and output panel <NUM> may include an input part <NUM> through which a user may enter a selection of a clothing processing course and an output part <NUM> visually displaying operation states of the laundry processing apparatus.

The drum <NUM> is installed in the installation space of the cabinet <NUM> to be rotatable. As shown in <FIG>, the drum <NUM> is supported to be rotatable by a roller <NUM> in the cabinet <NUM>. A plurality of rollers <NUM> may be installed to be in contact with an outer surface of the drum <NUM>. The drum <NUM> is formed in a cylindrical body having openings at front and rear surfaces thereof. Referring to <FIG>, a front opening <NUM> of the drum <NUM> communicates with the entrance <NUM> of the cabinet <NUM>, and a rear opening <NUM> is positioned at the opposite side of the front opening <NUM>.

High temperature and dry air passes through an inside space of the drum <NUM> to perform heat processing to the clothing to be processed. The high temperature and dry air is introduced through the rear opening <NUM> of the drum <NUM> into the inside of the drum <NUM> and then is discharged through the front opening <NUM> of the drum <NUM> to the outside of the drum <NUM>. In <FIG>, arrow ① indicates a direction in which the high temperature and high humidity air after performing heat processing (drying) to the clothing to be processed is discharged through the front opening <NUM> of the drum <NUM> to the outside of the drum <NUM>.

Referring to <FIG> and <FIG>, a front supporter <NUM> is provided at a front side where the door <NUM> is provided and a rear supporter <NUM> is provided at a rear side, with the drum <NUM> disposed between front supporter <NUM> and rear supporter <NUM>. The drum <NUM> is supported to be rotatable by the front supporter <NUM> and the rear supporter <NUM>.

A heat exchange module <NUM> will be described below, the heat exchange module <NUM> includes the evaporator <NUM> that is the heat exchanger, the condenser <NUM>, and the circulation fan <NUM> that are provided in the heat exchange module <NUM>. The heat exchange module <NUM> covers the above components and further includes components <NUM>, <NUM>, and <NUM> that form the circulation flow path (H) therein. The heat exchange module <NUM> is provided at a position corresponding to the opposite side to the compressor installation part <NUM> and the drum motor installation part <NUM>.

A front duct connector <NUM> is provided at a side of the heat exchange module <NUM> adjacent to the front opening <NUM> of the drum <NUM>. The front duct connector <NUM> is extended in a vertical direction to connect the front opening <NUM> of the drum <NUM> to a heat exchange guide <NUM> which will be described below. The front duct connector <NUM> may be an outlet duct <NUM> since the front duct connector <NUM> provides a flow path in the drum <NUM> to discharge the air after performing heat processing for the clothing to be processed.

A rear duct connector <NUM> is provided at a rear opening <NUM> of the drum <NUM>, and the rear duct connector <NUM> is also extended in the vertical direction to allow the high-temperature dry air to be introduced into the drum <NUM>. Therefore, as the rear duct connector <NUM> forms a flow path introduced into the drum <NUM>, the rear duct connector <NUM> may be an inlet duct <NUM>. As described above, the front duct connector <NUM> and the rear duct connector <NUM> are respectively positioned at the opposite ends of the heat exchange module <NUM> so that air before/after the heat exchange may be introduced inward and discharged outward.

The high temperature and humidity air after completing the heat processing for the clothing to be processed in the drum <NUM> is discharged through the front opening <NUM> (referring to arrow ② in <FIG>), is delivered through the front duct connector <NUM> that is the outlet duct <NUM> (referring to arrow (<NUM>) in <FIG>), and then is guided by the heat exchange guide <NUM> in a direction toward the heat exchanger (referring to arrow ③ in <FIG>). The heat exchange guide <NUM> corresponds to a part into which the air delivered through the front duct connector <NUM> is introduced. A direction of the air is switched toward the rear of the lower frame <NUM> while the air passes through the heat exchange guide <NUM> so that the air is introduced into the heat exchange space <NUM>. In <FIG> and <FIG>, arrow ④ indicates a direction in which the heat exchange is performed while the air passes through the heat exchange space <NUM>.

The heat exchange space <NUM> is a space in which the heat exchanger is installed, and the evaporator <NUM> removing moisture from the air introduced from the heat exchange guide <NUM> and the condenser <NUM> heating the dehydrated air are installed in parallel with each other therein. The heat exchange space <NUM> may be extended in a linear line from front to rear of the lower frame <NUM>. A side surface of the heat exchange space <NUM> is surrounded by a partition housing <NUM> connecting the heat exchange guide <NUM> to a circulation pan installation part <NUM> which will be described below. An upper portion of the heat exchange space <NUM> is covered by a base cover <NUM> so that the heat exchange space <NUM> may be cut off from the outside.

Referring to <FIG>, the heat pump system is briefly described below. A cycle is configured to sequentially evaporate, compress, condense, and expand refrigerant. When the heat pump system is operated, air is dried and becomes high temperature while sequentially performing heat exchange with the evaporator <NUM> and the condenser <NUM>. In detail, the refrigerant compressed in the compressor <NUM> becomes a high temperature and high pressure state and flows into the condenser <NUM>, and the refrigerant liquefies while discharging heat in the condenser <NUM>. The liquefied high pressure refrigerant is depressurized in an expander (E), the low temperature and low pressure liquid refrigerant flows into the evaporator <NUM>. The refrigerant becomes a low temperature and low pressure gas while evaporating in the evaporator <NUM>.

A process in which air passing through the heat pump system performs the heat exchange will be described below (referring to air flow in <FIG>). The high temperature and dry air that has passed through the condenser <NUM> passes through a circulation fan receiving part <NUM> and then supplies through the rear duct connector <NUM> to the drum <NUM> (referring to arrow ⑤ in <FIG> and <FIG>). The high temperature and dry air supplied to the drum <NUM> evaporates moisture of the clothing to be processed then becomes high temperature and humidity air. The high temperature and humidity air is recovered through the front duct connector <NUM>, and performs the heat exchange with the refrigerant in the evaporator <NUM> to become low temperature air.

As the temperature of air decreases, the amount of saturation water vapor in the air is recued and moisture contained in the air is condensed. Then, the low temperature dried air performs the heat exchange with the refrigerant in the condenser <NUM> to become high temperature and dry air and then is supplied to the drum <NUM> again. In the process, the condensed water is generated and the generated condensed water is collected in the condensed water collecting part <NUM> described above.

That is, the clothing to be processed in the drum <NUM> is dried by the high temperature and dry air supplied from the heat pump system by the circulation flow path (H), and the humidity air containing moisture after drying the clothing to be processed is supplied to the heat pump system thereby repeating circulated operation.

