US20110100043A1 - Air conditioning/ventilating system - Google Patents

Air conditioning/ventilating system Download PDF

Info

Publication number
US20110100043A1
US20110100043A1 US12/673,992 US67399208A US2011100043A1 US 20110100043 A1 US20110100043 A1 US 20110100043A1 US 67399208 A US67399208 A US 67399208A US 2011100043 A1 US2011100043 A1 US 2011100043A1
Authority
US
United States
Prior art keywords
air
heat exchanger
refrigerant
exhaust
heat
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.)
Abandoned
Application number
US12/673,992
Other languages
English (en)
Inventor
Mitunori Matubara
Yuuji Sugata
Masafumi Tsubouchi
Kei Takeshita
Yoshimasa Katsumi
Yoshihiro Nishizuru
Kazuhiro Saitou
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 Corp
Original Assignee
Panasonic Corp
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 Panasonic Corp filed Critical Panasonic Corp
Assigned to PANASONIC CORPORATION reassignment PANASONIC CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: MATUBARA, MITUNORI, NISHIZURU, YOSHIHIRO, TSUBOUCHI, MASAFUMI, KATSUMI, YOSHIMASA, SAITOU, KAZUHIRO, SUGATA, YUUJI, TAKESHITA, KEI
Publication of US20110100043A1 publication Critical patent/US20110100043A1/en
Abandoned legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
    • F24F5/0007—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning
    • F24F5/001—Compression cycle type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D5/00—Hot-air central heating systems; Exhaust gas central heating systems
    • F24D5/02—Hot-air central heating systems; Exhaust gas central heating systems operating with discharge of hot air into the space or area to be heated
    • F24D5/04—Hot-air central heating systems; Exhaust gas central heating systems operating with discharge of hot air into the space or area to be heated with return of the air or the air-heater
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D5/00—Hot-air central heating systems; Exhaust gas central heating systems
    • F24D5/12—Hot-air central heating systems; Exhaust gas central heating systems using heat pumps
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/13—Hot air central heating systems using heat pumps

