US3867979A - Air-conditioning method and apparatus with heat pump - Google Patents

Air-conditioning method and apparatus with heat pump Download PDF

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Publication number
US3867979A
US3867979A US159681A US15968171A US3867979A US 3867979 A US3867979 A US 3867979A US 159681 A US159681 A US 159681A US 15968171 A US15968171 A US 15968171A US 3867979 A US3867979 A US 3867979A
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United States
Prior art keywords
air
condenser
duct
temperature
heat
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US159681A
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English (en)
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Jean Carrasse
Denise Desbrosses
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Cegelec SA
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Cegelec SA
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F12/00—Use of energy recovery systems in air conditioning, ventilation or screening
    • F24F12/001—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air
    • F24F12/002—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air using an intermediate heat-transfer fluid
    • F24F12/003—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air using an intermediate heat-transfer fluid using a heat pump
    • 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
    • F24F3/001—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 in which the air treatment in the central station takes place by means of a heat-pump or by means of a reversible 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
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F12/00—Use of energy recovery systems in air conditioning, ventilation or screening
    • F24F12/001—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air
    • F24F2012/007—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air using a by-pass for bypassing the heat-exchanger
    • 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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/006—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass for preventing frost
    • 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]
    • Y02B30/52—Heat recovery pumps, i.e. heat pump based systems or units able to transfer the thermal energy from one area of the premises or part of the facilities to a different one, improving the overall efficiency
    • 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]
    • Y02B30/56—Heat recovery units

