EP1983276A1 - Installation de refroidissement - Google Patents

Installation de refroidissement Download PDF

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Publication number
EP1983276A1
EP1983276A1 EP08033514A EP08033514A EP1983276A1 EP 1983276 A1 EP1983276 A1 EP 1983276A1 EP 08033514 A EP08033514 A EP 08033514A EP 08033514 A EP08033514 A EP 08033514A EP 1983276 A1 EP1983276 A1 EP 1983276A1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
cooling circuit
additional
air
circuit
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Withdrawn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
EP08033514A
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German (de)
English (en)
Inventor
Matthias Dr.-Ing. Liehm
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.)
Dresdner Kuehlanlagenbau GmbH
Original Assignee
Dresdner Kuehlanlagenbau GmbH
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 Dresdner Kuehlanlagenbau GmbH filed Critical Dresdner Kuehlanlagenbau GmbH
Publication of EP1983276A1 publication Critical patent/EP1983276A1/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Withdrawn legal-status Critical Current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
    • F25B6/00—Compression machines, plants or systems, with several condenser circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
    • 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
    • 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
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • 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
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0403—Refrigeration circuit bypassing means for the condenser
    • 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
    • F25B2400/12—Inflammable refrigerants
    • 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
    • F25B2400/22—Refrigeration systems for supermarkets
    • 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
    • F25B2400/24—Storage receiver heat
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/31—Low ambient temperatures