Definitions

  • the present invention relates to a ventilating air-conditioning system using a heat pump to ventilate and to air-condition a sanitary space such as a bathroom.
  • one heat exchanger of the heat pump discharges or absorbs heat to or from air introduced from an indoor space other than the bathroom.
  • the air is blown out into the bathroom, and at the same time the other heat exchanger of the heat pump discharges or absorbs heat to or from air discharged from the bathroom to the outdoors to air-condition the bathroom during ventilation (refer to patent literature 1, for instance).
  • the heat pump is separated into outdoor and indoor units, and a heat exchanger placed in the outdoor unit discharges or absorbs heat to or from outdoor air.
  • a heat exchanger placed in the indoor unit discharges or absorbs heat to or from air in the bathroom to air-condition the bathroom, and a ventilating blower placed in the indoor unit ventilates the bathroom (refer to patent literature 2, for instance).
  • an indoor heat pump unit separated from the outdoor unit is provided with a sensible heat exchange ventilation element, which sensibly heat-exchanges during ventilation (refer to patent literature 3, for instance).
  • the bathroom air-conditioning system exemplified in patent literature 1 recovers heat from air discharged from the bathroom to the outdoors during ventilation to condition air in an indoor space other than the bathroom and to supply the air into the bathroom.
  • outdoor air flows into the indoor space other than the bathroom to cause the following problems. That is, comfort is impaired due to such as draft feeling; mold grows due to condensation near a natural air inlet; and a wall surface becomes dirty due to dust in outdoor air.
  • a ventilating air-conditioning system of the present invention includes an air supply fan that draws in outdoor air through an air inlet open to the outdoors and blows out the outdoor air through an air outlet open to an indoor space; an exhaust fan that draws in air in a sanitary space through an inlet open to the sanitary space and blows out the air in the sanitary space through an air outlet open to the outdoors; a compressor that compresses a refrigerant; a first heat exchanger that heat-exchanges between outdoor air sent by the air supply fan and the refrigerant; an expansion mechanism that expands the refrigerant; a second heat exchanger that heat-exchanges between air in the sanitary space sent by the exhaust fan and the refrigerant; and a refrigerant circuit piped so that the refrigerant circulates in order of the compressor, first heat exchanger, expansion mechanism, and second heat exchanger, or in order of the compressor, second heat exchanger, expansion mechanism, and first heat exchanger.
  • the system transfers heat between the first and second heat exchangers through the ref
  • Such a ventilating air-conditioning system prevents outdoor air not conditioned from flowing into an indoor space, thereby improving comfort, preventing mold from growing due to condensation near a natural air inlet, and preventing a wall surface from becoming dirty due to dust in outdoor air.
  • FIG. 1 is a sketch of an indoor space where a ventilating air-conditioning system according to an embodiment of the present invention is placed.
  • FIG. 2 is a configuration diagram of the air path of the ventilating air-conditioning system.
  • FIG. 3 is a diagram of the refrigerant circuit of the ventilating air-conditioning system.
  • FIG. 4 is a working diagram of the ventilating air-conditioning system.
  • FIG. 5 is an outline block diagram of the refrigerant heater of the ventilating air-conditioning system.
  • FIG. 6 is an outline sectional view of the refrigerant-water heat exchanger of the ventilating air-conditioning system.
  • FIG. 1 is a sketch of an indoor space where a ventilating air-conditioning system according to an embodiment of the present invention is placed.
  • Indoor space 1 is partitioned into living room 2 ; and sanitary space 6 such as bathroom 3 , washroom 4 , and toilet 5 .
  • the roof space of bathroom 3 is provided therein with main body 7 of the ventilating air-conditioning system.
  • Main body 7 is connected to exhaust duct 9 communicating between main body 7 and exhaust outlet 8 open to the outdoors; air supply duct 11 communicating between main body 7 and air supply inlet 10 open to the outdoors; and air outlet duct 13 communicating between main body 7 and air outlet 12 open to the ceiling of living room 2 .
  • FIG. 2 is a configuration diagram of the air path of the ventilating air-conditioning system of the present invention.
  • Main body 7 has exhaust fan 14 disposed therein, and exhaust fan 14 is provided with exhaust connection unit 19 connecting exhaust duct 9 at the air outlet side of exhaust fan 14 .
  • Main body 7 has exhaust air path 20 formed therein communicating between exhaust connection unit 19 and air inlet 16 of grill 15 placed in the ceiling surface of bathroom 3 .
  • operating exhaust fan 14 causes air in bathroom 3 to be drawn into exhaust fan 14 through air inlet 16 and to be discharged to the outdoors through exhaust duct 9 .
  • Main body 7 has air supply fan 17 disposed therein, and air supply fan 17 has air supply connection unit 21 connecting air supply duct 11 provided at the inlet side of air supply fan 17 .
  • Air supply fan 17 has air outlet connection unit 22 connecting air outlet duct 13 provided at the air outlet side of air supply fan 17
  • main body 7 has supply air path 23 communicating between air supply connection unit 21 and air outlet connection unit 22 formed inside main body 7 .
  • operating air supply fan 17 causes outdoor air to be drawn into air supply fan 17 through air supply duct 11 and to be blown out to living room 2 through air outlet duct 13 .
  • exhaust fan 14 and air supply fan 17 causes fresh outdoor air to be supplied into living room 2 , and the outdoor air flows into bathroom 3 through louvers or an undercut of the door to bathroom 3 . Then, vapor and smell in bathroom 3 are drawn through air inlet 16 of grill 15 and discharged to the outdoors.
  • the air supply and exhaust operation needs to be continuously performed for a building with high hermeticity (24-hour ventilation).
  • Exhaust fan 14 and air supply fan 17 are continuously operated so that a predetermined amount (e.g. approximately a half volume of indoor space 1 per hour) of air supply and exhaust is secured.
  • Living room 2 has air-conditioner 18 placed therein for controlling the room temperature, which appropriately maintains the temperature of the room through cooling operation in summer or heating operation in winter.
  • low-temperature air cooled by air-conditioner 18 in living room 2 is drawn into air inlet 16 through louvers or an undercut of the door to bathroom 3 in summer; and high-temperature air heated, in winter. Then, the cooled or heated air is discharged to the outdoors through main body 7 of the ventilating air-conditioning system.
  • the bottom of main body 7 of the ventilating air-conditioning system has air inlet 16 therein of grill 15 open to the ceiling surface of bathroom 3 , and air inlet 16 has an indoor filter (not shown) detachably disposed thereon for collecting dust.
  • supply air path 23 is provided at its upstream side from air supply fan 17 with supply air open/close device 24 opening and closing supply air path 23 (the degree of opening is adjustable); detachable outdoor filter 25 for collecting outdoor dust; and first heat exchanger 26 heat-exchanging mainly between outdoor air and a refrigerant, in order starting from air supply connection unit 21 .
  • auxiliary heater 27 heating at least part of outdoor air sent by air supply fan 17 is provided.
  • exhaust air path 20 The inside of exhaust air path 20 is provided at its upstream side from exhaust fan 14 with preheater 28 preheating air drawn from bathroom 3 ; and second heat exchanger 29 heat-exchanging mainly between the drawn air and the refrigerant, in order starting from air inlet 16 .
  • exhaust open/close device 30 opening and closing exhaust air path 20 (the degree of opening is adjustable) is provided.
  • Supply air path 23 is provided therein with air path changing/adjusting unit 31 communicating or blocking between the upstream side of first heat exchanger 26 and the upstream side of second heat exchanger 29 in exhaust air path 20 , or adjusting the amount of communication.
  • Supply air path 23 is provided therein with air supply bypass 32 blowing part of the outdoor air into living room 2 not through first heat exchanger 26 .
  • Exhaust air path 20 is provided therein with exhaust bypass 33 discharging part of the bathroom air to the outdoors not through second heat exchange 29 .
  • Exhaust air path 20 is provided therein with dehumidification changer 34 communicating or blocking between the downstream side from second heat exchanger 29 and the upstream side from first heat exchanger 26 in supply air path 23 , or adjusting the amount of communication.
  • Drain unit 35 is provided at its deepest part with drain pump 36 for draining water stored in drain unit 35 , thereby allowing the water to be drained to a position higher than main body 7 through drain piping 37 .
  • the outer shell of main body 7 including supply air path 23 and exhaust air path 20 is heat-insulated with heat insulator 38 stuck to the outer shell.
  • FIG. 3 is a diagram of the refrigerant circuit of the ventilating air-conditioning system according to the embodiment of the present invention.
  • Main body 7 is provided therein with refrigerant circuit 39 filled with a refrigerant such as any one of an HCFC refrigerant (contains atoms of chlorine, hydrogen, fluorine, and carbon in molecules); an HFC refrigerant (contains atoms of hydrogen, carbon, and fluorine in molecules); and a natural refrigerant (e.g. hydrocarbon, carbon dioxide).
  • Refrigerant circuit 39 includes compressor 40 compressing a refrigerant; first heat exchanger 26 ; expansion mechanism 41 composed of an electronic expansion valve expanding the refrigerant; and second heat exchanger 29 .
  • Refrigerant circuit 39 includes a path (heating cycle, hereinafter) through which a refrigerant compressed by compressor 40 passes in order of first heat exchanger 26 , expansion mechanism 41 , and second heat exchanger 29 , and then returns to compressor 40 .
  • Refrigerant circuit 39 includes a path (cooling cycle, hereinafter) through which a refrigerant compressed by compressor 40 passes in order of second heat exchanger 29 , expansion mechanism 41 , first heat exchanger 26 , and then returns to compressor 40 . Further, refrigerant circuit 39 is provided with flow path changing valve 42 changing between the heating cycle and cooling cycle.
  • Refrigerant circuit 39 is provided with first bypass circuit 43 split from the piping connecting flow path changing valve 42 to first heat exchanger 26 , and joining the piping connecting expansion mechanism 41 to second heat exchanger 29 .
  • Refrigerant circuit 39 is provided with second bypass circuit 44 split from the piping connecting first heat exchanger 26 to flow path changing valve 42 , and joining the piping connecting second heat exchanger 29 to flow path changing valve 42 .
  • First bypass circuit 43 is provided with first open/close valve 45 opening and closing first bypass circuit 43
  • second bypass circuit 44 is provided with second open/close valve 46 opening and closing second bypass circuit 44 and refrigerant heater unit 47 heating a refrigerant.
  • refrigerant heater unit 47 refrigerant heater 59 shown in FIG. 5 and refrigerant-water heat exchanger 66 shown in FIG. 6 can be used.
  • First heat exchanger 26 is placed in supply air path 23 ; second heat exchanger 29 , in exhaust air path 20 .
  • the refrigerant discharges or absorbs heat mainly to or from outdoor air sent by air supply fan 17 , in first heat exchanger 26 ; mainly to or from air discharged from bathroom 3 to the outdoors by exhaust fan 14 , in second heat exchanger 29 .
  • the piping through which a refrigerant in first heat exchanger 26 flows is equipped with decompression unit 50 composed of open/close mechanism 48 and capillary tube 49 .
  • decompression unit 50 composed of open/close mechanism 48 and capillary tube 49 .
  • exhaust air path 20 is provided at its upstream side from second heat exchanger 29 with preheater 28 having self temperature controllability. Activating preheater 28 causes air drawn from bathroom 3 into exhaust air path 20 to be heated and to be supplied to second heat exchanger 29 .
  • First heat exchanger 26 and second heat exchanger 29 are provided at their expansion mechanism 41 side with coil temperature sensors 51 , 52 detecting the temperature of a refrigerant.
