EP2725133B1 - Clothes dryer - Google Patents

Clothes dryer Download PDF

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Publication number
EP2725133B1
EP2725133B1 EP13189245.7A EP13189245A EP2725133B1 EP 2725133 B1 EP2725133 B1 EP 2725133B1 EP 13189245 A EP13189245 A EP 13189245A EP 2725133 B1 EP2725133 B1 EP 2725133B1
Authority
EP
European Patent Office
Prior art keywords
condenser
refrigerant
condenser part
air
condensation water
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP13189245.7A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2725133A3 (en
EP2725133A2 (en
Inventor
Seonghwan Kim
Seungphyo Ahn
Hyunwoo Noh
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
LG Electronics Inc
Original Assignee
LG Electronics Inc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by LG Electronics Inc filed Critical LG Electronics Inc
Publication of EP2725133A2 publication Critical patent/EP2725133A2/en
Publication of EP2725133A3 publication Critical patent/EP2725133A3/en
Application granted granted Critical
Publication of EP2725133B1 publication Critical patent/EP2725133B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • D—TEXTILES; PAPER
    • D06—TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
    • D06F—LAUNDERING, DRYING, IRONING, PRESSING OR FOLDING TEXTILE ARTICLES
    • D06F58/00—Domestic laundry dryers
    • D06F58/20—General details of domestic laundry dryers 
    • D06F58/206—Heat pump arrangements
    • D—TEXTILES; PAPER
    • D06—TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
    • D06F—LAUNDERING, DRYING, IRONING, PRESSING OR FOLDING TEXTILE ARTICLES
    • D06F58/00—Domestic laundry dryers
    • D06F58/02—Domestic laundry dryers having dryer drums rotating about a horizontal axis
    • D06F58/04—Details 
    • D—TEXTILES; PAPER
    • D06—TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
    • D06F—LAUNDERING, DRYING, IRONING, PRESSING OR FOLDING TEXTILE ARTICLES
    • D06F58/00—Domestic laundry dryers
    • D06F58/20—General details of domestic laundry dryers 
    • D06F58/24—Condensing arrangements