Definitions

  • ABSTRACT Toprevent icing on the vaporization surfaces of the condenser in a heat pump air-conditioning system the temperature of the air in contact with the condenser is raised by applying additional heat thereto, for example by an electric heating coil, bleeding of fresh air, or feedback of heated air.
  • FIG/l AIR-CONDITIONING METHOD AND APPARATU WITI-I HEAT PUMP The present invention relates at a process and an apparatus for air-conditioning of an enclosed space, for example residential, commercial or plant space, utilizing a heatpump cycle.
  • a heat exchange fluid When the interior temperature isless than the desired value, a heat exchange fluid is condensed with exterior air entering the space, and the heat exchange fluid is expanded and vaporized and heat is then exchanged with the air leaving the space; whereas, when the interior temperature is higher than the desired value,- the heat exchange fluid in the cycle is condensed by heat exchanging air leaving the space and the vaporization, or expansion heat exchange is carried out with exterior fresh air being supplied, or with air being recirculated.
  • Two temperature zones of exterior, ambient temperatures may be distinguished. These two zones are separated by a temperature level which may be termed a critical temperature, below which the power necessary in order to maintain the space at the desired temperature, due to heat losses of thespace and necessary reheating of the air to bev ventilated, is greater than the power which can be supplied by the compressor of the cycle,
  • a critical temperature below which the power necessary in order to maintain the space at the desired temperature, due to heat losses of thespace and necessary reheating of the air to bev ventilated, is greater than the power which can be supplied by the compressor of the cycle.
  • the critical temperature When the outside temperature is higher or greater than the critical temperature, then it is possible to operate the. cycle .without icing and without additional heating by an external source ofheat, since power supplied and heat losses will be, or can be maintained to be in balancelf, however, the exterior temperature is less than the critical temperature, additional heat energy must be supplied to restore the balance, for example by means of an auxiliary heating unit, such as one or more electrical resistance units.
  • the three embodiments may be used in It is an object of the present invention to overcome the disadvantages of known heat pump cycles by providing for operation of the heat pump evaporator under such condition that it will not ice, even if the outer side ambient temperatures drop substantially below freezing, that is below 0 C.
  • the heat pump cycle is to operate economically, regardless of outside temperatures, and continuously so that the temperature being maintained in the space to be controlled will be little different regardless of outside temperatures.
  • the heat energy being supplied should be efficiently utilized and permit different rates of ventilation and heat losses, as well as choice of interior temperature to be maintained; the heat pumps themselves should be capable of supplying sufficient heat while being of essentially uniform con- SUBJECTMATTER OF THE PRESENT INVENTION
  • the mean temperature of air in contact with the condenser is artifically increased over the mean temperature which would result from heat exchange by the condenser with air at outside temperature entering the space to be heated during those period of time when the vaporization temperature of the heat exchange fluid, in heat exchange with'the air leaving the space, is sufficientlylow to be subjected to risk of icing of the heat exchange surface, itself.
  • the mean temperature of the air in contact with the condenser can be raised by various means; in accordance with one-embodiment, an external, separate and independent heat source isprovided, preferably an electrical resistance unit; in accordance with anohter embodiment, a portion of the exterior air is bypassed and reunited with a portion of the air which passed the condenser, so that the condenser received additional heating by thelesser amount of heat being removed, due to the bypass; or, a portion of the heated air which already has contacted the condenser is rel-cycled and fed back to the condenser unit itself to pre-heat the air entering into the condenser, thus supplying additional heat to the condensing heat exchange step.
  • FIG. 1 is a schematic diagram of a heat pump installationlutilizing electrical resistance elements to supply additional heat
  • v 1 is a schematic diagram of a heat pump installationlutilizing electrical resistance elements to supply additional heat
  • FIG. 2 is a schematic diagram ofaheat-pump installa-- tion utilizing'bypass of fresh air
  • J FIG. 3 is a schematic diagram ofaheat pump installation using a re-cycling feedback of heated air.
  • the upper portion of the Figures represents the space to be temperature controlled, and'the lower portion of the Figures represents outside ambient atmosphere.
  • a compressor compresses the heat exchange fluid, such as a refrigeration fluid for example known under the tradename FREON (a fluorinated hydrocarbon) having a low boiling point at'atmospheric pressure.
  • FREON a fluorinated hydrocarbon
  • Other heat exchange fluids may be used, such as ammonia or sulphurous anhydride.
  • the compressed heat exchange gas is conducted over pipes 2 to a condenser 3.
  • the heat exchange gas liquefies in condenser 3, and, in the process, heats the air which is supplied from the outside atmosphere to the interior of the conditioned spacae.
  • the heat exchange fluid is then applied over pipe 4 to expansion valve 5, where the liquefled gas expands and passes over pipe 6 into evaporator 7 where it will vaporize, in the process cooling and de-humidifying used air being exhausted from the space to be temperature controlled and ventilated.
  • the heat exchange fluid is led back to the suction side of the compressor over pipe 8.
  • Air is exhausted from the conditioned space by a fan or exhaust ventilator 10 located in an air duct 9. It is cooled and de-humidified by contact with the evaporator 7. Condensation water is removed by mens well known in the art and not shown in the drawing. Fresh air is introduced into the space to be controlled by a fan or ventilator 12 located in a duct 11.
  • Duct 11 includes an electrical resistance unit 13 which provides for a first pre-heating of air before it comes in contact with condenser 3.
