WO2013014137A1 - Système de pompe à chaleur pour sèche-linge - Google Patents

Système de pompe à chaleur pour sèche-linge Download PDF

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Publication number
WO2013014137A1
WO2013014137A1 PCT/EP2012/064458 EP2012064458W WO2013014137A1 WO 2013014137 A1 WO2013014137 A1 WO 2013014137A1 EP 2012064458 W EP2012064458 W EP 2012064458W WO 2013014137 A1 WO2013014137 A1 WO 2013014137A1
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WO
WIPO (PCT)
Prior art keywords
heat exchanger
refrigerant
pump system
heat pump
compressor
Prior art date
Application number
PCT/EP2012/064458
Other languages
English (en)
Inventor
Francesco Cavarretta
Original Assignee
Electrolux Home Products Corporation N.V.
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 Electrolux Home Products Corporation N.V. filed Critical Electrolux Home Products Corporation N.V.
Publication of WO2013014137A1 publication Critical patent/WO2013014137A1/fr

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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

Definitions

  • the present invention relates to a heat pump system for a laundry dryer according to the preamble of claim 1. Further, the present invention relates to a corresponding laundry dryer.
  • the heat pump technology is at present the most efficient way to dry clothes in terms of energy consumption.
  • an air stream flows in a close air stream circuit.
  • the air stream is moved by a fan, passes through a laundry chamber, which is preferably formed as a rotatable laundry drum, removes water from wet clothes, is then cooled down and dehumidified in a heat pump evaporator, heated up in a heat pump condenser and at last re-inserted into the laun- dry drum again.
  • the refrigerant instead is compressed by a compressor, condensed in the condenser, laminated in an expansion device and then vaporized in the evaporator.
  • There ⁇ fore the temperatures of the air stream and the refrigerant are strictly connected each other.
  • the cycle of the heat pump laundry dryer is characterized by two phases: a transitory phase or warm-up phase and a steady state phase.
  • a transitory phase the tem ⁇ peratures of the air stream and the refrigerant, which are usually at an ambient temperature when the system begins to operate, increase up to a desired level.
  • the steady state phase the temperatures of the air stream and the re ⁇ frigerant are kept almost constant.
  • a cooling fan cools down the compressor or an auxiliary condenser, which removes excess heat from the heat pump system, in or- der to keep the temperatures of the air stream and the re ⁇ frigerant constant until the laundry is dried.
  • the traditional condenser in which the refrigerant coming from the outlet of the compressor condensates while the air stream is heated up, is substituted by a gas cooler, in which the carbon dioxide is cooled down while the air stream is heated up.
  • a gas cooler At the gas cooler outlet there is no refrigerant in liquid state, but a gas with a lower tem ⁇ perature and an increased density.
  • there could be a very short transient phase i.e. a few seconds or a few minutes, after the switching on the compressor in which the refrigerant is in the liquid phase in the high pressure portion of the heat pump circuit .
  • the heat pump system can be forced working in a totally-supercritical cycle.
  • the refrigerant is kept always in a gaseous phase, also in a low pressure portion of the heat pump circuit.
  • the evaporator is called gas heater, since the carbon dioxide is heated up without change of phase.
  • the terms evaporator and gas heater are hereinafter used as synonymous.
  • the heat pump system passes through a trans-critical cycle.
  • FIG 3 shows a temperature-entropy diagram of carbon dioxide in the trans-critical cycle.
  • FIG 4 shows the temperature-entropy diagram of carbon dioxide in the totally-supercritical cycle.
  • the temperature-entropy dia ⁇ grams comprise a high pressure isobaric line 40, a low pressure isobaric line 42, a saturation curve 44 of carbon dioxide, a compression phase 46 and a lamination phase 48. Further, a state a of the refrigerant at the gas heater outlet, a state b of the refrigerant at the gas cooler inlet, a state c of the refrigerant at the gas cooler out- let and a state d of the refrigerant at the gas heater inlet are indicated in the temperature-entropy diagrams.
  • the temperature and pres ⁇ sure of carbon dioxide increase.
  • the carbon dioxide follows the high pressure isobaric line 40.
  • the lamination phase 48 the temperature and pres- sure of carbon dioxide decrease.
  • the carbon dioxide follows the low pressure isobaric line 42.