As shown in <FIG>, the circulation flow path (H) is shown in the drawing. The circulation flow path (H) is a flow path through which air is circulated. The circulation flow path (H) includes: a guide space <NUM> provided in the heat exchange guide <NUM>, the heat exchange space <NUM> connected to the guide space <NUM> and provided in the partition housing <NUM>, and the circulation fan receiving part <NUM> connected to the heat exchange space <NUM> and receiving the circulation fan <NUM>. The outlet duct <NUM>, the inlet duct <NUM>, and an exhaust port (<NUM>, referring to <FIG> and <FIG>) may be seen as part of the circulation flow path (H).

A rear cover <NUM> is coupled to one side of the circulation fan receiving part <NUM>, and as the rear cover <NUM> in between, the circulation fan <NUM> is positioned in the circulation fan receiving part <NUM> and a fan motor <NUM> is positioned at the opposite side to the circulation fan <NUM>. The circulation fan <NUM> suctions air in the heat exchange space <NUM> and discharges the air to the exhaust port <NUM> while being rotated by an operational force of the fan motor <NUM>. The circulation fan <NUM> is installed toward the condenser <NUM> to suction the air in the heat exchange space <NUM>. That is, the air sequentially passing through the evaporator <NUM> and the condenser <NUM> in the circulation flow path (H) by the operation of the circulation fan <NUM> is supplied through the inlet duct <NUM> into the drum <NUM>. Air that has performed the heat exchange for the clothing to be processed in the drum <NUM> circulates in a cycle of passing sequentially through the outlet duct <NUM>, the evaporator <NUM> and the condenser <NUM> in the circulation flow path (H).

The compressor installation part <NUM> described above is equipped with the compressor <NUM> that generates compressed air for the heat exchange. The compressor <NUM> is a component constituting the heat pump system, but does not directly perform the heat exchange with air, thus it is unnecessary for the compressor <NUM> to be installed in the circulation flow path (H). When the compressor <NUM> is installed in the circulation flow path (H), air flow interferes with the compressor <NUM>, so the compressor <NUM> may be preferably installed in a position away from the circulation flow path (H). Reference number <NUM> is a gas-liquid separator, and the gas-liquid separator separates refrigerant flowing into the compressor <NUM> into gas and liquid so that the gas shaped refrigerant flows into the compressor <NUM>. Reference number <NUM> is a cooling fan for cooling the compressor <NUM>.

The washing unit (C, referring to indicated portion in <FIG>) will be described below. The washing unit (C) is installed at a position in the installation space which corresponds to the upper portion of the heat exchanger, and serves to spray the washing water on a front surface <NUM> of the evaporator <NUM> for washing, the evaporator <NUM> being the heat exchanger in which exhaust air flows. The washing water may be the condensed water that is generated during the heat exchange process by the heat pump system or water introduced from the outside. When the condensed water is insufficient to be used as the washing water, the water introduced from the outside may be used as the washing water. In the embodiment, the washing water that is the condensed water passing through the condensed water collecting part <NUM> and stored in the drainage tank <NUM> will be described as an example.

First, describing an object washed by the washing unit (C), the washing unit (C) washes the front surface <NUM> of the evaporator <NUM> that is the heat exchanger. Herein, the front surface <NUM> of the evaporator <NUM> means a surface of the evaporator <NUM> which face the guide space <NUM>, and is formed in approximately a flat surface as shown in <FIG>. Foreign matter such as lint and the like is easily collected on the front surface <NUM> of the evaporator <NUM>, since foreign matter detached from the clothing to be processed is mixed with air heat-processing the clothing to be processed. Of course, it is possible to primarily filter foreign matter by placing a filter module at a position ahead of the evaporator <NUM> on the circulation flow path (H). However, when the filter module is not provided or part of foreign matter is not filtered by the filter module, foreign matter may be collected on the front surface <NUM> of the evaporator <NUM>.

The foreign matter may be washed away by the condensed water. The washing rate may vary in response to the flow rate of the flow amount and flow velocity, and in particular, the washing rate may be reduced in response to a direction of spraying the condensed water. Referring to arrow that indicates a discharge path of the condensed water in <FIG>, the condensed water is sprayed between a nozzle part (S) and a front guide part <NUM> and has a tendency of deviating to the front surface <NUM> of the evaporator <NUM>. When the condensed water deviates to the front surface <NUM> of the evaporator <NUM>, the condensed water may not wash the front surface <NUM> of the evaporator <NUM> and may be introduced into the inside of the evaporator <NUM>. That is, the washing is performed only on an upper partial portion of the front surface <NUM> of the evaporator <NUM>, and the washing rate may be reduced toward a lower portion thereof. The deviation may be attributed to a factor: (i) the condensed water spraying toward a surface of the evaporator <NUM> flows into the evaporator <NUM> by a blowing force of air blown toward the evaporator <NUM> during the operational process of a heat pump; (ii) the surface tension of an outer surface of the evaporator <NUM> is reduced due to a coating layer treated on the outer surface of the evaporator <NUM> for waterproofing, so that the condensed water may penetrate into the inside of the evaporator <NUM>; or (iii) the washing water may be introduced into the inside of the evaporator by the Coanda effect in which fluid formed near a surface of an object is attached to the surface of the object by difference in pressure. The washing unit (C) of the present disclosure eliminates the problem.

The washing unit (C) includes the nozzle part (S), the front guide part <NUM>, and the like, and means a group of components that are organically constructed to perform the washing function of the evaporator <NUM>. The components constituting the washing unit (C) may not necessarily perform only the washing function. For example, in the embodiment, the nozzle part (S) and the front guide part <NUM> are integrally formed into a singly body with the base cover <NUM>. Herein, since the base cover <NUM> performs a function of covering an upper portion of the circulation flow path (H) to shield the circulation flow path (H), the nozzle part (S) and the front guide part <NUM> are considered to function as the base cover <NUM>. Alternately, the washing unit (C) may not be installed in the base cover <NUM>, but may be installed in a separate structure. For example, regardless of the base cover <NUM>, the nozzle part (S) and the front guide part <NUM> constituting the washing unit (C) may be installed by using a separate frame (not shown) that is provided for installing the washing unit (C).

The base cover <NUM> is assembled to an upper side of the lower frame <NUM> and is configured to cover and shield the upper portion of the circulation flow path (H). The base cover <NUM> may be formed of various materials such as synthetic resin, metal, etc., and in the embodiment, the base cover is formed of a synthetic resin material. The base cover <NUM> is formed approximately in a plate shape and is extended in a longitudinal direction of the circulation flow path (H), i.e., in an air flow direction.

