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EP2674698A1 - Installation de pompes à chaleur - Google Patents

Installation de pompes à chaleur Download PDF

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Publication number
EP2674698A1
EP2674698A1 EP12172087.4A EP12172087A EP2674698A1 EP 2674698 A1 EP2674698 A1 EP 2674698A1 EP 12172087 A EP12172087 A EP 12172087A EP 2674698 A1 EP2674698 A1 EP 2674698A1
Authority
EP
European Patent Office
Prior art keywords
heat
medium
heat exchanger
pressure
heat pump
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Withdrawn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
EP12172087.4A
Other languages
German (de)
English (en)
Inventor
Roland Steuri
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.)
Cadena Systems AG
Original Assignee
Cadena Systems AG
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 Cadena Systems AG filed Critical Cadena Systems AG
Priority to EP12172087.4A priority Critical patent/EP2674698A1/fr
Publication of EP2674698A1 publication Critical patent/EP2674698A1/fr
Withdrawn legal-status Critical Current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
    • F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/315—Expansion valves actuated by floats
    • 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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/04—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in series
    • 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
    • F25B6/00—Compression machines, plants or systems, with several condenser circuits
    • F25B6/02—Compression machines, plants or systems, with several condenser circuits arranged in parallel
    • 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
    • F25B2339/044—Condensers with an integrated receiver
    • F25B2339/0445—Condensers with an integrated receiver with throttle portions
    • 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
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/075—Details of compressors or related parts with parallel compressors
    • F25B2400/0751—Details of compressors or related parts with parallel compressors the compressors having different capacities
    • 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
    • F25B2400/13—Economisers
    • 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
    • F25B2400/16—Receivers
    • 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
    • F25B2400/23—Separators
    • 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
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2503—Condenser exit valves