  • the main one is connected to the fact that the temperature of the refrigerant at the inlet of the gas heater is greater than the temperature of the refrigerant at the inlet of the gas heater during the trans-critical cycle. This reduces the capacity of the refrigerant for de- humidifying the air stream.
  • FIG 5 shows a re ⁇ frigerant circuit according to the prior art.
  • the refriger ⁇ ant circuit includes a compressor 14 form as double stage compressor. Further, the refrigerant circuit includes a gas cooler 16, lamination means 18 and an evaporator 22.
  • the double stage compressor 14 is characterized by having two inlets and two outlets, namely a low pressure suction, an intermediate pressure discharge, an intermediate pressure suction and a high pressure discharge. For usual heat pump applications, the intermediate pressure discharge and the intermediate pressure suction are welded together, so that the compressor behaves as one single stage compressor.
  • the heat pump system of the laundry dryer using carbon dioxide as refrigerant can work in a trans-critical or total- supercritical cycle. Both cycle processes present some ad ⁇ vantages and disadvantages due to the heat pump perform- ances and the interaction between the refrigerant and the air stream.
  • the object of the present invention is achieved by the heat pump system according to claim 1.
  • the refrigerant circuit includes at least one series of further lamination means and a third heat exchanger, - the compressor includes an intermediate connection ar ⁇ ranged between the stages of the multi-stage compressor or between the serial compressors, respectively, the inlet of the further lamination means is connected to the outlet of the first heat exchanger, and
  • the present invention provides a heat pump system, wherein the structure of the refrigerant circuit results in three portions of said refrigerant circuit with different pres ⁇ sure levels.
  • the structure of the refrigerant circuit al ⁇ lows that the heat pump system can works in the totally- supercritical cycle and the trans-critical cycle at the same time, so that the advantages of said totally- supercritical cycle and trans-critical cycle are connected.
  • the refrigerant in the refrigerant circuit is carbon dioxide.
  • the refrigerant circuit and the air stream circuit may be thermally coupled by the third heat exchanger.
  • the third heat exchanger is provided for cooling down the air stream and heating up the refrigerant.
  • the second heat exchanger and the third heat exchanger form a common heat exchanger with at least two different cir ⁇ cuits for the refrigerant, wherein at least one circuit is provided for the second heat exchanger and at least one further circuit is provided for the third heat exchanger.
  • the heat pump system is provided for working in a trans-critical cycle and a totally-supercritical cycle at the same time.
  • the heat pump system may be provided for splitting the flow rate of the refrigerant at the outlet of the first heat exchanger.
  • the first heat exchanger forms a gas cooler.
  • the gas cooler is arranged within a high pressure portion of the refrigerant circuit.
  • the second heat exchanger forms an evapo ⁇ rator.
  • the evaporator is arranged within a low pressure portion of the refrigerant circuit.
  • the third heat exchanger forms a gas heater.
  • the gas heater is arranged within an intermediate pressure por ⁇ tion of the refrigerant circuit.
  • the heat pump system is provided for working in a totally-supercritical cycle through the first, second, third heat exchanger.
  • At least one of the lamination means is formed as a capillary tube.
  • At least one of the lamina ⁇ tion means is formed as an electronic expansion valves.
  • the refrigerant circuit includes at least one on-off valve arranged between the outlet of the third heat exchanger and the inlet of the compressor.
  • the refrigerant circuit includes at least one on-off valve arranged between the outlet of the third heat exchanger and the intermediate connection of the com ⁇ pressor .
  • the present invention relates to a laundry dryer with at least one heat pump system, wherein the laundry dryer comprises at least one heat pump system mentioned above .
  • the novel and inventive features believed to be the charac ⁇ teristic of the present invention are set forth in the ap ⁇ pended claims.
  • FIG 1 shows a schematic diagram of a heat pump system for a laundry dryer according to a first embodiment of the present invention
  • FIG 2 shows a schematic diagram of the heat pump system for the laundry dryer according to a second embodiment of the present invention
  • FIG 3 shows a temperature-entropy diagram of a trans- critical cycle in the heat pump system for the laundry dryer
  • FIG 4 shows a temperature-entropy diagram of a totally- supercritical cycle in the heat pump system for the laundry dryer