In the embodiment, the base cover <NUM> includes a front cover <NUM> and a rear cover <NUM>. The front cover <NUM> and the rear cover <NUM> are assembled together to form the one base cover <NUM>, and the front cover <NUM> and the rear cover <NUM> are provided as separate objects for convenience of manufacturing, but may be integrally formed into a single body. The front cover <NUM> is positioned at a side of the guide space <NUM> and the rear cover <NUM> relatively deviates to a side of the circulation pan installation part <NUM>. As shown in <FIG>, the front cover <NUM> covers a part of the heat exchange space <NUM> and a part of an upper portion of the guide space <NUM> and the rear cover <NUM> covers a remaining part of the heat exchange space <NUM>.

As shown in <FIG>, the front cover <NUM> is positioned to deviate toward the guide space <NUM> than the evaporator <NUM>, and may be configured to cover an upper portion of the evaporator <NUM> or not to cover the upper portion of the evaporator <NUM>. The front cover <NUM> has a locking structure for assembly with the rear cover <NUM>, but the locking structure is not shown in the drawings. The front cover <NUM> and the rear cover <NUM> may be assembled using a fastener in addition to the locking structure or be connected together by a hinge method.

The front guide part <NUM> protrudes from a lower surface of the front cover <NUM>. The front guide part <NUM> is extended from the lower surface of the front cover <NUM> to be downwardly inclined toward the front surface <NUM> of the evaporator <NUM>. In the embodiment, the front guide part <NUM> is formed in a thin plate shape protruding from the lower surface of the front cover <NUM>, but unlike the embodiment, the front guide part <NUM> may be formed thicker in thickness since an upper surface of the front guide part <NUM> is a part actually functioning.

The front guide part <NUM> serves to change a direction of the condensed water sprayed through the nozzle part (S) which will be described below. More precisely, the front guide part <NUM> is provided at an opposite side of the nozzle part (S) while being spaced apart therefrom, with the front surface <NUM> of the evaporator <NUM> interposed between the front guide part <NUM> and the nozzle part (S), and a protruding end <NUM> is extended toward the front surface <NUM> of the evaporator <NUM>. Accordingly, the spray direction of the condensed water discharged from the nozzle part (S) is switched toward the front surface <NUM> of the evaporator <NUM>.

The front guide part <NUM> is downwardly inclined toward the upper portion of the front surface <NUM> of the evaporator <NUM>. Referring to <FIG>, <FIG>, and <FIG> showing enlarged part A in <FIG>, the protruding end <NUM> of the front guide part <NUM> is spaced apart from the front surface <NUM> of the evaporator <NUM> and is in a position lower than an upper surface <NUM> of the evaporator <NUM>. When the protruding end <NUM> of the front guide part <NUM> is spaced apart from the front surface <NUM> of the evaporator <NUM> to a position retracted from the front surface <NUM> of the evaporator <NUM>, the condensed water sprayed from the nozzle part (S) may be smoothly supplied to the front surface <NUM> of the evaporator <NUM> i.e. the heat exchanger. Further, this is because the condensed water may be displayed to the upper surface <NUM> of the evaporator <NUM> when the protruding end <NUM> of the front guide part <NUM> is higher than the upper surface <NUM> of the evaporator <NUM>. In the embodiment, the upper surface of the front guide part <NUM> is a flat surface, but it may be configured by a curved surface or an inclined surface.

Regarding the rear cover <NUM> to be described below, the rear cover <NUM> has a plate shaped structure that has a width approximately same as the front cover <NUM>, and is extended from the front cover <NUM> to cover upper portions of the evaporator <NUM> and the condenser <NUM>. In the embodiment, the rear cover <NUM> has a length relatively longer than a length of the front cover <NUM>, and an end of the rear cover opposite to the front cover is connected to the circulation pan installation part <NUM>. A supply flow path of the condensed water is provided along the upper surface of the front cover <NUM>.

The supply flow path means a path supplying the condensed water from the drainage tank <NUM> to the nozzle part (S), and a part of the supply flow path is installed on an upper surface of the rear cover <NUM>. Referring to <FIG>, connection holes <NUM> pass through the upper surface of the rear cover <NUM>, and the connection holes <NUM> are connected to water tubes <NUM>, respectively. The water tubes <NUM> are connected to a control valve <NUM> at the rear of the water tubes through separate connection tubes <NUM>. The separate connection tubes <NUM> are omitted in <FIG>, but can be checked in <FIG> and <FIG>. Each of the water tubes <NUM> has a fixation flange <NUM>, and the water tubes <NUM> may be fixed to the rear cover <NUM> by using a fastening hole <NUM>' passing through the fixation flange <NUM>.

At least a part of the water tubes <NUM> is inserted into the connection holes <NUM> of the rear cover <NUM> to be connected to the nozzle part (S). Accordingly, the condensed water is delivered in the order of the drainage tank <NUM>-the control valve <NUM>-the connection tubes <NUM>-the connection holes <NUM>-the nozzle part (S) through the water tubes <NUM>. Of course, the water tubes <NUM> may be omitted and the drainage tank <NUM> or external supply means may be directly connected to the connection holes <NUM>.

The control valve <NUM> is provided for selectively supplying the condensed water to only at least one nozzle part (S) of a plurality of nozzle parts (S), and the control valve <NUM> may be omitted. In <FIG>, reference numerals <NUM> and <NUM> in the control valve <NUM> are an input port and an output port, respectively, and reference numeral <NUM> is a water supply port connected to the water tubes <NUM>. In the embodiment, as three nozzle parts (S) and three water tubes <NUM> are provided, so three water supply ports <NUM> are provided.

The nozzle part (S) will be described with reference to <FIG> and <FIG>, the nozzle part (S) has a structure in which a kind of empty space is provided, and the condensed water is sprayed through the nozzle part (S). Each of the nozzle parts (S) has a first side connected to each of the water tubes <NUM> and a second side opened toward the front surface <NUM> of the evaporator <NUM> to discharge the condensed water. At this time, the nozzle part (S) is extended to be inclined downward in a direction of the evaporator <NUM> thus the condensed water may be sprayed into a discharge channel <NUM> by gravity with supplied flow rate of the condensed water.