Definitions

  • the invention relates to a refrigeration system with an ambient temperature-dependent circuit and a method for operating this refrigeration system.
  • the main objective of using CO 2 plants is to replace conventional refrigerants with their high direct global warming potential, but this measure does not cause additional hazards due to combustibility or toxicity and does not worsen the energy efficiency of the entire plant.
  • a CO 2 system for the normal cooling circuit in which the heat is released without the use of an additional circuit, is greatly oversized in the partial load range. This leads to problems during partial load operation such as ensuring a safe oil return.
  • DE 31 11 469 A1 describes a multi-stage compression cold steam engine, which consists of at least two refrigerant circuits of different pressure levels and at least one connecting the individual circuits under medium pressure heat exchanger with integrated heat storage.
  • the aim of the invention is to design a refrigeration system so that o. G. Disadvantages are avoided.
  • the refrigeration system consists of at least two refrigeration circuits a normal refrigeration cycle, in which mainly the refrigerant CO 2 is contained, and an additional cooling circuit.
  • the refrigeration circuits each consist of at least one compressor, at least one air-cooled heat exchanger or condenser, at least one expansion device and at least one evaporator.
  • the two refrigeration circuits are connected in cascade with a heat exchanger, which is also the condenser of the normal cooling circuit and evaporator of the additional cooling circuit connected to each other.
  • the additional heat exchanger can be an air-cooled heat exchanger or condenser in the simplest case. So the heat is released directly into the ambient air.
  • the dissipated heat can be used by the additional heat exchanger, which may be a plate or tube bundle heat exchanger, for example, is connected to a brine circuit. About this brine circuit the heat absorbed by the brine in the additional heat exchanger is conducted to a heat utilization point.
  • the additional heat exchanger which may be a plate or tube bundle heat exchanger, for example.
  • a heat exchanger e.g. may be a plate or shell and tube heat exchanger, the heat at a much higher temperature than in the normal cooling cycle of a heat use, e.g. supplied for domestic water heating or for heating support.
  • heat use does not always require heat.
  • an additional use is omitted, so that in both circuits air-cooled heat exchangers are used for heat dissipation. Since both air-cooled heat exchangers are not operated simultaneously at full power, it is advisable to accommodate both so that the additional air-cooled heat exchanger of the normal cooling circuit is in the same housing as the air-cooled heat exchanger of the additional cooling circuit. In this way, the number of fans and thus the investment sum can be reduced.
  • the ambient temperature and thus also the condensing temperature and the condensing pressure, which gives the signal for the use of the additional cooling circuit, are constantly changing. For relatively short-term changes would be also constantly change the operating mode of the refrigeration system.
  • the heat exchanger between the normal cooling circuit and the additional cooling circuit can be designed as a heat storage. Thus, the heat can be delivered to a storage medium at short-term excesses of the switching pressure.
  • the mode of operation of the refrigeration system is dependent on the liquefaction temperature or the condensing pressure of the normal refrigeration cycle, which depend essentially on the ambient temperature but also on the design of the system and the current refrigeration needs of individual consumers. An additional influence on the mode of operation may result from the heat demand of the waste heat user.
  • the three main operating modes are the following: When operating at high ambient temperatures above the range of 5 to 20 ° C, called in the claims and summer operation, the resulting heat in the normal cooling circuit via a heat exchanger of the same time Condenser of the normal cooling circuit and evaporator of the additional cooling circuit is transferred to the additional circuit. This heat is then released via a heat exchanger or condenser of the additional cooling circuit to the environment.
  • the system When operating at low ambient temperatures below the range of 5 to 20 ° C, in the claims and subsequently called winter operation, the system is operated without the use of the additional cooling circuit.
  • the waste heat is supplied via an additional heat exchanger, e.g. an air-cooled heat exchanger can be delivered to the environment.
  • the heat is transferred to a part via a heat exchanger to the environment and to a part of the condenser of the normal cooling circuit to the evaporator of the additional cooling circuit. This heat is then released via an air-cooled heat exchanger of the additional cooling circuit to the environment.
  • the transient operation may also be at lower temperatures than stated above, e.g. if useful heat demand exists for removal from the additional cooling circuit.
  • the system described Compared with conventional cascade systems with CO 2 in the deep-freeze circuit and a refrigerant with high global warming potential in the normal refrigeration cycle, the system described has the advantage that even in the normal refrigeration cycle, the refrigerant CO 2 can be applied.
  • the plant described Compared to a cascade system, in which the cooling of the normal cooling circuit would always be done via an additional circuit, the plant described has the advantage that the losses due to the additional temperature difference in the heat exchanger between condenser of the normal cooling circuit and evaporator of the additional cooling circuit of the cascade only occur when the heat the system takes place via the additional cooling circuit, ie if the ambient temperature is above the switching range of the ambient temperature of 5 ° C to 20 ° C and summer operation is performed. Below this switching range so during winter operation, these losses do not occur because the heat is dissipated without the use of the additional circuit.
  • the refrigerant CO 2 could also be used in the additional cycle.
  • the described problems due to the high pressures could be reduced by using an industrially prefabricated unit that is designed only for high ambient temperatures.
  • Fig. 1 describes a supermarket refrigeration system with heat dissipation via additional air-cooled heat exchanger.
  • the refrigeration system is a cascade refrigeration system consisting of a normal refrigeration cycle B and an additional cycle C. Both are connected to each other via a heat exchanger 7, which is a plate heat exchanger in the embodiment.
  • the circulating in the normal cooling circuit B refrigerant CO 2 is compressed in a composite, which consists of several compressors and is symbolized as a compressor 3, to a higher pressure.
  • the liquefaction of the refrigerant takes place either in the condenser 4 with heat being released to the evaporator 11 of the additional circuit C or in the additional air-cooled heat exchanger 13.1 with heat being released to the ambient air.
  • the expansion device 5 consists of several expansion valves, which are located on the cooling furniture and are symbolized as an expansion device 5. Here, the expansion of the refrigerant takes place on the evaporation pressure.
  • the goods are cooled by evaporators in the individual refrigeration units, which are symbolized as an evaporator 6.
  • the air inside the cooling rack heat is removed, which is absorbed by the refrigerant CO 2 .
  • the refrigerant circulating in the additional circuit C R134a is compressed in a compressor 8, which is speed-controlled in this example, to a higher pressure, which is in contrast to the refrigerant CO 2 below 15 bar.
  • the cooling or liquefaction of the refrigerant R134a takes place in an air-cooled heat exchanger 15.1 and / or 9, wherein the resulting heat is released to the ambient air.
  • the expansion device 10 is here an electronically controlled expansion valve. Here, the expansion of the refrigerant to the evaporation pressure of the additional cooling circuit C.
  • the refrigerant R134a takes in the evaporator 11 of the heat exchanger 7, the resulting in the condenser 4 of the normal refrigeration cycle B liquefaction heat.
  • a line 14 branches off, which is led via an additional air-cooled heat exchanger 15.1 and is reconnected before and after the air-cooled heat exchanger 9.
  • the air-cooled heat exchanger may possibly also be dispensed with.
  • the air-cooled heat exchangers 13.1 and 15.1 are located in a common housing 16 with shared air fans and are successively flowed through by the ambient air.
  • the air-cooled heat exchanger 13.1 of the normal cooling circuit B in the flow direction of the air in front of the air-cooled heat exchanger 15.1 of the additional cooling circuit C. In this way, the ambient air flows through the heat exchanger 13.1 of the normal cooling circuit B only at a low temperature level and then the heat exchanger 15.1 of the Additional cooling circuit C.
  • the system At condensing pressures of the normal cooling circuit B from approx. 50 bar, which occur at ambient temperatures above approx. 10 ° C, the system is operated in summer mode.
  • the resulting in the normal cooling circuit B heat via a heat exchanger 7 is the same condenser 4 of the normal cooling circuit B and evaporator 11 of the additional cooling circuit C, transferred to the additional cooling circuit C.
  • This heat is then released via the additional air-cooled heat exchanger 15.1 and the air-cooled condenser 9 of the additional cooling circuit C to the environment.
  • the line 12 and the air-cooled heat exchanger 13.1 is not or hardly flows through it.
  • the system is operated in transition mode.
  • the refrigerant CO 2 first flows through the line 12 and the additional air-cooled heat exchanger 13.1 and gives off part of the liquefaction heat.
  • the refrigerant flows through the condenser 4 of the heat exchanger 7.
  • the heat is transferred either to the storage medium in the heat exchanger 7 or to the evaporator 11 of the additional cooling circuit C. Only when the storage medium can no longer absorb heat, the additional cooling circuit C must go into operation.
  • Fig. 2 shows in a further embodiment, a supermarket refrigeration system with Nutz policenikêtraumn.
  • the refrigeration system is a cascade refrigeration system, which consists of a freezing circuit A with the refrigerant CO 2 , a normal cooling circuit B with the refrigerant CO 2 and an additional circuit C with the refrigerant isobutane.
  • the refrigerant isobutane has no global warming potential, but is flammable. However, the application is possible because it is only used in the engine room and outside and not inside the supermarket.
  • the freezing circuit A is connected via the heat exchanger 2, which is a plate heat exchanger in the embodiment, connected to the normal refrigeration cycle B.
  • the normal cooling circuit B is connected via the heat exchanger 7, which is a plate heat exchanger in the embodiment, with the additional cooling circuit C.
  • compressor 8 and condenser 9 of the additional circuit C branches off a line 14, which is guided over a liquid-cooled heat exchanger 15.2 and is re-integrated before and after the air-cooled heat exchanger 9.
  • the resulting in the freezing cycle liquefaction of the refrigerant CO 2 is discharged via the condenser 1 of the freezing circuit A in the heat exchanger 2 to the evaporator 6.1 of the normal cooling circuit B.
  • the evaporator 6.1 in the heat exchanger 2 is a cooling point, the parallel to the evaporators in the refrigerated shelves, which are symbolized as evaporator 6 of the normal refrigeration cycle, connected.
  • the circulating in the normal cooling circuit B refrigerant CO 2 is compressed in a composite, which consists of several compressors and is symbolized as a compressor 3, to a higher pressure.
  • the liquefaction of the refrigerant takes place either in the condenser 4 with heat to the evaporator 11 of the additional circuit C or in the liquid-cooled heat exchanger 13.2 under heat to a brine circuit D.
  • the heat through the brine circuit D is led to a parking lot and there, if necessary, to Ice freeze used.
  • the expansion device 5 consists of several expansion valves, which are located on the cooling furniture and are symbolized as an expansion device 5. Parallel to this expansion device 5 is an expansion device 5.1. Here the expansion of the coolant takes place on the evaporation pressure. The coolant then becomes the evaporator 6.1. passed, which is located in the heat exchanger 2.
  • the goods are cooled by dissipating heat via evaporators in the individual refrigeration units, which are symbolized as an evaporator 6.
  • the evaporator 6.1 is connected, which receives the heat from the freezing circuit A.
  • the circulating in the additional cycle C isobutane is compressed in a compressor 8, which is speed-controlled in this example, to a higher pressure, the in contrast to the refrigerant CO 2 is below 15 bar.
  • the cooling or liquefaction of the refrigerant isobutane takes place in the liquid-cooled heat exchanger 15.2 when there is heat demand for a liquid circuit E, which in this case is a service water circuit. If no or only part of the liquefaction heat is required, the remaining heat is dissipated in an air-cooled heat exchanger 9 to the ambient air.
  • the expansion device 10 is in this case an electronically controlled expansion valve.
  • the expansion of the refrigerant to the evaporation pressure of the additional cooling circuit C is in this case an electronically controlled expansion valve.
  • the system is operated in summer mode.
  • the resulting in the normal cooling circuit B heat via a heat exchanger 7 is the same condenser 4 of the normal cooling circuit B and evaporator 11 of the additional cooling circuit C, transferred to the additional cooling circuit C.
  • This heat is then transferred via the additional liquid-cooled heat exchanger 15.2 to a liquid circuit E for heat utilization, in this case, a hot water circuit. If the entire heat is not required by the service water circuit, the residual heat is released via the air-cooled heat exchanger 9 of the additional cooling circuit C to the environment.
  • the line 12 and the liquid-cooled heat exchanger 13.2 is not or hardly flows through it.
  • the system At condensing pressures of the normal cooling circuit B below about 45 bar, which occur at temperatures below about 5 ° C, the system is run in winter operation. The system is operated without the use of the additional cooling circuit C. The refrigerant is transported after flowing through the conduit 12 to the liquid-cooled heat exchanger 13.2. There, the liquefaction heat is conducted by means of a brine circuit D for heat utilization to a parking lot, through the surface of the heat is released to the environment. The condenser 4 is not or hardly flowed through in this mode.
  • the system is operated in transition mode.
  • the refrigerant CO 2 first flows through the line 12 and the additional liquid-cooled heat exchanger 13.2 and releases some of the liquefaction heat. Thereafter, the refrigerant flows through the condenser 4 of the heat exchanger 7. Via the condenser 4, the heat is transferred either to the storage medium in the heat exchanger 7 or to the evaporator 11 of the additional cooling circuit C. Only when the storage medium can no longer absorb heat, the additional cooling circuit C must go into operation.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
EP08033514A 2007-04-19 2008-03-29 Installation de refroidissement Withdrawn EP1983276A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200710018439 DE102007018439B3 (de) 2007-04-19 2007-04-19 Kälteanlage