  • FIG 5 shows a schematic diagram of the heat pump system for the laundry dryer according to the prior art.
  • FIG 1 illustrates a schematic diagram of a heat pump system for a laundry dryer according to a first embodiment of the present invention.
  • the heat pump system includes a closed refrigerant circuit 10 and a drying air circuit 12.
  • the refrigerant circuit 10 includes a compressor 14, a gas cooler 16, first lamination means 18, second lamination means 20, an evaporator 22 and a gas heater 24.
  • the com- pressor 14 is formed as a multi-stage compressor and in a preferred embodiment the compressor is a double (two) stage compressor.
  • multi-stage compressor includes a compressor having at least two stages of compression wherein the refrigerant compressed in a compression chamber passes into a further compression chamber for further compression. The following description will refer to a double stage compressor only for convenience.
  • the double stage compressor 14 includes two single compres ⁇ sor stages connected in series.
  • the inlet of the compressor 14 corresponds with the inlet of a first compressor stage.
  • An intermediate connection of the compressor 14 corresponds with the outlet of the first compressor stage and the inlet of a second compressor stage.
  • the outlet of the compressor 14 corresponds with the outlet of the second compressor stage.
  • the compressor 14, the gas cooler 16, the first lamination means 18 and the evaporator 22 are switched in series and form a first loop of the refrigerant circuit 10.
  • the second stage of the compressor 14, the gas cooler 16, the second lamination means 20 and the gas heater 24 are switched in series and form a second loop of the refrigerant circuit 10.
  • the series of the second lamination means 20 and the gas heater 24 is arranged in parallel to the series of the first lamination means 18, the evaporator 22 and the first stage of the compressor 14.
  • the out- let of the evaporator 22 is connected to the inlet of the compressor 14, and the outlet of the gas heater 24 is connected to the intermediate connection of the compressor 14.
  • the drying air circuit 12 includes the gas heater 24, the evaporator 22, the gas cooler 16, a laundry treatment chamber 26, preferably a rotatable drum, and an air stream fan 28.
  • the gas cooler 16, the evaporator 22 and the gas heater 24 are heat exchangers and form the thermal interconnec- tions between the refrigerant circuit 10 and the drying air circuit 12.
  • the evaporator 22 and the gas heater 24 cool down and dehumidify the drying air, after said drying air has passed the laundry drum 26. Then the gas cooler 16 heats up the drying air, before the drying air is re- inserted into the laundry drum 26.
  • the drying air is driven by the air stream fan 28.
  • the drying air is preferably circulated in a closed loop in which the drying air is preferably continuously flown through the laundry treatment chamber.
  • a (preferably smaller) portion of the air stream is exhausted from the process air loop and fresh air (e.g. ambient air) is taken into the process air loop to replace the exhausted process air.
  • fresh air e.g. ambient air
  • the process air loop is temporally opened (preferably only a small fraction of the total processing time) to have an open loop dis ⁇ charge
  • the refrigerant circuit 10 is subdivided into a high pres ⁇ sure portion, a low pressure portion and an intermediate pressure portion.
  • the high pressure portion extends from the outlet of the compressor 14 via the gas cooler 16 to the inlets of the first lamination means 18 and the second lamination means 20.
  • the low pressure portion extends from the outlet of the first lamination means 18 via the evapo ⁇ rator 22 to the inlet of the compressor 14.
  • the intermedi ⁇ ate pressure portion extends from the outlet of the second lamination means 20 via the gas heater 24 to the intermedi ⁇ ate connection of the compressor 14.
  • the refrigerant is compressed and heated up by the compres ⁇ sor 14. Then, the gas cooler 16 cools down the refrigerant and heats up the air stream. At the outlet of the gas cooler 16 the flow rate of the refrigerant is divided into a first flow rate and a second flow rate.
  • the first flow rate of the refrigerant flows through the first lamination means 18.
  • the pressure of the refrigerant is decreased down to the pressure of the low pressure portion of the refrigerant circuit, i.e. the same pressure value as at the inlet of the compressor 14.
  • the refrigerant enters into the evaporator 22.
  • the evaporator 22 the refrigerant is vaporised and superheated.
  • the refrigerant is sucked by the inlet of the compressor 14 and compressed in the first stage of the compressor.
  • the second flow rate of the refrigerant flows through the second lamination means 20.
