WO2013075997A1 - Sèche-linge équipé d'un système de pompe à chaleur - Google Patents

Sèche-linge équipé d'un système de pompe à chaleur Download PDF

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Publication number
WO2013075997A1
WO2013075997A1 PCT/EP2012/072690 EP2012072690W WO2013075997A1 WO 2013075997 A1 WO2013075997 A1 WO 2013075997A1 EP 2012072690 W EP2012072690 W EP 2012072690W WO 2013075997 A1 WO2013075997 A1 WO 2013075997A1
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WO
WIPO (PCT)
Prior art keywords
heat exchanger
refrigerant
air stream
outlet
inlet
Prior art date
Application number
PCT/EP2012/072690
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.
Priority to CN201280057032.4A priority Critical patent/CN103946441B/zh
Publication of WO2013075997A1 publication Critical patent/WO2013075997A1/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 
    • 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 laundry dryer with a heat pump system according to the preamble of claim 1.
  • 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 closed air stream circuit.
  • the air stream is moved by a fan and passes through a laundry drum removing water from wet clothes.
  • the air stream is cooled down and dehumidified in an evaporator or gas heater and heated up in a condenser or gas cooler.
  • the air stream is re-inserted into the laundry drum again.
  • the refrigerant is compressed by a compressor.
  • the refrigerant is condensed in the condenser or cooled down in the gas cooler.
  • the refrigerant is laminated in an expansion device.
  • the refrigerant is vaporized in the evaporator or heated up in the gas heater. If the re- frigerant operates at the critical pressure, then it is cooled down in the gas cooler and heated up in the gas heater, respectively.
  • the temperatures of the air stream and the refrigerant are strictly connected to each other.
  • the temperature of the air stream at an out ⁇ let of the evaporator is relative low, e.g. about 25°C.
  • the temperature of the air stream at an inlet of the laundry drum should be relative high, e.g. about 65°C, so that the condenser has to heat up the refrigerant with a relative high temperature difference.
  • the relationships between the temperatures of the air stream require heat exchangers with disadvantageous dimensions.
  • WO 2011/080045 Al discloses a domestic appliance with a drying chamber and a heat pump circuit .
  • the heat pump cir- cuit includes a liquefier, an evaporator and two additional heat exchangers.
  • the process air is heated by the liquefier and cooled by the evaporator.
  • the one additional heat ex ⁇ changer cools the refrigerant and heats the process air.
  • the other additional heat exchanger undercools the conden- sate of the refrigerant and reduces the mass flow of the circulating refrigerant.
  • the heat pump circuit comprises a high number of components and a complicated control system. It is an object of the present invention to provide a laun ⁇ dry dryer with a heat pump system, which allows a reduced drying time and an improved performance of the heat pump system by low complexity.
  • the object of the present invention is achieved by the laundry dryer according to claim 1.
  • the additional heat ex ⁇ changer on the one hand and the first heat exchanger or the second heat exchanger on the other hand are formed as one heat exchanger assembly including one air stream channel and at least one refrigerant channel.
  • the present invention provides the arrangement of the first or second heat exchanger and the additional heat exchanger within one physical heat exchanger assembly.
  • Said heat ex- changer assembly includes one channel or at least two sepa ⁇ rate channels for the refrigerant, which penetrates or penetrate a channel for the air stream.
  • the channels for the refrigerant are connected to different parts of the re ⁇ frigerant circuit, wherein the refrigerant has different thermal states.
  • the heat exchanger assembly containing the first or second heat exchanger and the additional heat ex ⁇ changer reduces the complexity of the heat pump system.
  • the heat exchanger assembly comprises common fins and air stream channel between said fins and at least one refrigerant channel in thermal connection with the fins so as to define the first heat exchanger or the second heat exchanger and the additional heat exchanger side, the first heat exchanger or the second heat exchanger and the addi- tional heat exchanger side share the common fins.
  • thee refrigerant channel passes through the common fins.
  • an inlet of the refrigerant channel is arranged at the second heat exchanger and an outlet of the refriger ⁇ ant channel is arranged at the additional heat exchanger.