  • the ventilating air-conditioning system thus transfers heat through a refrigerant between first heat exchanger 26 and second heat exchanger 29 , and heats or cools indoor space 1 while ventilating sanitary space 6 such as bathroom 3 .
  • FIG. 4 is a working diagram of the ventilating air-conditioning system according to the embodiment of the present invention.
  • Hanging hook 54 of main body 7 is hung on bolt 53 placed at the roof space to suspend main body 7 so as not to contact the ceiling surface.
  • air drawn from bathroom 3 is assumed to be conveyed into main body 7 through inlet duct 55 , which is different from the configuration of FIG. 2 .
  • Main body 7 is connected to air outlet duct 13 , air supply duct 11 , and exhaust duct 9 for conveying air, and is connected to drain piping 37 for draining dew condensation water and power line 56 for supplying electric power.
  • main body 7 is provided therein with refrigerant circuit 39 sequentially linking at least compressor 40 , flow path changing valve 42 , first heat exchanger 26 , expansion mechanism 41 , and second heat exchanger 29 .
  • Compressor 40 has two rotors and is placed in a horizontal position to reduce vibration of main body 7 and to decrease the height of main body 7 .
  • Main body 7 includes vibration isolator 57 to further absorb vibration of compressor 40 , and bolt 53 includes vibration isolator 58 to suppress vibration propagating to the frame of main body 7 .
  • FIG. 5 is an outline block diagram of the refrigerant heater of the ventilating air-conditioning system according to the embodiment of the present invention.
  • Refrigerant heater 59 is composed of refrigerant pipe line 60 made of refrigerant piping coiled for conducting a refrigerant; electrothermal tube 61 placed in a U-shaped form at the inner circumferential side of coiled refrigerant pipe line 60 ; and heat transfer cylinder 65 formed in a solid cylinder-shaped form by casting a metallic material (e.g. aluminum) so as to cover all the surface except inlet 62 and outlet 63 of refrigerant pipe line 60 ; and terminals 64 of electrothermal tube 61 .
  • a metallic material e.g. aluminum
  • electrothermal tube 61 When a predetermined voltage is applied between terminals 64 of electrothermal tube 61 , electrothermal tube 61 generates heat, which then transfers through the inside of heat transfer cylinder 65 to heat refrigerant pipe line 60 disposed on the outer circumference of electrothermal tube 61 .
  • the refrigerant is introduced into refrigerant pipe line 60 through inlet 62 .
  • the refrigerant is heated through heat transfer cylinder 65 , and then led to outlet 63 .
  • Electrothermal tube 61 placed at the core of heat transfer cylinder 65 generates heat toward refrigerant pipe line 60 placed in the outer circumferential direction of heat transfer cylinder 65 , and thus a small amount of heat leaks outside. Heat generated by electrothermal tube 61 transfers through heat transfer cylinder 65 to uniformly heat refrigerant pipe line 60 , thereby improving the heating efficiency and downsizing refrigerant heater unit 47 .
  • FIG. 6 is an outline sectional view of the refrigerant-water heat exchanger of the ventilating air-conditioning system according to the embodiment of the present invention.
  • Refrigerant-water heat exchanger 66 has a dual-pipe structure, with refrigerant pipe line 69 (through which a refrigerant flows) disposed inside hot-water pipe line 68 (through which hot water from water heater 67 flows).
  • Refrigerant pipe line 69 is split into two parts inside hot-water pipe line 68 , and formed in a twisted manner (split refrigerant pipe line 69 is helically twisted), thereby increasing the heat transfer area to improve the heat exchange efficiency.
  • the hot water that has flown from hot-water flow-in part 70 of hot-water pipe line 68 into refrigerant-water heat exchanger 66 flows through the outer circumference of refrigerant pipe line 69 ; flows out from hot-water flow-out part 71 outside refrigerant-water heat exchanger 66 ; and then drops into drain unit 35 underneath hot-water flow-out part 71 .
  • Drain unit 35 doubles as a drain tray for dew condensation water generated at first heat exchanger 26 and second heat exchanger 29 .
  • the hot water that has dropped into drain unit 35 is drained together with drain water outside main body 7 through drain piping 37 by drain pump 36 . In this way, hot water that has heat-exchanged with the refrigerant is drained through drain unit 35 .
  • the refrigerant that has flown into refrigerant-water heat exchanger 66 from refrigerant flow-in part 74 of refrigerant pipe line 69 faces the flow of hot water to split into twisted tube 75 .
  • the refrigerant is heated by heat exchange with the hot water and flows out through refrigerant flow-out part 76 .
  • the hot water used for heating the refrigerant may be heated by whichever type of water heater: combustion or heat pump.
  • a heat pump water heater using atmospheric heat, further improves the heating efficiency of refrigerant heater unit 47 and lowers the running cost.
  • hot-water pipe line 68 can be supplied with circulating water for heating, not with hot water heated by water heater 67 .
  • hot-water pipe line 68 may be supplied with normal-temperature feed water directly, not with high-temperature water heated by a water heater.
  • refrigerant circuit 39 is supplied with a high-temperature, high-pressure refrigerant compressed by compressor 40 , which enables the refrigerant to be cooled in a process of heat exchange with normal-temperature water such as tap water.
  • refrigerant-water heat exchanger 66 may be supplied with normal-temperature water to be made heat-exchange with the refrigerant.
  • Tables 1, 2 list operating states in each operation pattern.
  • the lists of tables 1, 2 describe each operation pattern of the ventilating air-conditioning system in sequence column-wise, and operating states of main components in each operation pattern are described row-wise. As shown in the lists, this ventilating air-conditioning system can execute 10 different operation patterns: heat-exchanging ventilation operation, air supply/exhaust operation, air supply operation, exhaust operation, dehumidification operation, heating operation, cooling operation, heat-exchanging ventilation operation while slightly dehumidifying, heat-exchanging ventilation operation while slightly heating, and heat-exchanging ventilation operation while slightly cooling.
  • the heat-exchanging ventilation operation is an operation pattern in which, while rapidly discharging smell and moisture in sanitary space 6 , heat of air conditioned by such as air-conditioner 18 when outdoor fresh air is supplied into indoor space 1 is recovered into a refrigerant when exhausting; air supplied from the outdoors is heated by the refrigerant; and the air is supplied with its temperature and humidity brought to those of conditioned air in indoor space 1 .
  • exhaust fan 14 is set to “strong notch” (capable of rapid exhaust); air path changing/adjusting unit 31 is set to the air supply/exhaust position (exhaust air path 20 and supply air path 23 are secured, shown in the figure); and air supply fan 17 is set to “strong notch” (capable of supplying air of the same amount as exhaust).
  • Air supply bypass 32 , exhaust bypass 33 , and dehumidification changer 34 are all set to the closed state; auxiliary heater 27 and preheater 28 , to the stop state; and air supply open/close device 24 and exhaust open/close device 30 , to the open state.
  • compressor 40 In refrigerant circuit 39 , compressor 40 is operated at the lowest frequency (extremely low power consumption); flow path changing valve 42 is retained in the heating state in winter and in the cooling state in summer, according to the difference between outdoor and indoor temperatures, for instance; and expansion mechanism 41 is adjusted to an appropriate degree of opening for an optimum refrigeration cycle when needed.
  • Open/close mechanism 48 is set to the open state, and thus the refrigerant does not pass through capillary tube 49 .
  • Refrigerant heater unit 47 is set to the stop state; and first open/close valve 45 and second open/close valve 46 , to the closed state.
  • exhaust fan 14 In winter in this state, for instance, exhaust fan 14 is operated at “strong notch”. A large volume of air warmed by air-conditioner 18 in indoor space 1 passes through a hallway and/or the undercut of a door and travels through exhaust air path 20 from air inlet 16 of grill 15 placed in the ceiling together with air containing smell and moisture in sanitary space 6 .
  • Fin-tube-type second heat exchanger 29 that has been changed to a “vaporizer” by flow path changing valve 42 exhausts air with its heat absorbed into the refrigerant to the outdoors through exhaust open/close device 30 , exhaust connection unit 19 , exhaust duct 9 , and exhaust outlet 8 .
  • the refrigerant is changed to a gas of relatively low pressure and temperature by compressor 40 operated at the lowest frequency; discharged in a small circulation amount; and enters first heat exchanger 26 through flow path changing valve 42 .
  • open/close mechanism 48 With open/close mechanism 48 in the open state, the refrigerant discharges heat into a large volume of air from the outdoors at the entire first heat exchanger 26 to decrease its temperature, becoming a low-temperature liquid.
  • the refrigerant is decompressed by expansion mechanism 41 to enter a two-phase state with low pressure and low temperature; absorbs heat from a large volume of air in indoor space 1 at second heat exchanger 29 , becoming a low-pressure, low-temperature gas; and then returns to compressor 40 .
  • Moisture in sanitary space 6 condenses into dew condensation water on the fins of second heat exchanger 29 (i.e. “vaporizer”) and flows down to drain unit 35 .
  • the accumulated dew condensation water is drained through drain piping 37 to such as the outdoors and a catch basin by operation of drain pump 36 .
  • the dew condensation water is sprayed onto first heat exchanger 26 (i.e. “condenser”), and vaporized and exhausted when air in sanitary space 6 is heat-exchanged.
  • a large volume of air cooled by air-conditioner 18 in indoor space 1 enters main body 7 together with air containing smell and moisture in sanitary space 6 ; absorbs heat from the refrigerant at second heat exchanger 29 that has been changed to a “condenser” by flow path changing valve 42 ; and then discharged to the outdoors. Then, a large volume of outdoor, hot, fresh air enters main body 7 ; discharges heat to the refrigerant at first heat exchanger 26 that has been changed to a “vaporizer” as a result that the cooling state is retained by flow path changing valve 42 ; and is cooled and blown out into living room 2 .
  • compressor 40 is operated at the lowest frequency
  • the refrigerant circulates to first heat exchanger 26 and second heat exchanger 29 with low power consumption;
  • exhaust fan 14 and air supply fan 17 are operated at “strong notch”, a large volume of air is exhausted and supplied, which results in the heat-exchanging ventilation operation in which the heat of exhaust from indoor space 1 is recovered and discharged into the supplied air.
  • the operation is an operation pattern in which a ventilating air volume regulated by the Building Standards Law is secured for 24 hours and indoor space 1 is supplied with air while sanitary space 6 is exhausted.
  • exhaust fan 14 is set to “weak notch” (low power consumption); air path changing/adjusting unit 31 , to the air supply/exhaust position (exhaust air path 20 and supply air path 23 are secured, shown in the figure); and air supply fan 17 , to “strong notch” (capable of supplying air of the same amount as exhaust).
  • Air supply bypass 32 and exhaust bypass 33 are set to the open state; dehumidification changer 34 , to the closed state; auxiliary heater 27 and preheater 28 , to the stop state; and air supply open/close device 24 and exhaust open/close device 30 , to the open state.
  • Refrigerant circuit 39 stops compressor 40 to prevent a refrigerant from flowing, and thus flow path changing valve 42 , expansion mechanism 41 , open/close mechanism 48 , refrigerant heater unit 47 , first open/close valve 45 , and second open/close valve 46 are all set to the stop state.
  • exhaust fan 14 operates at “weak notch”, which causes air in indoor space 1 containing such as VOC generated from building materials and furniture to pass through a hallway and/or the undercut of a door. Then, the air travels through air inlet 16 of grill 15 placed in the ceiling of sanitary space 6 , exhaust air path 20 , mainly exhaust bypass 33 in the open state, exhaust open/close device 30 , exhaust connection unit 19 , exhaust duct 9 , and exhaust outlet 8 , and is discharged to the outdoors.