Definitions

  • the present disclosure relates to a heat pump type laundry machine, such as a combined washing and drying machine or a clothes dryer, and more particularly, to a heat pump type laundry machine for enhancing dehumidifying power in an evaporator using condensation water.
  • a laundry machine includes a clothes treating apparatus, such as a washing machine, a washer, a combined washing and drying machine or a dryer.
  • the laundry machine having a drying function such as a combined washer or a dryer is a device wherein the laundry is in the drum in a state that the washing is completed and a dehydration process is performed, supplying hot air into the drum to evaporate moisture of the laundry, thereby drying the laundry.
  • the foregoing dryer may include a drum rotatably provided within a cabinet to put the laundry thereinto, a drive motor configured to drive the drum, a blower fan configured to blow air into the drum, and a heating means configured to heat air brought into the drum.
  • the heating means may use high-temperature electric resistance heat generated using an electric resistance, or combustion heat generated by combusting gas.
  • air discharged from the drum contains the moisture of the laundry, and thus becomes high temperature and humid air.
  • the dryer may be classified according to a method for processing the high temperature and humid air, and thus divided into a condensation (circulation) type dryer for condensing moisture contained in the high temperature and humid air by cooling the air below the dew point temperature through a condenser while being circulated without discharging the high temperature and humid air out of the dryer, and an exhaustion type dryer for directly discharging the high temperature and humid air having passed through the drum to the outside.
  • a condensation (circulation) type dryer for condensing moisture contained in the high temperature and humid air by cooling the air below the dew point temperature through a condenser while being circulated without discharging the high temperature and humid air out of the dryer
  • an exhaustion type dryer for directly discharging the high temperature and humid air having passed through the drum to the outside.
  • the process of cooling the air below the dew point temperature should be carried out to heat the air through the heating means prior to being supplied to the drum again.
  • the loss of heat energy contained in the air is generated while being cooled down during the condensation process, and an additional heater or the like is required to heat the air to a temperature required for drying.
  • clothes treating apparatuses for collecting energy required to generate hot air and energy being discharged to the outside without being used have been introduced to increase energy efficiency
  • a clothes treating apparatus having a heat pump system has been introduced as an example of the clothes treating apparatus.
  • the heat pump system may include two heat exchangers, a compressor and an expansion apparatus, and energy contained in the discharged hot air is reused in heating up air being supplied to the drum, thereby increasing energy efficiency.
  • an evaporator is provided at the exhaust side, and a condenser at an inlet side of the drum, and thus thermal energy is transferred to refrigerant through the evaporator and then thermal energy contained in the refrigerant is transferred to air brought into the drum, thereby generating hot air using waste energy.
  • the size of the condenser may be restricted due to a lack of space within which the condenser is installed, thereby causing difficulty in achieving its condensation effect.
  • heat exchange efficiency may be reduced in the heat exchanger and the cooling of refrigerant may not be properly carried out, thereby reducing dehumidifying capability.
  • GB 1 363 292 A discloses a drying apparatus with a refrigeration plant, wherein a condenser of the refrigeration plant is divided into two parts, with one part serving as air heating means, and with the coils of the other part being housed within the lower part of the drying apparatus containing water.
  • CN 201 358 383 Y discloses a clothes drying device characterized in that the clothes drying device comprises a cabinet body main frame, a dehumidifying mechanism and an object placing cavity, the dehumidifying mechanism comprises a heat exchanger, an evaporator, a compressor, a condenser, and a second condenser submerged in a water tank in which condensation water is provided.
  • DE 44 09 607 A1 discloses a clothes dryer wherein a part of a condenser is disposed in a condensation water collection apparatus.
  • CN 2 595 848 Y discloses a device for drying clothes comprising a filter screen, a heat regenerator, a condenser, and a heat pump system which is composed of a compressor, a saturator, a condenser, a subcooler, a capillary pipe and an evaporator.
  • the condenser, the evaporator, the subcooler and the heat regenerator are tube fin type heat exchangers.
  • the heat regenerator is divided into an evaporating section and a condensing section, and the evaporator is arranged between the evaporating section and the section of the heat regenerator.
  • JP 2011 092510 A discloses a clothes dryer comprising a heat pump with a condenser, wherein heat conductive pipes for passing a refrigerant are formed in a plurality of lines from an entrance to an exit and many heat conductive fins are arranged in a direction crossing the aligning direction of the lines of the pipes and formed integrally with the pipes.
  • Thermal resistance parts divide the heat conductive fins of the condenser into at least a first line on the side of the entrance of the pipes, a second line on the side of the exit, and the middle lines.
  • the present disclosure is to solve the foregoing problems in the related art, and an object of the present disclosure is to provide a clothes dryer employing a circulation type heat pump in which a second condenser is added to a first condenser to maximize a condensation effect, thereby enhancing heat exchange efficiency.
  • Another object of the present disclosure is to provide a clothes dryer employing a heat pump structure in which refrigerant is extra-cooled, e.g. supercooled, for the cooling of the second condenser during the refrigerant cycle using condensation water generated from the heat exchanger unit, thereby enhancing dehumidifying capability.
  • Still another object of the present disclosure is to provide a clothes dryer employing a heat pump structure in which the second condenser itself has a separate independent condenser structure being submerged under condensation water, thereby removing a cooling fan that has been required for the use of a extra-cooling period.
