EP2581682A1 - Wärmepumpenwasserheizer unter verwendung mit co2-kältemittel - Google Patents

Wärmepumpenwasserheizer unter verwendung mit co2-kältemittel Download PDF

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Publication number
EP2581682A1
EP2581682A1 EP11774847.5A EP11774847A EP2581682A1 EP 2581682 A1 EP2581682 A1 EP 2581682A1 EP 11774847 A EP11774847 A EP 11774847A EP 2581682 A1 EP2581682 A1 EP 2581682A1
Authority
EP
European Patent Office
Prior art keywords
heat
refrigerant
water supply
supply system
hot water
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP11774847.5A
Other languages
English (en)
French (fr)
Other versions
EP2581682A4 (de
Inventor
Takuya Okada
Shigeru Yoshida
Yoichi Uefuji
Minemasa Omura
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.)
Mitsubishi Heavy Industries Ltd
Original Assignee
Mitsubishi Heavy Industries Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mitsubishi Heavy Industries Ltd filed Critical Mitsubishi Heavy Industries Ltd
Publication of EP2581682A1 publication Critical patent/EP2581682A1/de
Publication of EP2581682A4 publication Critical patent/EP2581682A4/de
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • 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
    • F24D17/00—Domestic hot-water supply systems
    • F24D17/02—Domestic hot-water supply systems using heat pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H4/00—Fluid heaters characterised by the use of heat pumps
    • F24H4/02—Water heaters
    • F24H4/04—Storage heaters
    • 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
    • F24D2200/00—Heat sources or energy sources
    • F24D2200/12—Heat pump
    • F24D2200/123—Compression type heat pumps
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/06—Several compression cycles arranged in parallel