  • the pre-heated air after contacting the condenser, may be subjected to additional heating to reach the desired temperature of air to be introduced in the space, usually at least 35 C.
  • Additional heaters l4, 15, which are electrical resistance heating units and which may be similar to unit 13 are provided to complete further heating ifthe outside temperature is very low.
  • the energy supplied by the resistance heating unit 14 may be calculated to provide for a desired temperature of air being introduced into the space when the outside temperature drops to about -C; the energy supplied by resistance 15 then may be calculated to assure heating if the temperature drops by another 5, that is, when the outside temperature is about C, both resistances 14 and are placed in circuit. Resistance 13 is connected when the temperature drops to close to freezing.
  • Embodiment of FIG. 2 The circuit of the heat exchange fluid is identical to that of FIG. 1 and will not be described again, and the same reference numerals have been used.
  • the inlet heat duct 11' supplying fresh air, is formed with .
  • a bypass line 16 in which a control valve or air flow regulator 17 is placed.
  • a portion of the air entering the duct 11, and drawn therethrough by ventilator 12 will flow through the bypass l6 and is then mixed with the major portion behind condenser 3.
  • the mean temperature of the air being supplied at the outlet of duct 11' will thus be less than the temperature to which the condenser is subjected, thus increasing the temperature of condensation.
  • heating unit 13 can be placed either before, or behind the entrance of bypass 16, preferably between the entrance to bypass l6 and condenser 3. Heating unit 14, 15 can be located preferably downstream from the exit of bypass 16.
  • Embodiment of FIG. 3 The heat exchange fluid cycle is identical to that of FIG. 1, has been given the same reference numerals, and will now be described again.
  • lnlet duct 11 through which fresh air is admit ted from the outside atmosphere has a re-cycling bypass 18 connected thereto, in which a control valve or air flow control blade 19 is installed.
  • re-cycling feedback duct 18 takes a portion of the air heated by the condenser and re-cycles it back to the advance of the condenser, for additional heat supply thereto.
  • the amount of air passing the condenser is thus increased and is larger than the amount of air introduced into the space to be temperature controlled; the temperature at the inlet to the condenser is greater than that which the air would have in the absence of recycling; the temperature at the outlet of duct 11 is for all practical purposes unaffected.
  • This form of the invention permits an increase of the temperature of the condensed heat exchange fluid, and thus an increase of the vaporization temperature and a ready means to avoid any risk of icing at the only costs of requiring a fan or ventilator 12 which is slightly more powerful than that necessary for the embodiment, for example, of FIG. 1,. or for a similar installation without the recycling arrangement formed of bypass and feedback tube 18 and the control element 19.
  • elements 13 may be upstream from the exit of duct 18 and elements 14,15 may be downstream from the entrance to duct 18.
  • the additional air introduced could be mixed not only with air re-cycled downstream from the condenser, but also with air taken from the space to be temperature controlled. This also increase the input temperature of the air to the condenser, but only very slightly, since the difference in temperature between the exteriorair' and the air in the interior of the space to be controlled is not sufficiently great to substantially affect the vaporization temperature at the condenser.
  • condenser is increased, such that the mean temperature of the air in contact with the condenser is notsufficiently increased to greatly affect the operation of the system. It is, therefore, a not generally satisfactory solution to utilize air from the space to be temperature controlled as a source for supplying additional heat to the condenser.
  • air may be split or re-cycled, or applied to only aportion of the heat exchange surface of the condensers.
  • the source of additional heat to be supplied need not be an electrical resistance wire, but may be obtained. from heat exchangers of any kind, boilers, gas or liquid heaters and the like.
  • the heat pump cycle may be by compression and/or fractionated expansion. Rather than utilizing ambient air from the atmosphere, a portion of the ambient air may be taken from the space, to be re-cycled and when reference is made to fresh air being introduced, such air may be withdrawn, filtered and re-cycled back to the space which is to be temperature controlled, at least in part.
  • Air-conditioning apparatus employing a heat pump of the kind continuously circulating air between a space to be conditioned and external ambient air and continuously performing inverse heat exchange operations relative to a refrigerant respectively on the intake air to said space and on the exhaust air therefrom, comprising a compressor, a condenser, and an evaporator c onnected in a closed circuit to form a heat pump and providing for the circulation of a refrigerant;
  • a first duct including air moving means for drawing exterior air over said condenser into an enclosed space
  • a second duct including air moving means for the exhaust of interior air over said evaporator from said enclosed space;
  • first duct for raising the temperature of condensation of said refrigerant within said condenser by reducing the cooling efnected to said first duct between the entrance thereof and said condenser and an outlet connected to said first duct beyond said condenser, and the air moving means of said first duct is positioned therein beyond the outlet of said bypass line; thereby to provide a bypass of said condenser for a part of the exterior air drawn into said a first duct.
  • the temperature raising means comprises a bypass line, including a regulator. having an inlet connected to said first duct between the entrance thereof and said condenser and an outlet connected to said first duct beyond said condenser, and the air moving means of said first duct is positioned therein between said condenser and the outlet of said bypass line; thereby to recycle a part of the exterior air drawn into said first duct.
US159681A 1970-07-07 1971-07-06 Air-conditioning method and apparatus with heat pump Expired - Lifetime US3867979A (en)

