WO2011136064A1 - Ｃｏ２冷媒を用いたヒートポンプ給湯装置 - Google Patents

Ｃｏ２冷媒を用いたヒートポンプ給湯装置 Download PDF

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Publication number
WO2011136064A1
WO2011136064A1 PCT/JP2011/059492 JP2011059492W WO2011136064A1 WO 2011136064 A1 WO2011136064 A1 WO 2011136064A1 JP 2011059492 W JP2011059492 W JP 2011059492W WO 2011136064 A1 WO2011136064 A1 WO 2011136064A1
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WIPO (PCT)
Prior art keywords
refrigerant
heat
heat pump
hot water
water supply
Prior art date
Application number
PCT/JP2011/059492
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English (en)
French (fr)
Japanese (ja)
Inventor
岡田　拓也
吉田　茂
陽一 上藤
峰正 大村
Original Assignee
三菱重工業株式会社
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.)
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Publication date
Application filed by 三菱重工業株式会社 filed Critical 三菱重工業株式会社
Priority to EP11774847.5A priority Critical patent/EP2581682A4/de
Publication of WO2011136064A1 publication Critical patent/WO2011136064A1/ja

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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 apparatus using CO2 refrigerant in which a refrigerant circulation circuit is provided in parallel to a plurality of systems with respect to a hot water supply heat exchanger.
  • the method (1) is mainly used.
  • the design pressure is 4.15 MPa on the high pressure side and 2.21 MPa on the low pressure side
  • the design pressure is several times higher, 14 MPa on the high pressure side and 8.5 MPa on the low pressure side. Because.
  • Patent Document 1 when a configuration in which a plurality of compressors are simply connected in parallel, the design pressure is as high as 8.5 MPa even on the low pressure side, and the compressor, oil separator, receiver, accumulator, etc.
  • the thickness of the container must be increased, and the tendency to increase as the capacity increases. This increases the cost, and increases the manufacturing difficulty.
  • the refrigerating capacity is 3 tons or more, it is necessary to comply with the High Pressure Gas Safety Law, and containers with an inner diameter of 160 mm or more fall under the container specified by the High Pressure Gas Safety Law. Costs have increased significantly, and this has become a bottleneck in increasing capacity.
  • the present invention has been made in view of such circumstances, and it is possible to increase the capacity of CO2 while keeping the container of the component equipment to a size equal to or less than a certain size specified by the High Pressure Gas Safety Law. It aims at providing the heat pump hot-water supply apparatus using a refrigerant
  • a heat pump water heater using the CO 2 refrigerant of the present invention employs the following means.
  • a heat pump water heater using a CO2 refrigerant according to one aspect of the present invention includes a refrigerant circulation circuit using a CO2 refrigerant including a compressor, a radiator, a decompression unit, and a heat absorber, and a water flow path for exchanging heat with the radiator.
  • the container size of each component device of each heat pump is configured to be 160 mm or less in inner diameter, and the total refrigeration capacity is 3 refrigeration tons or more.
  • the heat pump hot water supply apparatus using the CO2 refrigerant in which a plurality of refrigerant circulation circuits are provided in parallel with respect to the hot water supply heat exchanger,
  • the container size of each component device of each heat pump constituted by a plurality of refrigerant circulation circuits is set to an inner diameter of 160 mm or less, and the total refrigeration capacity is set to 3 refrigeration tons or more.
  • the capacity can be increased, and various problems associated with the increase in the size of the container can be solved.
  • the container sizes of the devices constituting the individual heat pumps are all containers with an inner diameter of 160 mm or less, they do not fall under the container stipulated in the High Pressure Gas Safety Law, simplify the manufacturing process, omit various tests, etc. Thus, the manufacturing cost can be greatly reduced.
  • multiple refrigerant circulation circuits are provided in parallel, the oil leveling mechanism and oil leveling control between the multiple compressors are no longer required, the configuration is simplified, and the reliability of individual heat pumps is improved. Can do.
  • each of the compressors of the plurality of refrigerant circulation circuits is a two-stage compressor, and is provided downstream of the radiator.
  • coolant compressed to the intermediate pressure may be sufficient.