  • “weak notch” causes air in indoor space 1 containing such as VOC generated from building materials and furniture to pass through a hallway and/or the undercut of a door. Then, the air travels through air inlet 16 of grill 15 placed in the ceiling of sanitary space 6 , exhaust air path 20 , mainly exhaust bypass 33 in the open state, exhaust open/close device 30 , exhaust connection unit 19 , exhaust duct 9 , and exhaust outlet 8 , and is discharged to the outdoors.
  • outdoor fresh air enters air supply inlet 10 and passes through air supply duct 11 , air supply connection unit 21 of body 7 , air supply opening and closing device 24 , outdoor filter 25 , and supply air path 23 . Then, the outdoor fresh air passes through mainly air supply bypass 32 in the open state, air outlet connection unit 22 , and air outlet duct 13 , and is blown out from air outlet 12 into living room 2 .
  • the operation is an operation pattern in which indoor space 1 is merely supplied with air when outdoor air provides more comfortable temperature and humidity or when outdoor air is cleaner than indoor.
  • exhaust fan 14 is stopped; air path changing/adjusting unit 31 is set to the air supply/exhaust position (exhaust air path 20 and supply air path 23 are secured, the state shown in the figure); and air supply fan 17 is operated at “weak notch” (low power consumption).
  • Air supply bypass 32 and exhaust bypass 33 are set to the open state; dehumidification changer 34 , to the closed state; auxiliary heater 27 and preheater 28 , to the stop state; and air supply open/close device 24 and exhaust open/close device 30 , to the open state.
  • Refrigerant circuit 39 stops compressor 40 to prevent the refrigerant from flowing, and thus flow path changing valve 42 , expansion mechanism 41 , open/close mechanism 48 , refrigerant heater unit 47 , first open/close valve 45 , and second open/close valve 46 are all set to the stop state.
  • outdoor fresh air enters air supply inlet 10 .
  • the outdoor fresh air passes through air supply duct 11 , air supply connection unit 21 , air supply open/close device 24 , outdoor filter 25 , and supply air path 23 of main body 7 ; through mainly air supply bypass 32 in the open state; through air outlet connection unit 22 and air outlet duct 13 ; and then is blown out from air outlet 12 into living room 2 .
  • the operation is an operation pattern in which sanitary space 6 is merely exhausted such as when the environment in indoor space 1 is not changed largely.
  • air supply fan 17 is stopped; air path changing/adjusting unit 31 is set to the air supply/exhaust position (exhaust air path 20 and supply air path 23 are secured, the state shown in the figure); and exhaust fan 14 is operated at “weak notch” (low power consumption).
  • Air supply bypass 32 and exhaust bypass 33 are set to the open state; dehumidification changer 34 , to the closed state; auxiliary heater 27 and preheater 28 , to the stop state; and air supply open/close device 24 and exhaust open/close device 30 , to the open state.
  • Refrigerant circuit 39 stops compressor 40 to prevent the refrigerant from flowing, and thus flow path changing valve 42 , expansion mechanism 41 , open/close mechanism 48 , refrigerant heater unit 47 , first open/close valve 45 , and second open/close valve 46 are all set to the stop state.
  • exhaust fan 14 operates at “weak notch”, which causes air in indoor space 1 containing such as VOC generated from building materials and furniture to pass through a hallway and/or the undercut of a door. Then, the air in indoor space 1 travels through air inlet 16 of grill 15 placed in the ceiling of sanitary space 6 , exhaust air path 20 , mainly exhaust bypass 33 in the open state, exhaust open/close device 30 , exhaust connection unit 19 , exhaust duct 9 , and exhaust outlet 8 , and is discharged to the outdoors.
  • “weak notch” causes air in indoor space 1 containing such as VOC generated from building materials and furniture to pass through a hallway and/or the undercut of a door. Then, the air in indoor space 1 travels through air inlet 16 of grill 15 placed in the ceiling of sanitary space 6 , exhaust air path 20 , mainly exhaust bypass 33 in the open state, exhaust open/close device 30 , exhaust connection unit 19 , exhaust duct 9 , and exhaust outlet 8 , and is discharged to the outdoors.
  • the operation is an operation pattern used when reheating and dehumidifying indoor space 1 to improve comfort against high humidity during a rainy season or against humidification by households and to restrain mold on such as a wall surface.
  • exhaust fan 14 is stopped; air path changing/adjusting unit 31 is set to the air supply/exhaust position” (exhaust air path 20 and supply air path 23 are secured, the state shown in the figure).
  • dehumidification changer 34 is set to the open state in which exhaust air path 20 communicates with supply air path 23 ; air supply open/close device 24 and exhaust open/close device 30 are set to the closed state; and air supply fan 17 is operated at “strong notch”.
  • Air supply bypass 32 and exhaust bypass 33 are set to the closed state; and auxiliary heater 27 and preheater 28 , to the stop state.
  • Refrigerant circuit 39 operates the compressor at a frequency adjusted according to the temperature and humidity of the air drawn into indoor space 1 ; retains flow path changing valve 42 to the heating state; and adjusts expansion mechanism 41 to an appropriate degree of opening for an optimum refrigeration cycle when needed.
  • Open/close mechanism 48 is set to the open state, and thus the refrigerant does not pass through capillary tube 49 .
  • Refrigerant heater unit 47 is set to the stop state; and first open/close valve 45 and second open/close valve 46 , to the closed state.
  • exhaust air path 20 is in a negative pressure when air supply fan 17 operates at “strong notch”.
  • a large volume of air containing much moisture in indoor space 1 passes through a hallway and/or the undercut of a door, and flows into exhaust air path 20 from air inlet 16 of grill 15 placed in the ceiling together with air in sanitary space 6 .
  • the large volume of air containing much moisture in indoor space 1 is heat-absorbed and dehumidified by the refrigerant at fin-tube-type second heat exchanger 29 that has been changed to a “vaporizer” by flow path changing valve 42 , and flows into supply duct 23 .
  • the refrigerant is changed to a gas of moderately high pressure and temperature by compressor 40 operating at an appropriate frequency and is discharged to enter first heat exchanger 26 through flow path changing valve 42 .
  • the refrigerant discharges heat into a large volume of air (its temperature and humidity have been lowered by second heat exchanger 29 ) sent from indoor space 1 to lower its temperature, changing into a low-temperature liquid at first heat exchanger 26 .
  • the refrigerant is decompressed by expansion mechanism 41 to enter a two-phase state with low pressure and low temperature; absorbs heat from a large volume of air in indoor space 1 at second heat exchanger 29 , becoming a low-pressure, low-temperature gas; and then returns to compressor 40 .
  • Moisture in sanitary space 6 condenses into dew condensation water on the fins of second heat exchanger 29 (i.e. “vaporizer”) and flows down to drain unit 35 .
  • the accumulated dew condensation water is drained through drain piping 37 to such as the outdoors and a catch basin by operation of drain pump 36 .
  • compressor 40 is operated at an appropriate frequency
  • the refrigerant circulates to first heat exchanger 26 and second heat exchanger 29 .
  • air supply fan 17 is operated at “strong notch” with exhaust open/close device 30 and air supply open/close device 24 in the closed state and with dehumidification changer 34 in the open state, the dehumidification operation is performed in which a large volume of air recovers heat when indoor space 1 is dehumidified and reheats indoor space 1 .
  • the operation is an operation pattern used to improve comfort by heating indoor space 1 such as in winter or to reduce a heating load on air-conditioner 18 .
  • air path changing/adjusting unit 31 sets supply air path 23 and exhaust air path 20 to the heating/cooling position at which air supplied from the outdoors passes through first heat exchanger 26 , and exhaust from indoor space 1 passes through second heat exchanger 29 .
  • exhaust fan 14 and air supply fan 17 are operated at “strong notch”.
  • Air supply bypass 32 , exhaust bypass 33 , and dehumidification changer 34 are all set to the closed state; auxiliary heater 27 and preheater 28 , to the stop state; and air supply open/close device 24 and exhaust open/close device 30 , to the open state.
  • Refrigerant circuit 39 operates the compressor while adjusting the frequency according to the temperature of the air in indoor space 1 and the outdoors; retains flow path changing valve 42 to the heating state; and adjusts expansion mechanism 41 to an appropriate degree of opening for an optimum refrigeration cycle when needed.
  • Open/close mechanism 48 is set to the open state, and thus the refrigerant does not pass through capillary tube 49 .
  • Refrigerant heater unit 47 is set to the stop state; and first open/close valve 45 and second open/close valve 46 , to the closed state.
  • air supply fan 17 is operated at “strong notch”, a large volume of outdoor air enters air supply inlet 10 and passes through air supply duct 11 , air supply connection unit 21 of main body 7 , air supply open/close device 24 , outdoor filter 25 , and supply air path 23 .
  • the large volume of outdoor air is retained in the heating state by air path changing/adjusting unit 31 set to the heating/cooling position; heat-absorbed by the refrigerant at second heat exchanger 29 that has been changed to a “vaporizer”; and discharged to the outdoors through exhaust open/close device 30 , exhaust connection unit 19 , exhaust duct 9 , and exhaust outlet 8 .
  • the refrigerant is changed to a gas of high pressure and temperature by compressor 40 operating at an appropriate frequency, and is discharged to enter first heat exchanger 26 through flow path changing valve 42 .
  • open/close mechanism 48 With open/close mechanism 48 in the open state, the refrigerant discharges heat into a large volume of air sent from indoor space 1 to lower its temperature at entire first heat exchanger 26 , changing into a low-temperature liquid. Further, the refrigerant is decompressed by expansion mechanism 41 to enter a two-phase state with low pressure and low temperature; absorbs heat from a large volume of outdoor air at second heat exchanger 29 , becoming a low-pressure, low-temperature gas; and then returns to compressor 40 .
  • compressor 40 is operated at an appropriate frequency
  • the refrigerant circulates to first heat exchanger 26 and second heat exchanger 29 .
  • air path changing/adjusting unit 31 is retained at the heating/cooling position, and exhaust fan 14 and air supply fan 17 are operated at “strong notch”, a large volume of air is warmed, which results in the heating operation in which indoor space 1 is heated.
  • auxiliary heater 27 can be switched between on and off according to preferences of the user. For instance, if the user feels a draft feeling and sets the system so as to reduce the air volume of air supply fan 17 , the refrigerant discharges less heat as the air volume supplied to first heat exchanger 26 decreases although draft feeling decreases, which lowers the temperature of indoor space 1 to impair comfortable feeling. If auxiliary heater 27 is operated in such a case, the air that has passed through first heat exchanger 26 is further heated by auxiliary heater 27 , and the high-temperature air is supplied to indoor space 1 , thereby suppressing a decrease of the room temperature.
  • defrosting operation 1 needs to be performed in which the temperature of the refrigerant piping of second heat exchanger 29 is monitored by coil temperature sensor 52 during the heating operation, and frost formed on second heat exchanger 29 is removed when the temperature decreases below a predetermined level.
  • the refrigerant that has discharged heat and dissolved frost at second heat exchanger 29 flows through expansion mechanism 41 , first heat exchanger 26 , and path changing valve 42 in sequence, and returns to compressor 40 to circulate in refrigerant circuit 39 . If this defrosting operation 1 is continued, the frost formed on second heat exchanger 29 dissolves completely and the temperature of the piping continues to rise. This temperature of the piping is continuously monitored by coil temperature sensor 52 , and the pattern is changed from defrosting operation 1 to the heating operation again when the temperature of the piping rises above a predetermined level.