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FR7025409A FR2109052A5 (es) 1970-07-07 1970-07-07

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JP (1) JPS4929325B1 (es)
BE (1) BE769626A (es)
DE (1) DE2133060C3 (es)
ES (1) ES196640Y (es)
FR (1) FR2109052A5 (es)
GB (1) GB1360072A (es)
NL (1) NL155939C (es)

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4024728A (en) * 1975-02-18 1977-05-24 Projectus Industriprodukter Ab Method of and an installation for controlling the temperature of a plurality of rooms having mutually differing and varying heating requirements, among which rooms there is normally a cooling requirement
US4141408A (en) * 1976-06-16 1979-02-27 Rheem Manufacturing Company Supplementary heat control for heat pump system
US4175403A (en) * 1976-06-07 1979-11-27 Jon Lunde Heat recovery system
US4232821A (en) * 1977-05-06 1980-11-11 Backlund Anders Daniel Heating and ventilation system
US4505327A (en) * 1981-04-09 1985-03-19 Lonnie L. Angle Heating and cooling apparatus having evaporative cooler and heat pump
US5299631A (en) * 1992-01-31 1994-04-05 Valeo Thermique Habitacle Heating and ventilating apparatus for the cabin of a motor vehicle having a low heat loss motor
US5425403A (en) * 1993-09-24 1995-06-20 Herrmann; Otto Device for filling bags with a powder-like or granular flowable material, especially sand
US5501088A (en) * 1994-02-14 1996-03-26 Yates; Jan B. Exhaust gas discharge system for a gas engine heat pump
US5715690A (en) * 1996-10-03 1998-02-10 Ponder; Henderson F. Microwave thermal heat pump defroster
US5722245A (en) * 1996-08-27 1998-03-03 Ponder; Henderson Frank Microwave heat pump defroster
US5771699A (en) * 1996-10-02 1998-06-30 Ponder; Henderson F. Three coil electric heat pump
WO2001075379A1 (en) * 2000-03-29 2001-10-11 Eversave Ab Method and apparatus for increasing the effect in air heat pumps
WO2009053726A2 (en) * 2007-10-24 2009-04-30 Thermal Energy Systems Limited Heat pump
US20100212334A1 (en) * 2005-11-16 2010-08-26 Technologies Holdings Corp. Enhanced Performance Dehumidification Apparatus, System and Method
US20100275630A1 (en) * 2005-11-16 2010-11-04 Technologies Holdings Corp. Defrost Bypass Dehumidifier
US20140144176A1 (en) * 2011-04-29 2014-05-29 Carrier Corporation Air Conditioner Exhaust Recycling
EP2997314A4 (en) * 2013-02-15 2016-10-26 Nortek Air Solutions Canada Inc PRE-HEAT SPECIALIZED EXTERIOR AIR SYSTEM AND METHOD THEREOF
CN108759015A (zh) * 2018-05-18 2018-11-06 广东美的暖通设备有限公司 新风机的预热控制方法及系统

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FR2280039A1 (fr) * 1974-07-24 1976-02-20 Alsthom Cgee Machine thermodynamique fonctionnant en pompe de chaleur
FR2288278A1 (fr) * 1974-10-18 1976-05-14 Bergeon Et Cie Systeme a pompe de chaleur pour conditionnement de l'interieur de batiments
SE397218B (sv) * 1975-03-21 1977-10-24 Svenska Flaektfabriken Ab Forfarande for vermeoverforing mellan franluft och tilluft i en ventilationsanleggning
FR2328163A1 (fr) * 1975-10-16 1977-05-13 Chauffe Cie Gle Perfectionnements aux dispositifs de chauffage des locaux par l'utilisation de pompes a chaleur
DE2627734C3 (de) * 1976-06-21 1981-08-20 Weiss Technik GmbH Umwelt-Klima-Messtechnik, 6301 Reiskirchen Klimatisier- und Lüftungsvorrichtung mit Wärmerückgewinnung
DE2630667C3 (de) * 1976-07-08 1982-01-07 Interliz Anstalt, Vaduz Lüftungsgerät
SE402486B (sv) * 1976-11-09 1978-07-03 Svenska Flaektfabriken Ab Vermeatervinningsanleggning
FR2451548A1 (fr) * 1979-03-12 1980-10-10 Totalgaz Cie Fse Procede perfectionne de rechauffage d'un fluide gazeux, par couplage d'une pompe a chaleur avec un generateur d'energie calorifique a combustible gazeux ou liquide
DE3018046A1 (de) * 1979-05-12 1980-11-20 Mckirdy Temperatur-regelsystem
WO1982003446A1 (en) * 1981-04-01 1982-10-14 Engel Alfred Three-fluid operating thermal assembly associating a heat collecting and transfer unit to a heating member
FR2503336A1 (fr) * 1981-04-01 1982-10-08 Dietrich De Ensemble de recuperation et de transfert d'energie calorifique a trois fluides et quatre circuits
FR2504246A1 (fr) * 1981-04-17 1982-10-22 Pvb Architectes Ste Civile Pro Procede et installation pour la ventilation d'un immeuble
DE3719391A1 (de) * 1987-06-08 1988-12-29 Hansa Ventilatoren Masch Raumlufttechnisches geraet
DE4412844C2 (de) * 1994-02-09 1999-06-17 Stiebel Eltron Gmbh & Co Kg Klimagerät
CZ299573B6 (cs) * 2004-04-05 2008-09-03 Mach@Stanislav Tepelné cerpadlo
JP7199574B2 (ja) 2019-12-09 2023-01-05 三菱電機株式会社 冷却装置および電力変換装置
CN116465063A (zh) * 2021-11-24 2023-07-21 广东美的制冷设备有限公司 新风机防结霜控制方法、新风机和计算机可读存储介质