Definitions

  • the aforementioned invention relates to a heat pump system according to the preamble of claim 1.
  • Heat pumps are used to raise heat from a heat source from its temperature level to a higher one.
  • a circuit of a medium is used, which passes at the temperature of the heat source by absorbing energy from the liquid to the gaseous state.
  • the medium is compressed in a compressor, with the temperature increasing to the desired target level.
  • the compressed medium is fed to a heat exchanger in which the medium condenses again.
  • the condensed medium is returned to the heat exchanger on the side of the heat source after passing through a pressure reducing stage, whereby the circuit is closed.
  • Refrigeration systems are based on the same cycle. They differ in that heat is withdrawn from a medium and this cools down, which corresponds to the purpose of plant operation. The extracted energy is brought by means of the previously described cooling process to a higher temperature level and released to the environment. Attachments In their function, they can also be switched from heat pumps to refrigeration systems or both functions can be used simultaneously.
  • Another aspect is the cooperation between the heat source side heat exchanger and the common heat output side combinations of a condenser and a subcooler.
  • the condenser the circulating medium is condensed, whereby the largest amount of heat is released.
  • subcooler further heat is removed from the then already condensed medium.
  • gas and liquid coexist, while the subcooler must be filled with liquid medium in order to be able to extract additional energy from the liquid refrigerant and thereby further improve the efficiency.
  • a so-called flooded heat exchanger is advantageous.
  • any liquid refrigerant immediately flows from the heat-discharge side into the flooded evaporator or heat exchanger. This raises constructive problems from the desired juxtaposition of the subcooler, which must be flooded, and the pressure reduction stage, for example, in connection with flooded evaporators or medium pressure cylinders are used.
  • An object of the present invention is therefore to provide a heat pump system with increased efficiency.
  • Another object is to provide a heat pump system that works with a compressor lower power and / or lower flow.
  • a further object is to provide a device which allows juxtaposition of subcooler and a pressure reduction stage which allows all liquid refrigerant to pass.
  • a heat pump system which fulfills at least the first-mentioned object is specified in claim 1.
  • the further claims indicate preferred embodiments.
  • a solution to the problem is to bring about the desired increase in temperature on the heat release side, that is, towards the heat sink, in at least two stages.
  • the first stage causes the greater part of the temperature rise.
  • the still relatively warm medium in the return of the heat pump cycle is used as a heat source for a second heat pump cycle.
  • Its heat release side is used to carry out the remaining temperature increase.
  • the outlet temperature of the first, larger stage is lower, which allows more efficient operation of the compressor.
  • Another measure to increase the efficiency is the usual at least in large systems sequence of condenser and subcooler with a drain control, z. B. substantially in the manner of an overflow to connect, so that on the heat source side a flooded heat exchanger can be used, which offers advantages in efficiency and properties in part-load operation over a dry evaporator.
  • the system 1 has on the input side a dry evaporator 3 as input heat exchanger.
  • the heat source 4 provides medium, most conveniently water, at a temperature of, for example, 10 ° C.
  • the effluent heat source medium 6 has, for example, only a temperature of 5 ° C. With this one Cooling corresponding heat is evaporated in the dry evaporator 3, the medium circulating in the heat pump system 1. It leaves via the output line 8 the dry evaporator 3 and passes to the first compressor 10. By the compression in the compressor 10, the vapor of the working medium is brought to the required temperature to the first heat exchanger 12, the medium of the heat sink 13, which via the line 14 will, to warm. The working fluid is cooled in accordance with the output heat exchanger 12 and leaves it via the line 15 to get into the second input heat exchanger 16.
  • the heat exchanger 16 serves to heat the working fluid of a second heat pump cycle and thereby extract additional heat from the backflowing working fluid of the first heat pump cycle.
  • the further cooled working fluid of the first heat pump cycle passes via the line 18 to the expansion valve 20.
  • the expansion valve 20 is controlled so that it only lets through as much working fluid as is needed to by heating the working fluid in the main inlet heat exchanger 3, the inflowing medium below bring a predetermined pressure to a desired temperature, which is above the boiling temperature at said pressure.
  • the vapor medium leaving the main inlet heat exchanger 3 thus has a defined, controlled overheating.
  • the necessary sensors and control device are known per se and in the Fig. 1 not shown.
  • the second heat pump cycle includes the heat release side of the second input heat exchanger 16, a line 22 leading to a second compressor 24, the second output heat exchanger 26 and the expansion valve 28 in the line 30 from the second output heat exchanger 26 to the heat output side of the second9.95sswêtschreibers 16th
  • the second heat pump cycle thus generally corresponds to the first heat pump cycle, except that no further heat exchanger is present in its return line 30 in order to still extract heat from the returning medium.
  • the second heat pump cycle is dimensioned also weaker, in particular, the compressor 24 has a much lower power than the first compressor 10. Accordingly, the inflowing from the heat sink 13 medium in the first output heat exchanger 12 is much more heated than in the second output heat exchanger 26, in which it from the first Output heat exchanger 12 passes via the line 34. The heated to the final temperature medium of the heat sink 13 is returned to this via the output line 36.
