EP4609777A1

EP4609777A1 - Dishwasher

Info

Publication number: EP4609777A1
Application number: EP23912730.1A
Authority: EP
Inventors: Jeong In Kim; Doo Hyun Kim; Hyung Man Park; Min Jae Jeong; Jungwon Kim
Original assignee: LG Electronics Inc
Current assignee: LG Electronics Inc
Priority date: 2022-12-26
Filing date: 2023-12-19
Publication date: 2025-09-03
Also published as: WO2024144055A1; KR20240102244A; EP4609777A4

Abstract

The present invention relates to a dishwasher wherein when a drying mode is in progress, the air which has dried a cleaning object is exhausted to the outside, and a heat exchanger acting as an evaporator and a heat exchanger acting as a condenser are arranged on a base to be exposed to the base, respectively, while the heat exchangers are arranged as close to each other as possible, thereby simplifying the installation structure of the dishwasher and improving space utilization.

Description

[Technical Field]

The present disclosure relates to a dishwasher and, more specifically, to a dishwasher in which air which has dried a washing target during a drying mode is discharged to an outside, and a heat-exchanger acting as an evaporator and a heat-exchanger acting as a condenser are disposed in an inner space of a base so as to be exposed to the inner space of the base, and are arranged so to be as close as possible to each other, thereby simplifying an installation structure of the dishwasher and improving space utilization thereof.

[Background Art]

A dishwasher is an apparatus that washes dishes and cooking utensils as washing targets stored therein by spraying washing water thereto. In this regard, the washing water may contain washing detergent.
A dishwasher generally includes a tub having a washing space defined therein, a dish rack that accommodates therein a washing target inside the tub, a spraying arm that sprays the washing water into the dish rack, and a sump that stores therein water and supplies the washing water to the spraying arm.
Using this dishwasher may allow a time and effort required to wash the dishes and other washing targets after a meal to be reduced, thereby contributing to user convenience.
In the washing process using the dishwasher, the washing water and air may be heated and used to increase the washing effect. An electric heater may be used as a device for heating the washing water and air. In one example, the washing water may be heated using a heat pump apparatus instead of the electric heater.
The heat pump apparatus has higher energy efficiency than the electric heater. Thus, when the washing water is heated by the heat pump apparatus, the consumption of electricity may be reduced.
In this regard, European Patent No. 3082554 (Prior Document 001) discloses a dishwasher including a heat pump apparatus for heating washing water and heating air, the heat pump apparatus including two switching valves for switching refrigerant flow paths between three heat-exchangers from each other and two switching dampers for switching air flow paths from each other in order to implement an air circulation type drying path structure for drying the washing target.
However, the structure disclosed in the prior document 001 is configured to change the flow direction of the refrigerant using a plurality of pipes and the two switching valves connecting the three heat-exchangers to each other, and thus the pipe connection structure of the refrigerant is very complicated and the plurality of pipes and the two switching valves are provided, thereby deteriorating the space utilization of the dishwasher and rapidly increasing a manufacturing cost thereof.
In addition, the structure disclosed in the prior document 001 has a problem in that the installation structure of the dishwasher is complicated and space utilization may be deteriorated because a separate structure and installation space for installing and accommodating both the heat-exchanger acting as the evaporator and the heat-exchanger acting as the condenser when a drying mode is progressed in order to form the air circulation type drying path structure are required.

[Disclosure]

[Technical Problem]

The present disclosure has been devised to solve the above-described problems of the prior art. Thus, a first purpose of the present disclosure is to provide a dishwasher in which air which has dried a washing target during a drying mode is discharged to an outside, and a heat-exchanger acting as an evaporator and a heat-exchanger acting as a condenser are disposed in an inner space of a base so as to be exposed to the inner space of the base, and are arranged so to be as close as possible to each other, thereby simplifying an installation structure of the dishwasher and improving space utilization thereof.
In addition, a second purpose of the present disclosure is to provide a dishwasher configured to have an air exhaust-type drying flow path structure instead of an air circulation-type drying flow path structure, thereby simplifying a structure of an air supply duct for drying the washing target.
Purposes of the present disclosure are not limited to the above-mentioned purpose. Other purposes and advantages of the present disclosure that are not mentioned may be understood based on following descriptions, and may be more clearly understood based on embodiments of the present disclosure. Further, it will be easily understood that the purposes and advantages of the present disclosure may be realized using means shown in the claims and combinations thereof.

[Technical Solution]

A dishwasher according to the present disclosure includes: A dishwasher according to the present disclosure includes: a tub having a washing space defined therein, wherein dishes are received in the washing space; a base disposed under the tub; and a heat pump apparatus for heating washing water to be introduced into the tub, wherein the heat pump apparatus includes: a compressor for compressing refrigerant; a first heat-exchanger configured to receive the refrigerant having flowed through the compressor and to heat the washing water to be supplied to the tub in a washing mode of the dishwasher; a second heat-exchanger configured to evaporate the refrigerant having flowed through the first heat-exchanger via heat-exchange between the refrigerant and air in the washing mode of the dishwasher; a third heat-exchanger configured to receive the refrigerant having flowed through the compressor and to heat the air to be supplied to the tub in a drying mode of the dishwasher; a first blower fan configured to generate a first airflow of air having flowed through the second heat-exchanger; and a second blower fan configured to generate a second airflow of air having flowed through the third heat-exchanger, wherein the third heat-exchanger may be disposed in the base in a state of being exposed to the first airflow.
Furthermore, the third heat-exchanger may be exposed to the first airflow before having flowed through the second heat-exchanger.
Furthermore, the third heat-exchanger may include: a plurality of main tubes extending so as to intersect the second airflow; and a plurality of connection tubes sequentially communicating the plurality of main tubes with each other, wherein the connection tubes may be exposed to the first airflow.
Furthermore, the second heat-exchanger may be disposed between the second blower fan and the third heat-exchanger.
Furthermore, the second heat-exchanger may be disposed in the base in a state of being exposed to the second airflow.
Furthermore, the second heat-exchanger may be exposed to the second airflow after having flowed through the third heat-exchanger.
Furthermore, the second heat-exchanger may include: a plurality of main tubes extending so as to intersect the first airflow; and a plurality of connection tubes sequentially communicating the plurality of main tubes to each other, wherein the connection tubes may be exposed to the second airflow.
Furthermore, the connection tubes of the second heat-exchanger may be disposed between the second blower fan and the third heat-exchanger.
Furthermore, the heat pump apparatus may further include a main guide duct disposed between the third heat-exchanger and the second blower fan and constructed to guide the second airflow having flowed through the third heat-exchanger to the second blower fan, wherein the main guide duct may be constructed to prevent the second heat-exchanger from being exposed to the second airflow.
Furthermore, the third heat-exchanger may include: a plurality of main tubes extending so as to intersect the second airflow; a plurality of connection tubes sequentially communicating the plurality of main tubes to each other; and a pair of holder plates for supporting the plurality of main tubes, wherein a passage area of the second airflow may be defined between the pair of holder plates, wherein the main guide duct may be constructed to allow the air having flowed through the passage area between the pair of holder plates to bypass the second heat-exchanger and to guide the air to the second blower fan.
Furthermore, an inlet end of the main guide duct may be connected to the pair of holder plates, wherein an outlet end of the main guide duct may be connected to an inlet of the second blower fan, wherein the main guide duct has a concave portion concave inwardly thereof in an area between the inlet end and the outlet end, wherein the concave portion bypasses the second heat-exchanger.
Furthermore, the heat pump apparatus may further include a sub-guide duct disposed between the second heat-exchanger and the first blower fan and constructed to guide the first airflow having flowed through the second heat-exchanger to the first blower fan.
Furthermore, the second heat-exchanger may include: a plurality of main tubes extending so as to intersect the first airflow; a plurality of connection tubes sequentially communicating the plurality of main tubes to each other; and a pair of holder plates for supporting the plurality of main tubes, wherein a passage area of the second airflow may be defined between the pair of holder plates, wherein an inlet end of the sub-guide duct may be connected to the pair of holder plates, wherein an outlet end of the sub-guide duct may be connected to an inlet of the first blower fan.

[Advantageous Effects]

In the dishwasher according to the present disclosure, the air which has dried the washing target during a drying mode is discharged to the outside, and the heat-exchanger acting as an evaporator and the heat-exchanger acting as a condenser are disposed in an inner space of the base so as to be exposed to the inner space of the base, and are arranged so to be as close as possible to each other, thereby simplifying an installation structure of the dishwasher and improving space utilization thereof.
In addition, the dishwasher according to the present disclosure is configured to have the air exhaust-type drying flow path structure instead of the air circulation-type drying flow path structure, thereby simplifying a structure of the air supply duct for drying the washing target.
In addition to the above-mentioned effects, the specific effects of the present disclosure as not mentioned will be described below along with the descriptions of the specific details for carrying out the present disclosure.