  • exhaust fan 14 that has been stopped is started at “strong notch”; the temperature of the refrigerant is monitored by coil temperature sensor 51 placed on the piping at the liquid side of first heat exchanger 26 ; and operation of air supply fan 17 is also started at “predetermined notch” when a certain level of temperature is reached. This operation prevents the heating performance from excessively deteriorating at low temperature, allowing sufficient heating.
  • defrosting operation 1 If defrosting is needed when the outdoor temperature is extremely low or the temperature in indoor space 1 is low, instead of defrosting operation 1 in which heating operation is once stopped and frost is removed by changing to defrosting operation, another defrosting operation is requested in which frost formed on second heat exchanger 29 is removed while continuing heating operation. Next, a description is made of such defrosting operation 2 .
  • Refrigerant heater unit 47 is provided with refrigerant heater 59 or refrigerant-water heat exchanger 66 as described above and heats the refrigerant to perform heat-absorbing operation.
  • second heat exchanger 29 is supplied with outdoor air through air supply inlet 10 and air supply duct 11 .
  • the refrigerant that has dissolved frost at second heat exchanger 29 merges with the refrigerant heated by refrigerant heater unit 47 to returns to compressor 40 through flow path changing valve 42 .
  • the air supplied to second heat exchanger 29 provides heat to the frost formed, the air is discharged to the outdoors through exhaust duct 9 .
  • second heat exchanger 29 can be defrosted while continuing heating indoor space 1 .
  • the temperature of the piping of second heat exchanger 29 is monitored by coil temperature sensor 52 for a level higher than a predetermined value, and when the temperature rises to the level, namely when removing the frost completes, regular heating operation is resumed, allowing continuous heating operation without impairing comfortable feeling of users.
  • the operation is an operation pattern used to lower the temperature in indoor space 1 at high temperature such as in summer to cool indoor space 1 for comfort or to reduce a cooling load on air-conditioner 18 .
  • air path changing/adjusting unit 31 is set to the heating/cooling position at which exhaust air path 20 and supply air path 23 are arranged so that the air supplied from the outdoors passes through first heat exchanger 26 and exhaust from indoor space 1 passes through second heat exchanger 29 ; and exhaust fan 14 and air supply fan 17 are operated at “strong notch”.
  • Air supply bypass 32 , exhaust bypass 33 , dehumidification changer 34 are all set to the closed state; auxiliary heater 27 and preheater 28 , to the stop state; and air supply open/close device 24 and exhaust open/close device 30 , to the open state.
  • Refrigerant circuit 39 operates the compressor while adjusting the frequency according to the temperature of the air in indoor space 1 and the outdoors; retains flow path changing valve 42 to the cooling state; and adjusts expansion mechanism 41 to an appropriate degree of opening for an optimum refrigeration cycle when needed.
  • Open/close mechanism 48 is set to the open state, and thus the refrigerant does not pass through capillary tube 49 .
  • Refrigerant heater unit 47 is set to the stop state; and first open/close valve 45 and second open/close valve 46 , to the closed state.
  • exhaust fan 14 is operated at “strong notch”
  • a large volume of air in indoor space 1 passes through a hallway and/or the undercut of a door, and passes through exhaust air path 20 from air inlet 16 of grill 15 placed in the ceiling together with air in sanitary space 6 .
  • the air that has been heat-absorbed and cooled by the refrigerant at first heat exchanger 26 that has been changed to a “condenser” passes through air outlet connection unit 22 and air outlet duct 13 by air path changing/adjusting unit 31 set to the heating/cooling position, and is blown out from air outlet 12 into living room 2 .
  • the refrigerant is changed to a gas of high pressure and temperature by compressor 40 operating at an appropriate frequency and is discharged to enter first heat exchanger 29 through flow path changing valve 42 , and discharges heat into a large volume of outdoor air to lower its temperature.
  • the refrigerant is decompressed by expansion mechanism 41 to enter a two-phase state with low pressure and low temperature, becoming a low-temperature liquid.
  • open/close mechanism 48 With open/close mechanism 48 in the open state, the refrigerant absorbs heat from a large volume of air sent from indoor space 1 to lower its temperature at entire first heat exchanger 26 , becoming a low-pressure, low-temperature gas; and then returns to compressor 40 through flow path changing valve 42 .
  • Moisture in indoor space 1 condenses into dew condensation water on the fins of first heat exchanger 29 (i.e. “vaporizer”) and flows down to drain unit 35 .
  • the accumulated dew condensation water is drained through drain piping 37 to such as the outdoors and a catch basin by operation of drain pump 36 . Instead, the dew condensation water is sprayed onto second heat exchanger 29 (i.e. “condenser”), and is vaporized and discharged when heat-exchanging the outdoor air.
  • compressor 40 is operated at an appropriate frequency
  • the refrigerant circulates to second heat exchanger 29 and first heat exchanger 26 .
  • air path changing/adjusting unit 31 is retained at the heating/cooling position; and exhaust fan 14 and air supply fan 17 are operated at “strong notch”, a large volume of air is cooled, which results in the cooling operation in which indoor space 1 is cooled.
  • the operation is an operation pattern for recovering heat of air conditioned such as by air-conditioner 18 to a refrigerant when supplying indoor space 1 with outdoor fresh air while rapidly discharging smell and moisture in sanitary space 6 ; and reheating and dehumidifying indoor space 1 while heating air supplied from the outdoor and sending the air, to improve comfort against high humidity during a rainy season or against humidification by households and to restrain mold on such as a wall surface.
  • exhaust fan 14 and air supply fan 17 are operated at “strong notch” while adjusting air path changing/adjusting unit 31 to an appropriate degree of opening between the heating/cooling position and the air supply/exhaust position (the state shown in the figure). Then, adjustment is made for each air volume of outdoor air passing through first heat exchanger 26 and second heat exchanger 29 ; and that in indoor space 1 .
  • the heating/cooling position of air path changing/adjusting unit 31 refers a state in which exhaust air path 20 and supply air path 23 are set so that air from the outdoors passes through first heat exchanger 26 ; and exhaust from indoor space 1 , through second heat exchanger 29 .
  • the air supply/exhaust position of air path changing/adjusting unit 31 refers a state in which exhaust air path 20 and supply air path 23 are secured.
  • Air supply bypass 32 , exhaust bypass 33 , and dehumidification changer 34 are all set to the closed state; auxiliary heater 27 and preheater 28 , to the stop state; and air supply open/close device 24 and exhaust open/close device 30 ; to the open state.
  • Refrigerant circuit 39 operates compressor 40 while adjusting the frequency according to the temperature and humidity of the air in indoor space 1 and the outdoors; retains flow path changing valve 42 to the heating state; and sets expansion mechanism 41 to the fully open state.
  • Open/close mechanism 48 is set to the closed state and passes the refrigerant flow through capillary tube 49 to be decompressed; the upstream side of first heat exchanger 26 from capillary tube 49 is used as a “condenser”; and the downstream, as a “vaporizer”.
  • Refrigerant heater unit 47 is set to the stop state; and first open/close valve 45 and second open/close valve 46 , to the closed state.
  • the air merged is dehumidified at the downstream side from capillary tube 49 , of first heat exchanger 26 that has been set to the heating state by flow path changing valve 42 to become a “vaporizer”; and reheated at the upstream side from capillary tube 49 , of first heat exchanger 26 that has become a “condenser”.
  • the air dehumidified and reheated is blown out from air outlet 12 into living room 2 through air outlet connection unit 22 and air outlet duct 13 .
  • the air merged is heat-absorbed by the refrigerant at second heat exchanger 29 retained in the heating state by flow path changing valve 42 to become a “vaporizer”; and discharged to the outdoors through exhaust open/close device 30 , exhaust connection unit 19 , exhaust duct 9 , and exhaust outlet 8 .
  • the refrigerant is changed to a gas of high pressure and temperature by compressor 40 operating at an appropriate frequency and is discharged to enter first heat exchanger 29 through flow path changing valve 42 .
  • open/close mechanism 48 With open/close mechanism 48 in the closed state, the refrigerant discharges heat into a large volume of air in indoor space 1 and from the outdoors, at the upstream side from capillary tube 49 , of first heat exchanger 26 to decrease its temperature, entering a two-phase state with medium-low temperature. Further, the refrigerant is decompressed at capillary tube 49 , entering a two-phase state with medium-low pressure and medium-low temperature.
  • the refrigerant slightly absorbs heat from a large volume of air in indoor space 1 and from the outdoors at the downstream side of first heat exchanger 26 from capillary tube 49 , entering a two-phase state with medium-low pressure and medium-low temperature.
  • the refrigerant With decompression mechanism 41 in the fully open state, the refrigerant is slightly decompressed to enter second heat exchanger 29 (i.e. “vaporizer”); further absorbs heat from a large volume of air from the outdoors and indoor space 1 , becoming a low-pressure, low-temperature gas; and returns to compressor 40 .
  • second heat exchanger 29 i.e. “vaporizer”
  • the accumulated dew condensation water is drained through drain piping 37 to such as the outdoors and a catch basin by operation of drain pump 36 .
  • Air path changing/adjusting unit 31 is retained at “adjusting the degree of opening”; and exhaust fan 14 and air supply fan 17 are operated at “strong notch”, which results in the slightly dehumidifying heat-exchanging ventilation, in which heat in indoor space 1 is recovered to be reheated and dehumidified; and sanitary space 6 is exhausted and supplied with outdoor air.
  • the operation is an operation pattern for recovering heat of air conditioned such as by air-conditioner 18 when supplying indoor space 1 with outdoor fresh air while rapidly discharging smell and moisture in sanitary space 6 ; and heating indoor space 1 while heating air supplied from the outdoor and sending the air, to improve comfort in winter or to reduce a heating load on air-conditioner 18 .
  • exhaust fan 14 and air supply fan 17 are operated at “strong notch” while adjusting air path changing/adjusting unit 31 to an appropriate degree of opening between the heating/cooling position and the air supply/exhaust position (the state shown in the figure). Then, adjustment is made for each air volume of outdoor air passing through first heat exchanger 26 and second heat exchanger 29 ; and that in indoor space 1 .
  • the other operation is the same as that of the heating.
  • the heating/cooling position of air path changing/adjusting unit 31 refers a state in which exhaust air path 20 and supply air path 23 are set so that air from the outdoors passes through first heat exchanger 26 and exhaust from indoor space 1 passes through second heat exchanger 29 .
  • the air supply/exhaust position of air path changing/adjusting unit 31 refers a state in which exhaust air path 20 and supply air path 23 are secured.
  • the operation is an operation pattern for recovering heat of air conditioned such as by air-conditioner 18 when supplying indoor space 1 with outdoor fresh air while rapidly discharging smell and moisture in sanitary space 6 ; and for cooling indoor space 1 with the refrigerant absorbing heat from air supplied from the outdoors, to improve comfort in summer or to reduce a cooling load on air-conditioner 18 .