The inside of the nozzle part (S) is formed in a flow space as a kind of empty space, the nozzle part (S) is provided between a base <NUM> that is a bottom surface extended to be downwardly inclined toward the front of the heat exchanger and a cover <NUM> that is a ceiling surface extended while being spaced upward from the base <NUM>. Each of the compartment vanes <NUM> connects between the base <NUM> and the cover <NUM> to form the sealed nozzle part (S). As shown in <FIG>, in the embodiment, the three nozzle parts (S) are provided and the nozzle parts (S) are partitioned from each other by the compartment vanes <NUM>. The three nozzle parts (S) are disposed in a left to right width direction of the evaporator <NUM> in separate sections, respectively, so that the evaporator <NUM> may be washed evenly. The number of the nozzle part (S) may be changed, and the nozzle parts may communicate with each other to form a single body. Reference numeral <NUM> (not described) is a hook for assembling the rear cover <NUM>, and reference numeral <NUM> is a fixation part for fixing a harness.

The base <NUM> of the nozzle part (S) is configured such that a connection channel <NUM> and the discharge channel <NUM> are connected together. The connection channel <NUM> is extended from an outlet <NUM> of the water tube <NUM> and is a portion where a height is gradually lowered toward the front surface <NUM> of the evaporator <NUM> in a direction of gravity, i.e., is a relatively gently inclined portion. The discharge channel <NUM> is a portion extended from the connection channel <NUM> toward the front of the heat exchanger and has an inclination angle larger than an inclination angle of the connection channel <NUM>. In other words, the discharge channel <NUM> has a steeper inclination than the connection channel <NUM>. Due to the structure, the condensed water passing through the discharge channel <NUM> may have a faster flow rate.

The washing unit (C) has a guide end <NUM> and <NUM>. The guide end <NUM> and <NUM> is provided on at least one of the nozzle part (S) or the front guide part <NUM>, and serves to guide a discharge direction of the condensed water toward the front surface <NUM> of the evaporator <NUM>.

In the embodiment, the guide end <NUM> and <NUM> is a nozzle guide end <NUM> provided in the nozzle part (S), and the nozzle guide end <NUM> is positioned at an end of the discharge channel <NUM>. The nozzle guide end <NUM> protrudes from an end of the nozzle part (S) toward the front guide part <NUM> to guide the discharge direction of the condensed water toward the front guide part <NUM>. The nozzle guide end <NUM> is shown likely as a protrusion when viewed from a side sectional view as shown in <FIG>, but is extended in a width direction of the nozzle part (S) as shown in <FIG>.

An upper surface of the nozzle guide end <NUM> through which the condensed water flows is extended at a more gradual angle than a downwardly inclination angle at which the nozzle part (S) is inclined toward the outer surface of the heat exchanger, or may be extended in an upwardly inclined direction toward the front guide part <NUM>. As described above, as the angle of the upper surface of the nozzle guide end <NUM> is generated, the condensed water may not be steeply sprayed in the direction of gravity, but may be guided in a direction of the front guide part <NUM> along the upper surface of the nozzle guide end <NUM>. In the embodiment, an internal angle (α, referring to <FIG>) between the upper surface of the nozzle guide end <NUM> and an outer surface of the discharge channel <NUM> is between <NUM>° to <NUM>°. When the internal angle (α) is less than <NUM>°, the flow of condensed water is interrupted, and when the internal angle (α) is higher than <NUM>°, the condensed water is not sufficiently delivered toward the front guide part <NUM>.

The nozzle guide end <NUM> is integrally formed with the end of the discharge channel <NUM> and is a portion formed during the injection molding of the base cover <NUM>. The nozzle guide end <NUM> is formed at a boundary portion between a moving side die and a slide core in a mold for forming the base cover <NUM>. That is, the nozzle guide end <NUM> is formed on a parting line, which is the boundary portion between the moving side die and the slide core where is difficult to perform the precise processing, so it is possible to reduce the influence of errors in the manufacturing process in comparison to the simply forming a continuous outer surface.

Referring to <FIG>, the nozzle guide end <NUM> is in a position retracted from the front surface <NUM> of the evaporator <NUM> based on a direction in which the condensed water is moved (right to left based on the drawing), and is spaced upward from the upper surface <NUM> of the evaporator <NUM>. When the nozzle guide end <NUM> is in a position ahead of the front surface <NUM> of the evaporator <NUM>, which is the heat exchanger, the condensed water may not be sufficiently sprayed to the front surface <NUM> of the evaporator <NUM>. Further, the evaporator <NUM> should be spaced upward from the upper surface <NUM>, so that the condensed water may be sprayed without interference with the evaporator <NUM>.

In addition, the nozzle guide end <NUM> is preferably positioned at a position relatively higher than the protruding end <NUM> of the front guide part <NUM> based on the direction of gravity. The front guide part <NUM> should guide a spray direction of the condensed water sprayed through the nozzle guide end <NUM>. The embodiment, since the nozzle guide end <NUM> at the relatively high position supplies the condensed water to the protruding end <NUM> of the front guide part <NUM> at a relatively low position, supply of the condensed water may be stable.

A distance (D1) between the protruding end <NUM> of the front guide part <NUM> and the nozzle guide end <NUM>, a height difference (H1) between the protruding end <NUM> of the front guide part <NUM> and the nozzle guide end <NUM>, a distance (D2) between the nozzle guide end <NUM> and the front surface <NUM> of the evaporator <NUM>, and a height difference (H2) between the nozzle guide end <NUM> and the upper surface <NUM> of the evaporator <NUM> are set within predetermined ranges. In the embodiment, (i) the distance (D1) between the protruding end <NUM> of the front guide part <NUM> and the nozzle guide end <NUM> is between <NUM> to <NUM>, (ii) the height difference (H1) between the protruding end <NUM> of the front guide part <NUM> and the nozzle guide end <NUM> is between <NUM> to <NUM>, (iii) the distance (D2) between the nozzle guide end <NUM> and the front surface <NUM> of the evaporator <NUM> is between <NUM> to <NUM>, and (iv) the height difference (H2) between the nozzle guide end <NUM> and the upper surface <NUM> of the evaporator <NUM> is between <NUM> to <NUM>. Of course, the above ranges may be changed somewhat in response to the flow rate of the condensed water and the amount of washing.

As described above, in a condition when the distance (D2) in which the nozzle guide end <NUM> is retracted from the front surface <NUM> of the evaporator <NUM> is between <NUM> to <NUM> and the height (H2) in which the nozzle guide end <NUM> is spaced upward from the upper surface <NUM> of the evaporator <NUM> is between <NUM> to <NUM>, a length (X) in which the nozzle guide end <NUM> protrudes toward the front guide part <NUM> is between <NUM> to <NUM>. The degree to which the nozzle guide end <NUM> protrudes affects a spray angle (β, referring to <FIG>) in which the condensed water is sprayed. The spray angle (β) is an angle formed between the sprayed condensed water and the front surface <NUM> of the evaporator <NUM>. When the spray angle (β) is small, the condensed water flows while deviating to the evaporator <NUM> thus the washing function of the condensed water may not properly performed. On the contrary, when the spray angle (β) is too large, the condensed water is sprayed in a direction away from the front surface <NUM> of the evaporator <NUM> thus the evaporator <NUM> may not be washed. That is, the condensed water discharged from the washing unit (C) is discharged between the nozzle guide end <NUM> and the front guide part <NUM> (P, referring to <FIG>), and it is preferable that the condensed water falls while having the predetermined spray angle (β) in a direction away from the front surface <NUM> of the evaporator <NUM> based on the direction of gravity.