[Description of Drawings]

FIG. 1 is a front perspective view of a dishwasher according to an embodiment of the present disclosure.
FIG. 2 is a schematic cross-sectional view of the dishwasher illustrated in FIG. 1.
FIG. 3 is a schematic view for illustrating a heat pump apparatus provided in the dishwasher of FIG. 2.
FIG. 4 is a schematic view of a dishwasher having a heat pump apparatus according to an embodiment of the present disclosure.
FIG. 5 is a schematic diagram for illustrating an operation of the heat pump apparatus when the dishwasher illustrated in FIG. 4 operates in a washing mode.
FIG. 6 is a schematic view for illustrating an operation of the heat pump apparatus when the dishwasher illustrated in FIG. 4 operates in a drying mode.
FIG. 7 is a plan view illustrating a state in which a second heat-exchanger and a third heat-exchanger are disposed in a base according to a first embodiment of the present disclosure.
FIG. 8 is a cross-sectional view showing a cross-section of a configuration shown in FIG. 7 taken along a line 12-12.
FIG. 9 is a partially enlarged view illustrating a cross-section of a second heat-exchanger, a first blower fan, a third heat-exchanger, and a second blower fan illustrated in FIG. 7, taken along a horizontal direction.
FIG. 10 is a partially enlarged view illustrating a cross-section of a second heat-exchanger, a first blower fan, a third heat-exchanger, and a second blower fan as taken along a horizontal direction according to a second embodiment of the present disclosure.

[Best Mode]

The above-mentioned purposes, features, and advantages will be described in detail later with reference to the attached drawings, so that those skilled in the art in the technical field to which the present disclosure belongs may easily implement the technical ideas of the present disclosure. In describing the present disclosure, upon determination that a detailed description of the publicly known technology related to the present disclosure may unnecessarily obscure the gist of the present disclosure, the detailed description will be omitted. Hereinafter, a preferred embodiment according to the present disclosure will be described in detail with reference to the attached drawings. In the drawings, identical reference numerals are used to indicate identical or similar components.
Although first, second, and the like are used to describe various components, these components are not limited by such terms. Such terms are only used to distinguish one component from another component, and unless specifically stated to the contrary, a first component may also be a second component.
Throughout the present document, unless otherwise stated, each component may be singular or plural.
Hereinafter, a first component being disposed "on top of (or under)" a second component may mean that the first component may be disposed in contact with a top surface (or a bottom surface) of the second component, as well as a third component may be interposed between the second component and the first component disposed "on top of (or under)" the second component.
Furthermore, when a first component is described as being "connected" or "coupled" to a second component, the components may be directly connected or coupled to each other, but a third component may be "interposed" between the components or the components may be "connected" or "coupled" to each other via the third components.
As used herein, the singular constitutes "a" and "an" are intended to include the plural constitutes as well, unless the context clearly indicates otherwise. In this application, terms such as "composed of" or "include" should not be construed as necessarily including all of various components or operations described herein, but should be construed that some components or operations among those may not be included or additional components or operations may be further included.
As used herein, the singular constitutes "a" and "an" are intended to include the plural constitutes as well, unless the context clearly indicates otherwise. In this application, terms such as "composed of" or "include" should not be construed as necessarily including all of various components or operations described herein, but should be construed that some components or operations among those may not be included or additional components or operations may be further included.
Throughout the present document, "A and/or B" means A, B, or A and B, unless otherwise specified, and "C to D" means equal to or greater than C and equal to or smaller than D unless otherwise specified.

[Overall structure of dishwasher]