  • the inlet of the refrigerant channel is con- nected to the outlet of the expansion device and an outlet of the refrigerant channel is connected to the inlet outlet of the compressor.
  • the refrigerant circuit includes an internal heat exchanger, wherein a high pressure side of said internal heat exchanger is interconnected between the first heat exchanger and the expansion device and a low pressure side of said internal heat exchanger is interconnected between the second heat exchanger and the additional heat ex ⁇ changer, so that the additional heat exchanger receives the refrigerant via said low pressure side of the internal heat exchanger .
  • a first refrigerant channel corresponds with the second heat exchanger and a second refrigerant channel corresponds with the additional heat exchanger, and wherein an inlet of the first refrigerant channel is connected to the outlet of the expansion device and an outlet of the first refrigerant channel is connected to an inlet of the low pressure side of the internal heat exchanger and an inlet of the second refrigerant channel is connected to an outlet of the low pressure side (of the internal heat ex ⁇ changer and an outlet of the second refrigerant channel is connected the inlet of the compressor.
  • a first refrigerant channel corresponds with the additional heat exchanger and is part of the low pres ⁇ sure portion of the refrigerant circuit
  • the second refrigerant channel corresponds with the first heat ex- changer and is part of the high pressure portion of the re ⁇ frigerant circuit.
  • the inlet of the first refrigerant channel is connected to the refrigerant outlet of the evaporator and the outlet of the first refrigerant channel is connected to the inlet of the compressor and the inlet of the second re ⁇ frigerant channel is connected to the outlet of the com ⁇ pressor and the outlet of the second refrigerant channel is connected the inlet of the expansion device.
  • the inlet of the first refrigerant channel is connected to the outlet of the low pressure side of the in ⁇ ternal heat exchanger and the outlet of the first refriger- ant channel is connected to the inlet of the compressor and the inlet of the second refrigerant channel is connected to the outlet of the compressor and the outlet of the second refrigerant channel is connected the inlet of the high pressure side of the internal heat exchanger.
  • the refrigerant circuit comprises a by-pass line so that the refrigerant can completely or partially by-pass said additional heat exchanger.
  • the by-pass line includes at least one on-off valve for opening and closing said by-pass line or the by ⁇ pass line includes at least one control valve for a con ⁇ tinuous opening of said by-pass line or the by-pass line includes at least one three-way valve for an alternating opening and closing of said by-pass line and a refrigerant side of the additional heat exchanger.
  • the by-pass line is controlled or controllable by the temperature of the refrigerant in at least one posi ⁇ tion of the refrigerant circuit or the by-pass line is con ⁇ trolled or controllable by the temperature of the air stream in at least one position of the air stream circuit.
  • the by-pass line is controlled or controllable by one of the following,
  • the first heat exchanger acts as a gas cooler, if the re ⁇ frigerant remains in a gaseous state.
  • the first heat exchanger acts as a condenser, if the refrigerant at least partially transfers from the gaseous state to a liquid state.
  • the second heat exchanger acts as a gas heater, if the re ⁇ frigerant remains in the gaseous state. Else, the second heat exchanger acts as an evaporator, if the refrigerant at least partially transfers from the liquid state to the gaseous state.
  • 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 schematic diagram of the heat pump system for the laundry dryer according to a third embodiment of the present invention, shows a schematic diagram of the heat pump system for the laundry dryer according to a fourth embodi ment of the present invention, shows a schematic diagram of the heat pump system for the laundry dryer according to a fifth embodi ment of the present invention
  • FIG 6 shows a schematic diagram of a heat exchanger as ⁇ sembly for the heat pump system according to the fifth embodiment of the present invention
  • FIG 7 shows a schematic diagram of the heat pump system for the laundry dryer according to a sixth embodiment of the present invention
  • FIG 8 shows a schematic diagram of the heat exchanger as ⁇ sembly for the heat pump system according to the sixth embodiment of the present invention
  • FIG 9 shows a schematic diagram of the heat pump system for the laundry dryer according to a seventh embodiment of the present invention.