  • the caused by the first output heat exchanger 12 temperature change in the medium of the heat sink 13 may be, for example, four times the temperature difference, which causes the second output heat exchanger 26.
  • the heat sink medium in line 14 may be 50 ° C
  • line 58 may be 58 ° C
  • output line 36 may be 60 ° C. These temperatures may vary, for example, according to the time of year or day. For a given system, however, the ratio of the temperature differences across the heat exchangers 12, 26 typically remains constant.
  • Fig. 2 shows another heat pump system 40 with two series-connected réelletownauertragern 12, 26.
  • a flooded evaporator 42 is used instead of a dry evaporator.
  • the medium-pressure bottle 44 is connected via the lines 46 and 47 with the first output heat exchanger 12 and the second output heat exchanger 26, in each of which a high-pressure float 49 and 50 is located to the Control flow from the heat exchangers.
  • the effect of the high-pressure floats 49, 50 is that liquid medium draining from the outlet heat exchangers 12, 26 reaches the medium-pressure bottle 44, but gaseous medium is retained. In other words, it can be assumed that the area in front of the high pressure floats 49, 50 is substantially free of liquid medium.
  • the high-pressure floats separate the high-pressure region behind the compressors 10, 24 and in the outlet heat exchangers 12, 26 from the medium-pressure part of the medium-pressure bottle 44 and the inlet line 22 of the second compressor 24.
  • a flooded heat exchanger is thus used as the main inlet heat exchanger 42, which is often advantageous.
  • the second input heat exchanger 16 is replaced by the medium-pressure cylinder 44, and instead of the expansion valves requiring control, high-pressure floats are used as pressure-reducing devices, which in the simplest case operate purely mechanically and require no further external precautions, in particular no control electronics or other control device.
  • the output heat exchangers 12, 26 mentioned in the above-mentioned embodiments may each be implemented as a series of the condenser 61 and the subcooler 63 for increasing the efficiency, as in FIG Fig. 3 shown. While a condenser 61 is operated in such a way that as far as possible all the condensate formed flows to the outside, the subcoolers generally require that they are filled at all times with condensate of the working medium. In a plant according to Fig. 1 , the works with expansion valves, which cause a backflow of condensate, this operating condition can be met in the rule. In connection with a flooded heat exchanger, as used for example in the second embodiment as a main inlet heat exchanger 42, this, however, causes difficulties, since here usually high-pressure float are used, which derive any condensate.
  • Fig. 3 shows a heat pump system 70, in which this problem is solved.
  • the arrangement 60 of condenser 61, subcooler 63 and high pressure float 65 shown therein is in principle suitable for use in front of any flooded heat exchanger, namely instead of one or both of the heat exchangers 12, 26 of the embodiments described above.
  • Another advantage of the system according to the invention is that the mass flow, ie. H. the amount of circulating medium is reduced.
  • the compressors have a correspondingly reduced geometric delivery volume. Overall, a significantly increased efficiency results.
  • heat pump system 70 has a flooded input heat exchanger 72, which communicates with the heat sink 4 via the input line 6 and the output line 5.
  • evaporated medium reaches the compressor 74, where it is raised by increasing the pressure to an elevated temperature. It flows through the condenser 61, where it is at least largely liquefied.
  • the largely liquefied medium enters the subcooler 63. In this it is cooled again by it gives off heat to the medium of the heat sink 13.
  • the medium of the heat sink 13 flows through the subcooler 63 and the condenser 61 in this order, that is opposite to the medium of the heat pump system by passing via the input line 77 to the subcooler 63, flows from this via the line 79 into the condenser 61 and then this leaves with the desired final temperature via line 81.
  • a condensate line 85 leads to the high pressure float 65.
  • the line 85 is designed as an overflow, which is indicated by the inverted U-shaped section 87.
  • the overflow 87 is designed such that a liquid level corresponding to the requirements of the subcooler 63 is established.
  • this arrangement also has an effect which counteracts an increase in the condensate level into the condenser 61. If the level of the condensate rises above the branching point 93, the branch line 91 is closed by the liquid medium, so to speak.
  • the branch line 91 is designed for pressure equalization by means of gaseous medium, so that it flows through liquid medium at most low level can be. Because of the thus blocked pressure equalization results in a suction effect on the condensate, as soon as the vacuum float 65 opens to drain condensate. This suction effect leads to a more rapid drainage of the condensate until the level has dropped below the branch 93 again. This effect is particularly advantageous if further units are arranged around the subcooler 63, which increase the flow resistance, such. B. a filter drier between the subcooler 63 and the high pressure float 65th
  • the system according to the invention can also be designed to remove heat by dissipating heat on the outlet side 13 to the medium on the input side (in the description the heat source 4), i. to achieve a cooling. It is also conceivable to use the system depending on the requirements for heating or cooling.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
EP12172087.4A 2012-06-14 2012-06-14 Installation de pompes à chaleur Withdrawn EP2674698A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP12172087.4A EP2674698A1 (fr) 2012-06-14 2012-06-14 Installation de pompes à chaleur

