EP1409936B1 - Abtauen von kaskadenkühlanlagen mittels co2-heissgas - Google Patents

Abtauen von kaskadenkühlanlagen mittels co2-heissgas Download PDF

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Publication number
EP1409936B1
EP1409936B1 EP02747250A EP02747250A EP1409936B1 EP 1409936 B1 EP1409936 B1 EP 1409936B1 EP 02747250 A EP02747250 A EP 02747250A EP 02747250 A EP02747250 A EP 02747250A EP 1409936 B1 EP1409936 B1 EP 1409936B1
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EP
European Patent Office
Prior art keywords
compressor
defrost
defrosting
refrigeration
evaporator
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.)
Expired - Lifetime
Application number
EP02747250A
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English (en)
French (fr)
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EP1409936A1 (de
Inventor
Per Skaerbaek Nielsen
Thomas Lund
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Johnson Controls Denmark ApS
Original Assignee
York Refrigeration ApS
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Publication date
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Publication of EP1409936A1 publication Critical patent/EP1409936A1/de
Application granted granted Critical
Publication of EP1409936B1 publication Critical patent/EP1409936B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • F25B47/022—Defrosting cycles hot gas defrosting
    • 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
    • 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
    • F25B2347/00—Details for preventing or removing deposits or corrosion
    • F25B2347/02—Details of defrosting cycles
    • F25B2347/023—Set point defrosting
    • 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
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D31/00—Other cooling or freezing apparatus
    • F25D31/001—Plate freezers