  • the pressure of the refrigerant is decreased down to the pressure of the intermediate pressure portion, i.e. the same pressure value as at the intermediate connector of the compressor 14.
  • the refrigerant enters the gas heater 24. In the gas heater 24 the refrigerant is heated up.
  • the first flow rate and the second flow rate of the refrig- erant are mixed at the intermediate connection of the com ⁇ pressor 14. Then, the whole refrigerant is compressed in the second stage of the compressor 14 and cooled down in the gas cooler 16. In this way the refrigerant works at three different pres ⁇ sure levels in the high pressure portion, the low pressure portion and the intermediate pressure portion, respec ⁇ tively.
  • the high pressure level occurs between the outlet of the compressor 14 and the inlets of the lamination means 18 and 20.
  • the intermediate pressure level occurs between the outlet of the second lamination means 20 and the inter ⁇ mediate connection of the compressor 14.
  • the low pressure level occurs between the first lamination means 18 and the inlet of the compressor 14.
  • a plurality of separate compressors arranged in se ⁇ ries may be used instead the multi-stage stage compressor 14.
  • the separate compressors (two in a preferred embodi- ment) work at different pressure levels, wherein the outlet of the compressor running at the lower pressure is con- nected to the inlet of the compressor running at the higher pressure .
  • At least an evaporator 22 and at least a gas heater 24 are connected between the gas cooler 16 and compressor means and working in parallel.
  • the evaporator 22 is connected to a first compression stage of the two-stage compressor, which provides a first level of refrigerant compression.
  • the gas heater 24 is connected to a second compression stage of the two-stage compressor and providing a second level of refrigerant compression.
  • gas cooler means that the refrigerant operates at least at critical pressure in the high pressure side of the heat pump cir- cuit .
  • the first flow rate of the refrigerant flows in two phases, namely as liquid and as vapour, and evaporates in the evaporator 22.
  • the first flow rate of the refrigerant oper- ates at least at the critical pressure in the high pressure portion of the refrigerant circuit 10.
  • the first flow rate of the refrigerant operates below the critical pressure in the low pressure portion side of the refrigerant circuit 10.
  • the second flow rate of the refrigerant which flows in the gas cooler 16, in the gas heater 24 and in the second stage of the compressor 14, can be in gaseous state.
  • the second flow rate of the refrigerant can operate at least at critical pressure in the low pressure portion as well as in the high pressure portion of the refrigerant circuit 10.
  • the gas heater 24 can work as an evaporator, until the intermediate pressure reaches the C02 critical pressure level.
  • the amounts of the first flow rate and second flow rate of the refrigerant are determined by the design of the first lamination means 18 and the second lamination means 20. The more is the amount of the second flow rate of the refriger ⁇ ant, the more is the efficiency of the heat pump system.
  • the difference between the pressures of the second flow rate i.e. between the intermediate pressure portion to the high pressure portion is lower than the difference between the pressures of the first flow rate from the low pressure portion to the high pressure portion.
  • the compres- sion power is reduced when the amount of the second flow rate increases.
  • the temperature level of the refrigerant flowing in the gas heater 24 is higher than the temperature level of the refrigerant flowing in the evaporator 22. If the second flow rate of the refrigerant is too high, then the drying capacity of the heat pump system can be penalized, and the efficiency of the drying process and of the laundry dryer decrease as well.
  • the ratio of the first and second flow rate of the refrig ⁇ erant can be chosen in order to maximize the efficiency of the drying process according to the considerations above, by properly designing the lamination means 18 and 20.
  • the evaporator 22 and the gas heater 24 can be two different heat exchangers.
  • the evaporator 22 and the gas heater 24 can be formed by the same finned coil with two different circuits for the refrigerant, wherein one circuit is provided for the evaporator 22 and one cir ⁇ cuit is provided for the gas heater 24.
  • the lamination means 18 and 20 are capillary tubes or similar passive lamination means, it is difficult to modu ⁇ late the ratio of the first and second flow rate of the re ⁇ frigerant during the cycle. Further, by using electronic expansion valves it is possible to change the ratio of the flow rates according to the variable thermodynamic condi ⁇ tions of the refrigerant in order to maximize the effi ⁇ ciency of the heat pump system.