Meanwhile, when a separate distance (L, referring to <FIG>) between the nozzle guide end <NUM> and the front guide part <NUM> and the protruding length (X) of the nozzle guide end <NUM> vary, a value of the spray angle (β) is as follows. Row <NUM> in table <NUM> below shows a ratio (X/L) of dividing the protruding length (X) of the nozzle guide end <NUM> by the separate distance (L) between the nozzle guide end <NUM> and the front guide part <NUM>, and the test was conducted three times. For reference, a value between <NUM> to <NUM> was tested as the separate distance (L) between the nozzle guide end <NUM> and the front guide part <NUM> and a value between <NUM> to <NUM> was tested as the protruding length (X) of the nozzle guide end <NUM>.

Results of calculating the washing rate in each case are shown in a graph in <FIG> is the graph showing the variations of the spray angle (β) and the washing rate in response to the protruding length (X) of the nozzle guide end <NUM>. That is, the graph shows that when the ratio (X/L) of dividing the protruding length (X) of the nozzle guide end <NUM> by the separate distance (L) between the nozzle guide end <NUM> and the front guide part <NUM> vary, how the spray angle (β) of the sprayed condensed water varies and how the washing rate varies in response to the spray angle (β).

As shown in the graph in <FIG>, as the ratio (X/L) of dividing the protruding length (X) of the nozzle guide end <NUM> by the separate distance (L) between the nozzle guide end <NUM> and the front guide part <NUM> is increased, the spray angle (β) is gradually increased. This means that when the nozzle guide end <NUM> relatively further protrudes, the condensed water sprayed through the nozzle part (S) is guided forward along the nozzle guide end <NUM> thereby increasing the spray angle (β). Further, when the ratio (X/L) becomes <NUM> or more, the increase of the spray angle (β) is reduced and converges to about <NUM>°. This means that the spray angle (β) may not be increased higher than a predetermined level due to the front guide part <NUM> facing the nozzle guide end <NUM>.

Meanwhile, in the graph, as the ratio (X/L) of dividing the protruding length (X) of the nozzle guide end <NUM> by the separate distance (L) between the nozzle guide end <NUM> and the front guide part <NUM> is increased higher than a predetermined level, the washing rate is increased and then reduced. For reference, the washing rate is obtained by measuring the amount of foreign matter remaining after spraying the condensed water for about <NUM> seconds on the front surface <NUM> of the evaporator <NUM> on which foreign matter is widely spread. Therefore, the high washing rate means that the amount of foreign matter remaining after washing is small. As shown in the graph, when the ratio (X/L) is <NUM>, the washing rate is about <NUM>%, and when the ratio (X/L) is <NUM>, the washing rate is higher than about <NUM>%. The washing rate which is continuously increased along the ratio (X/L) is reduced from a starting point when the ration (X/L) is <NUM>, and the washing rate is about <NUM>% when the ration (X/L) is <NUM>. The washing rate should be high in order not to decrease the efficiency of the heat pump system, therefore the ratio (X/L) is between <NUM> to <NUM> in order to maintain the washing rate at about <NUM>% or more. At this time, the spray angle is between <NUM>° to <NUM>°.

An inclined or curved spray surface <NUM> that is inclined downward in the direction of gravity is formed at an upper surface of the nozzle guide end <NUM>. The spray surface <NUM> corresponds to the upper surface of the nozzle guide end <NUM> where the condensed water is finally guided, and the spray surface <NUM> allows the condensed water to be delivered more smoothly toward the front guide part <NUM>.

<FIG> depicts views showing various embodiments of the nozzle guide end <NUM> different from each other. In the nozzle guide end <NUM> in <FIG>, the spray surface <NUM> is extended while having a gradual slope than a slope of the discharge channel <NUM> of the nozzle part (S). That is, an internal angle (α) formed between the spray surface <NUM> of the nozzle guide end <NUM> and an outer surface of the discharge channel <NUM> is less than <NUM>° and servers to make the discharge channel <NUM> more gradual. Herein, a thickness (Y2) of the spray surface <NUM> is smaller than a thickness (Y1) of the nozzle guide end <NUM>, and in the embodiment, the thickness (Y2) of the spray surface <NUM> is equal to or greater than <NUM>/<NUM> of the total thickness (Y1) of the nozzle guide end <NUM>. Therefore, a length of the spray surface <NUM> may be sufficiently secured.

In the nozzle guide end <NUM> in <FIG>, the spray surface <NUM> is extended with a gradual slope than the slope of the discharge channel <NUM> of the nozzle part (S). The spray surface <NUM> is divided into two portions that are a first inclined surface <NUM> and a second inclined surface <NUM>'. The first inclined surface <NUM> is a portion protruding from the discharge channel <NUM> of the nozzle part (S). The second inclined surface <NUM>' is a portion protruding from the first inclined surface <NUM> and extended more in a downward inclined direction toward the front of the heat exchanger than the first inclined surface <NUM> and a portion where an inclination angle become steep again.

The first inclined surface <NUM> guides the condensed water passing through the discharge channel <NUM> to flow smoothly toward the front guide part <NUM>, and the second inclined surface <NUM>' serves the same function as the first inclined surface <NUM> and reduces a front area of the nozzle guide end <NUM>. Herein an end of the nozzle guide end <NUM> does not have a flat surface, but has a sharp linear shape or a flat surface with a very low height, so that the condensed water flowing downward along a front surface of the nozzle guide end <NUM> may be minimized. In the embodiment, the protruding length of the nozzle guide end <NUM> is between <NUM> to <NUM>, and a height (Y2) of the spray surface <NUM> formed by the first inclined surface <NUM> and the second inclined surface <NUM>' is equal to or greater than <NUM>/<NUM> of the total thickness (Y1) of the nozzle guide end <NUM>.