Hereinafter, an overall structure of a dishwasher 1 according to an embodiment of the present disclosure will be described in detail with reference to the attached drawings.
FIG. 1 is a front perspective view showing the dishwasher according to the present disclosure. FIG. 2 is a simplified cross-sectional view briefly showing an internal structure of the dishwasher according to the present disclosure.
As illustrated in FIG. 1 to FIG. 2, the dishwasher 1 according to an embodiment of the present disclosure may include a casing 9 that constitutes an exterior appearance, a tub 2 installed in an inner space of the casing 9 and having a washing space 21 defined therein where the washing target is washed, wherein a front surface of the tub is open, a door 3 that opens/closes the open front surface of the tub 2, a sump 4 disposed under the tub 2 for storing therein the washing water for washing the washing target, a dish rack 5 removably provided in the inner washing space 21 of the tub 2 to receive therein the washing target, and a water sprayer 20 installed adjacent to the dish rack 5 to spray the washing water for washing the washing target thereto.
In this regard, the washing target received in the dish rack 5 may be, for example, dishes such as bowls, plates, spoons, and chopsticks, and other cooking utensils. Hereinafter, unless otherwise specified, the washing target will be referred to as a dish.
The tub 2 may be formed in a box shape with an entirely open front surface, and have a configuration of a so-called washing tub.
The washing space 21 may be defined inside the tub 2. The open front surface of the tub 2 may be opened/closing by the door 3.
The tub 2 may be formed via pressing of a metal plate resistant to high temperature and moisture, for example, a stainless steel plate.
Moreover, on an inner surface of the tub 2, a plurality of brackets may be disposed for the purpose of supporting and installing functional components such as the dish rack 5 and the water sprayer 20 which will be described later thereon within the tub 2.
In one example, the sump 4 may include storage 41 that stores therein washing water, a sump cover 42 that distinguishes the storage 41 from the tub 2, a water supply 43 that supplies washing water from an external source to the storage 41, a water discharger 44 that discharges the washing water of the storage 41 to an outside, and a washing pump 45 and a supply flow path 46 that supply the washing water of the storage 41 to the water sprayer 20.
The sump cover 42 may be disposed at a top of the sump 4 and may serve to distinguish the tub 2 and the sump 4 from each other. Moreover, the sump cover 42 may have a plurality of collecting holes defined therein for collecting washing water sprayed into the washing space 21 through the water sprayer 20 into the sump 4.
That is, the washing water sprayed from the water sprayer 20 toward the dish may fall down to a bottom of the washing space 21, and may be collected again through the sump cover 42 and into the storage 41.
The washing pump 45 may be disposed at a side or a bottom of the sump 4 and may serve to pressurize the washing water and supply the pressurized washing water to the water sprayer 20.
One end of the washing pump 45 may be connected to the storage 41 of the sump 4 and the other end thereof may be connected to the supply flow path 46. The washing pump 45 may be equipped with an impeller 451 and a motor 453. When power is supplied to the motor 453, the impeller 451 may rotate, and thus the washing water in the storage 41 may be pressurized, and then may be supplied to the water sprayer 20 through the supply flow path 46.
In one example, the supply flow path 46 may serve to selectively supply the washing water supplied from the washing pump 45 to the water sprayer 20.
For example, the supply flow path 46 may include a first supply flow path 461 connected to a lower spraying arm 26, and a second supply flow path 463 and 467 connected to an upper spraying arm 27 and a top nozzle 29. The supply flow path 46 may be provided with a supply flow path switching valve 465 that selectively opens/closes the supply flow paths 461, 463 and 467.
In this regard, the supply flow path switching valve 465 may be controlled so that the supply flow paths 461, 463 and 467 are opened sequentially or simultaneously.
In one example, the water sprayer 20 may be constructed to spray the washing water to the dishes stored in the dish rack 5.
More specifically, the water sprayer 20 may include the lower spraying arm 26 located under the tub 2 to spray the washing water to a lower rack 51, the upper spraying arm 27 located between the lower rack 51 and an upper rack 53 to spray the washing water to the lower rack 51 and the upper rack 53, and the top nozzle 29 located on top of the tub 2 to spray the washing water to a top rack or the upper rack 53.
In particular, the lower spraying arm 26 and the upper spraying arm 27 may be rotatably disposed in the washing space 21 of the tub 2 and may spray the washing water toward the washing target of the dish rack 5 while being rotating.
The lower spraying arm 26 may be rotatably supported on a top of the sump cover 42 so as to spray the washing water toward the lower rack 51 while being rotating and being disposed under the lower rack 51.
Moreover, the upper spraying arm 27 may be rotatably supported so as to spray the washing water on the dish while being rotating and being disposed between the lower rack 51 and the upper rack 53.
In one example, in order to increase washing efficiency, additional means for diverting the washing water sprayed from the lower spraying arm 26 into an upward direction (diverting in a U-direction) may be provided at a lower surface 25 of the tub 2.
In one example, the dish rack 5 for storing the washing target therein may be disposed in the washing space 21.
The dish rack 5 may be constructed to extend or retract from or into the inner space of the tub 2 through the open front surface of the tub 2.
For example, in FIG. 2, an embodiment is shown in which the dish rack 5 includes the lower rack 51 located at a lower portion of the tub 2 to accommodate therein relatively large dishes, the upper rack 5 located on top of the lower rack 51 to accommodate therein medium-sized dishes, and the top rack located at a top level of the tub 2 and capable of storing therein small dishes, etc. However, the present disclosure is not limited thereto. However, hereinafter, an example in which the dishwasher includes the three dish racks 5 as shown is described.
Each of the lower rack 51, the upper rack 53, and the top rack may be constructed to extend or retract from or into the inner space of the tub 2 through the open front surface of the tub 2.
For this purpose, guide rails (not shown) may be respectively disposed on both opposing walls constituting an inner surface of the tub 2. By way of example, the guide rails (not shown) may include an upper rail, a lower rail, and a top rail.
Wheels may be disposed on a bottom of each of the lower rack 51, the upper rack 53, and the top rack. The user may extend the lower rack 51, the upper rack 53, and the top rack from the inner space of the tub 2 through the open front surface of the tub 2 and may place the washing target thereon, or easily withdraw the washing target that have been washed out thereof.
The guide rail (not shown) may be embodied as a simple rail-type fixed guide rail to guide the extending or the retracting of the rack 5, or a telescopic guide rail capable of guiding the extending or the retracting of the rack 5 and at the same time, increasing an extension distance thereof as the rack 5 further extends from the inner space of the tub.
In one example, the door 3 is configured for opening/closing the open front surface of the tub 2 as described above.
A hinge (not shown) around which the door 3 is closed or opened may be provided at a bottom of the open front surface. Thus, the door 3 may pivot around the hinge as a pivot axis.
In this regard, a handle 3a for opening the door 3 and a control panel 3b for controlling the dishwasher 1 may be disposed on an outer side surface of the door 3.
As shown, the control panel 3b may include a display 3c that visually displays information regarding a current operating status of the dishwasher, etc., and a button unit 3d including a selection button through which a user's selection manipulation is input and a power button through which a user's manipulation for turning the dishwasher on and off is input.
In one example, a rear panel constituting an inner side surface of the door 3 may constitute one side surface of the tub 2 when the door 3 has been closed, and may constitute a seat surface on which the lower rack 51 of the dish rack 5 is supported when the door 3 is fully opened.
For this purpose, when the door 3 is fully opened downwardly, the rear panel of the door 3 may constitute a horizontal plane extending in the same direction as a direction in which the guide rail (not shown) guiding the displacement of the lower rack 51 extends.
In one example, the dishwasher 1 according to an embodiment of the present disclosure may further include a base 8.
The base 8 may be disposed under the tub 2 and may serve to support the tub 2.
Alternatively, the base 8 may provide a space in which the sump 4 is accommodated, and may provide an accommodation space in which various devices provided in the dishwasher 1 are accommodated.
Therefore, the base 8 may be manufactured to have an outer wall to support an entirety of the dishwasher, and to have an outer wall defining an accommodation space in which various devices are accommodated.
In one example, in the dishwasher according to an embodiment of the present disclosure, the washing water to be supplied to the tub 2 is heated and thus, the high-temperature washing water is sprayed to the washing target accommodated in the tub 2, thereby improving washing efficiency of the washing target and performance of the dishwasher 1.
To this end, the dishwasher according to an embodiment of the present disclosure may include a heat pump apparatus 10 for heating the washing water introduced into the tub 2. The heat pump apparatus 10 may heat the washing water so that the dishes are washed with high-temperature washing water, thereby improving the performance of the dishwasher.
The device for heating the washing water may be generally embodied as an electric heater that heats the washing water by converting electrical energy into thermal energy.
A coefficient of performance (COP) is a measure indicating the energy efficiency of each of the electric heater and the heat pump apparatus 10. As the coefficient of performance (COP) increases, the energy efficiency of the device increases.
The electric heater has a maximum COP of merely 1. However, when the washing water is heated using the heat pump apparatus 10 instead of the electric heater, the heat pump apparatus 10 may heat the washing water by transferring the heat from a low temperature thermal reservoir to a high temperature thermal reservoir.
Due to this structure, the COP of the heat pump apparatus 10 may exceed 1.
The COP of most of the heat pump apparatuses 10 actually used exceeds 1. Therefore, in the dishwasher that heats the washing water using the heat pump apparatus 10, energy efficiency may be improved compared to that when heating the washing water using the electric heater.

[Schematic Configuration of Heat Pump Apparatus]

Hereinafter, the heat pump apparatus 10 provided in the dishwasher 1 according to an embodiment of the present disclosure will be described in more detail with reference to FIG. 3 and subsequent drawings.
FIG. 3 is a schematic diagram schematically showing the configuration of the heat pump apparatus 10.
In the drawings of FIG. 3 and subsequent drawings, a refrigerant flow path Fr is indicated by a solid line, a washing water flow path Fw is indicated by a dashed line, and an air flow path Fa is indicated by a dotted line.
Referring to FIG. 3, the heat pump apparatus 10 may include a compressor 100, a condenser 201, an expansion valve 300, and an evaporator 202.
The compressor 100, the condenser 201, the expansion valve 300, and the evaporator 202 are connected to each other via a pipe, and the pipe provides the refrigerant flow path Fr through which the refrigerant may flow.
The refrigerant may function as a working fluid that absorbs heat or releases the heat while sequentially circulating through the compressor 100, the condenser 201, the expansion valve 300, and the evaporator 202 while a phase thereof is changing from liquid to gas, or from gas to liquid.
The compressor 100 may compress the refrigerant to discharge the refrigerant in a high-temperature and high-pressure state. The refrigerant discharged from the compressor 100 may be introduced into the condenser 201.
The refrigerant may radiate heat of QH while flowing through the condenser 201. The heat emitted from the condenser 201 may be used to heat the washing water or air introduced into the tub 2. Accordingly, respective flow paths through which the refrigerant, the washing water, and the air pass, respectively may be provided in the condenser 201. The refrigerant may dissipate the heat and thus may be phase-changed from gas to a liquid state while flowing through the condenser 201.
In this regard, the refrigerant having flowed through the condenser 201 may be a mixed gas of a liquid and a gas having a very small gas content, or may be a subcooled liquid.
The refrigerant discharged from the condenser 201 may be expanded while flowing through the expansion valve 300. As a result of the expansion of the refrigerant, the temperature of the refrigerant is lowered such that the refrigerator becomes a mixed gas in which gas and liquid are mixed with each other.
The refrigerant discharged from the expansion valve 300 absorbs heat QL from the air of the tub 2 and evaporates while flowing through the evaporator 202, and accordingly, the content of the gas in the refrigerant increases.
In a state in which the refrigerant has exited the evaporator 202, the refrigerant may be a mixed gas having a very small proportion of liquid or a superheated gas.
The refrigerant discharged from the evaporator 202 may be introduced into the compressor 100 again and compressed by the compressor to become a high-temperature and high-pressure gas.
In the above-described order, the refrigerant circulates through the heat pump apparatus 1. In this circulation process, the phase of the refrigerant changes, and accordingly, the refrigerant may absorb heat in the evaporator 202 and discharge heat in the condenser 201.
In order to allow active heat transfer in the evaporator 202, it is desirable to allow a large amount of air to flow toward the evaporator 202. To this end, the heat pump apparatus 10 may further include a blower fan 620 for blowing the air toward the evaporator 202.
In one example, the dishwasher 1 may operate in a washing mode in which the heated washing water is sprayed to the dishes as the washing target accommodated in the tub 2, and a drying mode in which the heated air is sprayed to the dishes accommodated in the tub 2 to remove moisture from a surface of the washing target after the washing mode is terminated.
In an embodiment as described below, a plurality of heat-exchangers are provided. When the washing mode or the drying mode is performed, each heat-exchanger may be used or not used, and may act as the condenser 201 or the evaporator 202.