  • exhaust fan 14 and air supply fan 17 are operated at “strong notch” while adjusting air path changing/adjusting unit 31 to an appropriate degree of opening between the heating/cooling position and the air supply/exhaust position (the state shown in the figure). Then, adjustment is made for each air volume of outdoor air passing through first heat exchanger 26 and second heat exchanger 29 ; and that in indoor space 1 .
  • the other operation is the same as that of the cooling.
  • the heating/cooling position of air path changing/adjusting unit 31 refers a state in which exhaust air path 20 and supply air path 23 are set so that air from the outdoors passes through first heat exchanger 26 and exhaust from indoor space 1 passes through second heat exchanger 29 .
  • the air supply/exhaust position of air path changing/adjusting unit 31 refers a state in which exhaust air path 20 and supply air path 23 are secured.
  • the ventilating air-conditioning system according to the embodiment of the present invention presents the following effects.
  • the system transfers air through a refrigerant between first heat exchanger 26 and second heat exchanger 29 ; and heats or cools outdoor air to supply indoor space 1 with the air by air supply fan 17 while discharging air in bathroom 3 by exhaust fan 14 .
  • This operation prevents outdoor air not conditioned from flowing into indoor space 1 , thereby improving comfort, preventing mold from growing due to condensation near a natural air inlet, and preventing a wall surface from becoming dirty due to dust in outdoor air.
  • saving energy is totally achieved including reducing running costs of air-conditioner 18 .
  • the low pressure loss of the heat exchanger increases the air volume for ventilating.
  • Air path changing/adjusting unit 31 adjusts each amount of outdoor air passing through first heat exchanger 26 and second heat exchanger 29 ; and that in the sanitary space to balance each amount of ventilation air, exhaust, and supply air according to environmental conditions such as indoor and outdoor temperature, indoor and outdoor humidity, and the pollution level of indoor air. This operation allows supplying indoor space 1 with air while ventilating sanitary space 6 , which allows air-conditioning with low energy.
  • the system sets air supply bypass 32 of first heat exchanger 26 and exhaust bypass 33 of second heat exchanger 29 to the open state during ventilation to supply and discharge air between indoor space 1 and the outdoors without passing part of air in the outdoors and sanitary space 6 through first heat exchanger 26 and second heat exchanger 29 .
  • This operation allows supplying indoor space 1 with air and exhausting sanitary space 6 with lower power for the same air volume of supply and exhaust.
  • the system changes the air path so that air drawn from sanitary space 6 is cooled at second heat exchanger 29 ; reheated at first heat exchanger 26 ; and blown out into indoor space 1 , thereby reducing temperature changes in indoor space 1 and dehumidifying indoor space 1 while reducing heat flowing out to the outdoors.
  • Flow path changing valve 42 changes the direction in which the refrigerant flows, which allows switching between heating and cooling in indoor space 1 .
  • the system operates so that air drawn from the outdoors is cooled at the downstream side of first heat exchanger 26 from decompression unit 50 , reheated at the upstream side from decompression unit 50 , and then blown out into indoor space 1 , which allows dehumidifying indoor space 1 without excessively decreasing the temperature in indoor space 1 while introducing outdoor fresh air into indoor space 1 .
  • the system When heating, cooling, or dehumidifying indoor space 1 , the system increases the air volume of air supply fan 17 or exhaust fan 14 , unlike when ventilating sanitary space 6 , thereby increasing the performance of recovering heat, and ventilating and air-conditioning with lower power consumption.
  • Drain unit 35 arranged under supply air path 23 and exhaust air path 20 reliably disposes of dew condensation water generated in the air path; condensate water from the heat exchanger flows to a single drain outlet to improve workability. Further, an increased amount of water allows the water to flow into the drain outlet smoothly to prevent retained water from developing bacteria.
  • Operating drain pump 36 allows condensate water or dew condensation water to be drained to a position higher than drain unit 35 , thereby enabling the system to be constructed where the drain cannot be sloped adequately due to a small roof space.
  • Insulating around supply air path 23 and exhaust air path 20 with heat insulator 38 prevents heat from leaking while preventing condensation from forming on the outer shell of main body 7 of the ventilating air-conditioning system, thereby further saving energy.
  • the inside of main body 7 of the ventilating air-conditioning system placed such as in the roof space of bathroom 3 contains all of compressor 40 , first heat exchanger 26 , expansion mechanism 41 , and second heat exchanger 29 composing refrigerant circuit 39 to save space and to improve workability.
  • Auxiliary heater 27 heats at least part of the air sent by air supply fan 17 , thereby covering deficiency in the heating performance in a low-temperature environment.
  • Preheater 28 preheats air before being supplied to second heat exchanger 29 , thereby restraining the heating performance from decreasing in a low-temperature environment and second heat exchanger 29 from being frosted, as well as removing frost formed.
  • the system changes flow path changing valve 42 according to the temperature of a refrigerant monitored by coil temperature sensors 51 , 52 , thereby removing frost formed.
  • the system opens the high- and low-pressure sides of refrigerant circuit 39 through first bypass circuit 43 and second bypass 44 to allow a high-temperature refrigerant to circulate to second heat exchanger 29 ; or increases the refrigerant pressure in second heat exchanger 29 , thereby removing frost formed.
  • Refrigerant heater unit 47 is interposed in refrigerant circuit 39 in series or parallel with second heat exchanger 29 ; and refrigerant heater unit 47 is activated when the heat-absorbing performance decreases such as due to frost forming on second heat exchanger 29 , thereby securing the heat-absorbing performance to maintain the heating performance.
  • Refrigerant heater unit 47 includes refrigerant heater 59 heating a refrigerant electrothermally, thereby downsizing refrigerant heater unit 47 .
  • Refrigerant heater unit 47 includes refrigerant-water heat exchanger 66 heating a refrigerant by heat exchange with hot water from water heater 67 , thereby reducing power usage at refrigerant heater unit 47 .
  • Using hot water heated by a heat pump water heater for hot water to be supplied to refrigerant-water heat exchanger 66 further reduces power usage at refrigerant heater unit 47 .
  • a drain path is used for draining dew condensation water generated in first heat exchanger 26 and/or second heat exchanger 29 , thereby simplifying construction without increasing the number of drain paths.
  • Arrangement is made so that a refrigerant discharges heat to normal-temperature water supplied to refrigerant-water heat exchanger 66 in case where the discharge heat performance decreases at high temperature such as in summer, thereby resolving deficiency in heat discharge to maintain the cooling performance.
  • indoor space 1 to be air-supplied and air-conditioned is living room 2 ; sanitary space 6 having air outlet opening is bathroom 3 ; however, a space to be air-supplied and air-conditioned and a space having an air outlet opening are not limited to the above, but may be any space as long as it is partitioned within indoor space 1 .
  • a space air-supplied and air-conditioned may be a hallway; a space having an air outlet opening, washroom 4 .
  • air outlet 12 and air inlet 16 respectively open to living room 2 and bathroom 3 one each; however, the numbers of air outlets 12 and air inlets 16 are not limited to the above case. For instance, two air outlets 12 may open to living room 2 and a hallway.
  • air inlet 16 for exhausting is a cassette-type one provided in grill 15 of main body 7 ; however, it may be a concealed type one in which a duct is connected to air inlet 16 of main body 7 , the end of the duct is connected to another air inlet in the ceiling of a space to be exhausted, and main body 7 is concealed in the roof space.
  • refrigerant circuit 39 is provided with two-series bypass circuits (first bypass circuit 43 and second bypass circuit 44 ); however, it may be provided with one-series bypass circuit.
  • refrigerant heater unit 47 is placed in parallel with second heat exchanger 29 ; however, it may be interposed in series with second heat exchanger 29 within refrigerant circuit 39 .
  • first open/close valve 45 and second open/close valve 46 are changed between the two levels (open and closed); however, the open/close valve may be any type as long as it opens and closes a bypass circuit such as an electronic expansion valve.
  • the configuration is shown in which open/close mechanism 48 is placed in parallel with capillary tube 49 as a decompression unit; however, the decompression unit may be any type as long as it can change the decompression action such as a type with an electronic expansion valve interposed.
  • refrigerant heater 59 and refrigerant-water heat exchanger 66 are shown as a concrete configuration of refrigerant heater unit 47 ; however, refrigerant heater unit 47 may be any type as long as it can heat a refrigerant, not limited to the above-described two types.
  • the configuration is shown in which the piping at the water side of refrigerant-water heat exchanger 66 is supplied with hot water from a combustion water heater or heat pump water heater; however, the piping may be supplied with high-temperature water (e.g. 40° C. to 90° C.) or normal-temperature feed water (e.g. 1° C. to 40° C.), not limited to hot water from a combustion water heater or heat pump water heater. Any type of water may be used such as hot water or feed water from a gas water heater, electricity water heater, kerosene water heater; circulating water such as for heating floors; normal-temperature city water; or water left in the bathtub.
  • high-temperature water e.g. 40° C. to 90° C.
  • normal-temperature feed water e.g. 1° C. to 40° C.
  • Any type of water may be used such as hot water or feed water from a gas water heater, electricity water heater, kerosene water heater; circulating water such as for heating floors; normal
  • the motor of air supply fan 17 , exhaust fan 14 , or compressor 40 is not particularly mentioned (e.g. AC or DC); however, a DC motor particularly saves energy.
  • compressor 40 has two rotors and is placed in the horizontal position; however, compressor 40 may be scroll-type as long as it is low-vibration type, and may be placed in a vertical position as long as it is low-profile type.
  • main body 7 is suspended in the roof space of bathroom 3 for installation; however, it may be installed at any location and in any way as long as a space for installing the main body, maintainability, sound insulation, and vibration insulation are secured.
  • floor-standing main body 7 may be placed in an indoor or outdoor machine room or embedded in a wall surface.
  • a ventilating air-conditioning system saves space and improves workability; and recovers heat from the air while rapidly discharging a large volume of air containing moisture and smell generated from a sanitary space.
  • the system air-conditions an indoor space while supplying outdoor fresh air to allow air-conditioning with low energy consumption while improving air quality. Consequently, besides ventilating a sanitary space and air-supplying/air-conditioning an indoor space, the invention is applicable to a ventilating, air-supplying, and air-conditioning system for a living space such as a living room, bedroom, kitchen, and washroom; an uninhabitable space such as a closet, underfloor, and storage; and a nonresidential space such as an office, meeting room, and warehouse.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • Physics & Mathematics (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Central Air Conditioning (AREA)
  • Domestic Hot-Water Supply Systems And Details Of Heating Systems (AREA)
  • Devices For Blowing Cold Air, Devices For Blowing Warm Air, And Means For Preventing Water Condensation In Air Conditioning Units (AREA)
  • Ventilation (AREA)
  • Air Conditioning Control Device (AREA)
US12/673,992 2007-08-31 2008-08-28 Air conditioning/ventilating system Abandoned US20110100043A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2007225558A JP5076745B2 (ja) 2007-08-31 2007-08-31 換気空調装置
JP2007-225558 2007-08-31
PCT/JP2008/002329 WO2009028184A1 (ja) 2007-08-31 2008-08-28 換気空調装置