Publications (1)

Publication Number Publication Date
EP1983276A1 true EP1983276A1 (fr) 2008-10-22

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP08033514A Withdrawn EP1983276A1 (fr) 2007-04-19 2008-03-29 Installation de refroidissement

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EP (1) EP1983276A1 (fr)
DE (1) DE102007018439B3 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2543086A (en) * 2015-10-08 2017-04-12 Isentra Ltd Refrigeration
CN107024017A (zh) * 2017-03-23 2017-08-08 北京国科天创建筑设计院有限责任公司 一种高进水温度的复迭式二氧化碳热泵系统

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT1393128B1 (it) * 2009-03-06 2012-04-11 Ecold S N C Di Colferai Roberta & C Impianto termico particolarmente per punti vendita di prodotti alimentari come supermercati e simili.
DE102020007489A1 (de) 2020-12-08 2022-06-09 Truma Gerätetechnik GmbH & Co. KG Temperierungsanordnung

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3111469A1 (de) 1981-03-24 1982-10-14 Hermann Prof. Dr.-Ing. 4600 Dortmund Schwind Mehrstufige kompressionskaltdampfmaschine mit waermespeicher
JPH09138046A (ja) * 1995-11-16 1997-05-27 Sanyo Electric Co Ltd 冷却装置
US5687579A (en) * 1994-09-12 1997-11-18 Vaynberg; Mikhail M. Double circuited refrigeration system with chiller
WO2003014637A2 (fr) * 2001-08-09 2003-02-20 Albert Robert Lowes Installation de refrigeration
JP2004271166A (ja) 2003-02-20 2004-09-30 Mitsubishi Electric Corp 冷凍空調装置、冷凍空調装置の運転方法
DE102004038640A1 (de) 2004-08-09 2006-02-23 Linde Kältetechnik GmbH & Co. KG Kältekreislauf und Verfahen zum Betreiben eines Kältekreislaufes

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3111469A1 (de) 1981-03-24 1982-10-14 Hermann Prof. Dr.-Ing. 4600 Dortmund Schwind Mehrstufige kompressionskaltdampfmaschine mit waermespeicher
US5687579A (en) * 1994-09-12 1997-11-18 Vaynberg; Mikhail M. Double circuited refrigeration system with chiller
JPH09138046A (ja) * 1995-11-16 1997-05-27 Sanyo Electric Co Ltd 冷却装置
WO2003014637A2 (fr) * 2001-08-09 2003-02-20 Albert Robert Lowes Installation de refrigeration
JP2004271166A (ja) 2003-02-20 2004-09-30 Mitsubishi Electric Corp 冷凍空調装置、冷凍空調装置の運転方法
DE102004038640A1 (de) 2004-08-09 2006-02-23 Linde Kältetechnik GmbH & Co. KG Kältekreislauf und Verfahen zum Betreiben eines Kältekreislaufes

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
CARETTA O: "HIGH EFFICIENCY, LOW CARBON SUPERMARKET REFRIGERATION", SCIENCE ET TECHNIQUE DU FROID - REFRIGERATION SCIENCE ANDTECHNOLOGY, PARIS, FR, 29 August 2004 (2004-08-29), pages COMPLETE, XP000962588, ISSN: 0151-1637 *

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2543086A (en) * 2015-10-08 2017-04-12 Isentra Ltd Refrigeration
GB2543086B (en) * 2015-10-08 2018-05-02 Isentra Ltd Water-cooled carbon dioxide refrigeration system
CN107024017A (zh) * 2017-03-23 2017-08-08 北京国科天创建筑设计院有限责任公司 一种高进水温度的复迭式二氧化碳热泵系统

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