Definitions

  • the present invention relates to a heat-pump hot water supply system employing CO 2 refrigerant in which multiple systems of refrigerant circulation circuits are provided in parallel for a hot-water supplying heat exchanger.
  • Patent Literature 1 in the case of the configuration in which the plurality of compressors are simply connected in parallel, the design pressure thereof is high at 8.5 MPa even on the low-pressure side, and thus, there is a problem in that it is necessary to increase the plate thickness of containers for the compressors, oil separators, receivers, accumulators, and so forth, and that, because this tendency increases with increasing capacity, this is a major cause of increasing cost, and it also causes increased difficulties related to manufacturing.
  • the refrigerating capacity is three tons or greater, compliance with the High Pressure Gas Safety Law is required, and because containers with inner diameters of 160 mm or greater correspond to containers regulated by the High Pressure Gas Safety Law, manufacturing costs and testing costs considerably increase, which is an obstacle to increasing the capacity.
  • the present invention has been conceived in light of the above-described circumstances, and an object thereof is to provide a heat-pump hot water supply system employing CO 2 refrigerant whose capacity can be increased while keeping the size of containers for constituent devices at or below a certain size regulated by the High Pressure Gas Safety Law.
  • a heat-pump hot water supply system employing CO 2 refrigerant according to an aspect of the present invention is a heat-pump hot water supply system employing CO 2 refrigerant provided with a refrigerant circulation circuit employing CO 2 refrigerant, which includes a compressor, a heat sink, depressurizing means, and a heat absorber, and a hot-water supplying heat exchanger having a water channel for performing heat exchange with the heat sink; and in which multiple systems of the refrigerant circulation circuits are provided in parallel for the hot-water supplying heat exchanger, wherein container sizes for all individual constituent devices of individual heat pumps formed in the multiple systems of the refrigerant circulation circuits are 160 mm or below in terms of inner diameters, and the total refrigerating capacity thereof is three refrigerating tons or greater.
  • the container sizes for all individual constituent devices of individual heat-pumps formed in the multiple systems of the refrigerant circulation circuits are 160 mm or below in terms of inner diameters, and total refrigerating capacity thereof is three refrigerating tons or greater.
  • two-stage compressors may be individually employed as the compressors in the multiple systems of the refrigerant circulation circuits; and a gas injection circuit may be provided which injects gaseous refrigerant separated at an intermediate-pressure receiver provided downstream of the heat sink into refrigerant that is compressed to intermediate pressure.
  • two-stage compressors are employed as the individual compressors in the multiple systems of the refrigerant, circulation circuits, and the gas injection circuits, which inject the gaseous refrigerant separated at the intermediate-pressure receivers provided downstream of the heat sinks into the refrigerant compressed to intermediate pressure, are provided, Because of this, the heating capacities and the coefficients of performance (COP) of the heat pumps can be enhanced due to the enhanced compression efficiency achieved by the two-stage compression of the CO 2 refrigerant and the economizer effect of the gas injection circuits, and therefore, the hot water supplying performance can be further enhanced.
  • the gas injection circuits are also provided individually for the individual refrigerant circulation circuits, the gas injection can be performed substantially equally for the individual compressors, and thus, it is possible to eliminate any imbalance in gas injection levels between the compressors.
  • the hot-water supplying heat exchanger and heat pumps formed in the two systems of the refrigerant circulation circuits may be integrated, thereby being modularized as a main unit, and heat pumps in a third and subsequent system may be individually modularized as subunits, which are employed in combination with the main unit in accordance with a required refrigerating capacity.
  • the hot-water supplying heat exchanger and the heat pumps formed in two systems of the refrigerant circulation circuits are integrated, thereby being modularized as the main unit; and the heat pumps of the third and subsequent systems are modularized as the subunits, which are employed by being combined with the main unit in accordance with the required refrigerating capacity. Accordingly, when developing a series of hot water supply systems in accordance with the refrigerating capacities, a series with a different refrigerating capacity can be developed merely by changing the number of subunits to be combined. Therefore, it is possible to easily increase the capacity, and productivity can be enhanced.
  • the main unit may have a configuration in which two heat absorbers formed of air heat exchangers having flat shapes or formed by being bent into L-shapes or angular U-shapes are assembled into a tetragon by being disposed to face each other on top of a bottom unit in which other devices are accommodated;
  • the subunits may have configurations in which heat absorbers formed of air heat exchangers formed by being bent into angular U-shapes are disposed above bottom units in which other devices are accommodated; and the main unit and the subunits, may be employed by being arranged next to each other in appropriate numbers.
  • the main unit has a configuration in which two heat absorbers formed of the air heat exchangers having flat shapes or formed by being bent into L-shapes or angular U-shapes are assembled into a tetragon by being disposed to face each other on top of the bottom unit in which other devices are accommodated; the subunits have configurations in which the heat absorbers formed of air heat exchangers formed by being bent into U-shapes are disposed above bottom units in which other devices are accommodated; and the main unit and the subunits are employed by being arranged next to each other in appropriate numbers. Accordingly, it is possible to modularize individual units by setting the widthwise sizes of the subunits to be about half the size of the widthwise size of the main unit. Therefore, the size of the hot water supply system can be predefined in accordance with the refrigerating capacities, thus making it possible to facilitate securing installation space as well as installation thereof.