  • the compressors of the refrigerant circulation circuits of a plurality of systems are each a two-stage compressor, and the gas refrigerant separated by the intermediate pressure receiver provided on the downstream side of the radiator is compressed to an intermediate pressure.
  • a gas injection circuit for injecting into the refrigerant for this reason, the heating efficiency and coefficient of performance (COP) of the heat pump can be improved by improving the compression efficiency by compressing the CO2 refrigerant in two stages and the economizer effect by the gas injection circuit. Can be improved.
  • the gas injection circuit is also provided for each refrigerant circulation circuit, gas injection can be performed almost equally to each compressor, and the imbalance of the gas injection amount between the compressors can be eliminated.
  • the system may be integrated and modularized as a main unit, and the third and subsequent heat pumps may be modularized as sub-units and used in combination with the main unit according to the required refrigeration capacity.
  • the heat pump constituted by the two refrigerant circulation circuits of the plural refrigerant circulation circuits and the heat exchanger for hot water supply are integrated into a module as a main unit, and the third and subsequent systems.
  • These heat pumps are modularized as sub-units and used in combination with the main unit according to the required refrigeration capacity. For this reason, when a hot water supply apparatus is made into a series for each refrigeration capacity, the refrigeration capacity can be changed and made into a series only by changing the number of combined subunits. Therefore, it is possible to easily increase the capacity, and productivity can be improved.
  • the main unit includes two air heat exchangers that are bent into a planar shape, an L shape, or a square U shape.
  • the heat sink is configured to be arranged in a quadrilateral shape so as to be opposed to each other on a lower unit in which other equipment is accommodated, and the sub-unit is formed by folding into a square U-shape.
  • the heat absorber constituted by the vessel may be configured to be disposed on the lower unit in which other equipment is accommodated, and the number of the main units and the subunits may be appropriately arranged and used.
  • the main unit is a lower part in which two heat absorbers configured by an air heat exchanger bent into a planar shape, an L shape, or a square U shape are accommodated with other devices.
  • the unit is arranged to be opposed to each other and assembled into a quadrilateral shape, and the sub unit is a heat absorber composed of an air heat exchanger formed by bending it into a U shape, and other devices are accommodated.
  • the number of main units and sub-units are suitably arranged in parallel and used. For this reason, the width dimension of the subunit can be configured to be approximately half the width dimension of the main unit, and each unit can be modularized. Therefore, the size of the hot water supply apparatus for each refrigeration capacity can be defined in advance, and installation space can be secured and installation can be facilitated.
  • the heat pump when the capacity of a heat pump water heater using CO2 refrigerant is increased, the heat pump having all the container sizes of the equipment constituting the refrigerant circulation circuit as a container having an inner diameter of 160 mm or less is compared with the heat exchanger for hot water supply.
  • a heat pump hot water supply apparatus using a large-capacity CO2 refrigerant having a total refrigeration capacity of 3 refrigeration tons or more can be configured.
  • the container sizes of the devices constituting the individual heat pumps are all containers with an inner diameter of 160 mm or less, they do not fall under the container stipulated in the High Pressure Gas Safety Law, simplify the manufacturing process, omit various tests, etc. Thus, the manufacturing cost can be greatly reduced.
  • multiple refrigerant circulation circuits are provided in parallel, the oil leveling mechanism and oil leveling control between the multiple compressors are no longer required, the configuration is simplified, and the reliability of individual heat pumps is improved. Can do.
  • FIG. 1 It is a circuit block diagram of the heat pump hot-water supply apparatus using the CO2 refrigerant
  • FIG. 1 shows a circuit configuration diagram of a heat pump water heater using a CO 2 refrigerant according to the first embodiment of the present invention.
  • a heat pump hot water supply apparatus 1 using CO2 refrigerant according to the present embodiment includes supercritical cycle heat pumps 2A and 2B using CO2 refrigerant constituted by independent refrigerant circulation circuits 3A and 3B.
  • Each of the heat pumps 2A and 2B includes, for example, a two-stage compressor 4A and 4B that compresses the refrigerant in two stages, a rotary compression mechanism on the lower stage side and a scroll compression mechanism on the higher stage side, and oil that separates the lubricating oil in the refrigerant gas.
  • radiators (gas coolers) 6A and 6B for radiating refrigerant gas radiators (gas coolers) 6A and 6B for radiating refrigerant gas
  • refrigerant Intermediate pressure receivers 8A and 8B that perform gas-liquid separation intercoolers 9A and 9B that exchange heat between the intermediate pressure refrigerant and the refrigerant gas sucked into the compressors 4A and 4B
  • a second electronic expansion valve that depressurizes the intermediate pressure refrigerant ( Pressure reducing means) 10A, 10B, supercooling coils 11A, 11B, and heat absorbers (air heat exchangers) 13A, 13B for exchanging heat with the outside air and refrigerant from fans 12A, 12B in this order.
  • Refrigerant circuit 3A closed cycles connected by refrigerant pipes, is made of 3B.
  • Each heat pump 2A, 2B includes oil return circuits 14A, 14B for returning the oil separated by the oil separators 5A, 5B to the two-stage compressors 4A, 4B, and a heat absorber (air heat exchanger) 13A at a low outside temperature.
  • 13B is equipped with solenoid valves 15A, 15B that defrost by introducing hot gas refrigerant discharged from the two-stage compressors 4A, 4B into the heat absorbers (air heat exchangers) 13A, 13B.
  • the intermediate pressure refrigerant gas separated by the gas bypass circuits 16A and 16B and the intermediate pressure receivers 8A and 8B is sucked into the high pressure side scroll compression mechanism of the two-stage compressors 4A and 4B.
  • Gas injection circuits 18A and 18B provided with electromagnetic valves 17A and 17B for injection (injection) are provided.
  • the radiators (gas coolers) 6A and 6B of the heat pumps 2A and 2B constitute a hot water supply heat exchanger 19 that heat-exchanges the water flowing through the water flow path 19A and the refrigerant and heats the water to produce hot water.
  • the hot water supply heat exchanger 19 is connected to a water flow path 19A and a hot water storage tank 20 via a water circulation circuit 23 having a water circulation pump 21 and an electromagnetic valve 22, and is circulated from the hot water storage tank 20 via the water circulation pump 21.
  • the water is heated to a predetermined temperature of warm water and stored in the hot water storage tank 20.
  • the water circulation circuit 23 is connected to a water supply pipe (not shown) such as tap water, and the hot water storage tank 20 is connected to a hot water supply pipe (not shown) for supplying hot water to a required location. It has become.
  • the heat pump hot water supply apparatus 1 of the present embodiment is configured such that the refrigerant circulation circuits 3A and 3B of a plurality of independent heat pumps 2A and 2B are connected in parallel to the hot water supply heat exchanger 19, respectively.
  • the water can be heated by the heat exchanger 19 for hot water supply via the radiators 6A and 6B of the heat pumps 2A and 2B.
  • the individual heat pumps 2A and 2B have all the container sizes such as the two-stage compressors 4A and 4B, the oil separators 5A and 5B, the intermediate pressure receivers 8A and 8B, and the accumulator (not shown) constituting the refrigerant circulation circuits 3A and 3B.
  • the container has an inner diameter of 160 mm or less.
  • the container sizes of the devices constituting the refrigerant circulation circuits 3A and 3B are all containers having an inner diameter of 160 mm or less. At least two or more heat pumps 2A, 2B are connected in parallel to form a large-capacity heat pump water heater 1.
  • the refrigerant compressed by the two-stage compressors 4A and 4B is separated from the oil in the refrigerant by the oil separators 5A and 5B, and then a radiator (gas cooler). 6A and 6B, where heat is exchanged with water flowing through the water flow path 19A of the hot water supply heat exchanger 19.
  • This water is heated and heated by heat radiation from the refrigerant, and then returns to the hot water storage tank 20 until the hot water temperature in the hot water storage tank 20 reaches a predetermined temperature, and the hot water storage tank 20 and the hot water supply heat exchanger 19.
  • the hot water storage operation is terminated when the hot water temperature reaches a predetermined temperature.
  • the refrigerant cooled by exchanging heat with water in the hot water supply heat exchanger 19 is depressurized by the first electronic expansion valves (decompression means) 7A and 7B, reaches the intermediate pressure receivers 8A and 8B, and is separated into gas and liquid.
  • the separated gas refrigerant is injected into the refrigerant gas compressed to an intermediate pressure by the low-stage compression mechanism of the two-stage compressors 4A and 4B via the electromagnetic valves 17A and 17B and the gas injection circuits 18A and 18B.
  • the liquid refrigerant is cooled, it is depressurized by the second electronic expansion valves (decompression means) 10A and 10B through the intercoolers 9A and 9B, and becomes a low-temperature and low-pressure refrigerant to the heat absorber (air heat exchanger) 13A, 13B.
  • the heat capacity and coefficient of performance (COP) of each heat pump 2A, 2B can be improved, and hot water supply performance can be improved.
  • the refrigerant that has flowed into the heat absorbers (air heat exchangers) 13A and 13B is heat-exchanged with the outside air blown through the fans 12A and 12B, and absorbs heat from the outside air to be evaporated.
  • the gasified refrigerant is sucked into the two-stage compressors 4A and 4B through the intercoolers 9A and 9B and is recompressed. Thereafter, the same operation is repeated to provide hot water.
  • the solenoid valves 15A and 15B are opened, and the hot and hot gas compressed by the two-stage compressors 4A and 4B is used as the hot gas.
  • a defrosting operation is performed by introducing the heat absorbers 13A and 13B via the bypass circuits 16A and 16B.
  • the heat pump 2A is configured such that the container size of the equipment constituting the refrigerant circulation circuits 3A, 3B is a container having an inner diameter of 160 mm or less with respect to the hot water supply heat exchanger. , 2B can be configured to connect two or more systems in parallel, whereby a large-capacity heat pump water heater 1 having a total refrigeration capacity of 3 refrigeration tons or more can be configured.
  • the CO2 refrigerant was used while the containers of the devices constituting the heat pumps 2A and 2B using the CO2 refrigerant having a high design pressure of 14 MPa on the high pressure side and 8.5 MPa on the low pressure side were kept to a certain size or less.
  • the capacity of the heat pump hot water supply device can be increased, and various problems such as an increase in pressure resistance due to an increase in wall thickness due to an increase in the size of each container, an improvement in manufacturing difficulty, and an increase in cost can be solved. .
  • the container sizes of the devices constituting the individual heat pumps 2A and 2B are all containers having an inner diameter of 160 mm or less, they do not fall under the container stipulated in the High Pressure Gas Safety Law, simplify the manufacturing process, and perform various tests. Manufacturing costs can be significantly reduced by omission.
  • the refrigerant circulation circuits 3A and 3B are configured to be connected in parallel to a plurality of systems, an oil leveling mechanism, oil leveling control, etc. between the plurality of two-stage compressors 4A and 4B are unnecessary, and the configuration is simple. And the reliability of the individual heat pumps 2A and 2B can be improved.
  • a plurality of refrigerant circulation circuits 3A and 3B inject gas refrigerant separated by the intermediate pressure receivers 8A and 8B into intermediate pressure refrigerant gas by the two-stage compressors 4A and 4B, respectively. Therefore, the heat capacity and coefficient of performance (COP) of the heat pumps 2A and 2B are improved by improving the compression efficiency by compressing the CO2 refrigerant in two stages and the economizer effect by the gas injection circuits 18A and 18B. Can do. Accordingly, the hot water supply performance can be further improved, and the gas injection circuits 18A and 18B are also provided for the refrigerant circulation circuits 3A and 3B. Therefore, the gas injection is performed almost equally to the two-stage compressors 4A and 4B. It is possible to eliminate the imbalance in the amount of gas injection between the compressors.
  • FIGS. 1 and 2B each of which is constituted by two refrigerant circulation circuits 3A and 3B, each having a container having an inner diameter of 160 mm or less, and a hot water supply heat exchanger 19 are provided.
  • the heat pump 3C (not shown) is modularized as the main unit 30 and the containers of the third and subsequent components are containers having an inner diameter of 160 mm or less. Is modularized as a subunit 31 and is configured to be used in combination with the main unit 30 as appropriate in accordance with the required refrigeration capacity.
  • the main unit 30 includes, in the upper unit 30A, two heat absorbers 13A and 13B, each of which includes fans 12A and 12B and an air heat exchanger that is bent into an L shape as shown in FIG.
  • the two heat absorbers 13A ′ and 13B ′ composed of a planar air heat exchanger, or folded into a square U-shape as shown in FIG.
  • Two heat absorbers 13A ′′, 13B ′′ composed of air heat exchangers are arranged to face each other and assembled in a quadrilateral shape, and other devices are accommodated in the lower unit 30B installed at the lower part thereof. It is supposed to be configured.
  • the sub unit 31 includes a fan 12C (not shown) and an air heat exchanger 13C formed by bending it into a square U shape so that the heat absorber 13C is accommodated in the upper unit 31A and installed in the lower part thereof.
  • the other unit 30B is accommodated in the lower unit 30B.
  • the containers of the respective constituent devices configured by the two refrigerant circulation circuits 3A and 3B have an inner diameter of 160 mm or less.
  • the heat pumps 2A, 2B and the hot water supply heat exchanger 19 are integrated into a module as a main unit 30, and the containers of the third and subsequent components are containers having an inner diameter of 160 mm or less (not shown) ) Is modularized as the subunit 31 and is used in combination with the main unit 30 according to the required refrigeration capacity, so that when the heat pump water heater 1 is serialized for each refrigeration capacity, the number of combinations of the subunits 31 is Just by changing the refrigeration capacity can be changed into a series. As a result, the capacity can be easily increased, and the productivity can be improved.
  • the main unit 30 includes two heat absorbers 13A, 13B, 13A ′, 13B ′, and 13A ′′ configured by an air heat exchanger that is bent into a planar shape, an L shape, or a square U shape.
  • 13B ′′ are arranged to be opposed to each other on the lower unit 30B in which other devices are accommodated and assembled into a quadrangular shape, and the subunit 31 is formed by bending it into a square U-shape.
  • the heat absorber 13C configured by a heat exchanger is configured on a lower unit 31B in which other devices are accommodated, and the main unit 30 and the sub units 31 are appropriately arranged in parallel and used.
  • the width dimension of the sub-unit 31 is approximately half the width dimension of the main unit 30, and each unit 30, 31 is modularized. It is possible. Therefore, the size of the heat pump water heater 1 for each refrigeration capacity can be defined in advance, and installation space can be secured and installation can be facilitated.
  • this invention is not limited to the invention concerning the said embodiment, In the range which does not deviate from the summary, it can change suitably.
  • the compressor may be a single-stage compressor.
  • the gas injection circuits 18A and 18B are not essential and may be configured without a gas injection circuit.
  • the example which used the gas-liquid separator intermediate pressure receiver 8A, 8B was demonstrated as gas injection circuit 18A, 18B, it may replace with this and may be set as the structure using an intermediate heat exchanger.

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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)
PCT/JP2011/059492 2010-04-28 2011-04-18 Ｃｏ２冷媒を用いたヒートポンプ給湯装置 WO2011136064A1 (ja)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP11774847.5A EP2581682A4 (de) 2010-04-28 2011-04-18 Wärmepumpenwasserheizer unter verwendung mit co2-kältemittel

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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
JP2010-103827 2010-04-28

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WO2011136064A1 true WO2011136064A1 (ja) 2011-11-03

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109458758A (zh) * 2018-11-02 2019-03-12 赵昕 多能源互补的空气源热泵
CN111023628A (zh) * 2019-12-02 2020-04-17 苏州荣轩环保有限公司 一种热泵常压双效低温蒸发器
CN111023627A (zh) * 2019-12-02 2020-04-17 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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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
DE102018222555A1 (de) * 2018-12-20 2020-06-25 Yack S.A.S. Anordnung zur Wärmeerzeugung

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EP2581682A1 (de) 2013-04-17
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JP5705455B2 (ja) 2015-04-22

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