Meanwhile, the discharge channel <NUM> is connected with a steeply inclined surface <NUM>. The steeply inclined surface <NUM> is a portion positioned between the discharge channel <NUM> and the nozzle guide end <NUM> and is extended with an inclination angle greater than an inclination angle of the discharge channel <NUM>. The steeply inclined surface <NUM> provides a steep slope to guide the flow rate of the condensed water to flow faster. As the condensed water having the increased flow rate is delivered toward the front guide part <NUM> while passing through the spray surface <NUM>, even when the flow amount of the condensed water is small and the flow rate thereof is low, the condensed water may not flow directly toward the evaporator <NUM>. In the embodiment, an internal angle (α) between the steeply inclined surface <NUM> and the first inclined surface <NUM> is between about <NUM>° to <NUM>°.

Finally, in the nozzle guide end <NUM> in <FIG>, the spray surface <NUM> has a curved shape. As shown in the side section view of the spray surface <NUM>, the nozzle guide end <NUM> has an approximately semicircular, and thus the spray surface <NUM> is entirely formed in the curved surface. Of course, a lower side surface <NUM> of the nozzle guide end <NUM> may have a non-curved surface and only a partial upper side thereof may be formed in the curved spray surface <NUM>. In the embodiment, the thickness (Y2) of the spray surface <NUM> is equal to or greater than <NUM>/<NUM> of the total thickness (Y1) of the nozzle guide end <NUM>. For reference, in the embodiment, although the spray surface <NUM> is not clearly distinguished, an upper side of the nozzle guide end <NUM> centered on a most protruding portion toward the front guide part <NUM> may refer to the spray surface <NUM>. In the embodiment, the protruding length (X) of the nozzle guide end <NUM> is between <NUM> to <NUM>.

Meanwhile, <FIG> depicts other embodiment of the nozzle guide end <NUM>. As shown in the drawing, the discharge channel <NUM> of the nozzle part (S) is connected with the steeply inclined surface <NUM> and the nozzle guide end <NUM> is positioned at end of the steeply inclined surface <NUM>. The nozzle guide end <NUM> is not connected continuously, but is arranged in a separate form. That is, a plurality of nozzle guide ends <NUM> which are spaced apart from each other is arranged in a left to right width direction of the discharge channel <NUM>, and a falling space <NUM> which is open along the direction of gravity is provided between the nozzle guide ends <NUM>.

The falling space <NUM> penetrates the nozzle guide end <NUM> in a vertical direction to provide a path for the condensed water to fall. As shown in <FIG>, a portion of the condensed water delivered through the nozzle part (S) to the nozzle guide end <NUM> is moved along the spray surface <NUM> toward the front guide part <NUM>, and the remaining thereof may fall through the falling space <NUM> downward. That is, as the falling space <NUM> which is open along the direction of gravity is provided at the nozzle guide end <NUM>, some of the condensed water is guided to fall in the direction of gravity to direct the front surface of the heat exchanger. The falling space <NUM> prevents all the condensed water from being sprayed away in front of the heat exchanger when the flow rate of the condensed water is fast. Accordingly, even when the amount and the flow rate of the condensed water are large or small, it is possible to stably spray more than a predetermined level of the condensed water.

Although not shown in the drawing, a length (X1) in which the nozzle guide end <NUM> protrudes toward the front guide part <NUM> or the thickness (Y1) of the nozzle guide end <NUM> may be formed different from each other along a left to right width direction of the nozzle part (S). In this way, the condensed water with the amount and flow rate of a wide range may be supplied to the front guide part <NUM> above the predetermined level.

As shown in <FIG> and <FIG>, the water pump <NUM> is installed in the installation space of the cabinet <NUM>. The water pump <NUM> is installed in the condensed water collecting part <NUM> to move the condensed water flowing into the condensed water collecting part <NUM> to the drainage tank <NUM>. When the condensed water is stored in the drainage tank <NUM> by the water pump <NUM>, the stored condensed water may be used as the washing water or may be discharged outward.

The drum motor <NUM> which generates a driving force for rotation of the drum <NUM> is installed in the drum motor installation part <NUM>. A belt (not shown) may be connected to the drum motor <NUM> to deliver the driving force of the drum motor <NUM> to the drum <NUM>, and the belt may be arranged to surround an outer circumference of the drum <NUM>. A pulley <NUM> and a spring (not shown) may be used to control tension applied to the belt.

A blowing fan <NUM> may be mounted to a shaft of the drum motor <NUM>. In the embodiment, the belt may be connected to one side of the drum motor <NUM> and the blowing fan <NUM> may be mounted to the other side thereof. Accordingly, shafts respectively provided at the both sides of the drum motor <NUM> may rotate the drum <NUM> and the blowing fan <NUM> while being rotated in the same direction and at the same speed.

As shown in <FIG>, the drainage tank <NUM> is installed at an upper side of the cabinet <NUM>. The drainage tank <NUM> may be disposed a left upper portion or a right upper portion of the drum <NUM>. <FIG> depicts the drainage tank <NUM> installed at the left upper portion of the drum <NUM>. A drainage cover <NUM> is disposed at a left upper end or a right upper end in a front surface of the laundry processing apparatus to correspond to a position of the drainage tank <NUM>. The drainage cover <NUM> is formed to be gripped by hand and exposed to the front surface of the laundry processing apparatus. When the drainage cover <NUM> is pulled in order to empty the condensed water collected in the drainage tank <NUM>, the drainage tank <NUM> is withdrawn from a water tank support frame <NUM> together with the drainage cover <NUM>.

Meanwhile, the controller <NUM> is installed in the laundry processing apparatus. The controller <NUM> is configured to control the operation of the laundry processing apparatus on the basis of a user input applied through the input part <NUM>. The controller <NUM> may consist of a circuit board and devices mounted on the circuit board. When the user selects a laundry processing course through the input part <NUM>, the controller <NUM> controls the operation of the laundry processing apparatus according to a preset algorithm.

Hereinafter, a process of washing the evaporator <NUM> by using the washing unit (C) constituting the present disclosure will be described. In a process of generating the condensed water, high temperature and dry air passing through the condenser <NUM> of the heat pump system passes through the circulation fan receiving part <NUM> and then is supplied to the drum <NUM> through the rear duct connector <NUM>. The high temperature and dry air supplied to the drum <NUM> evaporates moisture of the clothing to be processed and becomes high temperature and humidity air. The high temperature and humidity air is recovered through the front duct connector <NUM> and heat-exchanges with refrigerant in the evaporator <NUM> to become low temperature air, and as the temperature of the air is reduced, the amount of saturation water vapor in the air is reduced, so that the moisture contained the air is condensed. In the process, the condensed water is generated and the generated condensed water is collected in the condensed water collecting part <NUM> described above. The water pump <NUM> delivers the condensed water collected in the condensed water collecting part <NUM> to the drainage tank <NUM> to store the condensed water.

