WO2001096794A1 - Procede et dispositif de climatisation recuperant la chaleur perdue - Google Patents

Procede et dispositif de climatisation recuperant la chaleur perdue Download PDF

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Publication number
WO2001096794A1
WO2001096794A1 PCT/PL2001/000033 PL0100033W WO0196794A1 WO 2001096794 A1 WO2001096794 A1 WO 2001096794A1 PL 0100033 W PL0100033 W PL 0100033W WO 0196794 A1 WO0196794 A1 WO 0196794A1
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WO
WIPO (PCT)
Prior art keywords
air
evaporator
conditioned space
duct
condenser
Prior art date
Application number
PCT/PL2001/000033
Other languages
English (en)
Inventor
Bogusław ZAKRZEWSKI
Original Assignee
Zakrzewski Boguslaw
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 Zakrzewski Boguslaw filed Critical Zakrzewski Boguslaw
Priority to AU2001252801A priority Critical patent/AU2001252801A1/en
Publication of WO2001096794A1 publication Critical patent/WO2001096794A1/fr

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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
    • 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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/0001—Control or safety arrangements for ventilation
    • F24F2011/0002—Control or safety arrangements for ventilation for admittance of outside air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2221/00—Details or features not otherwise provided for
    • F24F2221/54—Heating and cooling, simultaneously or alternatively
    • 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