  • containers for the devices that form the individual heat pumps all have container sizes of 160 mm or below in terms of inner diameters, they do not correspond to containers regulated by the High Pressure Gas Safety Law, and it is possible to reduce manufacturing costs considerably by simplifying the manufacturing process, omitting various tests, so forth.
  • FIG. 1 a circuit configuration diagram of a heat-pump hot water supply system employing CO 2 refrigerant according to the first embodiment of the present invention.
  • a heat-pump hot water supply system 1 employing CO 2 refrigerant according to this embodiment is provided with supercritical cycle heat pumps 2A and 2B employing CO 2 refrigerant formed in refrigerant circulation circuits 3A and 3B that multiple independent systems.
  • the individual heat pumps 2A 2B formed of the closed-cycle refrigerant circulation circuits 3A and 3B in which refrigerant pipes connect, in the following order, two-stage compressors 4A and 4B having, for example, rotary compression mechanisms at lower stages and scroll compression mechanisms at higher stages; oil separators 5A and 5B that separate lubricant in refrigerant gas; heat sinks (gas coolers) 6A and 6B that release the heat of the refrigerant gas; first electronic expansion valves (depressurizing means) 7A and 7B that control outlet-side refrigerant temperature of the heat sinks 6A and 6B; intermediate-pressure receivers 8A and 8B that perform gas-liquid separation of the refrigerant; intercoolers 9A and 9B that perform heat exchange between intermediate-pressure refrigerant and intake refrigerant gas for the compressors 4A and 4B; second electronic expansion valves (depressurizing means) 10A 10B that depressurize the intermediate-pressure refrigerant; supercooling coils 11A and 11
  • the individual heat pumps 2A and 28 provided with oil returning circuits 14A and 14B that return oil separated at the oil separators 5A and 5B to the two-stage compressors 4A and 4B; hot-gas bypass circuits 16A and 16B provided with electromagnetic valves 15A and 15B that, when the external air temperature is low, remove frost accumulated on the heat absorbers (air heat exchangers) 13A and 13B by introducing hot gas refrigerant discharged from the two-stage compressors 4A and 48 to the heat absorbers (air heat exchangers) 13A and 13B; and gas injection circuits 18A and 18B provided with electromagnetic valves 17A and 17B that perform injection of (inject) the intermediate-pressure refrigerant gas separated at the intermediate-pressure receivers 8A and 8B into the intermediate-pressure refrigerant gas to be taken into the scroll compression mechanisms at the higher stages of the two-stage compressors 4A any 48.
  • the heat sinks (gas coolers) 6A 6B of the above-described heat pumps 2A and 2B form a hot-water supplying heat exchanger 19 that performs heat exchange between water flowing in the water channel 19A and the refrigerant, thereby producing hot water by heating the water.
  • This hot-water supplying heat exchanger 19 is configured so that the water channel 19A thereof is connected with a hot-water storage tank 20 via a water circulation circuit 23 provided with a water circulation pump 21 and an electromagnetic valve 22, and water circulated from the hot-water storage tank 20 via the water circulation pump 21 is heated to form hot water of a predetermined temperature and is stored in the hot-water storage tank 20.
  • a water supply pipe (not shown) for drinking water or the like is connected to the water circulation circuit 23, and a hot-water supply pipe (not shown) for supplying hot water to required locations is connected to the hot-water storage tank 20.
  • the heat-pump hot water supply system 1 of this embodiment has a configuration in which the individual heat pumps 2A and 2B, which are multiple independent systems, in the individual refrigerant circulation circuits 3A and 3B are connected in parallel to the hot-water supplying heat exchanger 19, such that water can be heated at the hot-water supplying heat exchanger 19 by means of the heat sinks 6A and 6B of the individual heat pumps 2A and 2B.
  • containers for the two-stage compressors 4A and 4B, oil 5A 5B, the intermediate-pressure receivers 8A and 8B, accumulators (not shown), and so forth that form the refrigerant circulation circuits 3A and 3B all have container sizes of 160 mm or below in terms of inner diameters.
  • the refrigerating capacity is made three refrigerating tons or greater when increasing the capacity of the heat-pump hot water supply system 1
  • at least two or more heat pumps 2A and 2B in which containers for devices that form the individual refrigerant circulation circuits 3A and 3B all have container sizes of 160 mm or below in terms of inner diameters, are connected in parallel to form a large-capacity heat-pump hot water supply system 1.
  • This water is heated by the heat released from the refrigerant, thus being increased in temperature, is subsequently returned to the hot-water storage tank 20, and is circulated between the hot-water storage tank 20 and the hot-water supplying heat exchangers 19 until the hot water temperature in the hot-water storage tank 20 reaches a predetermined temperature; a hot-water storing operation is ended at the point when the hot water temperature reaches the predetermined temperature.
  • the refrigerant that has been cooled by undergoing heat exchange with water at the hot-water supplying heat exchanger 19 is depressurized at the first electronic expansion valves (depressurizing means) 7A and 7B, reaches the intermediate pressure-receivers 8A and 8B, and undergoes gas-liquid separation thereat.
  • the gaseous refrigerant that has been separated here is injected into the refrigerant gas compressed to intermediate pressure by the lower-stage compression mechanisms of the two-stage compressors 4A and 4B via the electromagnetic valves 17A and 17B and the gas injection circuits 18A and 18D.
  • the liquid refrigerant after being cooled, passes through the intercoolers 9A and 9B, is depressurized at the second electronic expansion valves (depressurizing means) 10A and 10B, and flows into the heat absorbers (air heat exchangers) 13A and 13B in the form of low-temperature, low-pressure refrigerant. Due to the economizer effect of this gas injection, the heating capacities and coefficients of performance (COP) of the individual heat pumps 2A and 2B can be enhanced, and thus, the hot-water supplying performance can be enhanced.
  • COP heating capacities and coefficients of performance
  • This gasified refrigerant is taken into the two-stage compressors 4A and 4B via the intercoolers 9A and 9B and is recompressed. Thereafter, it is supplied for hot water production by repeating the same operations.
