EP2551402A1 - 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
EP2551402A1
EP2551402A1 EP11175739A EP11175739A EP2551402A1 EP 2551402 A1 EP2551402 A1 EP 2551402A1 EP 11175739 A EP11175739 A EP 11175739A EP 11175739 A EP11175739 A EP 11175739A EP 2551402 A1 EP2551402 A1 EP 2551402A1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
refrigerant
pump system
compressor
heat pump
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.)
Withdrawn
Application number
EP11175739A
Other languages
German (de)
English (en)
Inventor
Francesco Cavarretta
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.)
Electrolux Home Products Corp NV
Original Assignee
Electrolux Home Products Corp NV
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 Corp NV filed Critical Electrolux Home Products Corp NV
Priority to EP11175739A priority Critical patent/EP2551402A1/fr
Priority to PCT/EP2012/064469 priority patent/WO2013014145A1/fr
Publication of EP2551402A1 publication Critical patent/EP2551402A1/fr
Withdrawn legal-status Critical Current

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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 in a laundry dryer the most efficient way to dry clothes by reduced energy consumption.
  • a conventional heat pump laundry dryer an air stream flows in a close air stream circuit.
  • the air stream is moved by a fan, passes through a laundry drum, removes water from wet clothes, is then cooled down and dehumidified in an evaporator, heated up in a condenser and at last re-inserted into the laundry 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. Therefore the temperatures of the air stream and the refrigerant are strictly connected to each other.
  • FIG 2 shows a refrigerant circuit according to the prior art.
  • the refrigerant circuit includes a compressor 14 formed 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 object of the present invention is achieved by the heat pump system according to claim 1.
  • the present invention provides for dividing of the flow rate of the refrigerant at the outlet of compressor.
  • One part of the refrigerant leaves the compressor at the intermediate connection of said compressor.
  • the other part of the refrigerant leaves the compressor at the outlet of said compressor.
  • the flow rates of the refrigerant are at two different pressure levels.
  • the both flow rates of the refrigerant flow into different heat exchangers and release heat to the air stream. This results in a reduction of the power required by the compressor.
  • the heat pump system comprises carbon dioxide as refrigerant.
  • the refrigerant circuit and the air stream circuit are thermally coupled by the third heat exchanger.
  • the third heat exchanger is provided for heating up the air stream and cooling down the refrigerant.
  • the first heat exchanger and the third heat exchanger may form a common heat exchanger with at least two different circuits for the refrigerant, wherein at least one circuit is provided for the first heat exchanger and at least one further circuit is provided for the third heat exchanger.
  • the refrigerant is provided for releasing heat to the air stream at different pressure levels.
  • the first heat exchanger forms a high pressure gas cooler.
  • the second heat exchanger forms an evaporator.
  • the third heat exchanger forms an intermediate pressure gas cooler.
  • the lamination means may be formed as a capillary tube and/or as an expansion valve (electronic or mechanical valve).
  • the electronic expansion valve is an on-off valve and/or the opening of the electronic expansion valve is continuously variable.
  • the opening of the further lamination means depends on the pressure and/or the temperature of the refrigerant at the intermediate connection of the compressor.
  • the opening of the further lamination means depends on the temperature of the air stream at the outlet of the third heat exchanger or at the outlet of the first heat exchanger in the air stream circuit.
  • a control valve may be provided at the intermediate connection of the compressor in order to control the flow rates of the refrigerant to the first heat exchanger and to the third heat exchanger.
  • the heat pump system works at totally-supercritical conditions, wherein the refrigerant operates at least at the critical pressure through the first, second and third heat exchanger
  • the present invention relates further to a laundry dryer with at least one heat pump system, wherein the laundry dryer comprises at least one heat pump system mentioned above.
  • 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 high pressure gas cooler 16, an intermediated pressure gas cooler 18, first lamination means 20, second lamination means 22 and an evaporator 24.
  • the compressor 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 compressor 14 is formed as a double stage compressor.
  • the double stage compressor 14 includes two single compressor 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 high pressure gas cooler 16, the first lamination means 20 and the second evaporator 24 are switched in series and form a first loop of the refrigerant circuit 10.
  • the first stage of the compressor 14, the intermediated pressure gas cooler 18, the second lamination means 22 and the evaporator 24 are switched in series and form a second loop of the refrigerant circuit 10.
  • the intermediated pressure gas cooler 18 and the second lamination means 22 are arranged in parallel to the second stage of the compressor 14, the high pressure gas cooler 16 and the first lamination means 20.
  • the outlet of the compressor 14 is connected to the inlet of the high pressure gas cooler 16, and the intermediate connection of the compressor 14 is connected to the inlet of the intermediated pressure gas cooler 18.
  • the drying air circuit 12 includes the evaporator 24, the intermediated pressure gas cooler 18, the high pressure gas cooler 16, a laundry treatment chamber 26, preferably a rotatable drum, and an air stream fan 28.
  • the high pressure gas cooler 16, the intermediated pressure gas cooler 18 and the evaporator 24 are heat exchangers and form the thermal interconnections between the refrigerant circuit 10 and the drying air circuit 12.