  • the present invention relates to a method for regulation of air parameters in conditioned spaces, especially in stores of products sensitive to climatic conditions, system for regulation of air parameters in conditioned spaces, especially in stores of products sensitive to climatic conditions and apparatus for regulation of air parameters in conditioned spaces, especially in stores of products sensitive to climatic conditions.
  • a method and system for air-conditioning of frozen food packing compartments in cold stores with cooling, heating and dehumidifying air in layered heat exchangers filled with refrigerant is known from description of the Patent No PL 157065.
  • the method is characterized in simultaneous action of two separate recirculative air circulations.
  • the first circulation takes place in the upper part of the conditioned space and consists in cooling air in summer period and heating air in winter period to required temperature using fan heat exchangers.
  • the second circulation takes place in the lower part of the conditioned space and consists in dehumidifying moist air.
  • the air from the conditioned space is passed to the dehumidification unit where it is cooled to remove moisture.
  • the dehumidified air is heated to required temperature and passed to the conditioned space containing frozen food.
  • the essence of the system consists in that heat exchangers connected to the cooling arrangement are situated under the ceiling in opposite corners of the compartment.
  • Intake duct of dehumidified air connected to the fan and the dehumidification unit with built-in isolated heat exchanger blocked with tray and another exchanger and suction duct with inlet openings, is situated over the floor on the opposite side to outlet openings of the air intake duct.
  • Both exchangers of the dehumidification system and the tray are connected to refrigeration arrangement.
  • the device for continuos dehumidifying air with housing formed by ventilation duct is described in Patent No PL 157051.
  • Surface cooler with condensate tank, cooling compressor, air-cooled condenser and fan are situated in the ventilation duct.
  • the method of continuos dehumidifying air consists in that in the first stage stream of outdoor air passes through the cooler.
  • the cooler cools the air to temperature lower than dewpoint of outdoor air and, as a result, portion of moisture from dehumidified air is released on the cooler surface.
  • the second stage stream of dehumidified air, being in saturated state passes through the heater and is heated to temperature greater than dewpoint.
  • the device has neither a possibility to decrease air temperature below ambient temperature nor keep air temperature at required level.
  • the known air-conditioning system with air parameter control described in handbook "Heating and air-conditioning", Recknagel.Sprenger.Honmann.Scliramek EWFE, Gdansk, 1994, p. 1769 contains a cooling system composed of the compressor connected to heat exchangers, evaporator and condenser via the pipeline.
  • the system is equipped with an expansion valve, control valves, air fans and a device for automatic circulation adjustment. Air circulation in conditioned space is forced; fan impels air stream to the ventilation duct and evaporator situated there.
  • Each exchanger can operate as air cooler or condenser, after switching over the multi-way valve each exchanger can also operate as a condenser heating the conditioned space.
  • the method according to the invention using compressor cooling circulation and air circulation through the ventilation ducts equipped with dampers consists in that in the air cooling cycle in air conditioned space, indoor air is passed to the first heat exchanger of the cooling system being an evaporator, and air outdoor is passed to the second heat exchanger being a condenser.
  • direction of circulation is reversed so that the first heat exchanger is a condenser and the second one is an evaporator and the indoor air fan and outdoor air fan are switched off.
  • Indoor air is passed to the evaporator and further back to the conditioned space while outdoor air is passed to the condenser.
  • the conditioned space air fan When temperature of the evaporator surface is near its ambient temperature, the conditioned space air fan is switched on, and the fan forcing air stream around the condenser is switched on when temperature of the condenser surface is near its ambient temperature.
  • indoor air is supplied to the condenser and the air is passed back to the conditioned space while outdoor air is supplied to the evaporator.
  • direction of circulation is reversed so that the first heat exchanger is again an evaporator and the second one is again a condenser, air stream is shut off to the conditioned space and outdoor air is supplied to the evaporator and condenser.
  • the cycle of dehumidifying air is performed by cooling and heating air. Dependant on the requirements, either continuous dehumidifying air or alternately dehumidifying and heating can be carried out.
  • continuous dehumidifying air indoor air is supplied through the first ventilation duct to the first heat exchanger (evaporator), and indoor air is supplied to the another heat exchanger (condenser).
  • evaporator indoor air is supplied to the condenser and back to the conditioned space
  • outdoor air is supplied to evaporator. After temperature in the conditioned space obtains required value, the direction of air circulation is reversed.
  • indoor air is supplied to the evaporator and outdoor air is supplied to the condenser.
  • the air circulation is repeated many times until required humidity and/or temperature in conditioned space is obtained.
  • indoor air is supplied through the first ventilation duct to the first heat exchanger (evaporator), while to the second heat exchanger (condenser) indoor air is supplied through another ventilation duct (inner duct).
  • defrosting cycle is realized (outdoor air is now supplied to the both heat exchangers) and/or when required value of the monitored temperature in the conditioned space is obtained, outdoor air is periodically supplied to the condenser.
  • the method can be applied either if the temperature close to the heat exchanger surface is above 0 degrees C (32 degrees F) - condensate comes out on the surface, or if the temperature is below 0 degrees C (32 degrees F) - then frost is deposited.