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US2293482A (en) * 1941-06-26 1942-08-18 Gen Electric Heat pump
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Cited By (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4024728A (en) * 1975-02-18 1977-05-24 Projectus Industriprodukter Ab Method of and an installation for controlling the temperature of a plurality of rooms having mutually differing and varying heating requirements, among which rooms there is normally a cooling requirement
US4175403A (en) * 1976-06-07 1979-11-27 Jon Lunde Heat recovery system
US4141408A (en) * 1976-06-16 1979-02-27 Rheem Manufacturing Company Supplementary heat control for heat pump system
US4232821A (en) * 1977-05-06 1980-11-11 Backlund Anders Daniel Heating and ventilation system
US4505327A (en) * 1981-04-09 1985-03-19 Lonnie L. Angle Heating and cooling apparatus having evaporative cooler and heat pump
US5299631A (en) * 1992-01-31 1994-04-05 Valeo Thermique Habitacle Heating and ventilating apparatus for the cabin of a motor vehicle having a low heat loss motor
US5425403A (en) * 1993-09-24 1995-06-20 Herrmann; Otto Device for filling bags with a powder-like or granular flowable material, especially sand
US5501088A (en) * 1994-02-14 1996-03-26 Yates; Jan B. Exhaust gas discharge system for a gas engine heat pump
US5722245A (en) * 1996-08-27 1998-03-03 Ponder; Henderson Frank Microwave heat pump defroster
US5771699A (en) * 1996-10-02 1998-06-30 Ponder; Henderson F. Three coil electric heat pump
US5715690A (en) * 1996-10-03 1998-02-10 Ponder; Henderson F. Microwave thermal heat pump defroster
WO2001075379A1 (en) * 2000-03-29 2001-10-11 Eversave Ab Method and apparatus for increasing the effect in air heat pumps
US8769969B2 (en) 2005-11-16 2014-07-08 Technologies Holdings Corp. Defrost bypass dehumidifier
US20100212334A1 (en) * 2005-11-16 2010-08-26 Technologies Holdings Corp. Enhanced Performance Dehumidification Apparatus, System and Method
US20100275630A1 (en) * 2005-11-16 2010-11-04 Technologies Holdings Corp. Defrost Bypass Dehumidifier
US8316660B2 (en) 2005-11-16 2012-11-27 Technologies Holdings Corp. Defrost bypass dehumidifier
US8347640B2 (en) 2005-11-16 2013-01-08 Technologies Holdings Corp. Enhanced performance dehumidification apparatus, system and method
WO2009053726A3 (en) * 2007-10-24 2009-08-06 Thermal Energy Systems Ltd Heat pump
WO2009053726A2 (en) * 2007-10-24 2009-04-30 Thermal Energy Systems Limited Heat pump
US20140144176A1 (en) * 2011-04-29 2014-05-29 Carrier Corporation Air Conditioner Exhaust Recycling
US9920973B2 (en) * 2011-04-29 2018-03-20 Carrier Corporation Air conditioner exhaust recycling
EP2997314A4 (en) * 2013-02-15 2016-10-26 Nortek Air Solutions Canada Inc PRE-HEAT SPECIALIZED EXTERIOR AIR SYSTEM AND METHOD THEREOF
CN108759015A (zh) * 2018-05-18 2018-11-06 广东美的暖通设备有限公司 新风机的预热控制方法及系统

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NL7109347A (es) 1972-01-11
NL155939C (nl) 1979-10-15
BE769626A (fr) 1972-01-07
ES196640U (es) 1975-03-16
DE2133060A1 (de) 1972-01-13
NL155939B (nl) 1978-02-15
JPS4929325B1 (es) 1974-08-03
FR2109052A5 (es) 1972-05-26
DE2133060C3 (de) 1981-12-24
GB1360072A (en) 1974-07-17
ES196640Y (es) 1975-08-01
DE2133060B2 (de) 1981-04-23

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