  • FIG 10 shows a schematic diagram of the heat exchanger as ⁇ sembly for the heat pump system according to the seventh embodiment of the present invention
  • FIG 11 shows a schematic diagram of the heat pump system for the laundry dryer according to an eighth embodiment of the present invention.
  • FIG 12 shows a schematic diagram of the heat exchanger as ⁇ sembly for the heat pump system according to the eighth embodiment of the present invention.
  • 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 stream circuit 12.
  • the refrigerant circuit 10 includes a compressor 14, a con ⁇ denser 16, an expansion device 18, an evaporator 20 and an additional heat exchanger 22.
  • the compressor 14, the con- denser 16, the expansion device 18, the evaporator 20 and the additional heat exchanger 22 are switched in series and form a closed loop.
  • the air stream circuit 12 includes the evaporator 20, the additional heat exchanger 22, the con- denser 16, an air stream fan 24 and a laundry treatment chamber 26, preferably a rotatable drum.
  • the air stream circuit 12 forms also a loop.
  • the refrigerant is compressed by the compressor 14 and con- densed by the condenser 16.
  • the refrigerant is laminated in the expansion device 18 and vaporized in the evaporator 20.
  • the refrigerant is cooled down by the additional heat exchanger 22 and sucked by the compressor 14.
  • the drying air stream is driven by the air stream fan 24 and passes through the laundry drum 26 removing water from wet laundry.
  • the drying air stream is cooled down and dehumidified by the evaporator 20 and pre-heated by the addi ⁇ tional heat exchanger 22.
  • the drying air stream is heated up in the condenser 16 and re-inserted into the laundry drum 26 again.
  • the additional heat exchanger 22 is arranged inside the air stream circuit between the evaporator 20 and the condenser 16.
  • the refrigerant and the drying air stream are thermally coupled by the additional heat exchanger 22, by the evapo ⁇ rator 20 and condenser 16.
  • the additional heat exchanger 22 is arranged between a refrig ⁇ erant outlet of the evaporator 20 and an inlet of the com ⁇ pressor 14.
  • the refrigerant from the evaporator 20 is cooled down by the additional heat exchanger 22 before be ⁇ ing sucked by the compressor 14, while the drying air stream is pre-heated by said additional heat exchanger 22.
  • the drying air stream is cooled down in order to be dehumidified, while the refrigerant is va ⁇ porized and heated, preferably superheated, therein.
  • the temperature of the air stream at an air stream outlet of the laundry drum 26 and at an air stream inlet of the evaporator 20, respectively is about 40°C, for instance.
  • the temperature of the air stream at an air stream outlet of the evaporator 20 is about 25°C, for example.
  • the refrigerant enters the evaporator at a temperature of about 20 °C and is superheated by the evaporator up to about 35°C, for instance.
  • the air stream is pre-heated in the additional heat exchanger 22 by said superheated refrigerant.
  • the temperature of the air stream at an air stream outlet of the condenser 16 and an air stream inlet of the laundry drum 26, respectively, is about 65°C, for instance.
  • the additional heat ex ⁇ changer 22 supports the condenser 16 in heating up the air stream.
  • the additional heat exchanger 22 has the advantage that a higher heating power is transferred to the air stream, so that a warming up phase of the heat pump system is shorten. Further, the air stream can reach a higher temperature dur- ing a steady state phase of the heat pump system. Moreover, the temperature of the refrigerant at the inlet of the com ⁇ pressor 14 is lower, so that the power required by the com ⁇ pressor 14 decreases, if the other parameters are assumed being constant.
  • FIG 2 illustrates a schematic diagram of the heat pump sys ⁇ tem for the laundry dryer according to a second embodiment of the present invention.
  • the heat pump system of the sec ⁇ ond embodiment comprises the same components as the heat pump system of the first embodiment. Additionally, the re ⁇ frigerant circuit 10 of the second embodiment comprises a by-pass line 28.
  • the by-pass line 28 is arranged, preferably, in parallel to the additional heat exchanger 22.
  • a too low temperature of the refrigerant at the outlet of the compressor is avoided. Said too low temperature would provide, that the drying air stream cannot be heated up to desired levels.
  • the by-pass line 28 is switchable by one or more valves.
  • the valves are not shown in FIG 2.