  • the arrangement has much greater efficiency working in the "deep" dehumidification mode - when dewpoint is less than 0 degrees C (?? degrees F) - than the already-known dehumidification systems working in the temperature of evaporator surface below 0 degrees C (32 degrees F) in frosting conditions.
  • the method it is possible to obtain significantly less partial pressures of dehumidified air in conditioned space maintaining large energetic efficiency.
  • warm air from additional source marine power plant
  • Waste heat of marine power plant ventilation system can be applied.
  • the monitored parameter is at the evaporator is time of evaporator operation.
  • the parameter monitored at the evaporator is thickness of frost layer on the evaporator surface.
  • the parameter monitored at the evaporator is difference of the temperature of air in the conditioned space and temperature of the frost surface on the evaporator.
  • the parameter monitored at the evaporator is difference of the temperature of saturation point in the conditioned space and temperature of the frost surface on the evaporator.
  • the parameter monitored at the evaporator is mass of frost.
  • the parameter monitored at the evaporator (1,1') is difference of pressures of refrigerant in front of and behind the evaporator.
  • the parameter monitored at the evaporator is difference of temperatures of air in front of and behind the evaporator.
  • the parameter monitored at he evaporator is temperature of air in the conditioned space.
  • the parameter monitored at the evaporator is relative humidity of air in the conditioned space.
  • the parameter monitored at the evaporator is absolute humidity of air in the conditioned space.
  • a system for regulation of air parameters in conditioned space composed of compressor cooling system and system for air circulation containing ventilation ducts equipped with dampers and fans according to the invention is characterized in that conditioned space is connected to main ventilation duct and two auxiliary ducts connected to the main duct.
  • the first auxiliary duct is connected via first heat exchanger
  • second auxiliary duct is connected to the main duct via second heat exchanger.
  • split damper com ected to system for automatic control and regulation is positioned between the heat exchangers.
  • Auxiliary ducts are connected to conditioned space via inner air dampers and to outdoor space by outer air dampers.
  • first auxiliary duct and second auxiliary duct are connected to third auxiliary duct which is connected to the conditioned space.
  • the conditioned space is connected to the main duct via inner duct and fourth imier air damper, and the main duct is connected to outdoor space via third outer damper.
  • the main duct is connected via fourth damper to supply air duct which is connected to low-temperature waste heat source contained in air, and the main duct is connected to outdoor space via the third outer air damper.
  • split damper is a three-position sequential air damper which can be pivoted by 45°, where in first position "A” the first auxiliary ventilation duct is connected to the conditioned space, and in second position "B” the second auxiliary ventilation duct is connected to the conditioned space, and in null position "0" both ventilation ducts are connected to outdoor space.
  • Apparatus for regulation of air parameters in conditioned spaces equipped with cooling arrangement including compressor, ventilation ducts with dampers and fans according to the invention is characterized in that conditioned space is connected to main ventilation duct and first and second auxiliary ducts.
  • the main duct connects the conditioned space to outdoor space.
  • the first heat exchanger of cooling arrangement is situated between the main duct and first auxiliary duct, and the second heat exchanger is situated between main duct (KG) and second auxiliary duct.
  • Split damper is situated between the heat exchangers, connected to system for automatic control and regulation.
  • Inner dampers are situated on the walls of the ducts on the side of the conditioned space, and outer dampers are situated on the outer walls of the ducts on the side of conditioned space.
  • Outer and inner air fans are connected to the main duct.
  • split damper in the main duct is three-position sequential damper which can be pivoted by 45°, where in first position "A" first auxiliary ventilation duct is connected to the conditioned space, and in second position "B" second auxiliary ventilation duct is connected to the conditioned space, and in null position "0" both heat exchangers are connected to outdoor space.
  • first and second heat exchangers are situated parallelly and opposite to each other.
  • outer air fan is situated at inlet of main duct, and inner air fan is situated at outlet of the main duct to the conditioned space.
  • the method eliminates electric heaters for defrosting evaporators and electric energy for powering compressor decreases by 50% (COP:
  • both heat exchangers upper and lower heat source operate in similar temperatures what ensures maximal energetic efficiency of the heat pump.
  • This implementation gives a possibility of stabilization of air temperature in the conditioned space with accuracy unavailable in other systems, with very low energy consumption and using waste energy.
  • Fig. 1 presents schematically the system according to the invention in the mode of cooling air.
  • Continuous lines and arrows indicate directions of air streams and direction of refrigerant stream.
  • Fig. 2 presents a fragment of the system according to the invention in the defrosting mode during operation as a cooling arrangement.
  • Fig. 3 presents a scheme of the system in the heating air mode. Continuous lines and arrows indicate directions of air streams and direction of refrigerant stream. Dashed line indicate position of four-way valves when the direction of circulation is reversed.
  • Fig. 4 presents a fragment of the system in the mode of heating air and defrosting. Continuous lines and arrows indicate directions of air streams.
  • Fig. 5 presents schematically a modification of the system according to the invention in the mode of cooling air.
  • Fig. 6 presents schematically a modification of the system according to the invention in the mode of heating air using waste heat.
  • Fig. 7 presents schematically a modification of the system according to the invention in the mode of heating air using additional source of outdoor air.