Publications (1)

Publication Number Publication Date
US20110100043A1 true US20110100043A1 (en) 2011-05-05

Family

ID=40386923

Family Applications (1)

Application Number Title Priority Date Filing Date
US12/673,992 Abandoned US20110100043A1 (en) 2007-08-31 2008-08-28 Air conditioning/ventilating system

Country Status (4)

Country Link
US (1) US20110100043A1 (ja)
JP (1) JP5076745B2 (ja)
CN (1) CN101790667B (ja)
WO (1) WO2009028184A1 (ja)

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20130160985A1 (en) * 2011-12-21 2013-06-27 Nordyne Inc. Refrigerant charge management in a heat pump water heater
EP2719967A1 (de) * 2012-10-09 2014-04-16 Roth Werke GmbH Verfahren zur Temperierung eines Gebäudes
US9383126B2 (en) 2011-12-21 2016-07-05 Nortek Global HVAC, LLC Refrigerant charge management in a heat pump water heater
US20170010027A1 (en) * 2014-01-27 2017-01-12 Qingdao Hisense Hitachi Air-Conditionung Systems Co., Ltd Heat recovery variable-frequency multi-split heat pump system and control method thereof
CN107101287A (zh) * 2017-06-20 2017-08-29 合肥天鹅制冷科技有限公司 坑道除湿空调机
US10222085B2 (en) 2012-02-29 2019-03-05 Carrier Corporation Energy recovery ventilator with reduced power consumption
CN110145835A (zh) * 2019-05-17 2019-08-20 青岛海尔空调器有限总公司 空调新风系统
CN110398048A (zh) * 2019-07-23 2019-11-01 广东美的暖通设备有限公司 空调系统、空调控制方法、空调控制装置和存储介质
IT202000030143A1 (it) * 2020-12-09 2022-06-09 Giuseppe Polverelli Impianto di riscaldamento e deumidificazione simultanea di un locale.
WO2022122671A1 (en) 2020-12-09 2022-06-16 Polverelli Giuseppe System for simultaneously heating and dehumidifying a room
US11913460B2 (en) 2020-03-20 2024-02-27 Greenheck Fan Corporation Exhaust fan
US11982458B2 (en) 2022-01-18 2024-05-14 Haier Us Appliance Solutions, Inc. Air conditioner makeup air circulation

Families Citing this family (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2535652B1 (en) * 2010-02-10 2023-08-16 Mitsubishi Electric Corporation Air conditioner
CN102486325A (zh) * 2010-12-01 2012-06-06 西安中科麦特电子技术设备有限公司 带换气功能的高温老化房循环系统
US8408019B2 (en) * 2010-12-07 2013-04-02 Tai-Her Yang Air conditioning device utilizing temperature differentiation of exhausted gas to even temperature of external heat exchanger
CN102233316A (zh) * 2011-04-20 2011-11-09 江苏剑桥涂装工程有限公司 一种带有冷凝装置的换气装置
SE537022C2 (sv) * 2012-12-21 2014-12-09 Fläkt Woods AB Förfarande och anordning för avfrostning av en förångare vidett luftbehandlingsaggregat
JP6333110B2 (ja) * 2014-08-12 2018-05-30 株式会社Ｌｉｘｉｌ 換気装置
JP2016044877A (ja) * 2014-08-22 2016-04-04 株式会社Ｌｉｘｉｌ 換気装置
JP2016040504A (ja) * 2014-08-12 2016-03-24 株式会社Ｌｉｘｉｌ 換気装置
CN106574796A (zh) * 2014-08-12 2017-04-19 骊住株式会社 换气装置
TWI558954B (zh) * 2014-09-22 2016-11-21 建準電機工業股份有限公司 具室內外溫差調節功能的氣流交換裝置
CN107676892B (zh) * 2016-08-02 2020-10-02 青岛海尔智能技术研发有限公司 一种空调器及控制方法
JP2018028406A (ja) * 2016-08-18 2018-02-22 株式会社パイオニア・コーポレーション 集合住宅の浴室換気装置
TWI666411B (zh) * 2017-10-25 2019-07-21 陳韋任 暖通空調系統及其控制方法
CN108386914A (zh) * 2018-03-06 2018-08-10 青岛海尔空调器有限总公司 一种新风空调室内机
CN108361889A (zh) * 2018-03-06 2018-08-03 青岛海尔空调器有限总公司 一种新风空调室内机
CN108592298A (zh) * 2018-06-20 2018-09-28 珠海格力电器股份有限公司 一种空调室外机冷媒加热装置及包括该装置的空调
CN115950003A (zh) * 2018-12-07 2023-04-11 大金工业株式会社 空气调节系统
CN113465059B (zh) * 2021-05-31 2023-02-03 华为数字能源技术有限公司 一种蒸发冷却机组及数据中心
CN113983529A (zh) * 2021-11-17 2022-01-28 美智光电科技股份有限公司 浴霸的控制方法、计算机可读存储介质及浴霸
WO2023112428A1 (ja) * 2021-12-17 2023-06-22 ダイキン工業株式会社 換気装置、空調システム、換気方法、及び換気システム
JP7436877B2 (ja) * 2021-12-17 2024-02-22 ダイキン工業株式会社 換気装置、及び換気方法
WO2024127473A1 (ja) * 2022-12-12 2024-06-20 三菱電機株式会社 暖房換気システム

Citations (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4441335A (en) * 1982-08-19 1984-04-10 Honeywell Inc. Heat pump
US4766734A (en) * 1987-09-08 1988-08-30 Electric Power Research Institute, Inc. Heat pump system with hot water defrost
US5473907A (en) * 1994-11-22 1995-12-12 Briggs; Floyd Heat pump with supplementary heat
US6038879A (en) * 1995-08-08 2000-03-21 Yvon Turcotte Combined air exchange and air conditioning unit
US6212900B1 (en) * 1991-04-26 2001-04-10 Nippendenso Co., Ltd. Automotive air conditioner having condenser and evaporator provided within air duct
JP2002005487A (ja) * 2000-04-19 2002-01-09 Harman Co Ltd 換気装置
US20030070787A1 (en) * 2001-09-17 2003-04-17 Moffitt Ronnie R. Dual exhaust energy recovery system
US6595011B1 (en) * 2002-05-02 2003-07-22 Linda Forgy Chaney Water cooled air conditioner
US6604376B1 (en) * 1999-01-08 2003-08-12 Victor M. Demarco Heat pump using treated water effluent
US6675601B2 (en) * 2001-10-18 2004-01-13 Sanyo Electric Co., Ltd. Air conditioner
US6679321B2 (en) * 2001-08-31 2004-01-20 Keum Su Jin Heat pump system
US6759634B2 (en) * 2001-09-11 2004-07-06 Donglei Wang Electric fryer
US20050051310A1 (en) * 2002-12-10 2005-03-10 Matsushita Electric Industrial Co., Ltd. Double-pipe heat exchanger
US6895768B2 (en) * 2001-06-11 2005-05-24 Daikin Industries, Ltd. Refrigerant circuit
US20050252229A1 (en) * 2002-02-06 2005-11-17 Jose Moratalla Air conditioning system
US6974383B2 (en) * 2003-01-31 2005-12-13 American Standard International Inc. Cabinet for air handling equipment
US20070028640A1 (en) * 2005-08-02 2007-02-08 Little Giant Pump Company Condensate removal apparatus and method
JP2007051824A (ja) * 2005-08-18 2007-03-01 Matsushita Electric Ind Co Ltd 空気調和装置
US20070157660A1 (en) * 2006-01-09 2007-07-12 Samsung Electronics Co., Ltd. Air conditioner capable of selectively dehumidifying separate areas
US20070169927A1 (en) * 2004-02-19 2007-07-26 Kinji Isaka Heat exchange type ventilator