  • the pass line 28 comprises a pair of on-off valves arranged at the end portions of said by-pass line 28.
  • the by-pass line 28 is switchable by only one on-off valve.
  • the pass line 28 comprises a pair of control valves arranged at the end portions of said by-pass line 28, wherein the control valves can be opened completely or partially.
  • the by-pass line 28 is switchable by only one control valve.
  • the pass line 28 may comprise a three-away valve.
  • FIG 3 illustrates a schematic diagram of the heat pump sys- tern for the laundry dryer according to a third embodiment of the present invention.
  • the heat pump system of the third embodiment comprises the same components as the heat pump system of the first embodiment.
  • the refriger ⁇ ant circuit 10 of the third embodiment comprises an inter ⁇ nal heat exchanger 30.
  • the evaporator 20 and the addi ⁇ tional heat exchanger 22 which couple thermally the re ⁇ frigerant circuit 10 and the air stream circuit 12, the in ⁇ ternal heat exchanger 30 acts only within the refrigerant circuit 10.
  • the refrigerant circuit 10 couples thermally a high pressure portion and a low pressure portion of the re ⁇ frigerant circuit 10.
  • the high pressure portion extends from the outlet of the compressor 14 via the condenser 16 to the inlet of the expansion device 18.
  • the low pressure portion extends from the outlet of the expansion device 18 via the evaporator 20 and the additional heat exchanger 22 to the inlet of the compressor 14.
  • the internal heat exchanger 30 comprises a high pressure side 32 and a low pressure side 34.
  • the high pressure side 32 corresponds with the high pressure portion of the re ⁇ frigerant circuit 10.
  • the low pressure side 34 corresponds with the low pressure portion of the refrigerant circuit 10.
  • the refrigerant from the outlet of the evaporator 20 is heated up in the low pressure side 34 of the internal heat exchanger 30. Then, the refrigerant is cooled down in the additional heat exchanger 22.
  • the internal heat exchanger 30 allows that the air stream in the additional heat ex- changer 22 is heated up more as in the first and second em ⁇ bodiment without reaching the too low temperature level of the refrigerant at the inlet of the compressor 14.
  • FIG 4 illustrates a schematic diagram of the heat pump sys ⁇ tem for the laundry dryer according to a fourth embodiment of the present invention.
  • the heat pump system of the fourth embodiment comprises the same components as the heat pump system of the third embodiment.
  • the re ⁇ frigerant circuit 10 of the third embodiment comprises the by-pass line 28.
  • the fourth embodiment is a combination of the second and third embodiment.
  • the by-pass line 28 is, preferably, arranged in parallel to the additional heat exchanger 22.
  • the by-pass line 28 is also switchable by one or more valves.
  • the valves are not shown in FIG 4.
  • the pass line 28 comprises a pair of on-off valves arranged at the end portions of said by-pass line 28.
  • the by-pass line 28 is switchable by only one on-off valve.
  • the pass line 28 comprises the pair of control valves arranged at the end portions of said by-pass line 28, wherein the control valves can be opened completely or partially.
  • the by-pass line 28 is switchable by only one control valve.
  • the pass line 28 may comprise a three-away valve.
  • the low pressure side 34 of the internal heat exchanger 30 is arranged downstream of the additional heat exchanger 22. After the refrigerant has been cooled down by the air stream in the additional heat exchanger 22, is heated up in the low pressure side 34 of the internal heat exchanger 30, so that the too low temperature levels at the inlet and outlet of the compressor 14 are avoided.
  • This embodiment preferably, does not require the by-pass line 28, since the position of the low pressure side 34 of the internal heat exchanger 30 ensures the appropriate temperature levels at the inlet and outlet of the compressor 14.
  • the valve or valves of the by-pass line 28 may be con ⁇ trolled in dependence of the temperature levels of the air stream and/or the refrigerant.
  • the evaporator 20 may be flooded or the refrigerant may be superheated, i.e. the temperature of the refrigerant at the refrigerant outlet of the evaporator 20 could be lower than the temperature of the air stream.
  • the re ⁇ frigerant cannot heat up the air stream in the additional heat exchanger 22 and passes by said additional heat ex ⁇ changer 22.