  • Fig. 8 presents schematically a modification of the system in the cycle of dehumidifying air in the conditioned space.
  • the system for regulation of air parameters in conditioned space contains compressor 3.
  • the press pipeline of the compressor is connected to the inlet connector pipe of the first four-way valve Zl, and the remaining connector pipes of the valve are connected to the heat exchangers: first heat exchanger Wl and second heat exchanger W2, and tank 4 with regeneration exchanger
  • Tank 4 is connected to suction pipeline of compressor 3.
  • the inlet of regeneration exchanger is connected to suction pipeline of compressor 3.
  • Valves Zl and Z2 are in first position I in which the direction of circulation is such that first heat exchanger Wl is evaporator
  • Conditioned space (P) is connected to three ventilation ducts: main ventilation duct KG and adjoin auxiliary ducts Kl, K2.
  • first auxiliary duct Kl situated is first heat exchanger Wl
  • second auxiliary duct K2 situated is second heat exchanger W2.
  • First outer air damper is situated on the outer wall of first auxiliary duct Kl, and first heat exchanger Wl is situated on the wall common with main ventilation duct KG.
  • First heat exchanger Wl is evaporator 1, and after reversal of direction of cooling circulation it becomes condenser 2'.
  • Second heat exchanger W2 is condenser 2, and after reversal of direction of cooling circulation it becomes evaporator 1'.
  • Second inner air damper 13 is situated at the outlet of duct Kl to conditioned space P, and second outdoor air 12 is situated on the outer wall of duct Kl. Damper 12 controls air stream from outdoor space to duct Kl .
  • Second outer air damper 11 is situated on the wall of duct K2, and first im er air damper
  • indoor air fan 8 is situated at the outlet of the main duct to conditioned space P.
  • Third inner damper 14 is situated in main duct KG, opening or shutting off air stream to conditioned space P.
  • fan 8 impels air stream to conditioned space P.
  • the air flows to first auxiliary duct through open damper 13.
  • the air flows through the first heat exchanger which is evaporator 1 and further flows to main duct KG. Evaporator 1 cools the air.
  • Simultaneously split damper 9 is in position A and shuts off outdoor air to main duct KG, damper 14 is open, and inner damper 14 and outer damper 12 are closed. Cooled air is impelled by fan 8 from main duct KG back to conditioned space P. Simultaneously outdoor air, impelled by fan 7, passes through condenser 2 to second auxiliary duct K2. Condenser 2 heats outdoor air which flows through open second outdoor air damper 11 back to outdoor space. After required temperature of air in conditioned space P is obtained the circulation operates in regular mode controlled by temperature of air in conditioned space P.
  • Evaporator (so far condenser, which surface shortly after switching obtains ambient temperature) cools the air which passes through main duct KG and damper 14 back to conditioned space P. Simultaneously second outer damper 12 is open and outdoor air passes through condenser 2' and damper 12 outdoors.
  • fans 7 and 8 are turned off. Directly after the circulation is reversed, fans 7 and 8 are switched off.
  • Fan 8 impelling air stream to conditioned space P is switched on again when the temperature of the surface of evaporator 1 ' is near its ambient temperature.
  • Fan 7 is switched on when temperature of the evaporator surface is near its ambient temperature what happens with large delay.
  • the arrangement continues operation in cycle of cooling air in conditioned space P.
  • damper 13 In cycle of heating air in conditioned space P, presented in Fig. 3, damper 13 is opened, and split damper is pivoted to position A shutting off outdoor air stream to conditioned space P.
  • Fan 8 impels air flow to conditioned space P.
  • the air passes through damper 13 to duct Kl.
  • Hot condenser 2' heats the air, which passes through duct KG and open damper 14 and is further impelled by fan 8 to conditioned space P.
  • Simultaneously outdoor air is impelled by fan 7 to evaporator 1 ' and further to duct K2 and flows outdoor through open damper 11.
  • valves Zl and Z2 are placed in first position I.
  • the direction of circulation is reversed and first heat exchanger Wl becomes evaporator 1 again and second heat exchanger becomes condenser 2 again.
  • Fan 8 is switched off.
  • Simultaneously split damper 9 is pivoted from position A to position 0 and changed are positions of dampers 10,11,12,13,14. Now dampers 10,13,14 are closed and dampers 11,12 are open.
  • air from conditioned space P is supplied through duct Kl to first heat exchanger Wl (evaporator 1), and to second heat exchanger (condenser 2) outdoor air is supplied through main duct KG.
  • first heat exchanger Wl evaporator 1
  • second heat exchanger condenser 2
  • outdoor air is supplied to evaporator 1.
  • Such circulation is repeated many times until required humidity eg and/or temperature t in conditioned space P is obtained.
  • damper 16 can be open and damper
  • auxiliary ducts Kl and K2 are connected to conditioned space P via third auxiliary duct K3.
  • first auxiliary duct Kl is connected directly to conditioned space P via damper 13
  • second auxiliary duct K2 is connected directly to conditioned space P via damper 10
  • main duct KG to conditioned space P via auxiliary internal duct KW and fourth damper 15.
  • Main duct is connected via third damper 16 to outdoor space.
  • dehumidifying air is realized in constant temperature in conditioned space P, with steam condensating or frost deposited on the surface.
  • Air from conditioned space P is supplied through fourth internal damper 15 to main duct and further the air stream is impelled by fan 7 to condenser 2. The air is heated and flows back to conditioned space P.
  • Split damper 9 is in position "A".
  • cycle of dehumidifying air air from conditioned space P is supplied through first duct Kl to first heat exchanger Wl which is evaporator 1, and to second heat exchanger W2 which is condenser. Air is supplied from the conditioned space through internal duct KW. After the parameter monitored at evaporator 1 obtains required value, cycle of defrosting is carried out and/or when temperature in conditioned space P obtains required value, outdoor air is periodically supplied to the condenser.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Air Conditioning Control Device (AREA)