  • the second flow rate of the refrigerant can be reduced during the drying cycle when the temperature of the refrigerant at the inlet or at the out ⁇ let of the gas heater 24 becomes too high.
  • the refrigerant could work only in the trans-critical cycle. It means that the whole refrigerant should flow in the evaporator 22 via the first lamination valve 18. In this case, in addition to the electronic expansion valves, a more quiet complex cir ⁇ cuit is provided. In fact the evaporator 22 cannot vaporize the whole refrigerant, if it is designed for only a per- centage of it. Thus, also the gas heater 24 can work as an additional evaporator.
  • the refrigerant operates in trans- critical conditions only, since the temperature at the gas cooler 16 and the evaporator 22 is below the critical tern- perature, which is about 31° C for carbon dioxide. In prac ⁇ tise, the temperature of the air stream at the beginning of the drying cycle is still not enough high to promote the totally-supercritical cycle.
  • FIG 2 shows a schematic diagram of the heat pump system for the laundry dryer according to a second embodiment of the present invention.
  • the heat pump system for the laundry dryer according to the second embodiment has the same com ⁇ ponents as the first embodiment in FIG 1. Additionally, the heat pump system of the second embodiment comprises a first on-off valve 30 and a second on-off valve 32.
  • the first on-off valve 30 is interconnected between the outlets if the evaporator 22 and the gas heater 24.
  • the second on-off valve 32 is interconnected between the outlet if the gas heater 24 and the intermediate connection of the compressor 14.
  • the first on-off valve 30 When the heat pump system is working only in trans-critical cycle (or generally when the heat pump is working with the evaporator 22 and at the gas heater 24 at the same pressure levels), then the first on-off valve 30 is open, while the second on-off valve 32 is closed, so that the whole flow rate of the refrigerant is sucked by the low pressure suction of the compressor 14, i.e. the inlet of the compressor 14. In this case the lamination means 18 and 20 give the same pressure drop to the two refrigerant flow rates down to the low pressure level as explained above. Further, the first on-off valve 30 and the second on-off valve 32 may be actu ⁇ ated in response to the temperature and/or pressure of the refrigerant and the air stream.
  • FIG 3 shows a temperature-entropy diagram of a trans- critical cycle in the heat pump system for the laundry dryer.
  • the temperature-entropy diagrams comprise a high pressure isobaric line 40, a low pressure isobaric line 42, a saturation curve 44 of carbon dioxide, a compression phase 46 and a lamination phase 48.
  • a state a of the refrigerant at the outlet of the gas heater, a state b of the refrigerant at the inlet of the gas cooler, a state c of the refrigerant at the outlet of the gas cooler and a state d of the refrigerant at the inlet of the gas heater are indicated in the temperature-entropy diagrams.
  • FIG 4 shows a temperature-entropy diagram of a totally- supercritical cycle in the heat pump system for the laundry dryer.
  • the temperature-entropy diagrams comprise the high pressure isobaric line 40, the low pressure isobaric line 42, the saturation curve 44 of carbon dioxide, the compres ⁇ sion phase 46 and the lamination phase 48. Further, the state a of the refrigerant at the outlet of the gas heater, the state b of the refrigerant at the inlet of the gas cooler, the state c of the refrigerant at the outlet of the gas cooler and the state d of the refrigerant at the inlet of the gas heater are indicated in the temperature-entropy diagrams.
  • the temperature and pres ⁇ sure of carbon dioxide increase.
  • the carbon dioxide follows the high pressure isobaric line 40.
  • the lamination phase 48 the temperature and pres- sure of carbon dioxide decrease.
  • the carbon dioxide follows the low pressure isobaric line 42.
  • FIG 5 shows a schematic diagram of the heat pump system for the laundry dryer according to the prior art.
  • the refrigerant circuit includes a compressor 14, a gas cooler 16, lamination means 18 and an evaporator 22.
  • the compressor 14 is formed as double stage compressor.
  • the double stage compressor 14 is characterized by having two inlets and two outlets, namely a low pressure suction, an intermediate pressure discharge, an intermediate pressure suction and a high pressure discharge.
  • the intermediate pressure discharge and the intermediate pressure suction are welded together, so that the compressor behaves as one single stage compressor.