  • the by-pass line 28 is opened and the additional heat ex ⁇ changer 22 does not work, if
  • the temperature of the refrigerant at the refrigerant outlet of the evaporator 20 is lower than a predetermined value
  • the temperature difference of the refrigerant at the refrigerant inlet and outlet of the evaporator 20 is lower than a predetermined value, and/or
  • the temperature of the refrigerant at the refrigerant outlet of the evaporator 20 is lower than the tempera- ture of the air stream at the air stream outlet of the evaporator 20.
  • the additional heat exchanger 22 may be by-passed, if the air stream at the inlet of the laundry drum 26 cannot be kept at a higher level. This situation could occur at the beginning of the steady state phase. If the tempera ⁇ ture of the refrigerant at the refrigerant inlet or outlet of the evaporator 20 or the refrigerant outlet of the con ⁇ denser 16 is higher than a predetermined level correspond ⁇ ing to the beginning of the drying cycle and at the same time the temperature of the air stream at the inlet of the laundry drum 26 or the temperature of the refrigerant at the outlet of the compressor 14 is lower than another predetermined level, then the additional heat exchanger 22 may be passed by completely or partially. When the air stream reaches the desired value, then the additional heat ex ⁇ changer 22 is activated again. Thus, the additional heat exchanger 22 works in an on-off mode.
  • FIG 5 shows a schematic diagram of the heat pump system for the laundry dryer according to a fifth embodiment of the present invention.
  • the fifth embodiment differs from the first embodiment in that the evaporator 20 and the addi ⁇ tional heat exchanger 22 are formed by a heat exchanger as ⁇ sembly 36.
  • Said heat exchanger assembly 36 comprises common fins 38 and one refrigerant channel 44 in thermal connection with the fins 38 so as to define an evaporator side 20 for cool ⁇ ing down the air stream and heating up the refrigerant and an additional heat exchanger side 22 for pre-heating the air stream and cooling down the refrigerant.
  • FIG 6 shows a schematic diagram of a heat exchanger assem- bly 36 for the heat pump system according to the fifth embodiment of the present invention.
  • the heat exchanger as ⁇ sembly 36 comprises a plurality of fins 38.
  • the heat ex ⁇ changer assembly 36 comprises a common air stream channel 40 for the evaporator 20 and the additional heat exchanger 22, wherein the air stream channel 40 passes at first the evaporator 20 and then the additional heat exchanger 22.
  • the refrigerant channel 42 penetrates the air stream chan ⁇ nel 40 and is in thermal connection with the fins, prefera ⁇ bly the refrigerant channel 42 passes through the common fins 38.
  • the refrigerant channel 42 is, preferably, a ser ⁇ pentine.
  • An inlet 48 of the refrigerant channel 42 is con ⁇ nected to the outlet of the expansion device 18.
  • An outlet 50 of the refrigerant channel 42 is connected to the inlet outlet of the compressor 14.
  • the inlet 48 of the refrigerant channel 42 is arranged at the evaporator side of the heat exchanger assembly and the outlet 50 of the refrigerant channel 42 is arranged at the additional heat exchanger side the heat exchanger assembly.
  • the air stream is cooled down and dehumidified.
  • the air stream is pre-heated.
  • the refrigerant is vaporized and superheated.
  • the additional heat ex- changer side 22 of the heat exchanger assembly 36 the re ⁇ frigerant is cooled down.
  • FIG 7 shows a schematic diagram of the heat pump system for the laundry dryer according to a sixth embodiment of the present invention.
  • the sixth embodiment differs from the third embodiment in that the evaporator 20 and the addi ⁇ tional heat exchanger 22 are formed by the heat exchanger assembly 36.
  • Said heat exchanger assembly 36 comprises com ⁇ mon fins 38 and two refrigerant channels 44,46 in thermal connection with the fins 38 so as to define an evaporator side 20 for cooling down the air stream and heating up the refrigerant and an additional heat exchanger side 22 for pre-heating the air stream and cooling down the refrigerant .
  • FIG 8 shows a schematic diagram of the heat exchanger as ⁇ sembly 36 for the heat pump system according to the sixth embodiment of the present invention.
  • the heat exchanger as ⁇ sembly 36 comprises the plurality of fins 38 and the air stream channel 40 between said fins 38.
  • the air stream channel 40 passes at first the evaporator 20 side and then the additional heat exchanger 22 side of the heat exchanger assembly 36.
  • a first refrigerant channel 44 and a second refrigerant channel 46 penetrate the air stream channel 40.
  • the first refrigerant channel 44 and the second refrigerant channel 46 are, preferably, serpentine.
  • the first refrigerant channel 44 in FIG 8 corresponds with the evaporator 20 side of the heat exchanger assembly 36.
  • the second refrigerant channel 46 in FIG 8 corresponds with the additional heat exchanger 22 side of the of the heat exchanger assembly 36.
  • An inlet 52 of the first refrigerant channel 44 is connected to the outlet of the expansion de ⁇ vice 18.
  • An outlet 54 of the first refrigerant channel 44 is connected to an inlet of the low pressure side 34 of the internal heat exchanger 30.
  • An inlet 56 of the second re- frigerant channel 46 is connected to an outlet of the low pressure side 34 of the internal heat exchanger 30.
  • An out ⁇ let 58 of the second refrigerant channel 46 is connected the inlet of the compressor 14. Between the first refrigerant channel 44 and the second re ⁇ frigerant channel 46 the refrigerant passes the low pres ⁇ sure side 34 of the internal heat exchanger 30.
  • FIG 9 shows a schematic diagram of the heat pump system for the laundry dryer according to a seventh embodiment of the present invention.
  • the seventh embodiment differs from the first embodiment in that the additional heat exchanger 22 and the condenser 16 are formed by the heat exchanger as ⁇ sembly 36.
  • Said heat exchanger assembly 36 comprises common fins 38 and two refrigerant channels 44,46 in thermal con ⁇ nection with the fins 38 so as to define an additional heat exchanger side 22 for pre-heating the air stream and cooling down the refrigerant and a condenser side 16 for heat ⁇ ing up the air stream and cooling down the refrigerant.
  • FIG 10 shows a schematic diagram of the heat exchanger as ⁇ sembly 36 for the heat pump system according to the seventh embodiment of the present invention.
  • the heat exchanger as ⁇ sembly 36 comprises the plurality of fins 38.
  • the heat ex ⁇ changer assembly 36 comprises the common air stream channel 40 for the additional heat exchanger side 22 and the con- denser side 16, wherein the air stream channel 40 passes at first the additional heat exchanger 22 and the condenser 16.
  • the first refrigerant channel 44 preferably a serpen ⁇ tine
  • the second refrigerant channel 46 preferably a serpentine, penetrate the air stream channel 40.
  • the first refrigerant channel 44 in FIG 10 corresponds with the additional heat exchanger side 22.
  • the second refriger ⁇ ant channel 46 in FIG 10 corresponds with the condenser side 16.
  • the refrigerant circuit 10 is subdivided into a high pres ⁇ sure portion and a low pressure portion.
  • the high pressure portion extends from the outlet of the compressor 14 via the condenser 16 to the inlet of the expansion device 18.
  • the low pressure portion extends from the outlet of the ex- pansion device 18 via the evaporator 20 to the inlet of the compressor 14.
  • the first refrigerant channel 44 is part of the low pres ⁇ sure portion of the refrigerant circuit, whereas the second refrigerant channel 46 is part of the high pressure portion of the refrigerant circuit.
  • the inlet 52 of the first refrigerant channel 44 is con ⁇ nected to the refrigerant outlet of the evaporator 20.
  • the outlet 54 of the first refrigerant channel 44 is connected to the inlet of the compressor 14.
  • the inlet 56 of the sec ⁇ ond refrigerant channel 46 is connected to the outlet of the compressor 14.
  • the outlet 58 of the second refrigerant channel 46 is connected the inlet of the expansion device 18.
  • the drying air stream is pre-heated, while the refrigerant is cooled down.
  • the condenser side 16 the refrigerant is cooled down, while the air stream is warmed up .
  • the thermal conductivity of the fins 38 al ⁇ lows that the refrigerant flowing into the additional heat exchanger side 22 cools down the refrigerant flowing into the condenser side 16. Conversely, the refrigerant flowing into the condenser 16 heats up the refrigerant flowing into the additional heat exchanger 22, thus improving the effi- ciency of the heat pump system.
  • FIG 11 shows a schematic diagram of the heat pump system for the laundry dryer according to an eighth embodiment of the present invention.
  • the eighth embodiment differs from the third embodiment in that the additional heat exchanger 22 and the condenser 16 are formed by the heat exchanger assembly 36.
  • Said heat exchanger assembly 36 comprises common fins 38 and two refrigerant channels 44,46 in thermal connection with the fins 38 so as to define the additional heat ex ⁇ changer side 22 for pre-heating the air stream and cooling down the refrigerant and the condenser side 16 for heating up the air stream and cooling down the refrigerant.
  • FIG 12 shows a schematic diagram of the heat exchanger as ⁇ sembly for the heat pump system according to the eighth embodiment of the present invention.
  • the heat exchanger as- sembly 36 comprises the common air stream channel 40 for the additional heat exchanger side 22 and the condenser side 16, wherein the air stream channel 40 passes at first the additional heat exchanger 22 and the condenser 16.
  • the first refrigerant channel 44 preferably a serpentine
  • the second refrigerant channel 46 preferably a serpentine
  • the first refrigerant channel 44 in FIG 12 corresponds with the additional heat exchanger side 22.
  • the second refriger ⁇ ant channel 46 in FIG 12 corresponds with the condenser side 16.
  • the first refrigerant channel 44 is part of the low pressure portion of the refrigerant circuit, whereas the second refrigerant channel 46 is part of the high pres- sure portion of the refrigerant circuit.
  • the inlet 52 of the first refrigerant channel 44 is con ⁇ nected to the outlet of the low pressure side 34 of the in ⁇ ternal heat exchanger 30.
  • the outlet 54 of the first re- frigerant channel 44 is connected to the inlet of the com ⁇ pressor 14.
  • the inlet 56 of the second refrigerant channel 46 is connected to the outlet of the compressor 14.
  • the outlet 58 of the second refrigerant channel 46 is connected the inlet of the high pressure side 32 of the internal heat exchanger 30.
  • the heat exchanger assembly 36 is realized by one single component. Said single component is an air-to-liquid heat exchanger including one channel for the air stream and one, two or more channels for the refrigerant. The net result is favourable to an efficient heating up of the air stream.
  • the refrigerant e.g. carbon dioxide
  • the refrigerant circuit 10 If the refrigerant, e.g. carbon dioxide, operates at least at the critical pressure in the low pressure portion of the refrigerant circuit 10, then the refrigerant remains always in the gaseous state. In this case, no evaporation occurs and the evaporator 20 acts as a gas heater.
  • the air stream circuit 12 is a closed loop, in which the air stream flows continuously through the laundry drum 26.
  • a part of the air stream may be exhausted from the air stream circuit 12.
  • the exhausted air may be replaced by fresh air, e.g. ambient air.
  • the exhausted air and fresh air form a smaller part of the air stream.
  • the air stream circuit 12 may be temporar- ily opened, wherein the time of the open air stream circuit 12 is a small part of the total processing time. In any case, at least a part of the air stream passes always the condenser 16 after having passed the evaporator 20.
  • the heat pump system with the additional heat exchanger 22 and optionally the internal heat exchanger 30 allows a re ⁇ duction of the drying time and improves the performance of the heat pump dryer.
  • an auxiliary condenser can be provided in the refrigerant circuit, particularly between the main condenser 16 and the expansion device 18.

Abstract

La présente invention concerne un sèche-linge équipé d'un système de pompe à chaleur comprenant un circuit de refroidissement (10) pour un fluide frigorigène et un circuit d'écoulement d'air (12) pour un écoulement d'air. Le circuit de refroidissement (10) comprend un compresseur (14), un premier échangeur thermique (16), un détendeur (18), un second échangeur thermique (20) et un échangeur thermique supplémentaire (22) reliés en série et formant une boucle. Le circuit d'écoulement d'air (12) comprend au moins un ventilateur de circulation d'air (24), un tambour à linge (26), le second échangeur thermique (20), l'échangeur thermique supplémentaire (22) et le premier échangeur thermique (16) reliés en série et formant une boucle. Le circuit de refroidissement (10) et le circuit d'écoulement d'air (12) sont thermiquement couplés par le premier échangeur thermique (16), le second échangeur thermique (20) ainsi que par l'échangeur thermique supplémentaire (22). Le premier échangeur thermique (16) est utilisé pour chauffer l'écoulement d'air et refroidir le fluide frigorigène. Le second échangeur thermique (20) est utilisé pour chauffer l'écoulement d'air et refroidir le fluide frigorigène. L'échangeur thermique supplémentaire (22) est utilisé pour chauffer l'écoulement d'air et refroidir le fluide frigorigène. L'échangeur thermique supplémentaire (22) d'un côté, et le premier échangeur thermique (16) ou le second échangeur thermique (20) de l'autre côté, constituent un ensemble d'échangeurs thermiques (36) comprenant un canal d'écoulement d'air (34) et un ou deux canaux de fluide frigorigène (42, 44, 46).
PCT/EP2012/072690 2011-11-21 2012-11-15 Sèche-linge équipé d'un système de pompe à chaleur WO2013075997A1 (fr)

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CN201280057032.4A CN103946441B (zh) 2011-11-21 2012-11-15 具有热泵系统的衣物干燥机

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EP11189889.6A EP2594688B1 (fr) 2011-11-21 2011-11-21 Sèche-linge avec système de pompe à chaleur
EP11189889.6 2011-11-21

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KR102302326B1 (ko) * 2014-10-28 2021-09-15 엘지전자 주식회사 의류처리장치
CN106245266A (zh) * 2016-08-30 2016-12-21 无锡小天鹅股份有限公司 衣物烘干系统和具有其的干衣机、洗干一体机
CN108468193B (zh) * 2018-04-28 2023-12-19 海信冰箱有限公司 一种热泵干衣机
DE102019214687A1 (de) * 2019-09-25 2021-03-25 BSH Hausgeräte GmbH Gerät zum Trocknen von Wäsche und Verfahren zum Betreiben eines solchen Geräts

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DE202006018205U1 (de) * 2006-11-06 2007-02-15 V-Zug Ag Wäschetrockner mit Zusatzwärmetauscher
WO2009016173A1 (fr) * 2007-08-02 2009-02-05 Arcelik Anonim Sirketi Machine à laver/sécheuse
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WO2011080045A1 (fr) 2009-12-22 2011-07-07 BSH Bosch und Siemens Hausgeräte GmbH Appareil domestique doté d'un circuit de pompe à chaleur
EP2385169A1 (fr) * 2010-05-03 2011-11-09 Electrolux Home Products Corporation N.V. Machine à laver avec système de pompe à chaleur et procédé de fonctionnement de la machine à laver

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DE202006018205U1 (de) * 2006-11-06 2007-02-15 V-Zug Ag Wäschetrockner mit Zusatzwärmetauscher
WO2009016173A1 (fr) * 2007-08-02 2009-02-05 Arcelik Anonim Sirketi Machine à laver/sécheuse
EP2261416A1 (fr) * 2009-06-09 2010-12-15 Electrolux Home Products Corporation N.V. Échangeur thermique pour séchoir, spécialement pour un séchoir domestique
WO2011080045A1 (fr) 2009-12-22 2011-07-07 BSH Bosch und Siemens Hausgeräte GmbH Appareil domestique doté d'un circuit de pompe à chaleur
EP2385169A1 (fr) * 2010-05-03 2011-11-09 Electrolux Home Products Corporation N.V. Machine à laver avec système de pompe à chaleur et procédé de fonctionnement de la machine à laver

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EP2594688B1 (fr) 2016-08-31
CN103946441A (zh) 2014-07-23
CN103946441B (zh) 2016-12-14
EP2594688A1 (fr) 2013-05-22

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