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS52115548A (en) * 1976-03-24 1977-09-28 Matsushita Electric Ind Co Ltd Heat pump type air conditioning system
JPS62169960A (ja) * 1986-01-22 1987-07-27 Sanden Corp 浴室用ユニツト
JP2502097B2 (ja) * 1987-07-27 1996-05-29 松下電工株式会社 冷暖房換気装置
JPH0914694A (ja) * 1995-06-29 1997-01-17 Takasago Thermal Eng Co Ltd 水熱源型ヒートポンプユニット空調システムおよび水熱源型ヒートポンプ空調機
JP2002317998A (ja) * 2001-04-20 2002-10-31 Daikin Ind Ltd 換気システム
CN2497198Y (zh) * 2001-09-05 2002-06-26 董军 室内空气环境控制器
JP4338120B2 (ja) * 2002-12-05 2009-10-07 新晃工業株式会社 空気調和装置
JP2005055109A (ja) * 2003-08-06 2005-03-03 Matsushita Electric Ind Co Ltd ヒートポンプ式暖房乾燥装置
JP3969381B2 (ja) * 2003-11-12 2007-09-05 松下電器産業株式会社 多室型空気調和機
JP4042688B2 (ja) * 2003-12-16 2008-02-06 マックス株式会社 浴室空調装置
JP2005241160A (ja) * 2004-02-27 2005-09-08 Toto Ltd 浴室換気暖房乾燥装置
JP4425695B2 (ja) * 2004-05-12 2010-03-03 三菱電機株式会社 換気空調装置
CN2738150Y (zh) * 2004-06-08 2005-11-02 重庆大学 分体式热回收空调装置
JP3864982B2 (ja) * 2005-05-30 2007-01-10 ダイキン工業株式会社 空調システム
JP4696858B2 (ja) * 2005-11-04 2011-06-08 パナソニック株式会社 除湿システム

Patent Citations (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4441335A (en) * 1982-08-19 1984-04-10 Honeywell Inc. Heat pump
US4766734A (en) * 1987-09-08 1988-08-30 Electric Power Research Institute, Inc. Heat pump system with hot water defrost
US6212900B1 (en) * 1991-04-26 2001-04-10 Nippendenso Co., Ltd. Automotive air conditioner having condenser and evaporator provided within air duct
US5473907A (en) * 1994-11-22 1995-12-12 Briggs; Floyd Heat pump with supplementary heat
US6038879A (en) * 1995-08-08 2000-03-21 Yvon Turcotte Combined air exchange and air conditioning unit
US6604376B1 (en) * 1999-01-08 2003-08-12 Victor M. Demarco Heat pump using treated water effluent
JP2002005487A (ja) * 2000-04-19 2002-01-09 Harman Co Ltd 換気装置
US6895768B2 (en) * 2001-06-11 2005-05-24 Daikin Industries, Ltd. Refrigerant circuit
US6679321B2 (en) * 2001-08-31 2004-01-20 Keum Su Jin Heat pump system
US6759634B2 (en) * 2001-09-11 2004-07-06 Donglei Wang Electric fryer
US20030070787A1 (en) * 2001-09-17 2003-04-17 Moffitt Ronnie R. Dual exhaust energy recovery system
US7150314B2 (en) * 2001-09-17 2006-12-19 American Standard International Inc. Dual exhaust energy recovery system
US6675601B2 (en) * 2001-10-18 2004-01-13 Sanyo Electric Co., Ltd. Air conditioner
US20050252229A1 (en) * 2002-02-06 2005-11-17 Jose Moratalla Air conditioning system
US6595011B1 (en) * 2002-05-02 2003-07-22 Linda Forgy Chaney Water cooled air conditioner
US20050051310A1 (en) * 2002-12-10 2005-03-10 Matsushita Electric Industrial Co., Ltd. Double-pipe heat exchanger
US6974383B2 (en) * 2003-01-31 2005-12-13 American Standard International Inc. Cabinet for air handling equipment
US20070169927A1 (en) * 2004-02-19 2007-07-26 Kinji Isaka Heat exchange type ventilator
US20070028640A1 (en) * 2005-08-02 2007-02-08 Little Giant Pump Company Condensate removal apparatus and method
JP2007051824A (ja) * 2005-08-18 2007-03-01 Matsushita Electric Ind Co Ltd 空気調和装置
US20070157660A1 (en) * 2006-01-09 2007-07-12 Samsung Electronics Co., Ltd. Air conditioner capable of selectively dehumidifying separate areas

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8756943B2 (en) * 2011-12-21 2014-06-24 Nordyne Llc Refrigerant charge management in a heat pump water heater
US9383126B2 (en) 2011-12-21 2016-07-05 Nortek Global HVAC, LLC Refrigerant charge management in a heat pump water heater
US20130160985A1 (en) * 2011-12-21 2013-06-27 Nordyne Inc. Refrigerant charge management in a heat pump water heater
US10222085B2 (en) 2012-02-29 2019-03-05 Carrier Corporation Energy recovery ventilator with reduced power consumption
US11378300B2 (en) 2012-02-29 2022-07-05 Carrier Corporation Energy recovery ventilator with reduced power consumption
EP2719967A1 (de) * 2012-10-09 2014-04-16 Roth Werke GmbH Verfahren zur Temperierung eines Gebäudes
US20170010027A1 (en) * 2014-01-27 2017-01-12 Qingdao Hisense Hitachi Air-Conditionung Systems Co., Ltd Heat recovery variable-frequency multi-split heat pump system and control method thereof
US20190032968A1 (en) * 2014-01-27 2019-01-31 Qingdao Hisense Hitachi Air-conditioning Systems Co., Ltd. Outdoor Unit of an Air Conditioning System, Air Conditioning System, and Control Method Thereof
US10132530B2 (en) * 2014-01-27 2018-11-20 Qingdao Hisense Hitachi Air-conditioning Systems Co., Ltd. Heat recovery variable-frequency multi-split heat pump system and control method thereof
US11035597B2 (en) * 2014-01-27 2021-06-15 Qingdao Hisense Hitachi Air-conditioning Systems Co., Ltd. Outdoor unit of an air conditioning system, air conditioning system, and control method thereof
CN107101287A (zh) * 2017-06-20 2017-08-29 合肥天鹅制冷科技有限公司 坑道除湿空调机
CN110145835A (zh) * 2019-05-17 2019-08-20 青岛海尔空调器有限总公司 空调新风系统
CN110398048A (zh) * 2019-07-23 2019-11-01 广东美的暖通设备有限公司 空调系统、空调控制方法、空调控制装置和存储介质
US11913460B2 (en) 2020-03-20 2024-02-27 Greenheck Fan Corporation Exhaust fan
IT202000030143A1 (it) * 2020-12-09 2022-06-09 Giuseppe Polverelli Impianto di riscaldamento e deumidificazione simultanea di un locale.
WO2022122671A1 (en) 2020-12-09 2022-06-16 Polverelli Giuseppe System for simultaneously heating and dehumidifying a room
US11982458B2 (en) 2022-01-18 2024-05-14 Haier Us Appliance Solutions, Inc. Air conditioner makeup air circulation

Also Published As

Publication number Publication date
CN101790667A (zh) 2010-07-28
JP2009058175A (ja) 2009-03-19
CN101790667B (zh) 2013-03-06
JP5076745B2 (ja) 2012-11-21
WO2009028184A1 (ja) 2009-03-05

Similar Documents

Publication Publication Date Title
US20110100043A1 (en) Air conditioning/ventilating system
CN101490483B (zh) 换气空调装置
CN102767876B9 (zh) 热泵热回收空调机组
CN108679870A (zh) 一种带新风处理功能的温湿分控空调系统
JP5256828B2 (ja) 換気空調装置
JP4735573B2 (ja) 換気空調装置
KR100430278B1 (ko) 히트파이프를 적용한 에너지 절약형 폐열회수 공기조화기
JP4647399B2 (ja) 換気空調装置
JPH0814389B2 (ja) 直膨型熱交換器を用いたクリーンルーム
CN107763737B (zh) 一种空调室内机及空调
KR100728590B1 (ko) 절전형 고효율 히트펌프 환기장치
US6931868B1 (en) Air conditioning system
JP4302551B2 (ja) 冷房装置
JP4594552B2 (ja) 浴室乾燥装置
KR100712857B1 (ko) 혼합형 유니터리 공기조화장치의 냉매량 조절방법
CN215832055U (zh) 一种室内空气处理系统
KR100452807B1 (ko) 폐열회수식 냉난방 겸용 공기조화기
CN207299324U (zh) 再热型热泵热回收空调机组
CN104359166B (zh) 一种双冷源潜热处理低温空调机组及其控制方法
KR100871116B1 (ko) 히트 펌프를 이용한 엘리베이터 냉난방기
CN215675528U (zh) 一体化户式辐射空调能源系统
KR102597140B1 (ko) 인버터 압축기를 이용한 고효율 항온항습기
CN214791447U (zh) 一种具有余热回收功能的空调器
US20230250976A1 (en) Air conditioner
WO2024060836A1 (zh) 新风设备的控制方法、新风设备以及存储介质

Legal Events

Date Code Title Description
AS Assignment

Owner name: PANASONIC CORPORATION, JAPAN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:MATUBARA, MITUNORI;SUGATA, YUUJI;TSUBOUCHI, MASAFUMI;AND OTHERS;SIGNING DATES FROM 20100126 TO 20100201;REEL/FRAME:024191/0664

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION