EP1550829A1 - Appareil de sechage - Google Patents

Appareil de sechage Download PDF

Info

Publication number
EP1550829A1
EP1550829A1 EP03753945A EP03753945A EP1550829A1 EP 1550829 A1 EP1550829 A1 EP 1550829A1 EP 03753945 A EP03753945 A EP 03753945A EP 03753945 A EP03753945 A EP 03753945A EP 1550829 A1 EP1550829 A1 EP 1550829A1
Authority
EP
European Patent Office
Prior art keywords
radiator
evaporator
air
refrigerant
drying apparatus
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Withdrawn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
EP03753945A
Other languages
German (de)
English (en)
Other versions
EP1550829A4 (fr
Inventor
Fumitoshi Nishiwaki
Yuichi Yakumaru
Tomoichiro Tamura
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.)
Panasonic Holdings Corp
Original Assignee
Matsushita Electric Industrial Co Ltd
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 Matsushita Electric Industrial Co Ltd filed Critical Matsushita Electric Industrial Co Ltd
Publication of EP1550829A1 publication Critical patent/EP1550829A1/fr
Publication of EP1550829A4 publication Critical patent/EP1550829A4/fr
Withdrawn legal-status Critical Current

Links

Images

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
    • D06F58/20—General details of domestic laundry dryers 
    • D06F58/24—Condensing arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
    • F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
    • F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
    • F24F3/153—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification with subsequent heating, i.e. with the air, given the required humidity in the central station, passing a heating element to achieve the required temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F26—DRYING
    • F26B—DRYING SOLID MATERIALS OR OBJECTS BY REMOVING LIQUID THEREFROM
    • F26B21/00—Arrangements or duct systems, e.g. in combination with pallet boxes, for supplying and controlling air or gases for drying solid materials or objects
    • F26B21/06—Controlling, e.g. regulating, parameters of gas supply
    • F26B21/08—Humidity
    • F26B21/086—Humidity by condensing the moisture in the drying medium, which may be recycled, e.g. using a heat pump cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide

Definitions

  • the present invention relates to a drying apparatus with a heat pump apparatus that is constructed by circularly connecting a compressor, a radiator, a throttle apparatus and an evaporator.
  • the quantity of heat required to dry clothes is converted from electric energy with an electric heater. Since the quantity of heat has a limitation due to a current capacity of an outlet for home use, it becomes an obstacle to shorten the time required to dry clothes. Further, since the heat used to dry the clothes is discharged to the outside thereof without reuse, there is wasted energy.
  • FIG. 13 is a conventional drying apparatus disclosed in Japanese Patent Application Laid-open No. H7-178289.
  • a rotation drum 122 is rotatably provided in a drying apparatus body 121 and is a dry room for drying clothes 136 therein.
  • the rotation drum 122 is operated by a motor 127 through a drum belt 135.
  • a blower 123 sends drying air in a flow direction as indicated by arrows from the rotation drum 122 to a circulation duct 126 through a filter 124 and a rotation drum-side air intake 125.
  • the blower 123 is operated by the motor 127 through a fan belt 128.
  • an evaporator 129 provided within the circulation duct 126 cools and dehumidifies the drying air by evaporating a refrigerant, and a condenser 130 heats the drying air flowing in the circulation duct 126 by condensing the refrigerant.
  • the heated drying air is introduced into the circulation duct 126 again, and returns to the dry room.
  • a part of the drying air is discharged out of the drying apparatus body 121 through an exhaust port 134.
  • a compressor 131 generates a pressure difference in the refrigerant, and an expansion mechanism 132 constituted from a capillary tube or the like maintains the pressure difference of the refrigerant.
  • the heat pump apparatus is constructed by connecting the evaporator 129, the condenser 130, the compressor 131 and the expansion mechanism 132 in this order via pipes 133 through which the refrigerant flows.
  • HCFC refrigerant refrigerant including toms of chlorine, hydrogen, fluorine and carbon in its molecule
  • HFC refrigerant refrigerant including atoms of hydrogen, fluorine and carbon in its molecule
  • CO 2 natural refrigerant
  • Required electric energy can be reduced by switching from heating by means of an electric heater to heating by means of a heat pump.
  • it is an essential condition to provide a compressor, a condenser, an expansion mechanism and an evaporator constituting the refrigeration cycle, at least.
  • a drying apparatus in which an electric heater is used and such a drying apparatus has a large size, there is a problem to miniaturize such a drying apparatus.
  • quantity of heat discharged from the condenser to drying air is quantity of heat adding the quantity of heat corresponding to electric energy consumed in the compressor to quantity of heat drawn from the drying air in the evaporator.
  • the present invention has been accomplished to solve the conventional problems described above, and it is an object of the invention to provide a heat pump type drying apparatus in which when a refrigerant which can be brought into the supercritical state on the radiating side of the refrigeration cycle such as CO 2 is used, enlargement of the apparatus can be prevented and high efficiency is realized.
  • a first aspect of the present invention provides a drying apparatus including: a heat pump apparatus having a compressor, a radiator, a throttle apparatus and an evaporator connected in this order via pipes through which a refrigerant is circulated; a dry room wherein air heated in the radiator is introduced into the dry room, the air dried in the dry room is dehumidified by the evaporator, and the air dehumidified in the evaporator is reheated in the radiator; and a sprinkler mechanism for dropping or spraying water into the radiator.
  • the sprinkler mechanism drops or sprays drain water generated by dehumidifying the air in the evaporator.
  • the drying apparatus further includes a collection mechanism for collecting moisture or water included in the air between the evaporator and the radiator.
  • the drying apparatus further includes a pump, wherein the evaporator and the radiator are respectively constituted from a heat transfer tube and a fin, and wherein drain water generated by dehumidifying the air in the evaporator is drawn by the pump and the sprinkler mechanism drops or sprays the drain water into the radiator.
  • a fifth aspect of the present invention provides a drying apparatus including: a heat pump apparatus having a compressor, a radiator, a throttle apparatus and an evaporator connected in this order via pipes through which a refrigerant is circulated, the evaporator being provided above the radiator; a dry room wherein air heated in the radiator is introduced into the dry room, the air dried in the dry room is dehumidified by the evaporator, and the air dehumidified in the evaporator is reheated in the radiator, drain water being generated by dehumidifying the air in the evaporator; and a sprinkler mechanism for dropping or spraying the drain water into the radiator.
  • the sprinkler mechanism drops the drain water into the radiator by means of gravity of the drain water or force of wind.
  • the evaporator in the drying apparatus of the fifth aspect, includes a fin having a lower end surface with respect to the direction of gravity, the lower end surface having a saw-toothed structure.
  • the evaporator in the drying apparatus of the sixth aspect, includes a fin having a fin base, the fin being a corrugated fin in which the fin base is folded.
  • the drying apparatus further includes a pump, wherein the evaporator and the radiator are respectively constituted from a heat transfer tube and a fin, and wherein drain water generated by dehumidifying the air in the evaporator is drawn by the pump and the sprinkler mechanism drops or sprays the drain water into the radiator.
  • the drying apparatus further includes a collection mechanism for collecting moisture or water included in the air between the evaporator and the radiator.
  • An eleventh aspect of the present invention provides a drying apparatus including: a heat pump apparatus having a compressor, a radiator, a throttle apparatus, a first evaporator and a second evaporator connected in this order via pipes through which a refrigerant is circulated; a dry room wherein air heated in the radiator is introduced into the dry room, the air dried in the dry room is dehumidified by the first and second evaporators, and the air dehumidified in the first and second evaporators is reheated in the radiator; a drainage mechanism for draining drain water generated by dehumidifying the air in the first evaporator; and a sprinkler mechanism for dropping or spraying drain water generated by dehumidifying the air in the second evaporator into the radiator.
  • the drying apparatus further comprising a collection mechanism for collecting moisture or water included in the air between the second evaporator and the radiator.
  • the heat pump apparatus further has a bypass circuit through which the refrigerant bypasses the second evaporator.
  • the heat pump apparatus sets the temperature of the refrigerant run into the radiator to the temperature of boiling water or more.
  • the heat pump apparatus has a high pressure side and is constructed to operate so that the pressure of the high pressure side thereof becomes supercritical pressure.
  • carbon dioxide is used as the refrigerant.
  • FIG. 1 is a block diagram of a drying apparatus according to a first embodiment of the present invention.
  • a reference number 31 represents a compressor
  • a reference number 32 represents a radiator
  • a reference number 33 represents an expansion valve (expansion mechanism)
  • a reference number 34 represents an evaporator.
  • a heat pump apparatus is constructed by connecting these constituent elements to one another in this order through pipes and charging a refrigerant thereinto.
  • a refrigerant which can be brought into the supercritical state on the radiation side (from a discharge section of the compressor 31, to the radiator 32 and to an inset section of the expansion mechanism 33) such as a CO 2 refrigerant is charged thereinto.
  • a reference number 36 represents a subject to be dried (for example, clothes, a bathroom space, or the like), a reference number 37 represents a blower fan, a reference number 38 represents a heat exchanger for roughly drawing heat from drying air, a reference number 39 represents a blower fan for the heat exchanger 38 for roughly drawing heat from the drying air, and a reference number 40 represents a pan for drain water.
  • the evaporator 34 is provided at the windward side of the radiator 32 and above the radiator 32 in the direction of gravity.
  • solid arrows indicate the flow of the refrigerant
  • hollow arrows indicate the flow of the drying air
  • a hollow arrow with diagonal lines indicates the flow of outside air.
  • the refrigerant is compressed by the compressor 31 and brought into a high temperature and high pressure state.
  • the refrigerant is heat-exchanged in the radiator 32 with drying air received from the evaporator 34, and the refrigerant heats the drying air. This makes the refrigerant cooled.
  • the refrigerant is then decompressed by the expansion mechanism 33, and is brought into a low temperature and low pressure state.
  • the refrigerant is heat-exchanged with drying air which passes through the subject 36 by the evaporator 34, thereby cooling the drying air.
  • the drying air cooled and dehumidified by the evaporator 34 is heated by the radiator 32, and is brought into a high temperature and low moisture state.
  • the drying air brought into the high temperature and low moisture state removes moisture or water from the subject 36 and is brought into a humid state when the drying air is forcibly brought into contact with the subject 36 by the blower fan 37.
  • the drying air is again cooled and dehumidified by the evaporator 34.
  • the refrigerant is heat-exchanged with the humid drying air which passes through the subject 36 by the evaporator 34, thereby cooling the drying air.
  • the moisture or water included in the drying air is condensed on the surface of a fin of the evaporator 34, and resulting drain water is dropped into the radiator 32 using gravity thereof and shearing force due to blowing. Since the drying apparatus of the present embodiment has a structure described above, sensible heat exchange with the drying air and latent heat exchange with the drain water are carried out in the radiator 32, thereby accelerating heat transfer.
  • the heat transfer in the radiator 32 is accelerated, the temperature of the refrigerant is lowered at an outlet of the radiator 32 and cooling capacity of the evaporator 34 is increased, whereby energy conservation can be realized.
  • the refrigerant is brought into a near-critical refrigeration cycle.
  • the temperature of the refrigerant is lowered at the outlet of the radiator 32, and this results in the effort that it is possible to improve the refrigeration cycle COP largely, whereby it is possible to realize energy conservation further.
  • the drying apparatus utilizes near critical refrigeration cycle in which a CO 2 refrigerant is used, in comparison with the case of the subcritical refrigeration cycle in which a conventional HFC refrigerant is used, it is possible heighten heat exchange efficiency in which the high temperature CO 2 refrigerant is heat-exchanged with the drying air in the radiator 32, whereby it is possible to raise the temperature of the drying air to a high temperature. Therefore, the ability to remove moisture or water from the subject 36 can be increased, whereby the drying operation can be carried out in a short time.
  • the expansion valve is used as the expansion mechanism in the present embodiment, the same effect can be obtained even if a capillary tube is used as the expansion mechanism.
  • the CO 2 refrigerant which can be brought into the supercritical state on the radiation side is used in the present embodiment.