The condensed water may be supplied to the washing unit (C) when the laundry processing apparatus is in operation or stopped, thereby performing a washing process. In the washing process, the condensed water stored in the drainage tank <NUM> is delivered to the control valve <NUM> by the water pump <NUM> and the control valve <NUM> delivers the condensed water to the water tubes <NUM> through a connection tube <NUM>.

The condensed water is introduced into the nozzle part (S) through the outlet <NUM> of the water tubes <NUM> (referring to arrow A in <FIG> and <FIG>) and flows through the base <NUM> corresponding to a bottom of the nozzle part (S). The base <NUM> is configured such that the connection channel <NUM> and the discharge channel <NUM> are connected to each other. The connection channel <NUM> is a portion in which a height thereof is gradually lowered along the direction of gravity toward the front surface <NUM> of the evaporator <NUM> and a portion with a relatively gradual slope, thereby allowing the condensed water to flow. Since the discharge channel <NUM> has a steeper slope than the slope of the connection channel <NUM>, the condensed water passing through the discharge channel <NUM> may obtain a faster flow rate (referring to arrow B in <FIG> and <FIG>).

The condensed water passing through the discharge channel <NUM> is sprayed toward the front guide part <NUM> through the nozzle guide end <NUM>. In the embodiment, since the nozzle guide end <NUM> at a relatively high position supplies the condensed water to the protruding end <NUM> of the front guide part <NUM> at the relatively low position, the condensed water may be stably delivered. Herein, as described above, the length of the nozzle guide end <NUM> is between <NUM> to <NUM> and the spray angle (β) generated through the length is between <NUM>° to <NUM>°. Due to the spray angle (β), as shown in <FIG>, the condensed water is guided in the direction away from the front surface <NUM> of the evaporator <NUM> and then is delivered toward the front surface <NUM> of the evaporator <NUM> in a downward flow process (referring to arrow C in <FIG> and <FIG>). Accordingly, the condensed water is not directly guided to the inside of the evaporator <NUM> but flows evenly along the front surface <NUM> of the evaporator <NUM>, thereby sufficiently performing the washing function.

In particular, during the operation of the laundry processing apparatus, the high temperature and humidity air after performing heat processing on the clothing to be processed in the drum <NUM> is moved in a direction of arrow ③ in <FIG>. In the process, the condensed water may be pushed toward the front surface <NUM> of the evaporator <NUM>. However, in the embodiment, since the spray angle (β) is set between <NUM>° to <NUM>°, the condensed water falls downward while overcoming the force to some degree. Accordingly, the washing may be performed to a lower portion of the front surface <NUM> of the evaporator <NUM>.

Hereinafter, referring to <FIG>, a second embodiment of the present disclosure will be described. For reference, descriptions of the same structures as in the previous embodiment will be omitted, and different structures from the previous embodiment will be described.

The washing unit (C) has the guide end <NUM> and <NUM>. The guide end <NUM> and <NUM> is provided on at least one of the nozzle part (S) and the front guide part <NUM>, and the guide end <NUM> and <NUM> serves to guide the discharge direction of the condensed water toward the front surface <NUM> of the evaporator <NUM>.

In the embodiment, the guide end <NUM> and <NUM> is a front guide end <NUM> provided at the front guide part <NUM>. The front guide end <NUM> is a portion on which the condensed water sprayed from the nozzle part (S) touches, and the condensed water hits the front guide end <NUM> and then may be guided toward the front surface <NUM> of the evaporator <NUM>.

As shown in <FIG>, the front guide end <NUM> is extended from an end of the front guide part <NUM> in a perpendicular direction. Alternately, the front guide end <NUM> may not be parallel to the front surface <NUM> of the evaporator <NUM>, but may be extended with a predetermined relative angle.

The front guide end <NUM> is positioned at a relatively lower side than the end of the nozzle part (S) along the direction of gravity, that is, along a direction perpendicular to the end of the front guide part <NUM>. In this state, the condensed water sprayed from the nozzle part (S) may be brought into contact with a surface of the front guide end <NUM> and thereafter be guided toward the front surface <NUM> of the evaporator <NUM>.

Referring to <FIG>, a distance (D1) between an end <NUM> of the front guide end <NUM> and a nozzle guide end <NUM>, a protruding height (H1) of the front guide end <NUM>, a distance (D2) between the front guide end <NUM> and the front surface <NUM> of the evaporator <NUM>, and a height difference (H2) between the nozzle guide end <NUM> and the upper surface <NUM> of the evaporator <NUM> may be set within predetermined ranges. In the embodiment, (i) the distance (D1) between an end <NUM> of the front guide end <NUM> and a nozzle guide end <NUM> is between <NUM> to <NUM>, (ii) the protruding height (H1) of the front guide end <NUM> is between <NUM> to <NUM>, (iii) the distance (D2) between the front guide end <NUM> and the front surface <NUM> of the evaporator <NUM> is between <NUM> to <NUM>, and (iv) the height difference (H2) between the nozzle guide end <NUM> and the upper surface <NUM> of the evaporator <NUM> is between <NUM> to <NUM>. Of course, the above ranges may vary in response to the flow rate of the condensed water and the amount of washing.

As described above, in a condition in which the distance (D1) between the end <NUM> of the front guide end <NUM> and the nozzle guide end <NUM> is between <NUM> to <NUM> and the protruding height (H1) of the front guide end <NUM> is between <NUM> to <NUM>, the protruding height (H1) of the front guide end <NUM> affects the spray angle (β) of spraying the condensed water. Herein, the spray angle (β) is an angle formed between the sprayed condensed water and the front surface <NUM> of the evaporator <NUM>.

When the spray angle (β) is small, the condensed water is sprayed while deviating to the inside of the evaporator <NUM> so that the washing function may not be properly performed. On the contrary, when the spray angle (β) is too large, the condensed water is sprayed in the direction away from the front surface <NUM> of the evaporator <NUM> so that the evaporator <NUM> may not be washed. That is, the condensed water discharged from the washing unit (C) is discharged between the nozzle guide end <NUM> and the front guide part <NUM> (P, referring to <FIG>), and it is preferable that the condensed water falls with the predetermined spray angle (β) in the direction away from the front surface <NUM> of the evaporator <NUM> based on the direction of gravity.