[Pipe Connection Structure of Heat Pump Apparatus and Tub]

Hereinafter, a connection structure between the heat pump apparatus 10 and the tub 2 via a pipe and a duct according to an embodiment of the present disclosure will be described in detail with reference to FIGS. 4 to 6.
First, referring to FIG. 4, the heat pump apparatus 10 according to an embodiment may be configured to include the compressor 100, a first heat-exchanger 210, a first expansion valve 310, a second heat-exchanger 220, a second expansion valve 320, a third heat-exchanger 230, and a four-way valve 400a.
The first heat-exchanger 210 may act as the condenser 201 of transferring the heat from the refrigerant to the washing water so that the washing water is heated and the refrigerant is condensed during the washing mode.
In addition, as will be described later, the refrigerant flow path Fr is switched via the four-way valve 400a, so that the supply of the refrigerant to the first heat-exchanger 210 may be cut off during the drying mode.
The first expansion valve 310 may serve to receive the refrigerant from the first heat-exchanger 210 and expand the received refrigerant.
The refrigerant may be introduced through the first expansion valve 310 into the second heat-exchanger 220. In an embodiment, the second heat-exchanger 220 may act as the evaporator 202 both in the washing mode and in the drying mode.
The second expansion valve 320 and the first expansion valve 310 may be connected to each other in a parallel manner to each other. The second expansion valve 320 may receive the refrigerant from the first heat-exchanger 210 and expand the received refrigerant. When the dishwasher 1 operates in the washing mode, the second expansion valve 320 may operate to be opened. When the dishwasher 1 operates in the drying mode, the second expansion valve 320 may operate to be closed.
The third heat-exchanger 230 and the second heat-exchanger 220 may be connected to each other in a parallel manner to each other. The third heat-exchanger 230 may receive the refrigerant having flowed through the second expansion valve 320. In an embodiment, the third heat-exchanger 230 may act as the evaporator 202 when the washing mode is performed, and may act as the condenser 201 when the drying mode is performed.
The second heat-exchanger 220 and the third heat-exchanger 230 may be disposed on a bottom 81 of the base 8, and may be in an open or exposed state to the accommodation space of the base 8 as described below. In consideration of space utilization, the second heat-exchanger 220 and the third heat-exchanger 230 may be arranged so as to be close as possible to each other. A detailed configuration regarding the arrangement of the second heat-exchanger 220 and the third heat-exchanger 230 will be described later with reference to FIG. 7 and subsequent drawings.
The four-way valve 400a is connected to each of the compressor 100, the first heat-exchanger 210, the second heat-exchanger 220, and the third heat-exchanger 230 via each of corresponding pipes, and performs a function of changing the refrigerant flow path Fr.
The four-way valve 400a may allow the refrigerant flow path Fr in the washing mode and the refrigerant flow path Fr in the drying mode to be different from each other. Thus, the four-way valve 400a may allow each of the first heat-exchanger 210 to the third heat-exchanger 230 to be used or non-used, or may allow each of the first heat-exchanger 210 to the third heat-exchanger 230 to act as the condenser 201 or as the evaporator 202.
In one example, the heat pump apparatus 10 according to an embodiment may further include a first pipe 410 connecting the four-way valve 400a and the compressor 100 to each other, a second pipe 420 connecting the four-way valve 400a and the first heat-exchanger 210 to each other, a third pipe 430 connecting the four-way valve 400a and the second heat-exchanger 220 to each other, a fourth pipe 440 connecting the four-way valve 400a and the third heat-exchanger 230 to each other, and a fifth pipe 450 connecting the second heat-exchanger 220 and the compressor 100 to each other. Each of the pipes may provide the refrigerant flow path Fr through which the refrigerant flows and circulates.
In this regard, the third pipe 430 may be constructed to be connected to the fifth pipe 450. Accordingly, the refrigerant flowing through the third pipe 430 may be introduced into the compressor 100 through the fifth pipe 450.
The third pipe 430 may be provided with a first check valve 510 that prevents the refrigerant from flowing from the fifth pipe 450 toward the four-way valve 400a. As is generally known, the check valve serves to cause the refrigerant to flow in one of both opposite directions along the pipe and to prevent the refrigerant from flowing in the other thereof.
As shown in FIG. 4, the first check valve 510 allows the refrigerant to flow in a direction from the four-way valve 400a toward the compressor 100, but may prevent the refrigerant from flowing in a direction from the second heat-exchanger 220 toward the four-way valve 400a.
In one example, the heat pump apparatus 10 may include a first blower fan 621 disposed to face the second heat-exchanger 220 and configured to generate an airflow of air flowing through the second heat-exchanger 220 and a second blower fan 622 disposed to face the third heat-exchanger 230 and configured to generate an airflow of air flowing through the third heat-exchanger 230.
The first blower fan 621 may blow the air so that the air flows through the second heat-exchanger 220. The second blower fan 622 may blow the air so that the air flows through the third heat-exchanger 230. Thus, a large amount of air may flow through each of the second heat-exchanger 220 and the third heat-exchanger 230. Accordingly, the amount of heat transfer between the refrigerant flowing inside each of the second heat-exchanger 220 and the third heat-exchanger 230 and the air flowing outside each of the second heat-exchanger 220 and the third heat-exchanger 230 may be improved.
As illustrated, the first blower fan 621 may be disposed at a position facing the second heat-exchanger 220, and may be disposed between a rear surface 82 of the base 8 and the second heat-exchanger 220 as described below and by way of example.
In a similar manner thereto, the second blower fan 622 may be disposed at a position facing the third heat-exchanger 230, and may be disposed between the rear surface 82 of the base 8 and the third heat-exchanger 230 as described below and by way of example.
Details about the arrangement structure of the first blower fan 621 and the second heat-exchanger 220 and the arrangement structure of the second blower fan 622 and the third heat-exchanger 230 will be described below with reference to FIG. 7 and subsequent drawings.
In one example, the heat pump apparatus 10 may further include a bypass pipe 470 and a second check valve 520. Both opposing ends of the bypass pipe 470 may be connected to both opposing sides of the second expansion valve 320, respectively. Therefore, when the second expansion valve 320 is closed, the refrigerant may flow through the bypass pipe 470 while bypassing the second expansion valve 320.
The second check valve 520 may be disposed in the bypass pipe 470 and may prevent the refrigerant from flowing from an inlet to an outlet of the second expansion valve 320 through the bypass pipe 470.
When the washing mode is performed, the second expansion valve 320 may be opened. In this regard, the second check valve 520 may prevent the refrigerant from flowing from the inlet to the outlet of the second expansion valve 320 through the bypass pipe 470.
In addition, when the drying mode is in progress, the second expansion valve 320 may be closed. In this regard, the second check valve 520 may allow the refrigerant to flow from the outlet to the inlet of the second expansion valve 320 through the bypass pipe 470, and may prevent the refrigerant from flowing from the inlet to the outlet of the second expansion valve 320 through the bypass pipe 470.
In addition, the heat pump apparatus 10 may further include a sixth pipe 460 and a third check valve 530. The sixth pipe 460 may have one end connected to the first heat-exchanger 210 and the other end connected to each of the first expansion valve 310, the second expansion valve 320, and the bypass pipe 470.
The third check valve 530 may be disposed between one end and the other end of the sixth pipe 460 and may prevent the refrigerant from flowing from at least one of the first expansion valve 310, the second expansion valve 320, and the bypass pipe 470 toward the first heat-exchanger 210.
The first heat-exchanger 210 may not be used during the drying mode. Accordingly, the third check valve 530 may be disposed in the sixth pipe 460 connected to the outlet of the first heat-exchanger 210 so that the refrigerant does not flow in the first heat-exchanger 210. Accordingly, the third check valve 530 may prevent the refrigerant from flowing backward into the first heat-exchanger 210 through the outlet of the first heat-exchanger 210.
In one example, the dishwasher 1 may include the sump 4 disposed under the tub 2 and constructed to store therein the washing water, and the sprayer 20 disposed inside the tub 2, connected to the sump 4, and configured to spray the washing water.
The first heat-exchanger 210 and the sump 4 may be connected to each other via a pipe constituting the washing water flow path Fw through which the washing water circulates. To this end, the dishwasher 1 may include a first water supply flow path 31 and a washing pump 45. The first water supply flow path 31 may be disposed in the above-described supply flow path 46.
The first water supply flow path 31 may connect the first heat-exchanger 210 and the sprayer 20 to each other, and the washing water may flow in the first water supply flow path 31. The washing pump 45 may be disposed in a circulation flow path 50 connecting the sump 4 and the first heat-exchanger 210 to each other, or may be disposed in the first water supply flow path 31. An embodiment in which the washing pump 45 is disposed in the circulation flow path 50 is described below with reference to FIG. 4. The present disclosure is not limited thereto. However, the present disclosure will be described based on the illustrated embodiment.