Definitions

  • the present invention relates to a refrigeration system of the cascade type, comprising an operative refrigerating circuit working with CO 2or another refrigerant and having one or more refrigeration compressors connected so as to suction refrigerant gas from an evaporator equipment and compressing it into a condenser unit, which also acts as an evaporator in a precoupled second refrigerating circuit, and from which condensed refrigerant liquid is conveyed to said evaporator equipment, whereas a defroster circuit is arranged for selectively supplying hot refrigerant to said evaporator equipment for defrosting purposes.
  • Defrosting is necessary to remove ice built up on a freezer or a cooler. In most cases it is a question of proper and efficient function of the equipment, but in some cases it is a vital part of the function.
  • One of the latter cases is a plate freezer, where the product is frozen between two metal plates wherein refrigerant is circulated. To be able to remove the product it is necessary to defrost the plates.
  • Defrosting can be done in several ways, with the most common being:
  • Hot gas defrosting is very efficient as heat is delivered where the ice has built up and it is very economical since the heat used is present in the system. Electrical and hot liquid defrosting requires an external power source which hot gas defrosting does not. During hot gas defrosting the cooler/freezer acts as a secondary condenser dispersing the heat otherwise dispersed in the cooling media (usually water or air).
  • cascade systems are becoming more frequent. Due to the high saturation pressure of CO 2 , it is not possible to keep the pressure within the range normally encountered in refrigeration plants while still condensing it against air or water at ambient temperatures. Thus a cascade system is used, wherein a secondary refrigeration plant cools the CO 2 condenser. The secondary refrigeration plant condenses against the available cooling media. The condensing temperature of the CO 2 is usually in the range of-20°C to -5°C.
  • a valve in the outlet controls the defrosting pressure in the evaporator. This valve will close when the pressure is lower than the desired pressure. However, this restricts the liquid condensed during the defrosting from leaving the evaporator, thus resulting in a build up of liquid in the evaporator. The build up of liquid reduces the surface inside the evaporator available for condensing and as such reduces the overall effect of the defrosting.
  • the patent application DK200100310 describes a plant and a process using CO 2 for defrost.
  • This system is a unit that delivers both defrosting and standstill cooling, e.g. keeping system pressure down during standstill.
  • failure of the defrost system would mean that no standstill cooling is available and it is from some classification societies a demand that the standstill cooling is performed by a separate unit as a part of the safety system.
  • the above-mentioned system is connected to the "distribution system", defined as a vessel with gas/liquid equilibrium along with the piping to the consumers e.g. the evaporators. From the application and its definitions it appears that the possible connection points are: A pump separator, a high-pressure receiver, and the piping to the consumers.
  • defrosting compressor Connecting the defrosting compressor to the refrigeration cycle's low-pressure side results in a very large pressure difference, which most industrial refrigeration compressors cannot handle. Furthermore a defrosting compressor connected to the low pressure side needs to be about 4 times bigger (by swept volume) than one connected to the high pressure side to deliver the same defrosting capacity. Standard refrigeration equipment can be used when connecting to the high-pressure side, while this is not the case when connecting to the low-pressure side.
  • the receiver essentially collects liquid from the condenser and will normally not contain the large amounts of gas necessary for defrosting.
  • the present invention relates to a refrigeration system of the cascade type where the suction side of the defrost compressor is connected to the discharge side of one ore more compressors, said defrost compressor being operable to supply defrost gas at elevated pressure and temperature to at least one evaporator equipment, said defrost compressor being connectable so as to temporarily operate as a refrigeration compressor in parallel with said one or more refrigeration compressors.
  • the system according to the invention limits the high pressure to an absolute minimum number of components while employing as many standard components as possible.
  • a dedicated defrosting compressor another pressure level is created with the sole purpose of defrosting.
  • the high pressure can be limited to the defrosting compressor, the defrost pipe, the evaporator to be defrosted and a few valves at the evaporator.
  • the cascade cooler, refrigeration compressor and associated equipment can be held at the temperature/pressure yielding the most overall efficient plant and still be standard refrigeration components.
  • the defrosting compressor is connected to the refrigeration compressor outlet.
  • a system according to the invention has a specially dedicated compressor for defrosting.
  • This defroster compressor suction gas is the refrigeration compressor discharge gas.
  • the gas has been desuperheated before entering the defrost compressor to avoid too high discharge temperature that could create a problem with lubrication of the defrost compressor.
  • the COP (cooling capacity kW per power consumption kW) of the defrost compressor would be lower and oil cooling would be necessary.
  • Desuperheating (cooling) of the suction gas to the defrosting compressor has an effect on the overall power consumption of the plant.
  • Two methods of cooling are the most likely, the first one being cooling with the same media used in the secondary systems condenser (air or water) and the other method is using the cascade cooler.
  • a cascade cooler would desuperheat the gas before condensing, so introducing a nozzle in the appropriate place in the cascade cooler would yield a supply of cooled gas.
  • the cooling is performed by the secondary system so power will be required by the secondary system.
  • the gas supplied to the defrosting compressor does not contain liquid. A positive superheat is required to avoid liquid hammer (attempting to compress liquid) in the compressor.
  • the air/water cooled cooler offers some advantages. As mentioned earlier, it is not practically possible to condense the CO 2 against air/water at normal ambient temperature, but it is possible to use it to cool the gas before entry into the cascade cooler and defrosting compressor. The benefit is that every kW cooled by the cooler does not have to be removed in the cascade cooler. This results in a reduction of both the size and power consumption of the secondary system. In such a cooler the gas can be cooled to a temperature very close to the ambient temperature, but since the saturation (condensing) temperature is much lower the gas is still sufficiently superheated to avoid liquid hammer. The selection of one of these two systems will be a question of installation costs versus the savings in running costs.
  • the defrost compressor capacity regulation regulates after the discharge (defrost) pressure.
  • the condensing temperature determines the suction pressure in the cooling cycle. This pressure is kept constant by the "hot” refrigeration cycle.
  • a controllable bypass valve is used to bypass hot gas back to the cascade cooler.
  • the bypass valve is arranged in a connection from the discharge side of the defrost compressor and the discharge side of the one or more refrigerating compressors. A precise control of the defrost pressure and temperature is thereby enabled and the bypass valve will smoothen the capacity steps and secure that the pressure does not exceed the maximum design pressure. This control method makes it unnecessary to mount control valves on each cooler to control the pressure during defrost. All defrost control is done by the compressor and the bypass valve.
  • the defrost pressure/temperature can be set for each evaporator individually by changing the defrost compressor discharge pressure set point. This way the defrost can be optimised for the individual type of evaporator. Some applications can benefit from a more gradual defrost while some need a fast defrost. Considerations when selecting defrost temperature will include heat loss into the surroundings, water/steam contents in the room air and product quality.
  • the refrigerant outlet from the evaporator equipment can be connected to the suction side of the one or more refrigeration compressors through a liquid operated liquid draining device.
  • thermodynamic liquid drain designed for steam and compressed air application.
  • This device allows liquid to pass and stops gas in much the same way as a float valve mechanism.
  • Float valve mechanisms employ a floating ball but these have been difficult or expensive to get for the high pressure needed.
  • the liquid drain used is simple and can accept the pressures. The benefit is that when the compressor controls the pressure completely, the liquid drain only needs to drain the liquid in the freezer and not concern itself with regulating the pressure. The result is an extremely simple system with an efficient operation.
  • a system as described, wherein the entire gas conductor system from the defrost compressor through the evaporator equipment and to the drain pipe of the evaporator can generally be without pressure regulating means and will preferably be laid out for operating at pressures not exceeding 50 bar.
  • the gas will, after compression in the defrosting compressor, be condensed in the evaporator to be defrosted.
  • the COP cooling capacity kW per power consumption kW
  • the difference is naturally dependent on the type (refrigerant etc) of the secondary system and running conditions, but in general terms a factor of two is realistic. This means that for every 100 kW used by the defrosting compressor, the power consumption of the secondary system drops with 200 kW with a resulting overall drop of 100 kW.
  • the defrost compressor employed in this system will deliver approximately 600 kW heating. If electrical defrosting is to be used, all 600 kW is needed in electricity, so the comparison is really an increase of 600 kW compared to a drop of 100 kW. If hot glycol is to be used the heating could be extracted in the system (most likely the secondary systems hot side) so the power consumption only increases with the pump power. However, no gain similar to the one described above is achieved.
  • the compressors used are mainly large industrial compressors for industrial cooling purposes, but that the invention also can be used in connection with plants comprising commercial compressors capable of handling the given pressure and temperature.
  • cooling and freezing plants in butcher shops, in supermarkets or in other retail shops can be mentioned as places to use the system.
  • the defrost compressor capacity to supply hot gas to other elements than to a traditional evaporator e.g. to elements consisting of heating/evaporator pipes placed in areas where ice otherwise will built up.
  • Freezers that need defrosting is often used onboard fishing vessels and in such plants heating/evaporator pipes can be installed in the floor in the freezing area. In this area there will typically be ice formations, which today is removed or controlled by electrical heating elements. By replacing these elements with heating/evaporator pipes less electrical power is needed and the defrost compressor is used more efficient whereby energy is saved in the second condensing unit.
  • CO 2 hot gas from the defrost compressor can be used for traditional defrosting, for heating and for defrosing in all places where the temperature is below 10 °C.
  • fig. 1 which shows a system according to the invention, the systems function will be described. Please note that the fig. is simplified to ease understanding.
  • the freezing system 2 is executed in the traditional manner.
  • the pump separator 4 contains liquid refrigerant at the evaporating temperature.
  • the pumps 6 pump refrigerant liquid to the evaporator 8 through the valve station 10.
  • the refrigerant liquid is partially or completely evaporated and returned through the valve station 10 to the pump separator 4.
  • the gas generated in the evaporator 8 is removed by the refrigeration compressor 12, which compresses the gas to the condensing pressure. From the refrigeration compressor 12 the gas is primarily led to the cascade cooler 14 where the gas is condensed before being led back to the pump separator 4.
  • a secondary condensing unit 16 provides cooling for the cascade cooler 14.
  • the freezing system 2 as described here, is well known technology and is as such not interesting, but the defrosting system is the essence of the invention described here.
  • the defrost compressor 20 takes suction from the discharge of the refrigeration compressor 12 (e.g. at condensing pressure) and compresses it to the desired defrost pressure. Please note that the gas from the refrigeration compressor 12 is significantly superheated. To avoid too high discharge temperature (oil problems) from the defrost compressor 20 it could be necessary to desuperheat (cool) the gas before entry into the defrost compressor 20.
  • This cooler has not been included on the sketch because the function is not vital to the principal function of the defrost system.
  • the gas cooling could take place in an external heat exchanger or it could take place in the cascade cooler 14. As mentioned this gas cooling is not essential for the principal function of the system 2, but since some energy efficiency issues arise from this it will be discussed later in detail.
  • the gas is led to the evaporator 8.
  • the gas is led to the liquid/gas "outlet" 22 of the evaporator 8, resulting in a defrosting backward.
  • backward defrosting is considered most efficient and thus it is outlined here.
  • backward defrosting is safer since the risk of liquid bullets being shot through the system is reduced.
  • the defrost gas condenses and it is led out through the liquid "inlet" 24 of the evaporator 8.
  • the compressor 20 capacity regulation will regulate according to the discharge pressure as opposed to the "normal" suction pressure regulation. This method of regulation is common in heat pumps.
  • the suction pressure for the defrosting compressor 20 e.g. the condensing pressure in the CO 2 circuit
  • the suction pressure for the defrosting compressor 20 is kept constant by the secondary condensing unit 16.
  • Regulating the pressure with the compressor 20 while the float valve 28 drains the evaporator 8 has some benefits:
  • a controllable bypass 32 valve is arranged in a connection from the discharge side of the defrost compressor and the discharge side of the one or more refrigerating compressors to bypass hot gas back to the cascade cooler 14.
  • Fig. 2 is showing a log(P)-H diagram of defrost according to the invention in cascade systems.
  • the diagram shows the normal refrigeration cycle (34). From evaporating pressure (36) the refrigerant is compressed (38) up to the condensing pressure (40). From the compressor discharge (42) the gas is cooled and eventually condensed before it is flashed back to the evaporating pressure (36).
  • the system according to the invention connects the defrosting compressor (20) after the refrigeration compressors discharge port (42) and before condensing takes place (44) in the condenser/cascade cooler.
  • the defrost compressor is connected at the refrigeration compressors suction side (46) or after the condenser/cascade cooler (48).