  • the evaporator 24 cools down and de-humidifies an during air, after said drying air has passed the laundry drum 26. Then, the intermediated pressure gas cooler 18 and the high pressure gas cooler 16 heat up the drying air, before the drying air is re-inserted into the laundry drum 26.
  • the drying air stream 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 discharge
  • the refrigerant circuit 10 is subdivided into a high pressure portion, a low pressure portion and an intermediate pressure portion.
  • the high pressure portion extends from the outlet of the compressor 14 via the high pressure gas cooler 16 to the inlet of the first lamination means 20.
  • the low pressure portion extends from the outlets of the lamination means 20 and 22 via the evaporator 24 to the inlet of the compressor 14.
  • the intermediate pressure portion extends from the intermediate connection of the compressor 14 via the intermediated pressure gas cooler 18 to the inlet of the second lamination means 22.
  • the whole flow rate of the refrigerant is compressed and heated up by the first stage of the compressor 14.
  • a certain part of the refrigerant leaves the compressor 14 via the intermediate connection of said compressor 14 and is cooled down in the intermediated pressure gas cooler 18 and laminated in the second lamination means 22.
  • the other part of the refrigerant is further compressed and heated up by the second stage of the compressor 14, cooled down in the high pressure gas cooler 16 and laminated in the first lamination means 20.
  • the two parts of the refrigerant are mixed before the inlet of the evaporator 24. Then, the whole flow rate of the refrigerant is vaporized by the evaporator 24 and sucked by the inlet of the compressor 14.
  • the refrigerant works at three different pressure levels in the high pressure portion, the low pressure portion and the intermediate pressure portion, respectively.
  • the high pressure level occurs between the outlet of the compressor 14 and the inlet of the first lamination means 20.
  • the intermediate pressure level occurs between the intermediate connection of the compressor 14 and the inlet of the second lamination means 22.
  • the low pressure level occurs between the outlets of the lamination means 20 and 22 and the inlet of the compressor 14.
  • the temperature of the refrigerant in the high pressure gas cooler 16 is higher than the temperature of the refrigerant in the intermediated pressure gas cooler 18.
  • the air stream coming from the evaporator 24 flows at first through the intermediated pressure gas cooler 18 and then through the high pressure gas cooler 16.
  • the high pressure gas cooler 16 and the intermediated pressure gas cooler 18 can be formed as two separate heat exchangers. Alternatively, one heat exchanger with two circuits for the refrigerant can be used. The one heat exchanger with two circuits is more compact.
  • the lamination means 20 and 22 can be realized by capillary tubes or by electronic valves.
  • the second lamination means 22 downstream the intermediated pressure gas cooler 18 is an electronic valve. In this way, the amount of the refrigerant flowing into the intermediated pressure gas cooler 18 can be modulated in dependence of the pressure and/or the temperature of the refrigerant at the intermediate connection of the compressor 14.
  • the electronic valve is completely closed until the pressure and/or the temperature of the refrigerant at the intermediate connection of the compressor 14 are higher than predetermined levels, so that the refrigerant is able to heat up the air stream in the air stream circuit 12.
  • the electronic valve can be kept open at a fixed value, so that an on-off valve can be used.
  • the opening of the electronic valve is modulated in dependence of the temperature of the air stream at the outlet of the intermediated pressure gas cooler 18 or at the outlet of the high pressure gas cooler 16 in the air stream circuit 12. The opening of the electronic valve is increasing until said temperature of the air stream starts decreasing. Then, the opening of the electronic valve is reduced.
  • the efficiency of the heat pump system increases with the amount of the refrigerant flowing into the intermediated pressure gas cooler 18. However, a minimum amount of the refrigerant must flow into the high pressure gas cooler 16 in order to heat up the air stream up to a desired level.
  • the refrigerant in the high pressure gas cooler 16 is at a higher temperature level than the refrigerant in the intermediated pressure gas cooler 18.
  • a control valve can be provided at the intermediate connection of the compressor 14 in order to modulate the flow rates of the refrigerant to the intermediated pressure gas cooler 18 and to the high pressure gas cooler 16.
  • Said control valve may be actuated in dependence of the pressure and/or the temperature of the refrigerant and/or the temperature of the air stream in the air stream circuit 12 in order to assure a proper flow rate of the refrigerant through the high pressure gas cooler 16.
  • a plurality of separate compressors (two in preferred embodiment) arranged in series may be used instead the multi-stage compressor 14.
  • the separate compressors work at different pressure levels, wherein the outlet of the compressor running at the lower pressure is connected to the inlet of the compressor running at the higher pressure.
  • FIG 2 shows a schematic diagram of the heat pump system for the laundry dryer according to the prior art. Same or comparable components of the heat pump system have the same reference numerals as in FIG 1 .
  • 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)
EP11175739A 2011-07-28 2011-07-28 Système de pompe à chaleur pour sèche-linge Withdrawn EP2551402A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP11175739A EP2551402A1 (fr) 2011-07-28 2011-07-28 Système de pompe à chaleur pour sèche-linge
PCT/EP2012/064469 WO2013014145A1 (fr) 2011-07-28 2012-07-24 Système de pompe à chaleur pour sèche-linge

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP11175739A EP2551402A1 (fr) 2011-07-28 2011-07-28 Système de pompe à chaleur pour sèche-linge

Publications (1)

Publication Number Publication Date
EP2551402A1 true EP2551402A1 (fr) 2013-01-30

Family

ID=46579024

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11175739A Withdrawn EP2551402A1 (fr) 2011-07-28 2011-07-28 Système de pompe à chaleur pour sèche-linge

Country Status (2)

Country Link
EP (1) EP2551402A1 (fr)
WO (1) WO2013014145A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015180228A1 (fr) * 2014-05-29 2015-12-03 青岛胶南海尔洗衣机有限公司 Sèche-linge à pompe à chaleur avec système de compresseur à double échappement et procédé de commande de celui-ci
EP3333305A1 (fr) * 2016-12-12 2018-06-13 BSH Hausgeräte GmbH Sèche-linge

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102020205594A1 (de) 2020-05-04 2021-11-04 BSH Hausgeräte GmbH Wäschebehandlungsmaschine mit einem gehäuse und einer wärmepumpe
KR102472995B1 (ko) * 2021-01-25 2022-12-01 엘지전자 주식회사 세탁기

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19738735A1 (de) * 1997-09-04 1999-03-11 Bosch Siemens Hausgeraete Kondensationstrockner mit einem geschlossenen Trocknungsluftkreislauf
US20050072022A1 (en) * 2003-09-24 2005-04-07 Etsushi Nagae Washing/drying machine
EP1811076A1 (fr) * 2006-01-20 2007-07-25 SANYO ELECTRIC Co., Ltd. Sécheur
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

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19738735A1 (de) * 1997-09-04 1999-03-11 Bosch Siemens Hausgeraete Kondensationstrockner mit einem geschlossenen Trocknungsluftkreislauf
US20050072022A1 (en) * 2003-09-24 2005-04-07 Etsushi Nagae Washing/drying machine
EP1811076A1 (fr) * 2006-01-20 2007-07-25 SANYO ELECTRIC Co., Ltd. Sécheur
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

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015180228A1 (fr) * 2014-05-29 2015-12-03 青岛胶南海尔洗衣机有限公司 Sèche-linge à pompe à chaleur avec système de compresseur à double échappement et procédé de commande de celui-ci
CN105297370A (zh) * 2014-05-29 2016-02-03 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
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
US10633784B2 (en) 2014-05-29 2020-04-28 Qingdao Jiaonan Haier Washing Machine Co., Ltd. Heat pump dryer with dual-exhaust compressor system and control method thereof
EP3333305A1 (fr) * 2016-12-12 2018-06-13 BSH Hausgeräte GmbH Sèche-linge

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