  • a clothes dryer of the present disclosure includes a cabinet; a drum rotatably provided within the cabinet; a drying duct provided in the cabinet to circulate air discharged from the drum by resupplying it thereto; an evaporator and a condenser sequentially provided on a flow path formed by the drying duct; and a compressor and an expansion apparatus configured to form a refrigerant cycle along with the evaporator and the condenser, wherein a part of the condenser is arranged below a condensation water line of the drying duct.
  • the condenser includes a first condenser part or first condenser configured to liquefy a high-temperature and high-pressure refrigerant circulated from the compressor.
  • a second condenser part or second condenser is further provided and configured to condense the refrigerant condensed from the first condenser part again to extra-cool refrigerant during the refrigerant cycle, thereby enhancing dehumidifying capability in the evaporator.
  • a lower portion of the drying duct is configured to accumulate condensation water from the evaporator up to a condensation water line for cooling the second condenser.
  • the second condenser is formed at the lower portion of the drying duct below the condensation water line. Accordingly, the second condenser is formed below a condensation water line at a lower portion of the drying duct and/or at a lower portion of the first condenser to cool the second condenser using condensation water generated by the evaporator.
  • the second condenser may be formed as a refrigerant line extended from the first condenser and integrally formed therewith. For instance, the refrigerant pipe of the second condenser may be formed to be extended from the refrigerant pipe of the first condenser.
  • the condensation water line refers to a level in the drying duct, to which condensation water normally fills up.
  • the refrigerant pipe of the first condenser may be vertically arranged, e.g. in a meandering pattern or in a zigzag pattern.
  • the lowest end portions or lower bends of the refrigerant pipe of the first condenser are disposed on the condensation water line.
  • the refrigerant pipe of the first condenser may be horizontally arranged, e.g. in a meandering pattern or in a zigzag pattern. Then, the lowest column or level of the refrigerant pipe of the first condenser are disposed on the condensation water line
  • the refrigerant pipe of the second condenser may be horizontally arranged, e.g. in a meandering pattern or in a zigzag pattern, below the condensation water line.
  • the refrigerant pipe of the second condenser is disposed below the condensation water line, e.g. extended from the lowest end portion or lowest column of the refrigerant pipe of the first condenser to be arranged below the condensation water line.
  • the second condenser includes an independent refrigerant line separated from the first condenser.
  • This independent refrigerant line of the second condenser is disposed below a condensation water line at a lower portion of the drying duct to cool the second condenser using condensation water condensed by the evaporator.
  • At least one heat dissipation fin of the first condenser is configured as an independent heat dissipation fin separated from the heat dissipation fin(s) of the second condenser.
  • the heat dissipation fins of the first condenser and the heat dissipation fin of the second condenser are formed separately from each other, respectively.
  • the refrigerant pipe of the first condenser may be vertically arranged in a zigzag pattern, and the lowest end portion of the refrigerant pipe of the first condenser may be disposed on the condensation water line, and the refrigerant pipe of the second condenser may be horizontally arranged in a zigzag pattern below the condensation water line.
  • the first condenser and the second condenser may be connected by a refrigerant circulation line as a whole.
  • a heater for reheating air that has been heated up while passing through the evaporator may be additionally provided therein.
  • the heater may be included in an intake duct for providing heated air to the drum.
  • a second condenser may be added to a first condenser in a clothes dryer employing a circulation type heat pump to maximize a condensation effect, thereby enhancing heat exchange efficiency.
  • refrigerant may be extra-cooled for the cooling of the second condenser during the refrigerant cycle using condensation water generated from the heat exchanger unit, thereby enhancing dehumidifying capability.
  • the second condenser itself may have a separate independent condenser structure configured to be submerged under condensation water.
  • the dryer is only one example of a laundry machine according to the present invention. The same can be applied to a combined washing and drying machine and the like.
  • FIGS. 1 and 2 are views illustrating the internal structure of a heat pump type dryer
  • FIG. 3 is a block diagram illustrating the drying method of the heat pump.
  • FIG. 4 is a view illustrating the circulation path of a refrigerant using a second condenser according to the present disclosure
  • FIG. 5 is a view illustrating dryer air passing through the evaporator and condenser according to the related art.
  • FIGS. 6 and 7 are views illustrating a second condenser according to other embodiments of the present disclosure.
  • the present disclosure may include a cabinet 100 forming the outside of the clothes dryer, and a drum 110 rotatably provided within the cabinet.
  • the drum is rotatably supported by a supporter (not shown) at the front and rear sides thereof and may be driven by a motor 10.
  • An intake duct 170 provided in the cabinet to inhale outside air and supply the air to an inner portion of the drum is provided in the vertical direction of the drum at the rear side of the drum.
  • An intake flow path through which the air inhaled into the drum flows is formed by the intake duct.
  • the air inhaled through the intake duct may be brought in from the outside of the cabinet separately from the drying duct 190.
  • a heater 180 for heating the inhaled air to become high temperature air required for drying the laundry may be provided within the intake duct 170.
  • the heater 180 receives electrical energy to sufficiently and quickly heat air to be supplied to the drum, and further supplies heating such that the refrigerant cycle is stably managed in a normal state.
  • heating required for drying can be sufficiently supplied in a short period of time, thereby having an effect of reducing dry time.
  • additional heating can be supplied in a short period of time since the heating cannot be sufficiently supplied in a short period of time using only air on the circulation flow path with the drying duct.
  • the air brought into the drum may be supplied through a circulation flow path formed in the drying duct 190 separately from the air through the intake flow path.
  • the drying duct 190 is provided in the cabinet to circulate air discharged from the drum by resupplying it thereto.
  • the air brought into the drum dries the laundry and then is brought into a front surface duct (not shown) located at a lower front side of the drum and supplied to the drum again through the drying duct by way of a lint filter (not shown) or discharged to the outside of the cabinet through an exhaust duct which will be described later.
  • a blower fan 120 for inhaling air within the drum to forcibly blow it to the outside of the dryer may be provided on the circulation flow path of the drying duct.
  • an evaporator 130 and a condenser 140 are sequentially provided on a flow path formed by the drying duct.
  • the air brought into the drum is heated by the heater 180 on the intake flow path or the condenser 140 on the circulation flow to become high-temperature dry air at about 150-250 °C when being brought into the drum.
  • the high-temperature air is brought into contact with an object to be dried to evaporate the moisture of the object to be dried.
  • the evaporated moisture is to be contained in middle-temperature air and exhausted out of the drum.
  • the moisture should be removed. Since the moisture content in the air is affected by the temperature, the moisture can be removed when cooling the air. Accordingly, the air on the circulation flow path is cooled by heat exchange with the evaporator 130.
  • the condenser 140 In order to supply the air cooled by the evaporator 130 again to the drum, it should be heated by high temperature air, and the heating of the air is carried out by the condenser 140.
  • a refrigerant cycle performs heat exchange with the environment using the phase change of refrigerant flowing through the inside thereof. Briefly described, refrigerant is transformed into a low-temperature and low-pressure gas by absorbing heat from the environment in the evaporator, compressed into a high-temperature and high-pressure gas in the compressor, transformed into a high-temperature and high-pressure liquid by dissipating heat to the environment in the condenser, transformed into a low-temperature and low-pressure liquid by dropping its pressure in the expansion apparatus, and brought into the evaporator again. Due to the circulation of refrigerant, heat is absorbed from the environment in the evaporator and heat is supplied to the environment in the condenser.
  • the refrigerant cycle may be also referred to as a heat pump.
  • the refrigerant cycle may include the compressor 150 and expansion apparatus 160 along with the evaporator 130 and condenser 140.
  • FIGS. 2 and 3 The flow path of air in heat exchange with the refrigerant cycle is illustrated in FIGS. 2 and 3 .
  • an arrow passing through the evaporator and condenser and a line connecting between the evaporator and condenser does not indicate the flow path of the refrigerant but indicate the flow path of the air in FIGS. 2 and 3 , and the air is sequentially brought into contact with the evaporator and the like to perform heat exchange.
  • the evaporator 130 and condenser 140 are sequentially disposed, respectively, on the circulation flow path (a large circulation line formed along a bold arrow in FIG. 3 ) formed by the drying duct 190.
  • the air (Ad) on the circulation flow path performs heat exchange with the heat pump during the refrigerant cycle, specifically the air (Ad) on the circulation flow path dissipates heat in heat exchange with the evaporator, and absorbs heat in heat exchange with the condenser. As a result, the air on the circulation flow path absorbs heat dissipated by itself again.
  • the evaporator and condenser are mainly in charge of heat exchange during the refrigerant cycle, and the air from which heat is taken in the evaporator liquefies moisture contained therein to exhaust it as condensation water, and dry air is heated by the compressor and condenser to be changed into high temperature and dry air.
  • part of the air brought into the drum and used in the drying process is exhausted to the outside of the dryer, and part thereof is reused, and supplied to the air reused by absorbing only part of waste heat using the refrigerant cycle.
  • the embodiments of the present invention may also be employed in a circulation type dryer without exhausting air or in an exhaustion type dryer, in which all of the air is exhausted to the outside of the dryer.
  • waste heat is typically collected using the refrigerant cycle, and the present disclosure provides an optimization means not to cause a overload during the refrigerant cycle.
  • the heat exchange of refrigerant should be carried out by phase change at the optimal operating temperature and pressure, and to this end, an heat exchanger such as an evaporator and a condenser, a compressor, an expansion apparatus and the like are used. Accordingly, in order to collect more heat, the size of the heat exchanger or compressor is inevitably increased. However, in case of a typical clothes dryer, it has a spatial restriction and thus the heat exchanger, compressor or the like is limited in their size.
  • the heater 180 for heating the inhaled air to become high-temperature air required for drying the laundry is provided within the intake duct to continuously replenish the inhaled air with heating.
  • heating may be replenished through the heater 180 to sufficiently supply the heating required for drying, thereby reducing dry time.
  • the heat exchange of refrigerant should be carried out by a phase change at the optimal operating temperature and pressure, and to this end, heating should be sufficiently supplied. Otherwise, it may cause a problem such as refrigerant being supplied to the compressor in a liquid phase or the like, and thus the cycle cannot be stably operated, thereby reducing the reliability of the cycle.
  • the air brought into the drum may be additionally replenished with heating by the heater 180, and thus it is preferable that the refrigerant cycle can be stably operated in a normal state.
  • an additional blower fan 120 may be provided on the intake flow path to provide more airflow. Furthermore, the additional blower fan provides more airflow and thus the heater 180 is not overheated on the intake flow path.
  • the configuration provided with the additional blower fan 120 is illustrated in FIGS. 2 through 4 .
  • the present disclosure may be configured such that part of the air is exhausted to the outside of the cabinet at the upstream of the evaporator on the circulation flow path.
  • the present disclosure may further include an exhaust duct 15 branched from the upstream of the evaporator 130 in the drying duct 190, and the exhaust duct is configured to exhaust part of the air to the outside of the cabinet at the upstream of the evaporator on the circulation flow path.
  • the exhaust duct forms an exhaust flow path for discharging hot air coming out of the drum to exhaust part of the air to the outside of the cabinet.
  • waste heat is absorbed from part of the middle temperature and humid air coming out of the drum only within a range that can be processed by the refrigerant cycle, and the rest of the air is exhausted. Accordingly, it may be possible to reduce energy waste as well as not to cause an overload during the refrigerant cycle. Furthermore, it may be possible to reduce power consumption as well as enhance reliability for the operation of the refrigerant cycle.
  • a clothes dryer may include an evaporator 130, a condenser 140, a compressor 150 and an expansion apparatus 160 as a heat pump type dryer. It has been sufficiently described in the above, and thus the description thereof will be omitted below.
  • the condenser 140 may include a first condenser part or first condenser 140 configured to liquefy a high-temperature and high-pressure refrigerant circulated from the compressor; and a second condenser or second condensing unit 141 configured to condense the refrigerant condensed from the first condenser again to extra-cool refrigerant during the refrigerant cycle, thereby enhancing dehumidifying capability in the evaporator.
  • refrigerant passes through the compressor 150 to follow the path of the condenser 140, expansion apparatus 160 and evaporator 130, and according to the present disclosure, a separate second condensing unit 141 may be included therein when refrigerant that has passed through the compressor 150 is condensed in the condenser 140, thereby enhancing the condensation effect.
  • the level of extra-cooling may be further increased through the first condenser 140 and second condensing unit 141 in the condenser to enhance dehumidifying capability in the evaporator, thereby increasing the efficiency of the heat pump.
  • the second condensing unit 141 may further include a cooling fan 146 for enhancing the extra-cooling performance of a second condenser 143 in addition to the second condenser 143 separately provided therein.
  • the cooling fan 146 may inhale external air at ambient temperature to cool the second condenser 143.
  • refrigerant flowing into the pipe from the outlet of the condenser passes through the second condenser before passing through the expansion apparatus (or expansion valve) to enhance dehumidifying capability in the evaporator for removing moisture in the dry flow path.
  • the expansion apparatus e.g. an expansion valve
  • a separate cooling fan as well as the second condenser and connecting pipe should be additionally provided to increase the extra-cooling of refrigerant, thereby causing an increase in the raw material cost of the product.
  • the second condenser 148 is formed below a condensation water line at a lower portion of the drying duct as a refrigerant line extended from the first condenser and integrally formed therein. Furthermore, the second condenser is cooled using condensation water condensed by the evaporator.
  • FIG. 5 a conventional heat pump structure comprising an evaporator 130 and a condenser 140 in a drying duct is shown.
  • the evaporator 130 and the condenser 140 are arranged at the same height and above the condensation water line WL of the drying duct, up to which condensation water W is collected.
  • the refrigerant lines or refrigerant pipes P E and P C of the evaporator 130 and the condenser 140 are connected to each other via the compressor 150.
  • the refrigerant pipe of the first condenser 140 and the refrigerant pipe of the second condenser are intrusively formed in the same heat dissipation fins.
  • the refrigerant pipe P C1 of the first condenser is vertically arranged in a zigzag or meandering pattern, and the lowest end portion of the refrigerant pipe thereof is arranged on a condensation water line WL, and the refrigerant pipe P C2 of the second condenser 148 is horizontally arranged below the condensation water line.
  • Vertically or horizontally arranged respectively refers to a plurality of subsequent bends of the refrigerant pipe of the condenser being arranged in a vertical or horizontal plane with respect to the installed condenser.
  • the condenser 140 may not be required to be cooled with a separate cooling fan for the cooling of the condenser, and space utilization is enhanced, thereby promoting economical efficiency.
  • the second condenser 148 can be considered as a partial lower portion of the condenser 140 being submerged under condensation water (W), and the relevant lower portion of the condenser exhibits a structure for enhancing the extra-cooling efficiency of the condenser using the condensation water. Accordingly, a rear end portion at the outlet side of the pipe coming out of the condenser 148should be submerged under condensation water to achieve extra-cooling without reducing the performance of the condenser.
  • the second condenser 148 is disposed below a condensation water line at a lower portion of the drying duct as an independent refrigerant line separated from the first condenser 140 to cool the second condenser using condensation water generated by the evaporator.
  • the at least one heat dissipation fin of the first condenser 140 and the at least one heat dissipation fin of the second condenser 149 may be configured as independent heat dissipation fins separated from each other, respectively.
  • the refrigerant circulation line (Pc1) in the first condenser and the refrigerant circulation line (Pc2) in the second condenser may be preferably connected by a separate refrigerant circulation line that does not penetrate the heat dissipation fin.
  • refrigerant (Pc1) circulated from the compressor (not shown in the drawing) is all circulated through the condenser 140, and then circulated again through the second condenser 149 via a separate refrigerant circulation path.
  • the refrigerant circulation (Pc2) of the second condenser 149 may be submerged under the surface of condensation water (W), i.e. below the condensation water line (WL) of the drying duct.
  • an additional cooling fan according to the foregoing embodiment may be provided to one or both of the condenser parts in order to maximize cooling efficiency.
  • a cooling function can already be promoted through condensation water (W) generated by the evaporator 130 without having an additional cooling fan according to the present embodiment, thereby avoiding an additional configuration as well as maximizing space utilization.
  • the refrigerant pipe P c1 of the first condenser 140 is vertically arranged, e.g. in a zigzag pattern, and the lowest end portion of the refrigerant pipe P c1 is disposed not to be brought into contact with condensation water on the condensation water line WL, and the refrigerant pipe P c2 of the second condenser is horizontally arranged below the condensation water line, e.g. in a zigzag pattern, to be submerged under condensation water.
  • the second condenser itself has a separate independent condenser structure and the second condenser has a structure being submerged under condensation water. Accordingly, refrigerant that has passed through the condenser may be extra-cooled while being circulated through the second condenser submerged under condensation water, and as a result, a cooling fan that has been required for the use of a extra-cooling period in the foregoing embodiment is not required, and the cost is reduced and an additional space is not occupied, thereby increasing space efficiency.

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  • Engineering & Computer Science (AREA)
  • Textile Engineering (AREA)
  • Detail Structures Of Washing Machines And Dryers (AREA)
EP13189245.7A 2012-10-22 2013-10-18 Clothes dryer Not-in-force EP2725133B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
KR1020120117467A KR101989522B1 (ko) 2012-10-22 2012-10-22 의류건조기

Publications (3)

Publication Number Publication Date
EP2725133A2 EP2725133A2 (en) 2014-04-30
EP2725133A3 EP2725133A3 (en) 2016-03-30
EP2725133B1 true EP2725133B1 (en) 2017-12-06

Family

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EP13189245.7A Not-in-force EP2725133B1 (en) 2012-10-22 2013-10-18 Clothes dryer

Country Status (7)

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US (1) US20140109428A1 (zh)
EP (1) EP2725133B1 (zh)
KR (1) KR101989522B1 (zh)
CN (1) CN103774402B (zh)
AU (1) AU2013245540B2 (zh)
BR (1) BR102013026927B8 (zh)
DE (1) DE202013104695U1 (zh)

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KR102300343B1 (ko) 2014-10-28 2021-09-09 엘지전자 주식회사 의류처리장치
KR102343262B1 (ko) 2014-10-28 2021-12-23 엘지전자 주식회사 의류처리장치
KR101613966B1 (ko) 2014-12-29 2016-04-20 엘지전자 주식회사 의류처리장치
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EP2725133A3 (en) 2016-03-30
BR102013026927A2 (pt) 2015-04-28
CN103774402A (zh) 2014-05-07
BR102013026927B8 (pt) 2021-12-14
BR102013026927B1 (pt) 2021-07-20
EP2725133A2 (en) 2014-04-30
KR101989522B1 (ko) 2019-09-30
US20140109428A1 (en) 2014-04-24
AU2013245540A1 (en) 2014-05-08
DE202013104695U1 (de) 2014-01-22
AU2013245540B2 (en) 2015-12-03
KR20140050980A (ko) 2014-04-30
CN103774402B (zh) 2017-03-01

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