Meanwhile, when the separate distance (L, referring to <FIG>) between the front guide end <NUM> and the nozzle guide end <NUM> and the protruding height (H1) of the front guide end <NUM> vary, a value of the spray angle (β) is as follows. Row <NUM> in table <NUM> below shows a ratio (H1/L) obtained by dividing the protruding height (H1) of the front guide end <NUM> by the separate distance (L) between the front guide end <NUM> and the nozzle guide end <NUM>. Rows <NUM> to <NUM> in table <NUM> show the spray angle (β), and the test was conducted three times. For reference, a value between <NUM> to <NUM> was tested as the separate distance (L) between the front guide end <NUM> and the nozzle guide end <NUM> and a value between <NUM> to <NUM> was tested as the protruding height (H1) of the front guide end <NUM>.

Results of calculating the washing rate in each case are shown in a graph in <FIG> is the graph showing the variations of the spray angle (β) and the washing rate in response to the protruding height (H1) of the front guide end <NUM>. That is, the graph shows that when the ratio (H1/L) obtained by dividing the protruding height (H1) of the front guide end <NUM> by the separate distance (L) between the end <NUM> of the front guide end <NUM> and the nozzle guide end <NUM> varies, how the spray angle (β) of the sprayed condensed water varies and how the washing rate varies in response thereto.

As shown in the graph, as the ratio (H1/L) obtained by dividing the protruding height (H1) of the front guide end <NUM> by the separate distance (L) between the nozzle guide end <NUM> and the end <NUM> of the front guide end <NUM> is increased, the spray angle (β) is gradually reduced and converges to a predetermined level. This means that the spray angle (β) becomes small since as the front guide end <NUM> further protrudes, the condensed water sprayed through the nozzle part (S) hits the surface of the front guide end <NUM> and then is guided to the front surface <NUM> the evaporator <NUM>. When the ratio (H1/L) is equal or higher than <NUM>, the decrease of the spray angle (β) is reduced and converges to about <NUM>°.

Meanwhile, as the ratio (H1/L) obtained by dividing the protruding height (H1) of the front guide end <NUM> by the separate distance (L) between the nozzle guide end <NUM> and the end <NUM> of the front guide end <NUM> is increased, the washing rate is increased and then is reduced again. For reference, the washing rate is obtained by measuring the amount of foreign matter remaining after spraying the condensed water for about <NUM> seconds on the front surface <NUM> of the evaporator <NUM> on which foreign matter is widely spread. Accordingly, this means that when the washing rate is higher, the amount of the remaining foreign matter after washing is small. As shown in the graph, when the ratio (H1/L) is <NUM>, the washing rate is about <NUM>%, and when the ratio (H1/L) is <NUM>, the washing rate is higher than about <NUM>%. The washing rate which is continuously increased along the ratio (H1/L) is continuously reduced from a starting point when the ratio is <NUM>, and the ratio (H1/L) is <NUM>, the washing rate is about <NUM>%. The washing rate should be high in order to maintain the efficiency of the heat pump system, so it is preferable that the ratio (H1/L) is between <NUM> to <NUM> in order to maintain the washing rate at about <NUM>% or more. At this time, the spray angle (β) is between <NUM>° to <NUM>°.

Hereinafter, a third embodiment of the present disclosure will be described with reference to <FIG> and <FIG>. For reference, descriptions of the same structures as in the previous embodiments will be omitted, and different structures from the previous embodiments will be described.

The washing unit (C) has the guide end <NUM> and <NUM>. The guide end <NUM> and <NUM> is provided at each of the nozzle part (S) and the front guide part <NUM> and serves to guide the discharge direction of the condensed water toward the front surface <NUM> of the evaporator <NUM>.

In the embodiment, the guide end <NUM> and <NUM> includes the nozzle guide end <NUM> provided in the nozzle part (S) and the front guide end <NUM> provided in the front guide part <NUM>. Herein, the front guide end <NUM> is a portion where the condensed water sprayed from the nozzle part (S) touches, the condensed water may hit the front guide end <NUM> and then be guided toward the front surface <NUM> of the evaporator <NUM>.

As shown in <FIG>, the front guide end <NUM> is extended from the end of the front guide part <NUM> in the perpendicular direction. Alternately, the front guide end <NUM> may not be parallel to the front surface <NUM> of the evaporator <NUM>, but may be extended with a predetermined relative angle.

The nozzle guide end <NUM> is positioned at an end of the discharge channel <NUM>. The nozzle guide end <NUM> further protrudes from the end of the nozzle part (S) toward the front guide part <NUM> and serves to guide the discharge direction of the condensed water toward the front guide part <NUM>. The nozzle guide end <NUM> looks like a protrusion when the nozzle guide end is shown from the side section view as shown in <FIG>, but the nozzle guide end <NUM> is extended in a long shape in a width direction of the nozzle part (S) as shown in <FIG>.

Claim 1:
A laundry processing apparatus comprising:
a cabinet (<NUM>) having an installation space therein;
a heat exchanger (<NUM>) provided in the installation space of the cabinet (<NUM>) and configured to transfer heat generated from exhaust air after heat-processing clothing; and
a washing unit (C) provided at a position inside the installation space which corresponds to an upper portion of the heat exchanger (<NUM>), the washing unit (C) being configured to spray washing water on a front surface (<NUM>) of the heat exchanger (<NUM>) into which the exhaust air flows,
wherein the washing unit (C) comprises:
a nozzle part (S) provided at the upper portion of the heat exchanger (<NUM>) in an inclined direction to guide the washing water toward the heat exchanger (<NUM>), the nozzle part (S) having a first side connected to a water tube (<NUM>) supplying the washing water and a second side extended to a position adjacent to the front surface (<NUM>) of the heat exchanger (<NUM>);
a front guide part (<NUM>, <NUM>) provided at an opposite side of the nozzle part (S) while being spaced apart therefrom, with the front surface (<NUM>) of the heat exchanger (<NUM>) interposed between the front guide part (<NUM>, <NUM>) and the nozzle part (S), in which a protruding end of the front guide part (<NUM>, <NUM>) is extended toward the front surface (<NUM>) of the heat exchanger (<NUM>) to guide the washing water discharged from the nozzle part (S) toward the front surface (<NUM>) of the heat exchanger (<NUM>); and
a guide end (<NUM>) protruding from an end of the nozzle part (S) toward the front guide part (<NUM>, <NUM>) so that the guide end (<NUM>) guides the washing water toward the front surface (<NUM>) of the heat exchanger (<NUM>),
characterized in that the guide end is a nozzle guide end (<NUM>), the nozzle guide end (<NUM>) protruding from the end of the nozzle part (S) toward the front guide part (<NUM>), and
a ratio X/L between a length X in which the nozzle guide end (<NUM>) protrudes and a distance L between the nozzle guide end (<NUM>) and the front guide part (<NUM>) is between <NUM> to <NUM>.