  • the defrost operation is performed by opening the electromagnetic valves 15A and 15B and by introducing the high-temperature, high-pressure hot gas compressed at the two-stage compressors 4A and 4B to the heat absorbers 13A and 13B via the hot-gas bypass circuits 16A and 16B.
  • the containers for the devices that form the individual heat pumps 2A and 2B all have container sizes of 160 mm or below in terms of inner diameters, they do not correspond to containers regulated by the High Pressure Gas Safety Law, and it is possible to reduce manufacturing costs considerably by simplifying the manufacturing process, omitting various tests, and so forth. Furthermore, because the multiple systems of the refrigerant circulation circuits 3A and 3B are connected in parallel, an oil equalization mechanism, oil equalization control, etc. are not required between the plurality of two-stage compressors 4A and 4B, thus making it possible to simplify the configuration thereof and to enhance the reliability of the individual heat pumps 2A and 2B.
  • the multiple systems of the refrigerant circulation circuits 3A and 3B are individually provided with the gas injection circuits 18A and 18B that inject the gaseous refrigerant separated at the intermediate-pressure receivers 8A and 8B into the intermediate-pressure refrigerant gas at the two-stage compressors 4A and 4B, the heating capacities and the coefficients of performance (COP) of the heat pumps 2A and 2B can be enhanced due to the enhanced compression efficiency achieved by the two-stage compression of the CO 2 refrigerant and the economizer effect of the gas injection circuits 18A and 18B.
  • COP coefficients of performance
  • the hot-water supplying performance can be further enhanced, and, because the gaz injection circuits 18A and 18B are also provided in the individual refrigerant circulation circuits 3A and 3B, the gas injection can be performed substantially equally for the individual two-stage compressors 4A and 4B, and thus, it is possible to eliminate any imbalance in gas injection levels between the individual compressors.
  • FIG. 2 to 4 differs from the first embodiment described above, in that the heat-pump hot water supply system 1 employing CO 2 refrigerant, is specifically configured for the case where it is formed as a unit. Because other points are the same as those in the first embodiment, descriptions thereof wilt be omitted.
  • containers for constituent devices are containers with inner diameters of 160 mm or below, are modularized as subunits 31, which are combined with the main unit 30 in appropriate numbers in accordance with the required refrigerating capacity.
  • the main unit 30 has a configuration in which the two heat absorbers 13A and 13B formed of air heat exchangers formed by being bent into L-shapes, as shown in Fig. 2 , or two heat absorbers 13A' and 13B' formed of flat air heat exchangers, as shown in Fig. 3 , or two heat absorbers 13A'' and 13B'' formed of air heat exchangers formed by being bent into angular U-shapes, as shown in Fig. 4 , are assembled into a tetragon by being disposed to face each other in a top unit 30A along with the fans 12A and 12B, and a bottom unit 30B placed therebelow accommodates other devices therein.
  • subunits 31 have configurations in which heat absorbers 13C formed of air heat exchangers formed by being bent into angular U-shapes are accommodated in top units 31.A along with fans 12C (not shown), and bottom units 30B placed therebelow accommodate other devices therein.
  • the system is configured such that, of the multiple systems of the refrigerant circulation circuits 3A and 3B, the hot-water supplying heat exchanger 19 and the heat pumps 2A and 2B, in which the containers for the individual constituent devices are containers with inner diameters of 160 mm or below, formed in the two systems of the refrigerant circulation circuits 3A and 3B are integrated thereby being modularized as the main unit 30; and a third system, that is, the heat pump 2C (not shown), and subsequent systems in which containers for constituent devices are containers with inner diameters of 160 mm or below are modularized as the subunits 31, which are employed by being combined with the main unit 30 in accordance with the required refrigerating capacity; by doing so, when developing a series of the heat-pump hot water supply systems 1 in accordance with the refrigerating capacities, a series with a different refrigerating capacity can be developed merely by changing the number of subunits 31 to be combined. Accordingly, it is possible to easily increase the capacity, and productivity can be enhanced.
  • the main unit 30 has the configuration in which two heat absorbers 13A and 13B, 13A' and 13B' or 13A'' and 13B'' formed of air heat exchanger having flat shapes or formed by being bent into L-shapes or angular U-shapes are assembled into a tetragon by being disposed to face each other on top of the bottom unit 31B in which other devices are accommodated; because the subunits 31 have the configurations in which the heat absorbers 13C formed of air heat exchangers formed by being bent into angular U-shapes are disposed above the bottom unit 30B in which other devices are accommodated; and because the main unit 30 and the subunits 31 are employed by being arranged next to each other in appropriate numbers, it is possible to form modules of individual units 30 and 31 by setting the widthwise sizes of the subunits 31 to be about half the size of the widthwise size of the main unit 30. Therefore, the size of the heat-pump hot water supply system 1 can be predefined in accordance with the refriger
  • the present invention is not limited to the inventions according to the embodiments described above, and appropriate modifications are possible within a range that does not depart from the spirit thereof.
  • the compressors may be single-stage compressors.
  • the gas injection circuits 18A and 18B are not essential, and a configuration without the gas injection circuits may be employed.
  • gas-liquid separators intermediate-pressure receivers 8A and 8B
  • a configuration in which intermediate heat exchangers are employed is permissible.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Combustion & Propulsion (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
EP11774847.5A 2010-04-28 2011-04-18 Wärmepumpenwasserheizer unter verwendung mit co2-kältemittel Withdrawn EP2581682A4 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2010103827A JP5705455B2 (ja) 2010-04-28 2010-04-28 Ｃｏ２冷媒を用いたヒートポンプ給湯装置
PCT/JP2011/059492 WO2011136064A1 (ja) 2010-04-28 2011-04-18 Ｃｏ２冷媒を用いたヒートポンプ給湯装置

Publications (2)

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EP2581682A1 true EP2581682A1 (de) 2013-04-17
EP2581682A4 EP2581682A4 (de) 2013-11-27

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EP11774847.5A Withdrawn EP2581682A4 (de) 2010-04-28 2011-04-18 Wärmepumpenwasserheizer unter verwendung mit co2-kältemittel

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EP (1) EP2581682A4 (de)
JP (1) JP5705455B2 (de)
WO (1) WO2011136064A1 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3674610A1 (de) * 2018-12-20 2020-07-01 Yack S.A.S. Anordnung zur wärmeerzeugung

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104534714A (zh) * 2014-11-24 2015-04-22 合肥圣三松冷热技术有限公司 一种co2热泵系统及其控制方法
JP6594707B2 (ja) 2015-08-27 2019-10-23 三菱重工サーマルシステムズ株式会社 ２段圧縮冷凍システム
CN109458758A (zh) * 2018-11-02 2019-03-12 赵昕 多能源互补的空气源热泵
CN111023628B (zh) * 2019-12-02 2021-10-01 苏州荣轩环保有限公司 一种热泵常压双效低温蒸发器
CN111023627B (zh) * 2019-12-02 2021-10-01 苏州荣轩环保有限公司 一种热泵常压单效蒸发器及其使用方法

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US4918942A (en) * 1989-10-11 1990-04-24 General Electric Company Refrigeration system with dual evaporators and suction line heating
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US20040144528A1 (en) * 2002-02-12 2004-07-29 Keijiro Kunimoto Heat pump water heater
EP1707887A2 (de) * 2005-03-24 2006-10-04 Hitachi Home & Life Solutions, Inc., Wärmepumpen-Warmwasserversorgungsgerät
WO2008130359A1 (en) * 2007-04-24 2008-10-30 Carrier Corporation Refrigerant vapor compression system with dual economizer circuits
US20100031686A1 (en) * 2008-05-15 2010-02-11 Multistack Llc Modular outboard heat exchanger air conditioning system

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US4745777A (en) * 1986-03-31 1988-05-24 Mitsubishi Denki Kabushiki Kaisha Refrigerating cycle apparatus
US4918942A (en) * 1989-10-11 1990-04-24 General Electric Company Refrigeration system with dual evaporators and suction line heating
US20040144528A1 (en) * 2002-02-12 2004-07-29 Keijiro Kunimoto Heat pump water heater
US20030178498A1 (en) * 2002-03-20 2003-09-25 Kenichi Saitoh Heat pump hot-water supply system
EP1707887A2 (de) * 2005-03-24 2006-10-04 Hitachi Home & Life Solutions, Inc., Wärmepumpen-Warmwasserversorgungsgerät
WO2008130359A1 (en) * 2007-04-24 2008-10-30 Carrier Corporation Refrigerant vapor compression system with dual economizer circuits
US20100031686A1 (en) * 2008-05-15 2010-02-11 Multistack Llc Modular outboard heat exchanger air conditioning system

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See also references of WO2011136064A1 *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3674610A1 (de) * 2018-12-20 2020-07-01 Yack S.A.S. Anordnung zur wärmeerzeugung

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JP2011232000A (ja) 2011-11-17
WO2011136064A1 (ja) 2011-11-03
EP2581682A4 (de) 2013-11-27
JP5705455B2 (ja) 2015-04-22

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