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP12172087.4A EP2674698A1 (fr) 2012-06-14 2012-06-14 Installation de pompes à chaleur

Publications (1)

Publication Number Publication Date
EP2674698A1 true EP2674698A1 (fr) 2013-12-18

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EP12172087.4A Withdrawn EP2674698A1 (fr) 2012-06-14 2012-06-14 Installation de pompes à chaleur

Country Status (1)

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107355929A (zh) * 2017-08-25 2017-11-17 郝勇 一种蓄能式热泵装置
WO2018008053A1 (fr) * 2016-07-04 2018-01-11 三菱電機株式会社 Système à cycle frigorifique
CN115654773A (zh) * 2022-09-27 2023-01-31 珠海格力电器股份有限公司 热回收装置和烘干设备
CN116693154A (zh) * 2023-06-28 2023-09-05 广州市创景市政工程设计有限公司 一种压滤设备及压滤方法

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1502607A (en) * 1975-05-19 1978-03-01 Star Refrigeration Low pressure receivers for a refrigerating system
EP0123638A2 (fr) * 1983-04-18 1984-10-31 Carrier Corporation Système de vidange du réfrigérant liquide d'un sous refroidisseur dans un système frigorifique à compression de vapeur
WO1992022777A2 (fr) * 1991-06-18 1992-12-23 Paradis Marc A Refroidisseur de liquide tres efficace se pretant a des utilisations tres diverses
EP1203916A1 (fr) * 2000-11-02 2002-05-08 Kwt Kälte-Wärmetechnik Ag Installation de chauffage avec pompe à chaleur
KR100897131B1 (ko) * 2008-03-05 2009-05-14 유인석 한냉지용 중압 2원사이클 냉난방 히트펌프 시스템
WO2010098005A1 (fr) * 2009-02-25 2010-09-02 株式会社岩谷冷凍機製作所 Pompe à chaleur binaire et réfrigérateur
EP2257749A2 (fr) * 2008-02-22 2010-12-08 Carrier Corporation Système de réfrigération et son procédé d'exploitation

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1502607A (en) * 1975-05-19 1978-03-01 Star Refrigeration Low pressure receivers for a refrigerating system
EP0123638A2 (fr) * 1983-04-18 1984-10-31 Carrier Corporation Système de vidange du réfrigérant liquide d'un sous refroidisseur dans un système frigorifique à compression de vapeur
WO1992022777A2 (fr) * 1991-06-18 1992-12-23 Paradis Marc A Refroidisseur de liquide tres efficace se pretant a des utilisations tres diverses
EP1203916A1 (fr) * 2000-11-02 2002-05-08 Kwt Kälte-Wärmetechnik Ag Installation de chauffage avec pompe à chaleur
EP2257749A2 (fr) * 2008-02-22 2010-12-08 Carrier Corporation Système de réfrigération et son procédé d'exploitation
KR100897131B1 (ko) * 2008-03-05 2009-05-14 유인석 한냉지용 중압 2원사이클 냉난방 히트펌프 시스템
WO2010098005A1 (fr) * 2009-02-25 2010-09-02 株式会社岩谷冷凍機製作所 Pompe à chaleur binaire et réfrigérateur

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018008053A1 (fr) * 2016-07-04 2018-01-11 三菱電機株式会社 Système à cycle frigorifique
JPWO2018008053A1 (ja) * 2016-07-04 2019-02-28 三菱電機株式会社 冷凍サイクルシステム
GB2566381A (en) * 2016-07-04 2019-03-13 Mitsubishi Electric Corp Refrigeration cycle system
GB2566381B (en) * 2016-07-04 2020-11-25 Mitsubishi Electric Corp Refrigeration cycle system
CN107355929A (zh) * 2017-08-25 2017-11-17 郝勇 一种蓄能式热泵装置
CN115654773A (zh) * 2022-09-27 2023-01-31 珠海格力电器股份有限公司 热回收装置和烘干设备
CN116693154A (zh) * 2023-06-28 2023-09-05 广州市创景市政工程设计有限公司 一种压滤设备及压滤方法

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