  • the conventional HFC refrigerant by dropping drain water generated in an evaporator into a radiator, the amount of heat exchange in the radiator can be increased in the same manner. Therefore, it is possible to miniaturize the size of the radiator, and this makes it possible to miniaturize the heat pump apparatus.
  • FIG. 2 is a block diagram of a drying apparatus according to a second embodiment of the present invention.
  • FIG. 3 is an enlarged view of a main portion of a fin constituting an evaporator according to the second embodiment of the present invention.
  • a reference number 31 represents a compressor
  • a reference number 42 represents a radiator
  • a reference number 33 represents an expansion valve (expansion mechanism)
  • a reference number 44 represents an evaporator.
  • a heat pump apparatus is constructed by connecting these constituent elements to one another in this order through pipes and charging a refrigerant thereinto.
  • a CO 2 refrigerant which can be brought into the supercritical state on the radiation side is charged thereinto.
  • Differences between the first and second embodiments are a point that the evaporator 44 and the radiator 42 are provided on a slant and a point that a saw-toothed structure 46 is formed on a lower end surface of a fin 45 constituting the evaporator 44 with respect to the direction of gravity.
  • the point that the evaporator 44 is provided at the windward side of the radiator 42 and above the radiator 42 in the direction of gravity is the same.
  • solid arrows indicate the flow of the refrigerant
  • hollow arrows indicate the flow of the drying air
  • a hollow arrow with diagonal lines indicates the flow of outside air.
  • the refrigerant is compressed by the compressor 31 and brought into a high temperature and high pressure state.
  • the refrigerant is heat-exchanged in the radiator 42 with drying air received from the evaporator 44, and the refrigerant heats the drying air. This makes the refrigerant cooled.
  • the refrigerant is then decompressed by the expansion mechanism 33, and is brought into a low temperature and low pressure state.
  • the refrigerant is heat-exchanged with drying air which passes through the subject 36 by the evaporator 44, thereby cooling the drying air.
  • the drying air cooled and dehumidified by the evaporator 44 is heated by the radiator 42, and is brought into a high temperature and low moisture state.
  • the drying air brought into the high temperature and low moisture state removes moisture or water from the subject 36 and is brought into a humid state when the drying air is forcibly brought into contact with the subject 36 by the blower fan 37.
  • the drying air is again cooled and dehumidified by the evaporator 44.
  • the evaporator 44 and the radiator 42 are provided on a slant, it is possible to reduce the installation space of the heat exchanger, and this makes it possible to miniaturize a heat pump type drying apparatus.
  • the saw-toothed structure 46 (convex portion 46a) is formed on the lower end surface of the fin 45 with respect to the direction of gravity, drain water generated and condensed by dehumidifying the drying air on the surface of the fin 45 of the evaporator 44 is concentrated on the convex portions 46a to form droplets 47.
  • the droplets 47 grow up and drop into the radiator 42 using gravity thereof and shearing force due to blowing.
  • the droplets 47 are formed by concentrating the drain water on the convex portions 46a in this way, there is no instability of places where the droplets 47 are formed.
  • the convex portions 46a By uniformly forming the convex portions 46a over the evaporator 44 on which the droplets 47 are formed, since the droplets 47 drop into the radiator 42 uniformly, a liquid film of the drain water is formed over the radiator 42 uniformly.
  • sensible heat exchange with the drying air and latent heat exchange with the drain water are carried out in the radiator 42, thereby accelerating heat transfer.
  • the amount of heat exchange is increased and heat transfer to the refrigerant that flows inside the radiator 42 is accelerated, it is possible to further miniaturize the size of the radiator 42. Therefore, it is possible to miniaturize the heat pump apparatus.
  • the heat transfer in the radiator 42 is accelerated, the temperature of the refrigerant is lowered at an outlet of the radiator 42 and cooling capacity of the evaporator 44 is increased, whereby energy conservation can be realized.
  • the refrigerant is brought into a near-critical refrigeration cycle which can be brought into the supercritical state on the radiation side of the drying apparatus and the temperature of the refrigerant is lowered at the outlet of the radiator 42, this results in the effect that it is possible to improve the refrigeration cycle COP largely, whereby it is possible to realize energy conservation further.
  • FIGS. 4(a) and 4(b) show a cross-sectional view and an enlarged view of a main portion of a fin constituting an evaporator of a drying apparatus according to another embodiment of the present invention, respectively.
  • a fin 55 constituting the evaporator is a corrugated fin provided with folded portions 56.
  • the ridgeline direction of the folded portions 56 is substantially the direction of gravity. Since the folded portions 56 are formed in the direction of gravity of the fin 55 in this manner, drain water generated and condensed by dehumidifying the drying air on the surface of the fin 55 of the evaporator 44 is concentrated on the troughs 57 of the folded portions 56 to form droplets 47.
  • the droplets 47 are formed by concentrating the drain water on the troughs 57 in this way, there is no instability of places where the droplets 47 are formed.
  • the droplets 47 drop into the radiator 42 uniformly, a liquid film of the drain water is formed over the radiator 42 uniformly.
  • sensible heat exchange with the drying air and latent heat exchange with the drain water are carried out in the radiator 42, thereby accelerating heat transfer.
  • the amount of heat exchange is increased and heat transfer to the refrigerant that flows inside the radiator 42 is accelerated, it is possible to further miniaturize the size of the radiator 42. Therefore, it is possible to miniaturize the heat pump apparatus.
  • the drying apparatus in comparison with the saw-toothed structure is formed on the lower end surface in the direction of gravity of the fin, it is possible to increase a heat transfer area of the fin extremely. For this reason, it is possible to improve the ability of heat transfer of the evaporator. As a result, since the drying apparatus has the effect that it is possible to improve the refrigeration cycle COP largely as well as ability to dehumidify drying air can be improved, it is possible to realize energy conservation further.
  • FIG. 5 is a block diagram of a drying apparatus according to a third embodiment of the present invention.
  • a reference number 31 represents a compressor
  • a reference number 62 represents a radiator
  • a reference number 33 represents an expansion valve (expansion mechanism)
  • a reference number 64 represents an evaporator.
  • a heat pump apparatus is constructed by connecting these constituent elements to one another in this order through pipes and charging a refrigerant thereinto. As the refrigerant, a CO 2 refrigerant which can be brought into the supercritical state on the radiation side is charged thereinto.
  • Difference between the first and third embodiments is a point that drain water condensed and generated by dehumidifying drying air in the evaporator 64 is received by a pan for drain water 65, the drain water collected in the drain water pan 65 is drawn by a pump 66, and a spray mechanism 67 is provided to spray the drain water into the radiator 62.
  • FIG. 5 solid arrows indicate the flow of the refrigerant, hollow arrows indicate the flow of the drying air, and a hollow arrow with diagonal lines indicates the flow of outside air.
  • the drying apparatus is constituted so that the drying air flows from the lower side of the subject 36 to be dried to the radiator 62 through the evaporator 64 in this order. Namely, the evaporator 64 is provided at the windward side of the radiator 62 and under the radiator 62.
  • the refrigerant is compressed by the compressor 31 and brought into a high temperature and high pressure state.
  • the refrigerant is heat-exchanged in the radiator 62 with drying air received from the evaporator 64, and the refrigerant heats the drying air. This makes the refrigerant cooled.
  • the refrigerant is then decompressed by the expansion mechanism 33, and is brought into a low temperature and low pressure state.
  • the refrigerant is heat-exchanged with the drying air which passes through the subject 36 by the evaporator 64, thereby cooling the drying air.
  • the drying air cooled and dehumidified by the evaporator 64 is heated by the radiator 62, and is then brought into a high temperature and low moisture state.
  • the drying air brought into the high temperature and low moisture state removes moisture or water from the subject 36 and is brought into a humid state when the drying air is forcibly brought into contact with the subject 36 by the blower fan 37.
  • the drying air is again cooled and dehumidified by the evaporator 64.
  • the drying apparatus has a structure in which the drain water condensed and generated by dehumidifying drying air in the evaporator 64 is received by a pan for drain water 65, the drain water collected in the drain water pan 65 is drawn by a pump 66, and a spray mechanism 67 is provided to spray the drain water into the radiator 62.
  • a spray mechanism 67 is provided to spray the drain water into the radiator 62.
  • the heat transfer in the radiator 62 is accelerated, the temperature of the refrigerant is lowered at an outlet of the radiator 62 and cooling capacity of the evaporator 64 is increased, whereby energy conservation can be realized.
  • the refrigerant is brought into a near-critical refrigeration cycle which can be brought into the supercritical state on the radiation side of the drying apparatus and the temperature of the refrigerant is lowered at the outlet of the radiator 62, this results in the effect that it is possible to improve the refrigeration cycle COP largely, whereby it is possible to realize energy conservation further.
  • the drain water condensed and generated by dehumidifying the drying air in the evaporator 64 is supplied to the radiator 62 by the pump 66, the same effect can be obtained even if no drain water but water supplied from the outside thereof is used.
  • the drying apparatus has a structure in which moisture or water is removed from the subject 36 to dry it by forcibly running the drying air from an upper side to a lower side with respect to the subject 36 so that the drying air is brought into contact with the subject 36.
  • the drying apparatus has a feature that it is easy to apply heat pump type drying apparatus to a vertical washer-dryer.
  • the structure in which the drying air is forcibly run from an upper side to a lower side with respect to the subject 36 has been described in the present embodiment, but the structure is not limited thereto. It should be noted that even though the drying apparatus has a structure in which the drying air is forcibly run from a lower side to an upper side with respect to the subject 36 as well as the first and second embodiments, the same effect can be obtained in case of supplying the drain water condensed and generated in the evaporator 64 to the radiator 62 by means of the pump 66.
  • FIG. 6 is a block diagram of a drying apparatus according to a fourth embodiment of the present invention.
  • a heat pump apparatus is constructed from a compressor 1, a radiator 2, a throttle apparatus 3 and an evaporator 4 connected to each other in this order via pipes through which a refrigerant is circulated as indicated by solid arrows.
  • the drying apparatus is provided with a dry room 5, a circulation duct 6, a blower fan 7, a sprinkler mechanism 8, a pan for drain water 9 and a collection mechanism 10.
  • the drying apparatus has a structure in which the drying air that circulates as indicated by hollow arrows M is delivered by means of the blower fan 7 to enter the circulation duct 6 from a lower side of the dry room 5, and then, the drying air passes through the evaporator 4 and the radiator 2 in this order to flow toward an upper side of the dry room 5.
  • the evaporator 4 is provided at the windward side of the radiator 2 and under the radiator 2.
  • the sprinkler mechanism 8 for supplying water from the outside through the pipes is provided at the leeward side of the radiator 2 and above the radiator 2 in the direction of gravity.
  • the drain water pan 9 is provided at the windward side of the evaporator 4 and under the evaporator 4 in the direction of gravity.
  • the drying apparatus has a structure in which the collection mechanism 10 is provided between the radiator 2 and the evaporator 4.
  • the refrigerant becomes a high temperature and high pressure state by being compressed by the compressor 1, and is heat-exchanged with the drying air got out of the evaporator 4 in the radiator 2, whereby the refrigerant is cooled by heating the drying air.
  • the refrigerant is then decompressed by the throttle apparatus 3, and is brought into a low temperature and low pressure state.
  • the refrigerant is heat-exchanged with the drying air which passes through the subject 16 by the evaporator 4, thereby cooling the drying air.
  • Moisture or water included in the drying air is condensed and dehumidified, thereby heating the refrigerant, and the refrigerant is again sucked into the compressor 31.
  • the drying air cooled and dehumidified by the evaporator 4 is heated by the radiator 2, and is then brought into a high temperature and low moisture state.
  • the drying air brought into the high temperature and low moisture state is delivered to the dry room 5 by the blower fan 7, and forcibly brought into contact with the subject 16.
  • the drying air is brought into a humid state by removing moisture or water from the subject 16 and is again cooled and dehumidified by the evaporator 4.
  • the sprinkler mechanism 8 drops or sprays water into the radiator 2 from the upper side thereof.
  • the drain water pan 9 receives the drain water dropped from the evaporator 4 to discharge the drain water collected in the drain water pan 9 to the outside of the drying apparatus.
  • the collection mechanism 10 brings the drying air between the radiator 2 and the evaporator 4 into contact with the low temperature outside air to collect moisture or water included in the drying air.
  • the drying apparatus has a structure in which the water is dropped or sprayed into the radiator 2 using the sprinkler mechanism 8.
  • the sprinkler mechanism 8 it is possible to sprinkle (or spray) the specific amount of water over the radiator 2 stably and uniformly.
  • a liquid film of the water is formed over the radiator 2 uniformly.
  • sensible heat exchange with the drying air and latent heat exchange with the water are carried out in the radiator 2, thereby accelerating heat transfer.
  • the amount of heat exchange in the radiator 2 is increased and heat transfer to the refrigerant that flows to the inside of the radiator 2 is accelerated, it is possible to further miniaturize the size of the radiator 2. Therefore, it is possible to miniaturize the heat pump apparatus.
  • the moisture or water condensed and generated by cooling and dehumidifying the drying air in the evaporator 4 drops on the drain water pan 9 to be discharged to the outside.
  • the collection mechanism 10 provided at the position where the moisture or water is brought into contact with the low temperature outside air and discharging it to the outside, it is possible to accelerate the removal of the moisture or water included in the subject 16.
  • the collection mechanism 10 may have a structure in which the moisture or water is not only brought into contact with the outside air, but also is forcibly cooled by a fan or the like, whereby it is possible to further accelerate the drying of the subject 16.
  • the heat transfer in the radiator 2 is accelerated, the temperature of the refrigerant is lowered at an outlet of the radiator 2 and cooling capacity of the evaporator 4 is increased, whereby energy conservation can be realized.
  • the refrigerant is brought into a near-critical refrigeration cycle which can be brought into the supercritical state on the radiation side of the refrigerant and the temperature of the refrigerant is lowered at the outlet of the radiator 2, this results in the effect that it is possible to improve the refrigeration cycle COP largely, whereby it is possible to realize energy conservation further.
  • the drying apparatus has a structure in which moisture or water is removed from the subject 16 to dry it by forcibly running the drying air from an upper side to a lower side with respect to the subject 16 so that the drying air is brought into contact with the subject 16.
  • the drying apparatus has a feature that it is easy to apply heat pump type drying apparatus to a vertical washer-dryer.
  • FIG. 7 is a block diagram of a drying apparatus according to a fifth embodiment of the present invention.
  • common constituent elements shown in the fourth embodiment of FIG. 6 are designated with the same reference numbers, and explanation thereof will be omitted.
  • the structure of the drying apparatus of the fifth embodiment is different from the structure of the fourth embodiment in the presence of a sprinkler mechanism 8a in which the drain water collected in the drain water pan 9 is pumped up by a pump 14 to supply it to the sprinkler mechanism 8a through a pipe to drop or spray it into the radiator 2.
  • the drying apparatus of the present embodiment since the low temperature drain water condensed and generated in the evaporator 4 is dropped or sprayed into the radiator 2, it is possible to reduce the pressure at the high pressure side of the heat pump apparatus by carrying out latent heat exchange with a larger difference of temperature from the refrigerant temperature in the radiator 2. Therefore, it is possible to reduce power requirement of the compressor 1, that is, to realize energy conservation of the heat pump apparatus.
  • FIG. 8 is a block diagram of a drying apparatus according to a sixth embodiment of the present invention.
  • common constituent elements shown in the fourth embodiment of FIG. 6 are designated with the same reference numbers, and explanation thereof will be omitted.
  • the structure of the drying apparatus of the sixth embodiment is different from the structure of the fourth embodiment in the ways of the structure for circulating the drying air and a sprinkler mechanism.
  • the drying apparatus of the present embodiment has a structure in which the drying air is delivered by means of the blower fan 7 to enter the circulation duct 6 from an upper side of the dry room 5, and then, the drying air passes through the evaporator 4 and the radiator 2 in this order to run in circle toward a lower side of the dry room 5.
  • the sprinkler mechanism is constructed so that the evaporator 4 is provided at the windward side of the radiator 2 and above the radiator 2 in the direction of gravity, and the drain water generated by dehumidification due to the evaporator 4 is dropped into the radiator 2 by its gravity or the force of wind.
  • the drain water pan 9 is constructed so that the drain water pan 9 is provided at the leeward side of the radiator 2 and under the radiator 2 in the direction of gravity, and the drain water that is dropped from the evaporator 4 and passed through the radiator 2 is collected in the drain water pan 9.
  • the refrigerant becomes a high temperature and high pressure state by being compressed by the compressor 1, and is heat-exchanged with the drying air got out of the evaporator 4 in the radiator 2, whereby the refrigerant is cooled by heating the drying air.
  • the refrigerant is then decompressed by the throttle apparatus 3, and is brought into a low temperature and low pressure state.
  • the refrigerant is heat-exchanged with the drying air which passes through the subject 16 by the evaporator 4, thereby cooling the drying air.
  • Moisture or water included in the drying air is condensed and dehumidified, thereby heating the refrigerant, and the refrigerant is again sucked into the compressor 1.
  • the drying air cooled and dehumidified by the evaporator 4 is heated by the radiator 2, and is then brought into a high temperature and low moisture state.
  • the drying air brought into the high temperature and low moisture state is delivered to the dry room 5 by the blower fan 7, and forcibly brought into contact with the subject 16.
  • the drying air is brought into a humid state by removing moisture or water from the subject 16 and is again cooled and dehumidified by the evaporator 4.
  • the drain water generated in the evaporator 4 is dropped into the radiator 2 from the upper side thereof with its gravity or the like by means of the sprinkler mechanism. Moreover, the drain water collected in the drain water pan 9 is discharged to the outside of the drying apparatus. Furthermore, in the same manner as the fourth embodiment, the collection mechanism 10 carries out the operation that the drying air flowing between the radiator 2 and the evaporator 4 is brought into contact with the low temperature outside air to collect moisture or water included in the drying air.
  • the refrigerant is heat-exchanged with the humid drying air which passes through the subject 16 by the evaporator 4, thereby cooling the drying air.
  • the moisture or water included in the drying air is condensed on the surface of a fin of the evaporator 4, and resulting drain water is dropped into the radiator 2 using gravity thereof and shearing force due to blowing.
  • the drying apparatus of the present embodiment has a structure described above, sensible heat exchange with the drying air and latent heat exchange with the drain water are carried out in the radiator 2, thereby accelerating heat transfer.
  • the amount of heat exchange at the radiator 2 is increased and heat transfer to the refrigerant that flows inside the radiator 2 is accelerated, it is possible to miniaturize the size of the radiator 2 to the same level as the size of the evaporator 4.
  • the sprinkler mechanism having the structure in which the drain water generated in the evaporator 4 is used has been described in the sixth embodiment, this structure is not limited thereto. It should be noted that the same effect can be achieved even in the case of a sprinkler mechanism having a structure in which supply of water from the outside or pumping power is used as well as the fourth and fifth embodiments.
  • FIG. 9 is a block diagram of a drying apparatus according to a seventh embodiment of the present invention.
  • common constituent elements shown in the sixth embodiment of FIG. 8 are designated with the same reference numbers, and explanation thereof will be omitted.
  • the structure of the drying apparatus of the seventh embodiment is different from the structure of the sixth embodiment in the way that the drying apparatus is provided with first and second evaporators 4a and 4b, first and second circulation ducts 6a and 6b, and first and second pans for drain water 9a and 9b.
  • the drying apparatus of the present embodiment has a structure in which the drying air is delivered by means of the blower fan 7 to enter the first circulation duct 6a from the upper side of the dry room 5, and passes through the first evaporator 4a, and then, the drying air enters the second circulation duct 6b and passes through the second evaporator 4b and the radiator 2 in this order to run in circle toward a lower side of the dry room 5.
  • first evaporator 4a is provided at the windward side of the second evaporator 4b.
  • the drainage mechanism is constructed so that the first drain water pan 9a is provided at the leeward side of the first evaporator 4a and under the first evaporator 4a in the direction of gravity, and the drain water generated by dehumidification due to the first evaporator 4a is received by the first drain water pan 9a to discharge the collected drain water to the outside of the drying apparatus.
  • the sprinkler mechanism is constructed so that the second evaporator 4b is provided at the windward side of the radiator 2 and above the radiator 2 in the direction of gravity, and the drain water generated by dehumidification due to the second evaporator 4b is dropped into the radiator 2 by its gravity or the force of wind.
  • the second drain water pan 9b is constructed so that the second drain water pan 9b is provided at the leeward side of the radiator 2 and under the radiator 2 in the direction of gravity, and the drain water that is dropped from the second evaporator 4b and passed through the radiator 2 is collected in the second drain water pan 9b.
  • the refrigerant becomes a high temperature and high pressure state by being compressed by the compressor 1, and is heat-exchanged with the drying air got out of the second evaporator 4b in the radiator 2, whereby the refrigerant is cooled by heating the drying air.
  • the refrigerant is then decompressed by the throttle apparatus 3 to be brought into a low temperature and low pressure state.
  • the refrigerant is heat-exchanged with the drying air which passes through the subject 16 by the first and second evaporators 4a and 4b, thereby cooling the drying air.
  • Moisture or water included in the drying air is condensed and dehumidified, thereby heating the refrigerant, and the refrigerant is again sucked into the compressor 1.
  • the drying air cooled and dehumidified by the first and second evaporators 4a and 4b is heated by the radiator 2, and is then brought into a high temperature and low moisture state.
  • the drying air brought into the high temperature and low moisture state is delivered to the dry room 5 by the blower fan 7, and forcibly brought into contact with the subject 16.
  • the drying air is brought into a humid state by removing moisture or water from the subject 16 and is again cooled and dehumidified by the first and second evaporators 4a and 4b.
  • the drain water generated in the second evaporator 4b is dropped into the radiator 2 from the upper side thereof with its gravity or the like by means of the sprinkler mechanism. Moreover, the drain water collected in the second drain water pan 9b is discharged to the outside of the drying apparatus. Furthermore, in the same manner as the fifth embodiment, the collection mechanism 10 carries out the operation that the drying air flowing between the second evaporator 4b and the radiator 2 is brought into contact with the low temperature outside air to collect moisture or water included in the drying air.
  • the first drain water pan 9a is provided under the first evaporator 4a, and the radiator 2 is provided under the second evaporator 4b.
  • the humid drying air which passes through the subject 16 is heat-exchanged with the first evaporator 4a, and the moisture or water condensed and generated by the first evaporator 4a is dropped on the first drain water pan 9a to be discharged to the outside of the drying apparatus.
  • the drying air after heat exchange with the first evaporator 4a is heat-exchanged with the second evaporator 4b.
  • FIG. 10 is a block diagram of a drying apparatus according to an eighth embodiment of the present invention.
  • FIG. 10 common constituent elements shown in the seventh embodiment of FIG. 9 are designated with the same reference numbers, and explanation thereof will be omitted.
  • the structure of the drying apparatus of the eighth embodiment is different from the structure of the seventh embodiment in the way that the drying apparatus is provided with a bypass circuit.
  • the bypass circuit is constructed from a three-way valve 12 provided between the first evaporator 4a and the second evaporator 4b and a bypass pipe 13 that connects the three-way valve 12 to the inlet of the compressor 1.
  • the refrigerant becomes a high temperature and high pressure state by being compressed by the compressor 1, and is heat-exchanged with the drying air got out of the second evaporator 4b in the radiator 2, whereby the refrigerant is cooled by heating the drying air.
  • the refrigerant is then decompressed by the throttle apparatus 3 to be brought into a low temperature and low pressure state. Further, after the refrigerant is heat-exchanged with the drying air which passes through the subject 16 by the first evaporator 4a to be heated, the refrigerant is delivered toward the A direction by the three-way valve 12. Then, the refrigerant flows into the second evaporator 4b and is heat-exchanged with the drying air again. Moisture or water included in the drying air is condensed and dehumidified, thereby heating the refrigerant, and the refrigerant is sucked into the compressor 1.
  • the drying air cooled and dehumidified by the first and second evaporators 4a and 4b is heated by the radiator 2, and is then brought into a high temperature and low moisture state.
  • the drying air brought into the high temperature and low moisture state is delivered to the dry room 5 by the blower fan 7, and forcibly brought into contact with the subject 16.
  • the drying air is brought into a humid state by removing moisture or water from the subject 16 and is again cooled and dehumidified by the first and second evaporators 4a and 4b.
  • the refrigerant is heat-exchanged with the first evaporator 4a and delivered toward the bypass pipe 13, and the refrigerant is then sucked into the compressor 1. Therefore, since the refrigerant is delivered to the second evaporator 4b, drain water is not dropped into the radiator 2, whereby it is possible to prevent moisture or water from being reevaporated in the radiator 2. By repeating the operation described above, it is possible to carry out the drying operation for removing moisture or water from the subject 16 entered into the inside of the dry room 5.
  • T minutes for example, 60 minutes
  • the bypass circuit constructed from the three-way valve 12 and the bypass pipe 13 is provided, and by switching the flow direction of the refrigerant with the bypass circuit, it is possible to prevent moisture or water from being reevaporated in the radiator 2 after predetermined amount of time elapses from the start time of operation of the heat pump. Therefore, it is possible to carry out removal of moisture or water from the subject 16 surely.
  • the structure in which the temperature of the refrigerant run into the radiator 2 of the heat pump apparatus is set to the temperature of boiling water or more may be adopted.
  • the present structure it is possible to heat the temperature of the drain water which drops into the radiator 2 to the temperature of boiling water or more. This makes it possible to prevent or reduce growth of mold or the like that gets on the fin of the radiator 2.
  • FIG. 11 is a drawing which shows temperature changes in refrigerant and air in the radiator of a drying apparatus according to a ninth embodiment of the present invention in the case of using a refrigerant (for example, CO 2 ) in which the pressure at the high pressure side can be brought into the supercritical state in the heat pump apparatus of any one of the fourth to ninth embodiments.
  • FIG. 12 is a drawing which shows temperature changes in refrigerant and air in the radiator of the drying apparatus in case of using a CFC refrigerant.
  • the refrigerant in the case of the CFC refrigerant, the refrigerant is heat-exchanged with the air in the radiator 2 so as to state-change from a superheated state to a supercooled state through a gas-liquid two-phase state, whereby the temperature at the air outlet of the radiator 2 rises to the point C.
  • the temperatures To at the refrigerant inlet in both cases are the same, the temperature D at the air outlet in the case of using the CO 2 refrigerant can be heightened in comparison with the temperature C at the air outlet in the case of using the CFC refrigerant. Therefore, the ability to remove moisture or water from the subject 16 can be increased, and this makes it possible to carry out the drying operation in a short time.
  • the drying apparatus of the ninth embodiment by operating the drying apparatus so that the pressure at the high pressure side of the heat pump apparatus becomes supercritical pressure, it is possible to heighten the temperature of the drying air further. Therefore, it is possible to shorten the drying time, and the operation of the drying apparatus can be carried out with high efficiency.
  • drying apparatus explained in any one of the embodiments described above can be utilized for a drying apparatus for tableware, a drying apparatus for garbage disposal or the like in addition to a drying apparatus for clothes or a bathroom.
  • the drying apparatus of the present invention since the drying apparatus has a structure in which the water is dropped or sprayed into the radiator using the sprinkler mechanism, sensible heat exchange with the drying air and latent heat exchange with the water are carried out in the radiator. As a result, since the amount of heat exchange in the radiator is increased and heat transfer to the refrigerant that flows to the inside of the radiator is accelerated, it is possible to further miniaturize the size of the radiator, and this makes it possible to miniaturize the heat pump apparatus.
  • the drying apparatus of the present invention since the low temperature drain water condensed and generated in the evaporator is dropped or sprayed into the radiator, it is possible to reduce the pressure at the high pressure side of the heat pump apparatus by carrying out latent heat exchange with a larger difference of temperature from the refrigerant temperature in the radiator. Therefore, it is possible to reduce power requirement of the compressor, that is, to realize energy conservation of the heat pump apparatus.
  • the drying apparatus of the present invention by taking the structure in which the drain water condensed and generated in the evaporator is dropped into the radiator using gravity thereof and shearing force due to blowing, since it is possible to bring the water into contact with the radiator only by gravity thereof and shearing force due to blowing without supply of water and pumping power, it is possible to realize energy conservation further.
  • the drying apparatus of the present invention by dividing the evaporator into the first and second evaporators, it is possible to surely discharge the moisture or water condensed and generated in the first evaporator to the outside from the drain water pan. Therefore, since it is possible to collect the moisture or water that cannot be condensed by the collection mechanism perfectly more surely, it is possible to shorten the time required to remove the moisture or water from the subject and to realize energy conservation further.
  • the three-way valve is provided between the first and second evaporators, and by switching the flow direction of the refrigerant with the three-way valve, it is possible to prevent moisture or water from being reevaporated in the radiator after predetermined amount of time from the start time of operation of the heat pump. Therefore, it is possible to carry out removal of moisture or water from the subject surely.
  • the drying apparatus of the present invention since the temperature of the drain water that drops into the radiator is heated by heating the refrigerant that flows in the radiator to the temperature of boiling water or more, it is possible to prevent or reduce growth of mold or the like that gets on the fin of the radiator.
  • the drying apparatus of the present invention by operating the drying apparatus so that the pressure at the high pressure side of the heat pump apparatus becomes supercritical pressure, it is possible to heighten the temperature of the drying air further. Therefore, it is possible to shorten the drying time further, and the operation of the drying apparatus can be carried out with high efficiency.

Landscapes

  • Engineering & Computer Science (AREA)
  • Textile Engineering (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Detail Structures Of Washing Machines And Dryers (AREA)
  • Drying Of Solid Materials (AREA)
  • Accessory Of Washing/Drying Machine, Commercial Washing/Drying Machine, Other Washing/Drying Machine (AREA)
  • Devices For Blowing Cold Air, Devices For Blowing Warm Air, And Means For Preventing Water Condensation In Air Conditioning Units (AREA)
EP03753945A 2002-09-26 2003-09-25 Appareil de sechage Withdrawn EP1550829A4 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
JP2002280982A JP2004116899A (ja) 2002-09-26 2002-09-26 ヒートポンプ式乾燥機
JP2002280982 2002-09-26
JP2003179188A JP2005016779A (ja) 2002-09-26 2003-06-24 乾燥装置
JP2003179188 2003-06-24
PCT/JP2003/012189 WO2004029516A1 (fr) 2002-09-26 2003-09-25 Appareil de sechage

Publications (2)

Publication Number Publication Date
EP1550829A1 true EP1550829A1 (fr) 2005-07-06
EP1550829A4 EP1550829A4 (fr) 2006-12-27

Family

ID=32044623

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03753945A Withdrawn EP1550829A4 (fr) 2002-09-26 2003-09-25 Appareil de sechage

Country Status (5)

Country Link
US (1) US20050204755A1 (fr)
EP (1) EP1550829A4 (fr)
JP (2) JP2004116899A (fr)
CN (1) CN1695029A (fr)
WO (1) WO2004029516A1 (fr)

Cited By (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007023510A1 (fr) 2005-08-25 2007-03-01 Renzacci S.P.A. Industria Lavatrici Sèche-linge
WO2007074040A1 (fr) * 2005-12-29 2007-07-05 BSH Bosch und Siemens Hausgeräte GmbH Appareil menager pour laver des vetements
EP1811077A1 (fr) * 2006-01-20 2007-07-25 SANYO ELECTRIC Co., Ltd. Machine à sécher
EP1811076A1 (fr) * 2006-01-20 2007-07-25 SANYO ELECTRIC Co., Ltd. Sécheur
WO2008004802A3 (fr) * 2006-07-04 2008-03-13 Lg Electronics Inc Appareil de blanchissage
WO2008004803A3 (fr) * 2006-07-04 2008-03-13 Lg Electronics Inc Unité d'adoucissement de blanchissage et appareil de blanchissage équipé de celle-ci
WO2008155263A1 (fr) * 2007-06-18 2008-12-24 BSH Bosch und Siemens Hausgeräte GmbH Sécheur à condensation muni d'une pompe à chaleur, et procédé pour le faire fonctionner
WO2009077336A1 (fr) * 2007-12-18 2009-06-25 BSH Bosch und Siemens Hausgeräte GmbH Sèche-linge et procédé de séchage de linge
EP2075368A1 (fr) * 2007-12-27 2009-07-01 BSH Bosch und Siemens Hausgeräte GmbH Procédé d'élimination d'un condensat dans un appareil ménager d'entretien du linge
CH699018B1 (de) * 2006-01-27 2010-01-15 V Zug Ag Wäschetrockner mit Kohlendioxid-Wärmepumpe.
EP2203585A2 (fr) * 2007-09-04 2010-07-07 Lg Electronics Inc. Déshumidificateur pour sèche-linge
WO2009020311A3 (fr) * 2007-08-03 2010-11-11 Lg Electronics Inc. Dispositif de traitement de vêtements et procédé associé
WO2009123402A3 (fr) * 2008-04-01 2010-12-02 Lg Electronics Inc. Machine de traitement de linge
WO2011039251A1 (fr) * 2009-10-01 2011-04-07 Arcelik Anonim Sirketi Sèche-linge à pompe à chaleur
ITPR20130106A1 (it) * 2013-12-30 2015-07-01 Indesit Co Spa Elettrodomestico di asciugatura panni.
EP3023533A1 (fr) * 2014-11-20 2016-05-25 LG Electronics Inc. Appareil de traitement de vêtements avec cycle à pompe à chaleur
USD782059S1 (en) 2014-11-28 2017-03-21 3M Innovative Properties Company Mixing screw for dental impression material
USD782692S1 (en) 2014-11-28 2017-03-28 3M Innovative Properties Company Mixing nozzle for dental impression material
WO2017174766A1 (fr) * 2016-04-08 2017-10-12 Arcelik Anonim Sirketi Machine à laver et/ou sécher le linge à pompe à chaleur
US20190145043A1 (en) * 2017-11-16 2019-05-16 Haier Us Appliance Solutions, Inc. Dryer appliances including an air circulation duct
WO2019100122A1 (fr) * 2017-11-27 2019-05-31 Glaciem Cooling Technologies Système de réfrigération
WO2020088847A1 (fr) * 2018-11-01 2020-05-07 Arcelik Anonim Sirketi Sèche-linge hybride
US10928131B2 (en) 2016-06-10 2021-02-23 Force Technology Dryer and method of drying
CN113137710A (zh) * 2021-03-31 2021-07-20 青岛海尔空调电子有限公司 蒸发式冷凝器机组的控制方法
CN114225441A (zh) * 2021-12-16 2022-03-25 钥准医药科技(启东)有限公司 一种连续真空喷雾干燥装置

Families Citing this family (67)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3696224B2 (ja) * 2003-03-19 2005-09-14 株式会社グリーンセイジュ 乾燥システム
JP2005304987A (ja) * 2004-04-26 2005-11-04 Matsushita Electric Ind Co Ltd 衣類乾燥装置
JP2006046767A (ja) * 2004-08-03 2006-02-16 Ebara Refrigeration Equipment & Systems Co Ltd 除湿機
JP4326445B2 (ja) * 2004-10-20 2009-09-09 三洋電機株式会社 洗濯乾燥機
DE102005013051A1 (de) * 2005-03-18 2006-09-21 BSH Bosch und Siemens Hausgeräte GmbH Kondensations-Wäschetrockner
JP4783125B2 (ja) * 2005-11-17 2011-09-28 株式会社東芝 衣類乾燥機
JP5049495B2 (ja) * 2006-01-19 2012-10-17 株式会社前川製作所 木材の人工乾燥方法及びシステム
JP4607774B2 (ja) * 2006-01-20 2011-01-05 株式会社東芝 洗濯乾燥機
JP2008075949A (ja) * 2006-09-20 2008-04-03 Daikin Ind Ltd 空気調和装置
KR100811487B1 (ko) * 2007-02-13 2008-03-07 엘지전자 주식회사 덕트리스 건조기
CN100436383C (zh) * 2007-03-29 2008-11-26 广州市科伟电气有限公司 热泵式火药烘干方法及装置
JP4314284B2 (ja) 2007-04-19 2009-08-12 株式会社東芝 衣類乾燥機
KR100925738B1 (ko) * 2007-09-04 2009-11-11 엘지전자 주식회사 건조기의 온습도 조절 장치
JP4912265B2 (ja) * 2007-09-20 2012-04-11 三洋電機株式会社 衣類用乾燥装置およびヒートポンプユニット
WO2009073937A1 (fr) * 2007-12-10 2009-06-18 Vilani Oliveira Junior Jose Unité de déshumidification ou de déshydratation utilisable en apiculture
US20090205220A1 (en) * 2008-02-20 2009-08-20 Dewald Iii Charles Robert Dryer and adapter having ducting system
JP5131039B2 (ja) * 2008-06-10 2013-01-30 パナソニック株式会社 浴室換気空調装置
US8490438B2 (en) 2009-02-05 2013-07-23 Lg Electronics Inc. Laundry treatment device
KR101542389B1 (ko) 2009-02-05 2015-08-06 엘지전자 주식회사 히트펌프모듈 및 히트펌프모듈을 이용한 건조장치
EP2398948B1 (fr) 2009-02-23 2018-09-12 LG Electronics Inc. Lave-linge
CN102292489B (zh) * 2009-02-23 2013-05-01 Lg电子株式会社 洗衣机
KR101603106B1 (ko) 2009-03-03 2016-03-14 엘지전자 주식회사 세탁 장치
CN101614424B (zh) * 2009-07-27 2011-07-27 深圳市安健科技有限公司 一种为密闭空间除湿的方法及除湿系统
WO2011022479A2 (fr) * 2009-08-18 2011-02-24 Whirlpool Corporation Ensemble lavage et séchage accouplé à une pompe à chaleur (desserte)
CN101936021A (zh) * 2010-08-21 2011-01-05 马军 从干燥空气中取水的方法与装置
JP5948661B2 (ja) * 2010-09-30 2016-07-06 パナソニックＩｐマネジメント株式会社 乾燥装置
EP2458074A1 (fr) * 2010-11-29 2012-05-30 Electrolux Home Products Corporation N.V. Sèche-linge à pompe à chaleur
EP2460928B1 (fr) * 2010-12-02 2014-02-26 Electrolux Home Products Corporation N.V. Procédé de fonctionnement d'un séchoir à pompe à chaleur et séchoir à pompe à chaleur
JP5730074B2 (ja) * 2011-02-28 2015-06-03 三菱重工業株式会社 給湯システム
AU2012237107B2 (en) * 2011-03-29 2015-09-17 Lg Electronics Inc. Laundry Machine
US9834882B2 (en) 2011-07-07 2017-12-05 Haier Us Appliance Solutions, Inc. Device and method for heat pump based clothes dryer
CN102322735A (zh) * 2011-09-23 2012-01-18 宁建付 节能型热泵抽湿干燥设备
JP5506773B2 (ja) * 2011-12-27 2014-05-28 株式会社タクボ精機製作所 除湿機
CN102620534B (zh) * 2012-04-16 2014-07-02 武汉理工大学 一种应用于太阳能干燥器的低熔点合金相变蓄热装置
CN102692119B (zh) * 2012-04-20 2014-04-30 东莞市永淦节能科技有限公司 玉米种子烘干设备
KR101989522B1 (ko) * 2012-10-22 2019-09-30 엘지전자 주식회사 의류건조기
KR101987695B1 (ko) * 2012-10-22 2019-06-11 엘지전자 주식회사 2차 응축기가 설치된 증발기를 구비한 의류건조기
CN104019643B (zh) * 2013-02-28 2016-02-10 中国科学院理化技术研究所 带废热回收的农产品热泵干燥系统
KR102127383B1 (ko) * 2013-08-01 2020-06-26 엘지전자 주식회사 의류처리장치
CN103471367A (zh) * 2013-08-30 2013-12-25 于田县瑞阳空气能科技服务有限公司 一种汽化潜热循环利用型空气源热泵烘干机
CN103644714A (zh) * 2013-11-14 2014-03-19 广东威而信实业有限公司 闭环除湿热泵干燥系统
CN103791712B (zh) * 2014-01-28 2015-10-28 滁州奥岚格机械有限公司 粮食烘干机
CN103836900A (zh) * 2014-03-18 2014-06-04 新乡市鼎鑫机械有限公司 人造革合成革生产线塑化烘箱的热交换装置
KR101613966B1 (ko) 2014-12-29 2016-04-20 엘지전자 주식회사 의류처리장치
JP6545967B2 (ja) * 2015-01-28 2019-07-17 東芝ライフスタイル株式会社 衣類乾燥機
CN104964525A (zh) * 2015-07-01 2015-10-07 天津市傲绿农副产品集团股份有限公司 一种热泵型果蔬烘干机
DE102015216435A1 (de) * 2015-08-27 2017-03-02 BSH Hausgeräte GmbH Haushaltsgerät mit Abreinigungseinrichtung für Wärmetauscher
KR102483707B1 (ko) 2015-11-06 2023-01-02 엘지전자 주식회사 스파이크 고정부재 및 스파이크 고정부재가 구비된 의류처리장치
US10648125B2 (en) * 2015-12-18 2020-05-12 Whirlpool Corporation Laundry treating appliance and method of operation
CN105783447B (zh) * 2016-05-04 2018-07-27 长沙跃奇节能电气设备有限公司 一种双模式烟火药干燥系统
DE102016013589A1 (de) * 2016-11-09 2018-05-09 M+W Group GmbH Trockenraum
DK3542114T3 (da) * 2016-11-18 2020-11-23 Gea Process Eng A/S Tørresystem med forbedret energieffektivitet og kapacitetsregulering
CN107014198B (zh) * 2016-12-29 2019-08-09 石曾矿 可调温的四效除湿干燥系统
CN107568766A (zh) * 2017-09-26 2018-01-12 重庆汇田机械制造有限公司 均匀干燥式果蔬烘干烤房
JP6998179B2 (ja) * 2017-11-08 2022-02-10 日立グローバルライフソリューションズ株式会社 洗濯乾燥機
US10774463B2 (en) * 2018-03-14 2020-09-15 Haier Us Appliance Solutions, Inc. Dryer appliance
CN108800898B (zh) * 2018-05-24 2020-06-16 浙江理工大学 一种热泵沸腾干燥机装置
CN109553270B (zh) * 2018-12-06 2021-11-26 江苏天舒电器有限公司 一种热泵型闭式污泥干化系统及其控制方法
CN109708457A (zh) * 2018-12-28 2019-05-03 扬州大学 一种基于非共沸混合工质实现双蒸发温度的闭式热泵烘干装置
JP7473908B2 (ja) 2019-12-24 2024-04-24 青島海爾洗衣机有限公司 衣類処理装置
EP4259980A1 (fr) * 2020-12-09 2023-10-18 Polverelli, Giuseppe Système de chauffage et de déshumidification simultanés d'une pièce
CN112923676B (zh) * 2021-02-07 2022-10-18 长江师范学院 热泵烘干机组
CN113701292A (zh) * 2021-08-25 2021-11-26 珠海格力电器股份有限公司 空气净化装置
CN113719910A (zh) * 2021-09-02 2021-11-30 珠海格力电器股份有限公司 一种一体化空调器
US20230363616A1 (en) * 2022-05-13 2023-11-16 Haier Us Appliance Solutions, Inc. Dishwashing appliance having an air-drying dehumidification assembly
CN115560562B (zh) * 2022-09-23 2024-03-12 北京金雕建材检测有限公司 一种电热鼓风干燥箱
US20240247889A1 (en) * 2023-01-25 2024-07-25 Whirlpool Corporation Heat exchanger cleaning system for laundry appliance

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4304226A1 (de) * 1993-02-12 1994-08-18 Miele & Cie Trockengerät, insbesondere Kondensationswäschetrockner mit einer Wärmepumpe
DE4409607A1 (de) * 1993-04-21 1994-10-27 Miele & Cie Kondensationswäschetrockner mit einer Wärmepumpe
JPH07178289A (ja) * 1993-12-24 1995-07-18 Matsushita Electric Ind Co Ltd 衣類乾燥機
EP0999302A1 (fr) * 1998-10-21 2000-05-10 Whirlpool Corporation Sèche-linge à tambour avec pompe à chaleur
GB2349687A (en) * 1999-03-19 2000-11-08 Glaciation Air Conditioning Sy Air conditioning apparatus

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2090782A (en) * 1934-08-27 1937-08-24 Carraway Engineering Company I Air conditioning system
US3673698A (en) * 1970-11-25 1972-07-04 Albert S Guerard Process for freeze drying with carbon dioxide
IT1160889B (it) * 1978-10-26 1987-03-11 Berti Furic Impianto di essiccazione particolarmente per legname
US4471537A (en) * 1982-01-18 1984-09-18 Indesit Industria Elettrodomestici Italiana S.P.A. Dryer apparatus having an improved air circulation
JPS5981488A (ja) * 1982-11-02 1984-05-11 株式会社省熱学研究所 冷凍機と熱交換器による乾燥システム
US5181387A (en) * 1985-04-03 1993-01-26 Gershon Meckler Air conditioning apparatus
JPS6297415U (fr) * 1985-12-09 1987-06-22
US5119571A (en) * 1990-08-01 1992-06-09 Richard Beasley Dehydration apparatus and process of dehydration
JP3287171B2 (ja) * 1994-06-15 2002-05-27 株式会社デンソー 一体型冷房機
US5970723A (en) * 1996-03-05 1999-10-26 Kinkel; Stephen W. Heating and cooling unit
US20030208923A1 (en) * 2002-04-01 2003-11-13 Lewis Donald C. High temperature dehumidification drying system
EP1614976A4 (fr) * 2003-04-02 2006-08-02 Matsushita Electric Ind Co Ltd Dispositif de sechage et mode de fonctionnement de ce dispositif

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4304226A1 (de) * 1993-02-12 1994-08-18 Miele & Cie Trockengerät, insbesondere Kondensationswäschetrockner mit einer Wärmepumpe
DE4409607A1 (de) * 1993-04-21 1994-10-27 Miele & Cie Kondensationswäschetrockner mit einer Wärmepumpe
JPH07178289A (ja) * 1993-12-24 1995-07-18 Matsushita Electric Ind Co Ltd 衣類乾燥機
EP0999302A1 (fr) * 1998-10-21 2000-05-10 Whirlpool Corporation Sèche-linge à tambour avec pompe à chaleur
GB2349687A (en) * 1999-03-19 2000-11-08 Glaciation Air Conditioning Sy Air conditioning apparatus

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of WO2004029516A1 *

Cited By (38)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007023510A1 (fr) 2005-08-25 2007-03-01 Renzacci S.P.A. Industria Lavatrici Sèche-linge
WO2007074040A1 (fr) * 2005-12-29 2007-07-05 BSH Bosch und Siemens Hausgeräte GmbH Appareil menager pour laver des vetements
EP1811077A1 (fr) * 2006-01-20 2007-07-25 SANYO ELECTRIC Co., Ltd. Machine à sécher
EP1811076A1 (fr) * 2006-01-20 2007-07-25 SANYO ELECTRIC Co., Ltd. Sécheur
CH699018B1 (de) * 2006-01-27 2010-01-15 V Zug Ag Wäschetrockner mit Kohlendioxid-Wärmepumpe.
WO2008004803A3 (fr) * 2006-07-04 2008-03-13 Lg Electronics Inc Unité d'adoucissement de blanchissage et appareil de blanchissage équipé de celle-ci
WO2008004802A3 (fr) * 2006-07-04 2008-03-13 Lg Electronics Inc Appareil de blanchissage
US8973413B2 (en) 2006-07-04 2015-03-10 Lg Electronics Inc. Laundry refresher unit and laundry treating apparatus having the same
WO2008155263A1 (fr) * 2007-06-18 2008-12-24 BSH Bosch und Siemens Hausgeräte GmbH Sécheur à condensation muni d'une pompe à chaleur, et procédé pour le faire fonctionner
WO2009020311A3 (fr) * 2007-08-03 2010-11-11 Lg Electronics Inc. Dispositif de traitement de vêtements et procédé associé
US9134067B2 (en) 2007-09-04 2015-09-15 Lg Electronics Inc. Dehumidifying apparatus for dryer
EP2203585A4 (fr) * 2007-09-04 2013-11-27 Lg Electronics Inc Déshumidificateur pour sèche-linge
EP2203585A2 (fr) * 2007-09-04 2010-07-07 Lg Electronics Inc. Déshumidificateur pour sèche-linge
US9207014B2 (en) 2007-09-04 2015-12-08 Lg Electronics Inc. Dehumidifying apparatus for dryer
WO2009077336A1 (fr) * 2007-12-18 2009-06-25 BSH Bosch und Siemens Hausgeräte GmbH Sèche-linge et procédé de séchage de linge
EP2075368A1 (fr) * 2007-12-27 2009-07-01 BSH Bosch und Siemens Hausgeräte GmbH Procédé d'élimination d'un condensat dans un appareil ménager d'entretien du linge
CN102282304A (zh) * 2008-04-01 2011-12-14 Lg电子株式会社 衣物处理机
WO2009123402A3 (fr) * 2008-04-01 2010-12-02 Lg Electronics Inc. Machine de traitement de linge
WO2011039251A1 (fr) * 2009-10-01 2011-04-07 Arcelik Anonim Sirketi Sèche-linge à pompe à chaleur
WO2015101860A1 (fr) * 2013-12-30 2015-07-09 Indesit Company S.P.A. Appareil électroménager pour sécher le linge
ITPR20130106A1 (it) * 2013-12-30 2015-07-01 Indesit Co Spa Elettrodomestico di asciugatura panni.
EP3023533A1 (fr) * 2014-11-20 2016-05-25 LG Electronics Inc. Appareil de traitement de vêtements avec cycle à pompe à chaleur
AU2015258183B2 (en) * 2014-11-20 2017-01-19 Lg Electronics Inc. Clothes treating apparatus with heat pump cycle and method for controlling the same
US10240276B2 (en) 2014-11-20 2019-03-26 Lg Electronics Inc. Clothes treating apparatus with heat pump cycle and method for controlling the same
USD782059S1 (en) 2014-11-28 2017-03-21 3M Innovative Properties Company Mixing screw for dental impression material
USD782692S1 (en) 2014-11-28 2017-03-28 3M Innovative Properties Company Mixing nozzle for dental impression material
WO2017174766A1 (fr) * 2016-04-08 2017-10-12 Arcelik Anonim Sirketi Machine à laver et/ou sécher le linge à pompe à chaleur
US10928131B2 (en) 2016-06-10 2021-02-23 Force Technology Dryer and method of drying
US10494756B2 (en) * 2017-11-16 2019-12-03 Haier Us Appliance Solutions, Inc. Dryer appliances including an air circulation duct
US20190145043A1 (en) * 2017-11-16 2019-05-16 Haier Us Appliance Solutions, Inc. Dryer appliances including an air circulation duct
WO2019100122A1 (fr) * 2017-11-27 2019-05-31 Glaciem Cooling Technologies Système de réfrigération
CN111527357A (zh) * 2017-11-27 2020-08-11 格雷舍姆冷却技术公司 制冷系统
CN111527357B (zh) * 2017-11-27 2022-05-13 格雷舍姆冷却技术公司 制冷系统
US11747052B2 (en) 2017-11-27 2023-09-05 Glaciem Cooling Technologies Pty Ltd. Refrigeration system
WO2020088847A1 (fr) * 2018-11-01 2020-05-07 Arcelik Anonim Sirketi Sèche-linge hybride
CN113137710A (zh) * 2021-03-31 2021-07-20 青岛海尔空调电子有限公司 蒸发式冷凝器机组的控制方法
CN114225441A (zh) * 2021-12-16 2022-03-25 钥准医药科技(启东)有限公司 一种连续真空喷雾干燥装置
CN114225441B (zh) * 2021-12-16 2023-02-03 钥准医药科技(启东)有限公司 一种连续真空喷雾干燥装置

Also Published As

Publication number Publication date
WO2004029516A1 (fr) 2004-04-08
JP2004116899A (ja) 2004-04-15
EP1550829A4 (fr) 2006-12-27
CN1695029A (zh) 2005-11-09
US20050204755A1 (en) 2005-09-22
JP2005016779A (ja) 2005-01-20

Similar Documents

Publication Publication Date Title
EP1550829A1 (fr) Appareil de sechage
CN101275357B (zh) 干燥装置以及具有该装置的洗衣干燥机
CN100334290C (zh) 烘干机
US7866061B2 (en) Clothes dryer
CN1886628B (zh) 热泵式干衣机
CN103774402B (zh) 洗衣机
EA014949B1 (ru) Конденсационная сушилка с тепловым насосом и способ её работы
US20070163277A1 (en) Heat pump apparatus and operating method thereof
CN105625006A (zh) 具有热泵循环的衣物处理装置及其控制方法
US20060179681A1 (en) Heat pump type drying apparatus drying apparatus and drying method
EP2385169A1 (fr) Machine à laver avec système de pompe à chaleur et procédé de fonctionnement de la machine à laver
CN105671850A (zh) 具有热泵循环的衣物处理装置
JP2005279257A (ja) 乾燥装置及びその運転方法
JP2018102992A (ja) 冷凍サイクル装置
WO2011080244A2 (fr) Système de pompe à chaleur pour sécheuse à culbutage
CN213772594U (zh) 烘干系统及包括该系统的衣物处理设备
JP4026469B2 (ja) 衣類乾燥装置
JP2006336874A (ja) ヒートポンプ式乾燥機
JPH10235091A (ja) 乾燥機及び衣類乾燥機
KR100521851B1 (ko) 물탱크가 구비된 히트펌프시스템
JP4026451B2 (ja) 衣類乾燥装置
CN102353103A (zh) 一种溶液除湿空调器
JP6518498B2 (ja) 洗濯乾燥機
CN100532691C (zh) 烘干机
JP6321870B2 (ja) 冷凍サイクル装置

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20050414

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PT RO SE SI SK TR

A4 Supplementary search report drawn up and despatched

Effective date: 20061127

RIC1 Information provided on ipc code assigned before grant

Ipc: F24F 3/153 20060101AFI20061121BHEP

Ipc: D06F 58/20 20060101ALI20061121BHEP

Ipc: D06F 58/24 20060101ALI20061121BHEP

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20070125