Abstract

Selon l'invention, l'espace climatisé (P) est relié à une conduite de ventilation principale (KG) et à des conduites secondaires (K1, K2), lesquelles sont également reliées à la conduite principale, la conduite (K1) par l'intermédiaire d'un premier échangeur de chaleur (W1) et la conduite (K2) par l'intermédiaire d'un second échangeur de chaleur (W2). Entre les échangeurs de chaleur, on a monté un registre à deux blocs (9), relié au système aux fins de commande et régulation automatiques (17), les conduites secondaires (K1, K2) étant reliées à l'espace climatisé (P) par l'intermédiaire de registres d'air intérieur (13, 10) et à l'espace extérieur par des registres d'air extérieur (12, 11). Un registre d'air intérieur (14) est placé entre la conduite principale (KG) et l'espace climatisé (P). Les registres sont commandés par le système de manière à fonctionner automatiquement et de façon régulée (17).
PCT/PL2001/000033 2000-06-15 2001-04-13 Procede et dispositif de climatisation recuperant la chaleur perdue WO2001096794A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU2001252801A AU2001252801A1 (en) 2000-06-15 2001-04-13 Method and device for air conditioning using waste heat

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
PLP.340843 2000-06-15
PL340843A PL191519B1 (pl) 2000-06-15 2000-06-15 Sposób regulacji parametrów powietrza w pomieszczeniach klimatyzowanych, zwłaszcza w przechowalniach produktów wrażliwych na warunki klimatyczne, układ do regulacji parametrów powietrza w pomieszczeniach klimatyzowanych, zwłaszcza w przechowalniach produktów wrażliwych na warunki klimatyczne oraz urządzenie do regulacji parametrów powietrza w pomieszczeniach klimatyzowanych, zwłaszcza w przechowalniach produktów wrażliwych na warunki klimatyczne

Publications (1)

Publication Number Publication Date
WO2001096794A1 true WO2001096794A1 (fr) 2001-12-20

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ID=20076843

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PCT/PL2001/000033 WO2001096794A1 (fr) 2000-06-15 2001-04-13 Procede et dispositif de climatisation recuperant la chaleur perdue

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Country Link
AU (1) AU2001252801A1 (fr)
PL (1) PL191519B1 (fr)
WO (1) WO2001096794A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1734317A1 (fr) * 2005-06-16 2006-12-20 LG Electronics, Inc. Système de cogénération
FR2961293A1 (fr) * 2010-06-09 2011-12-16 Ther Eco Systeme de conditionnement d'air
CN103900181A (zh) * 2013-11-29 2014-07-02 李世镜 一种户式新风机组
ITUB20160029A1 (it) * 2016-01-18 2017-07-18 Zoppellaro S R L Unita’ di rinnovo aria e relativa procedura di conduzione
EP3193090A1 (fr) * 2016-01-18 2017-07-19 Zoppellaro S.r.l. Unité de renouvellement d'air et son procédé de fonctionnement

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4655278A (en) * 1985-09-27 1987-04-07 Cambridge Manufacturing Climate Control Products Inc. Heat recirculation apparatus and method
WO1997006390A1 (fr) * 1995-08-08 1997-02-20 Turcotte Inc. Unite combinee de renouvellement et de conditionnement de l'air
EP0909926A1 (fr) * 1997-10-14 1999-04-21 Aldes Aeraulique Système de ventilation à double flux

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4655278A (en) * 1985-09-27 1987-04-07 Cambridge Manufacturing Climate Control Products Inc. Heat recirculation apparatus and method
WO1997006390A1 (fr) * 1995-08-08 1997-02-20 Turcotte Inc. Unite combinee de renouvellement et de conditionnement de l'air
EP0909926A1 (fr) * 1997-10-14 1999-04-21 Aldes Aeraulique Système de ventilation à double flux

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1734317A1 (fr) * 2005-06-16 2006-12-20 LG Electronics, Inc. Système de cogénération
FR2961293A1 (fr) * 2010-06-09 2011-12-16 Ther Eco Systeme de conditionnement d'air
WO2011154635A3 (fr) * 2010-06-09 2012-02-02 Ther Eco Système de conditionnement d'air
CN103900181A (zh) * 2013-11-29 2014-07-02 李世镜 一种户式新风机组
ITUB20160029A1 (it) * 2016-01-18 2017-07-18 Zoppellaro S R L Unita’ di rinnovo aria e relativa procedura di conduzione
EP3193090A1 (fr) * 2016-01-18 2017-07-19 Zoppellaro S.r.l. Unité de renouvellement d'air et son procédé de fonctionnement

Also Published As

Publication number Publication date
AU2001252801A1 (en) 2001-12-24
PL340843A1 (en) 2001-12-17
PL191519B1 (pl) 2006-05-31

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