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  • Engineering & Computer Science (AREA)
  • Textile Engineering (AREA)
  • Detail Structures Of Washing Machines And Dryers (AREA)
  • Drying Of Solid Materials (AREA)

Abstract

La présente invention concerne un système de pompe à chaleur pour sèche-linge, ledit système de pompe à chaleur comportant un circuit (10) d'agent frigorigène destiné à un agent frigorigène et un circuit (12) de flux d'air destiné à un flux d'air. Le circuit (10) d'agent frigorigène comprend un compresseur (14), un premier échangeur (16) de chaleur, un moyen (18) de laminage et un deuxième échangeur (22) de chaleur, reliés en série et formant une boucle. Le circuit (12) de flux d'air comprend le premier échangeur (16) de chaleur, un tambour (26) à linge, au moins un ventilateur (26) de flux d'air et le deuxième échangeur (22) de chaleur, reliés en série et formant une boucle fermée. Le circuit (10) d'agent frigorigène et le circuit (12) de flux d'air sont couplés thermiquement par le premier échangeur (16) de chaleur et le deuxième échangeur (22) de chaleur. Le compresseur (14) est constitué d'un compresseur multi-étage ou d'une pluralité de compresseurs en série. Le circuit (10) d'agent frigorigène comprend au moins une série de moyens supplémentaires (20) de laminage et un troisième échangeur (24) de chaleur. Le compresseur (14) comprend une interconnexion disposée respectivement entre les étages du compresseur multi-étage ou entre les compresseurs en série. L'entrée des moyens supplémentaires (20) de laminage est reliée à la sortie du premier échangeur (16) de chaleur. La sortie du troisième échangeur (24) de chaleur est reliée à l'interconnexion du compresseur (14).
PCT/EP2012/064458 2011-07-28 2012-07-24 Système de pompe à chaleur pour sèche-linge WO2013014137A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP11175681A EP2551401A1 (fr) 2011-07-28 2011-07-28 Système de pompe à chaleur pour sèche-linge
EP11175681.3 2011-07-28

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JP2016154604A (ja) * 2015-02-23 2016-09-01 株式会社東芝 衣類乾燥機

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KR101989522B1 (ko) * 2012-10-22 2019-09-30 엘지전자 주식회사 의류건조기
WO2014127842A1 (fr) * 2013-02-25 2014-08-28 Electrolux Appliances Aktiebolag Sèche-linge à pompe à chaleur et procédé d'exploitation d'un sèche-linge à pompe à chaleur
ITPR20130106A1 (it) * 2013-12-30 2015-07-01 Indesit Co Spa Elettrodomestico di asciugatura panni.
CN105297370B (zh) * 2014-05-29 2019-08-27 青岛胶南海尔洗衣机有限公司 一种带双排气压缩机系统的热泵干衣机及控制方法
KR101613966B1 (ko) * 2014-12-29 2016-04-20 엘지전자 주식회사 의류처리장치
CN106868831A (zh) * 2015-12-11 2017-06-20 上海日立电器有限公司 热泵型干衣机及其工作方法
WO2020132894A1 (fr) * 2018-12-25 2020-07-02 广东美的白色家电技术创新中心有限公司 Compresseur, système de pompe à chaleur, chauffe-eau et sèche-linge

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US20050044744A1 (en) * 2003-08-07 2005-03-03 Masaya Tadano Drying apparatus
EP1811077A1 (fr) * 2006-01-20 2007-07-25 SANYO ELECTRIC Co., Ltd. Machine à sécher
EP1983095A2 (fr) * 2008-08-08 2008-10-22 V-Zug AG Sèche-linge doté d'un chauffage dans le circuit de pompe à chaleur
EP2060671A1 (fr) * 2007-11-19 2009-05-20 Electrolux Home Products Corporation N.V. Séchoir à linge pour usage domestique
EP2251622A1 (fr) * 2008-01-30 2010-11-17 Daikin Industries, Ltd. Dispositif de refroidissement

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Publication number Priority date Publication date Assignee Title
DE19738735A1 (de) * 1997-09-04 1999-03-11 Bosch Siemens Hausgeraete Kondensationstrockner mit einem geschlossenen Trocknungsluftkreislauf
US20050044744A1 (en) * 2003-08-07 2005-03-03 Masaya Tadano Drying apparatus
EP1811077A1 (fr) * 2006-01-20 2007-07-25 SANYO ELECTRIC Co., Ltd. Machine à sécher
EP2060671A1 (fr) * 2007-11-19 2009-05-20 Electrolux Home Products Corporation N.V. Séchoir à linge pour usage domestique
EP2251622A1 (fr) * 2008-01-30 2010-11-17 Daikin Industries, Ltd. Dispositif de refroidissement
EP1983095A2 (fr) * 2008-08-08 2008-10-22 V-Zug AG Sèche-linge doté d'un chauffage dans le circuit de pompe à chaleur

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2016154604A (ja) * 2015-02-23 2016-09-01 株式会社東芝 衣類乾燥機

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