The circulation flow path 50 may be connected to the first heat-exchanger 210. Thus, the washing water may be heated by absorbing the heat from the refrigerant flowing through the first heat-exchanger 210 while flowing through the first heat-exchanger 210 through the circulation flow path 50. The refrigerant may be condensed while the heat therefrom is taken away by the washing water in the first heat-exchanger 210 acting as the condenser 201.
The heated washing water discharged from the first heat-exchanger 210 may be introduced into the sprayer 20 through the first water supply flow path 31 and may be sprayed to the tub 2 through the sprayer 20.
The washing water may drop downwardly from the tub 2 and re-enter the sump 4. The sump 4 may be disposed under the tub 2. Therefore, the washing water may drop downwardly of the tub 2 under the gravity and be introduced into the sump 4.
In one example, the heat pump apparatus 10 of the dishwasher 1 according to an embodiment may further include an air flow channel 600 that provides an air flow path Fa along which the air to be supplied to the tub 2 and the air discharged from the tub 2 flow during the drying mode.
First, as illustrated in FIG. 4, the air flow channel 600 may include a supply duct 640 defining an introduction flow path for guiding air having flowed through the second blower fan 622 toward the tub 2.
The supply duct 640 may have a first inlet 641 formed at one end thereof, and a second outlet 644 formed at the other end thereof. The air introduction flow path may be formed between the first inlet 641 and the second outlet 644.
The first inlet 641 of the supply duct 640 may always communicate with a fan housing 622 (see FIG. 9) of the second blower fan 622. Accordingly, second airflow F2 of the air having flowed through the second blower fan 622 may be introduced into the supply duct 640 through the first inlet 641.
The second outlet 644 of the supply duct 640 may communicate with the tub 2. By way of example, the second outlet 644 may be formed in a lower surface of the tub 2 so that air may be effectively sprayed onto the washing target and drying efficiency for drying the washing target may be secured.
Between the first inlet 641 and the second outlet 644, a first outlet 643 opened toward the base 8 and a second inlet 642 constituting an inner flow path of the supply duct 640 may be formed.
As described above, the third heat-exchanger 230 functions as an evaporator during the washing mode and functions as a condenser during the drying mode.
The first outlet 643 serves to discharge the air cooled while flowing through the third heat-exchanger 230 toward the base 8 during the washing mode.
The second inlet 642 serves as an intermediate inlet for introducing the air heated while flowing through the third heat-exchanger 230 toward the second outlet 644 during the drying mode.
As described above, the flow path Fa of the air generated inside the supply duct 640 may be switched such that the flow path Fa of the air generated inside the supply duct 640 in the washing mode and the flow path Fa of the air generated inside the supply duct 640 in the drying mode are different from each other.
The air flow channel 600 may include a damper 632 as a means for switching the internal air flow path Fa of the supply duct 640.
The first outlet 643 and the second inlet 642 may be selectively opened and closed by the damper 632.
In this regard, the selective opening and closing may mean that one of the two opening and closing targets is opened and one thereof is closed.
Accordingly, the damper 632 selectively opening and closing the first outlet 643 and the second inlet 642 of the supply duct 640 may be interpreted as that the second inlet 642 is closed when the first outlet 643 is opened, and the formulation second inlet 642 is opened when the first outlet 643 is closed.
Accordingly, during the drying mode, when the first outlet 643 is closed by the damper 632, the air discharged from the second blower fan 622 may be introduced into the second inlet 642 of the supply duct 640, and may flow along the air flow path Fa formed inside the supply duct 640, flow through the second outlet 644 of the supply duct 640, and then be introduced into the tub 2.
However, as will be described later, when the washing mode is performed, the second inlet 642 of the supply duct 640 may be blocked by the damper 632, and the first outlet 643 may be opened by the damper 632.
In order to easily perform such selective opening and closing, the damper 632 may be embodied as a flap-type damper that is pivotable about one end thereof as shown in FIG. 4.
However, this is merely an example, and any means capable of implementing the selective opening and closing may be applied as the damper 632 without limitation. Hereinafter, the present disclosure will be described based on an embodiment in which the damper 632 is provided as the flap-type damper. However, the present disclosure is not limited thereto.
[Refrigerant, Air Flow Path in Washing Mode]
Hereinafter, the operation of the heat pump apparatus 10 when washing water is heated during the washing mode according to an embodiment of the present disclosure will be described with reference to FIG. 5.
When the dishwasher 1 operates in the washing mode, the four-way valve 400a may connect the first pipe 410 and the second pipe 420 to each other and may also connect the third pipe 430 and the fourth pipe 440 to each other.
In this case, the first pipe 410 is not connected to the third pipe 430 or the fourth pipe 440, and the second pipe 420 is not connected to the third pipe 430 or the fourth pipe 440.
Accordingly, the first pipe 410 and the second pipe 420 may be separated from the third pipe 430 and the fourth pipe 440, and similarly, the third pipe 430 and the fourth pipe 440 may be separated from the first pipe 410 and the second pipe 420.
Accordingly, the refrigerant flowing out from the compressor 100 may flow through the first pipe 410 and the second pipe 420 to flow into the first heat-exchanger 210, the refrigerant flowing out from the second heat-exchanger 220 may flow through the fifth pipe 450 to flow into the compressor 100, and the refrigerant flowing out from the third heat-exchanger 230 may sequentially flow through the fourth pipe 440, the third pipe 430, and the fifth pipe 450 to flow into the compressor 100.
In this regard, since the refrigerant flowing into the first heat-exchanger 210 is in a high-temperature/high-pressure state, the heat therefrom may be taken away by the washing water flowing through the first heat-exchanger 210 and thus the refrigerant may be condensed. Accordingly, the first heat-exchanger 210 may operate as a condenser that heats the washing water.
The refrigerant discharged from the first heat-exchanger 210 may be distributed into the first expansion valve 310 and the second expansion valve 320 connected in parallel with each other, and may be expanded while flowing through the first expansion valve 310 and the second expansion valve 320 such that the temperature thereof is lowered. When the washing mode is performed, the second expansion valve 320 may be opened to allow the refrigerant to flow therethrough, and the second check valve 520 may prevent the refrigerant from flowing through the bypass pipe 470.
The refrigerant discharged from the first expansion valve 310 may sequentially flow through the second heat-exchanger 220 and the fifth pipe 450 and be introduced into the compressor 100. In this regard, the refrigerant introduced into the second heat-exchanger 220 absorbs the heat from the air and evaporates while flowing through the second heat-exchanger 220. Thus, the second heat-exchanger 220 acts as an evaporator.
Since the third pipe 430 has the first check valve 510, the first check valve 510 may prevent the refrigerant from flowing into the four-way valve 400a through the third pipe 430.
The refrigerant discharged from the second expansion valve 320 may sequentially flow through the third heat-exchanger 230, the fourth pipe 440, the four-way valve 400a, the third pipe 430, and the fifth pipe 450 and may be introduced into the compressor 100.
In this regard, like the second heat-exchanger 220, the refrigerant introduced into the third heat-exchanger 230 absorbs heat from air and evaporates while flowing through the third heat-exchanger 230. Thus, the third heat-exchanger 230 acts as an evaporator.
On the other hand, when the washing mode is performed, the damper 632 pivots to a position at which the damper closes the second inlet 642 as described above.
Accordingly, the air flow path Fa inside the supply duct 640 may be closed, and the inflow and outflow of air to and from the tub 2 may be blocked.
In this case, the first outlet 643 of the supply duct 650 is opened toward the base 8.
Accordingly, when the second blower fan 622 operates, the air of the base 8 may be converted to second airflow F2 which may flow through the third heat-exchanger 230 and may heat exchange with the refrigerant therein. The air having flowed through the third heat-exchanger 230 may be introduced into the second fan housing 62 2a and then flow through the first outlet 643 of the supply duct 640 and then may be discharged toward the rear surface 82 of the base 8.
In this case, the first blower fan 621 may also operate together with the second blower fan 622.
When the first blower fan 621 operates, the air of the base 8 may be converted to the first airflow F1 which may heat-exchange with the refrigerant while flowing through the second heat-exchanger 220. The air having flowed through the second heat-exchanger 220 may be discharged toward the rear surface of the base 8 through the first blower fan 621.
Accordingly, the air cooled via the heat exchange with the refrigerant in each of the second heat-exchanger 220 and the third heat-exchanger 230 may be discharged toward the rear surface 82 of the base 8.

[Refrigerant and Air Flow Paths in Drying Mode]

Next, an operation of the heat pump apparatus 10 when the dishwasher 1 condenses water vapor included in the air and heats the air during the drying mode according to an embodiment of the present disclosure will be described with reference to FIG. 6.
After the washing mode has been terminated, the dishwasher 1 may proceed to a drying mode in which the washing target accommodated in the tub 2 is dried using heated air.
The flow of washing water in the heat pump apparatus 10 may be stopped during the drying mode. Accordingly, in the drying mode, the washing water may not be sprayed to the tub 2, but instead, the heated air may be sprayed to the tub 2 through the air flow channel 600.
When the dishwasher 1 operates in the drying mode, the four-way valve 400a may connect the first pipe 410 and the fourth pipe 440 to each other, and the second pipe 420 and the third pipe 430 may be separated from the first pipe 410 and the fourth pipe 440.
In this case, the first pipe 410 is not connected to the second pipe 420 or the third pipe 430, and the fourth pipe 440 is not connected to the second pipe 420 or the third pipe 430. Instead, the second pipe 420 and the third pipe 430 may be connected to each other.
Accordingly, a refrigerant flow path Fr along which the refrigerant flowing out from the compressor 100 flows through the first pipe 410 and the fourth pipe 440 and flows into the third heat-exchanger 230, the refrigerant flowing out from the second heat-exchanger 220 flows through the fifth pipe 450 and flow into the compressor 100, and the first check valve 510 and the third check valve 530 prevents the refrigerant from flowing into the first heat-exchanger 210 may be established.
More specifically, the refrigerant discharged from the compressor 100 may sequentially flow through the first pipe 410, the four-way valve 400a, and the fourth pipe 440 and may be introduced into the third heat-exchanger 230.
The high-temperature refrigerant having flowed through the third heat-exchanger 230 may be condensed while the heat therefrom is taken away by the air. Accordingly, the third heat-exchanger 230 may operate as the condenser 201 during the drying mode.
When the drying mode is in progress, the second expansion valve 320 may be closed.
The refrigerant may bypass the closed second expansion valve 320, flow through the bypass pipe 470, the second check valve 520, and the sixth pipe 460, and flow into the first expansion valve 310. The sixth pipe 460 is connected to the first heat-exchanger 210. However, the third check valve 530 is disposed in the sixth pipe 460, such that the third check valve 530 may prevent the refrigerant from flowing into the first heat-exchanger 210.
The refrigerant may be expanded while flowing through the first expansion valve 310 such the temperature thereof is lowered. The low-temperature refrigerant may be introduced into the second heat-exchanger 220, and may evaporate by taking away the heat from the flowing air having a relatively high temperature in the second heat-exchanger 220. Accordingly, in the drying mode, the second heat-exchanger 220 may operate as the evaporator 202.
The refrigerant discharged from the second heat-exchanger 220 may flow through the fifth pipe 450 and be introduced into the compressor 100. The fifth pipe 450 is connected to the third pipe 430, and the third pipe 430 is connected to the four-way valve 400a. However, the first check valve 510 is disposed in the third pipe 430, such that the first check valve 510 may prevent the refrigerant from flowing into the first heat-exchanger 210 through the four-way valve 400a.
Accordingly, in the drying mode, the first heat-exchanger 210 may not be used as the evaporator 202 or another type of the heat-exchanger because the first check valve 510 and the third check valve 530 prevent the refrigerant from flowing through the first heat-exchanger 210 and the washing water does not flow through the first heat-exchanger 210.
In the drying mode, as described above, the damper 632 pivots to a position at which the damper closes the first outlet 643 of the supply duct 640.
Accordingly, the air flow path Fa inside the supply duct 640 communicates with the second fan housing 622a of the second blower fan 622.
Accordingly, when the second blower fan 622 operates, the air discharged from the second blower fan 622 through the third heat-exchanger 230 is introduced into the second inlet 642 of the supply duct 640, and is supplied to the tub 2 through the second outlet 644.
After the air supplied to the tub 2 has dried the washing target, the air is discharged to the outside through a partially opened door 3 as shown in the drawing.
The first blower fan 621 may be activated even during the drying mode.
When the first blower fan 621 operates to form the first airflow F1, heat exchange may be performed between the air of the base 8 and the refrigerant in the second heat-exchanger 220.
In this regard, since the second heat-exchanger 220 acts as an evaporator, the water vapor included in the first airflow F1 may be at least partially condensed while flowing through the second heat-exchanger 220.
Although not shown, the base 8 may further include a means for collecting the condensed water condensed by the second heat-exchanger 220.

[Arrangement Structure of Second and Third Heat-exchangers According to First Embodiment]

Hereinafter, the arrangement structure of the second heat-exchanger 220 and the third heat-exchanger 230 provided in the heat pump apparatus 10 according to the first embodiment of the present disclosure will be described with reference to FIGS. 7 to 9.
As described above, a purpose of the present disclosure is to simplify the structure of the air flow path by configuring the air flow path as an exhaust type drying flow path rather than a circulation type drying flow path.
To this end, the second heat-exchanger 220 acting as an evaporator in the drying mode and the third heat-exchanger 230 acting as a condenser in the drying mode may be installed and supported on the bottom 81 of the base 8 in a state of being exposed to the accommodation space of the base 8.
Accordingly, an accommodation member or a duct member for accommodating therein the second heat-exchanger 220 and the third heat-exchanger 230 together and allowing air to flow therethrough sequentially may be omitted.
However, as described above, the supply duct 640 for guiding the air heated while flowing through the third heat-exchanger 230 to the tub 2 during the drying mode may be connected to an outlet of the second fan housing 622a.
For example, each of the second heat-exchanger 220 and the third heat-exchanger 230 may be embodied as a tube-type heat-exchanger having a relatively low manufacturing cost and excellent heat exchange performance.
Hereinafter, an example in which each of the second heat-exchanger 220 and the third heat-exchanger 230 is embodied as the tube-type heat-exchanger will be described. However, embodiments of the present disclosure is not limited thereto.
As illustrated, each of the second heat-exchanger 220 and the third heat-exchanger 230 may include each of refrigerant tubes 221 and 231 in which a phase change of the refrigerant occurs while the refrigerant flows therein.
In this case, each of the refrigerant tubes 221 and 231 of the second heat-exchanger 220 and the third heat-exchanger 230 may be provided in a form of being bent a plurality of times, similarly to a general tube-type heat-exchanger, in order to extend the flow path of the refrigerant as long as possible and improve heat transfer efficiency.
More specifically, the refrigerant tube 221 of the second heat-exchanger 220 may include a plurality of main tubes 2211 linearly extending in a direction intersecting the first airflow F1 generated by the first blower fan 621, and a plurality of connection tubes 2212 bent in a U shape to sequentially communicate the plurality of main tubes 2211 with each other.
Similarly, the refrigerant tube 231 of the third heat-exchanger 230 may include a plurality of main tubes 2311 linearly extending in a direction intersecting the second airflow F2 generated by the second blower fan 622, and a plurality of connection tubes 2312 bent in a U shape to sequentially communicate the plurality of main tubes 2311 with each other.
The refrigerant tube 221 of the second heat-exchanger 220 may be supported by a pair of holder plates 222 extending in the vertical direction, and the refrigerant tube 231 of the third heat-exchanger 230 may also be supported by a pair of holder plates 232 extending in the vertical direction.
In this case, the main tube 2211 of the second heat-exchanger 220 may extend linearly between the pair of holder plates 222, and the main tube 2311 of the third heat-exchanger 230 may extend linearly between the pair of holder plates 232.
As described above, the first airflow F1 of the air generated by the first blower fan 621 flows through an area between the pair of holder plates 222 of the second heat-exchanger 220 and exchanges heat with the refrigerant in the main tube 2211.
Similarly, the second airflow F2 of the air generated by the second blower fan 622 may flow through an area between the pair of holder plates 232 of the third heat-exchanger 230 and perform heat exchange with the refrigerant in the main tube 2311.
Accordingly, substantial heat exchange occurs in a first heat exchange area defined between the pair of holder plates 222 of the second heat-exchanger 220 and a second heat exchange area defined between the pair of holder plates 232 of the third heat-exchanger 230.
However, in order for the second heat-exchanger 220 and the third heat-exchanger 230 to secure sufficient heat exchange performance, the dishwasher should be manufactured such that the size of each of the first heat exchange area and the second heat exchange area be equal to or greater than a predetermined value.
That is, the horizontal length of each of the refrigerant tubes 221 of the second heat-exchanger 220 and the refrigerant tubes 231 of the third heat-exchanger 230 need to be increased, or the vertical length of each of an arrangement of the refrigerant tubes 221 of the second heat-exchanger 220 and an arrangement of the refrigerant tubes 231 of the third heat-exchanger 230 should be large.
However, since a vertical length of the accommodation space which is formed between the base 8 and the tub 2 and in which the second heat-exchanger 220 and the third heat-exchanger 230 are disposed is limited, the left-right directional length or the front-rear directional length of each of the second heat-exchanger 220 and the third heat-exchanger 230 is inevitably increased.
In addition, since the sump 4 occupying a relatively large volume is disposed between the base 8 and the tub 2, the second heat-exchanger 220 and the third heat-exchanger 230 should be disposed at positions at which the sump 4 is not disposed.
For this reason, as illustrated, the second heat-exchanger 220 and the third heat-exchanger 230 may be positioned as close as possible to the rear surface 82 of the base 8 so that the left-right direction thereof is the longitudinal direction.
More specifically, the arrangement of each of the second heat-exchanger 220 and the third heat-exchanger 230 may be in parallel to the rear surface 82 of the base 8.
In the illustrated embodiment, each of the second heat-exchanger 220 and the third heat-exchanger 230 is disposed close to the rear surface 82 and a left surface 83 of the base 8. Alternatively, each of the second heat-exchanger 220 and the third heat-exchanger 230 nay be disposed close to a right surface 84of the base 8. Hereinafter, the present disclosure will be described based on an embodiment in which each of the second heat-exchanger 220 and the third heat-exchanger 230 is close to the rear surface 82 and the left side surface 83 of the base 8. However, the present disclosure is not limited thereto.
In addition, the second heat-exchanger 220 and the third heat-exchanger 230 need to be disposed as close as possible to each other due to the limitation of the accommodation space of the base 8.
However, when the second heat-exchanger 220 and the third heat-exchanger 230 are arranged in a line in a length direction, the total length of a combination of the second heat-exchanger 220 and the third heat-exchanger 230 may be excessively increased.
Accordingly, as illustrated, the arrangement of the tubes of the second heat-exchanger 220 and the arrangement of the tubes of the third heat-exchanger 230 may be parallel with each other, and the front-rear positions thereof do not coincide with each other, and the arrangement of the tubes of the second heat-exchanger 220 and the arrangement of the tubes of the third heat-exchanger 230 nay partially overlap each other in the front-rear direction.
That is, the second heat-exchanger 220 may be disposed between the second blower fan 622 and the third heat-exchanger 230 in the front-rear direction.
However, as described above, each of the second heat-exchanger 220 and the third heat-exchanger 230 are configured to exchange heat with the air of the base 8 while being exposed to the accommodation space of the base 8.
Accordingly, when the second heat-exchanger 220 and the third heat-exchanger 230 are arranged as close as possible to each other, there is a high possibility that a portion of the first airflow F1 having flowed through the second heat-exchanger 220 flows into the second blower fan 622 or a portion of the second airflow F2 having flowed through the third heat-exchanger 230 flows into the first blower fan 621.
In particular, when the drying mode is performed, the third heat-exchanger 230 acts as a condenser to heat the second airflow F2 such that the heated second airflow is fed to the tub 2, and the second heat-exchanger 220 acts as an evaporator to cool the first airflow F1 such that the cooled airflow is discharged toward the rear surface 82 of the base 8.
Accordingly, if the third heat-exchanger 230 is disposed in rear of the second heat-exchanger 220, there is a possibility that a portion of the second airflow F2 cooled by the second heat-exchanger 220 may flow into the third heat-exchanger 230.
Accordingly, there is a possibility that the heating efficiency of the third heat-exchanger 230 may deteriorate during the drying mode, and there is a possibility that the temperature of the second airflow F2 may not sufficiently increase.
In order to prevent such a phenomenon, the second heat-exchanger 220 may be disposed in rear of the third heat-exchanger 230.
That is, as illustrated, when the first blower fan 621 and the second blower fan 622 have substantially the same front-rear position, a distance between the first blower fan 621 and the second heat-exchanger 220 may be smaller than a distance between the second blower fan 622 and the third heat-exchanger 230.
In this case, a distance between the second blower fan 622 and the third heat-exchanger 230 may be greater than a width in a front-rear direction of the second heat-exchanger 220 so that the second heat-exchanger 220 and the third heat-exchanger 230 may partially overlap each other in the front-rear direction.
In one example, as shown in FIG. 9, when the second heat-exchanger 220 and the third heat-exchanger 230 partially overlap each other in the front-rear direction, the amount of overlapping or the overlapping range therebetween may be limited so as to minimize the adverse effect of the heat exchange performance thereof onto each other.
As described above, substantial heat exchange between the first airflow F1 and the refrigerant is performed while the first airflow F1 flows through the first heat exchange area defined between the pair of holder plates 222 of the second heat-exchanger 220, and substantial heat exchange the second airflow F2 and the refrigerant occurs while the second airflow F2 flows through the second heat exchange area defined between the pair of holder plates 232 of the third heat-exchanger 230.
Accordingly, the second heat-exchanger 220 and the third heat-exchanger 230 may be arranged such that the first heat exchange area of the second heat-exchanger 220 and the second heat exchange area of the third heat-exchanger 230 do not overlap each other in the front-rear direction so that the adverse influence of the heat exchange performance thereof onto each other may be minimized.
In this case, the overlapping range may be each of the connection tube 2212 of the second heat-exchanger 220 and the connection tube 2312 of the third heat-exchanger 230
That is, the connection tube 2212 of the second heat-exchanger 220 may be disposed to overlap the second heat exchange area of the third heat-exchanger 230 in the front-rear direction. The connection tube 2312 of the third heat-exchanger 230 may be disposed to overlap the first heat exchange area of the second heat-exchanger 220 in the front-rear direction.
In other words, the second heat-exchanger 220 may be disposed between the connection tube 2312 of the third heat-exchanger 230 and the first blower fan 621, such that the connection tube 2312 of the third heat-exchanger 230 may be exposed to the first airflow F1 before flowing through the second heat-exchanger 220.
In addition, the connection tube 2212 of the second heat-exchanger 220 may be disposed between the third heat-exchanger 230 and the second blower fan 622, such that the connection tube 2212 of the second heat-exchanger 220 may be exposed to the second airflow F2 before flowing through the third heat-exchanger 230.

[Arrangement Structure of Second and Third Heat-exchangers According to Second Embodiment]

Hereinafter, the arrangement structure of the second heat-exchanger 220 and the third heat-exchanger 230 provided in the heat pump apparatus 10 according to the second embodiment of the present disclosure will be described with reference to FIG. 10.
As illustrated in FIG. 10, unlike the first embodiment, the second heat-exchanger 220 and the third heat-exchanger 230 may be arranged such that the first heat exchange area of the second heat-exchanger 220 and the second heat exchange area of the third heat-exchanger 230 partially overlap each other in the front-rear direction.
Therefore, the total length of the combination of the second heat-exchanger 220 and the third heat-exchanger 230 according to the second embodiment may be additionally reduced compared to the first embodiment, and accordingly, space utilization may be improved.
However, there is a possibility that the heat exchange performance or efficiency of the third heat-exchanger 230 may be deteriorated due to the partial overlap between the first heat exchange area of the second heat-exchanger 220 and the second heat exchange area of the third heat-exchanger 230.
That is, since the first heat exchange area of the second heat-exchanger 220 is partially exposed to the second airflow and the second heat exchange area of the third heat-exchanger is partially exposed to the first airflow, a portion of the second airflow F2 heated while flowing through the second heat exchange area of the third heat-exchanger 230 may be introduced into the first heat exchange area of the second heat-exchanger 220 under the operation of the first blower fan 621 and then may be mixed with the first airflow F1.
In addition, a phenomenon in which a portion of the first airflow F1 that has become cold while flowing through the first heat exchange area of the second heat-exchanger 220 is suctioned by the second blower fan 622 and then is mixed with the second airflow F2 may occur.
The heat pump apparatus 10 according to the second embodiment of the present disclosure may further a means for preventing the mixing between the first airflow F1 and the second airflow F2. This mean may be embodied as a main guide duct 660 disposed between the third heat-exchanger 230 and the second blower fan 622 and constructed to guide the second airflow having flowed through the third heat-exchanger 230 to the second blower fan 622.
As illustrated, an inlet end 661 of the main guide duct 660 may be connected to the pair of holder plates 232 of the third heat-exchanger 230, while an outlet end 662 of the main guide duct 660 may be connected to the inlet of the second fan housing 622a of the second blower fan 622.
As described above, the second airflow F2 having flowed through the second heat exchange area of the third heat-exchanger 230 may be introduced into the inlet of the second fan housing 622a of the second blower fan 622 by the main guide duct 660 without leakage and without mixing with the first airflow F1.
The second airflow F2 introduced to the inlet of the second fan housing 622a may be introduced into the first inlet 641 of the supply duct 640 through the second blower fan 622 and the outlet of the second fan housing 622a.
As described above, during the drying mode, the first airflow F1 introduced into the first inlet 641 may flow through the second inlet 642 opened by the damper 632 and be supplied to the supply duct 640. During the washing mode, the first airflow F1 introduced into the first inlet 641 may flow through the first outlet 643 opened by the damper 632 and be discharged to the base 8. FIG. 9 illustrates a state in which the second airflow F2 is supplied to the tub 2 according to the progress state of the drying mode.
In one example, the inlet end 661 of the main guide duct 660 may have a shape and size determined such that the inlet end 661 is capable of entirely covering the second heat exchange area of the third heat-exchanger 230. To this end, the inlet end 661 of the main guide duct 660 may be formed to have a rectangular cross section.
In addition, the outlet end 662 of the main guide duct 660 may have a shape and size determined such that the outlet end 662 is capable of entirely covering the inlet of the second fan housing 622a. To this end, the outlet end 662 of the main guide duct 660 may be formed to have a circular cross-section.
In one example, as illustrated, the connection tube 2212 of the second heat-exchanger 220 is brought into a state of entirely blocking an area between the second heat exchange area of the third heat-exchanger 230 and the second blower fan. The main tube 2211 of the second heat-exchanger 220 is brought into a state of partially blocking an area between the second heat exchange area of the third heat-exchanger 230 and the second blower fan.
That is, since the second heat-exchanger 220 protrudes into the area between the third heat-exchanger 230 and the second blower fan 622, interference between the second heat-exchanger 220 and the main guide duct 660 may occur.
In order to prevent such interference, as illustrated, the main guide duct 660 may be concavely formed inwardly thereof in the area between the inlet end 661 and the outlet end 662, and may include a concave portion 663 for avoiding interfering with the connection tube 2212 of the second heat-exchanger 220.
The concave portion 663 may be formed by depressing a portion of an outer surface of the main guide duct 660 concavely and inwardly thereof.
The concave portion 663 serves to avoid interfering with the connection tube 2212 of the second heat-exchanger 220.
Accordingly, an outer contour of the concave portion 663 may have a shape and a size corresponding to a size and a shape of the outer contour of the connection tube 2212 of the second heat-exchanger 220.
In addition, along the concave portion 663 of the main guide duct 660, the second airflow F2 having flowed through the second heat exchange area of the third heat-exchanger 230 may bypass and avoid the second heat-exchanger 220 so as to be guided to the second blower fan 622.
In one example, in a similar manner to the main guide duct 660, a sub-guide duct 670 may be further provided between the second heat-exchanger 220 and the first blower fan 621 to guide the second airflow F2 having flowed through the second heat-exchanger 220 to the first blower fan 621.
In a similar manner to the main guide duct 660, an inlet end of the sub-guide duct 670 may be connected to the pair of holder plates 222 of the second heat-exchanger 220, and an outlet end of the sub-guide duct 670 may be connected to the inlet of the first fan housing 621a of the first blower fan 621.
However, as illustrated, since the distance between the first blower fan 621 and the second heat-exchanger 220 is smaller than the distance between the second blower fan 622 and the third heat-exchanger 230, a length in the front-rear direction of the sub guide duct 670 may be smaller than a length in the front-rear direction of the main guide duct 660.
Although the embodiments of the present disclosure have been described in more detail with reference to the accompanying drawings, the present disclosure is not necessarily limited to these embodiments, and may be modified in a various manner within the scope of the technical spirit of the present disclosure. Accordingly, the embodiments as disclosed in the present disclosure are intended to describe rather than limit the technical idea of the present disclosure, and the scope of the technical idea of the present disclosure is not limited by these embodiments. Therefore, it should be understood that the embodiments described above are not restrictive but illustrative in all respects. In addition, even though an effect of a configuration of the present disclosure is not explicitly described in describing the embodiment of the present disclosure above, it is obvious that the predictable effect from the configuration should be recognized.

Claims

A dishwasher comprising:
a tub having a washing space defined therein, wherein dishes are received in the washing space;

a base disposed under the tub; and

a heat pump apparatus for heating washing water to be introduced into the tub,

wherein the heat pump apparatus includes:
a compressor for compressing refrigerant;

a first heat-exchanger configured to receive the refrigerant having flowed through the compressor and to heat the washing water to be supplied to the tub in a washing mode of the dishwasher;

a second heat-exchanger configured to evaporate the refrigerant having flowed through the first heat-exchanger via heat-exchange between the refrigerant and air in the washing mode of the dishwasher;

a third heat-exchanger configured to receive the refrigerant having flowed through the compressor and to heat the air to be supplied to the tub in a drying mode of the dishwasher;

a first blower fan configured to generate a first airflow of air having flowed through the second heat-exchanger; and

a second blower fan configured to generate a second airflow of air having flowed through the third heat-exchanger,

wherein the third heat-exchanger is disposed in the base in a state of being exposed to the first airflow.
The dishwasher of claim 1, wherein the third heat-exchanger is exposed to the first airflow before having flowed through the second heat-exchanger.
The dishwasher of claim 1, wherein the third heat-exchanger includes:
a plurality of main tubes extending so as to intersect the second airflow; and

a plurality of connection tubes sequentially communicating the plurality of main tubes with each other,

wherein the connection tubes are exposed to the first airflow.
The dishwasher of claim 1, wherein the second heat-exchanger is disposed between the second blower fan and the third heat-exchanger.
The dishwasher of claim 1, wherein the second heat-exchanger is disposed in the base in a state of being exposed to the second airflow.
The dishwasher of claim 5, wherein the second heat-exchanger is exposed to the second airflow after having flowed through the third heat-exchanger.
The dishwasher of claim 5, wherein the second heat-exchanger includes:
a plurality of main tubes extending so as to intersect the first airflow; and

a plurality of connection tubes sequentially communicating the plurality of main tubes to each other,

wherein the connection tubes are exposed to the second airflow.
The dishwasher of claim 5, wherein the connection tubes of the second heat-exchanger are disposed between the second blower fan and the third heat-exchanger.
The dishwasher of claim 4, wherein the heat pump apparatus further includes a main guide duct disposed between the third heat-exchanger and the second blower fan and constructed to guide the second airflow having flowed through the third heat-exchanger to the second blower fan,
wherein the main guide duct is constructed to prevent the second heat-exchanger from being exposed to the second airflow.
The dishwasher of claim 9, wherein the third heat-exchanger includes:
a plurality of main tubes extending so as to intersect the second airflow;

a plurality of connection tubes sequentially communicating the plurality of main tubes to each other; and

a pair of holder plates for supporting the plurality of main tubes, wherein a passage area of the second airflow is defined between the pair of holder plates,

wherein the main guide duct is constructed to allow the air having flowed through the passage area between the pair of holder plates to bypass the second heat-exchanger and to guide the air to the second blower fan.
The dishwasher of claim 10, wherein an inlet end of the main guide duct is connected to the pair of holder plates,
wherein an outlet end of the main guide duct is connected to an inlet of the second blower fan,

wherein the main guide duct has a concave portion concave inwardly thereof in an area between the inlet end and the outlet end, wherein the concave portion bypasses the second heat-exchanger.
The dishwasher of claim 9, wherein the heat pump apparatus further includes a sub-guide duct disposed between the second heat-exchanger and the first blower fan and constructed to guide the first airflow having flowed through the second heat-exchanger to the first blower fan.
The dishwasher of claim 12, wherein the second heat-exchanger includes:
a plurality of main tubes extending so as to intersect the first airflow;

a plurality of connection tubes sequentially communicating the plurality of main tubes to each other; and

a pair of holder plates for supporting the plurality of main tubes, wherein a passage area of the second airflow is defined between the pair of holder plates,

wherein an inlet end of the sub-guide duct is connected to the pair of holder plates,

wherein an outlet end of the sub-guide duct is connected to an inlet of the first blower fan.