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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)
  • Defrosting Systems (AREA)
  • Fertilizers (AREA)

Claims (7)

  1. Kühlsystem vom Kaskadentyp (2), umfassend einen wirksamen, kühlenden Kreislauf, der mit CO2 oder einem anderen Kühlmittel funktioniert und umfassend einen oder mehrere Kühlkompressoren (12), die so verbunden sind, dass sie Kühlgas von einem Verdampferapparat (8) saugen und das Gas in eine Kondensatoreinheit (14) komprimieren, welche Kondensatoreinheit auch als Verdampfer in einem vorgekoppelten zweiten Kühlkreislauf (16) funktioniert, und von welcher Einheit kondensierte Kühlflüssigkeit zum Verdampferapparat (8) geleitet wird, worin ein Enteisungskreislauf (18) für die selektive Versorgung des genannten Verdampferapparats (8) mit heissem Kühlmittel für Enteisungszwecke angeordnet ist, wobei der Enteisungskreislauf (18) einen Enteisungskompressor (20) umfasst, dadurch gekennzeichnet, dass die Saugseite des Enteisungskompressors (20) mit der Entlastungsseite von einem oder mehreren der Kühlkompressoren (12) verbunden ist, wobei der Enteisungskompressor (20) dafür ausgelegt ist, Enteisungsgas bei erhöhtem Druck und Temperatur wenigstens einem Verdampferapparat (8) zuzuführen, wobei der Enteisungskompressor (20) derart verbindbar ist, dass er sich zeitweise als Kühlkompressor in parallel mit dem oder den genannten einen oder mehreren Kühlkompressoren (12) betriebbar ist.
  2. Kühlsystem nach Anspruch 1, worin die Saugseite des Enteisungskompressors (20) mit der Entlastungsseite eines oder mehrerer Kühlkompressoren (12) durch eine vorzugsweise aus der Kondensatoreinheit (14) gestalteten Enthitzungseinheit verbunden ist.
  3. System nach Anspruch 1, worin ein regelbares Überlaufventil (32) in einem Anschluss zwischen der Entlastungsseite des Enteisungskompressors (20) und der Entlastungsseite eines oder mehrerer Kühlkompressoren (12) angeordnet ist.
  4. System nach Anspruch 1, worin der Kühlmittelauslass des Verdampferapparats (8) während der Enteisung mit der Saugseite eines oder mehrerer Kühlkompressoren (12) durch ein flüssigkeitsbetriebenes Flüssigkeitsableitungsgerät (28) verbunden ist.
  5. System nach Anspruch 1, worin das ganze Gasleitungssystem zwischen dem Enteisungskompressor (20) durch den Verdampferapparat (8) und dem Auslassrohr (24) des Verdampferapparats (8) generell ohne Druckreguliermittel und für Betrieb bei Drücke ausgelegt ist, die nicht 50 bar überschreiten.
  6. System nach Anspruch 1, worin die Entlastungsseite des Enteisungskompressors (20) mit irgendeinem oder mehreren von einer Reihe von Verdampfereinheiten (8) während der Enteisung im genannten Verdampferapparat selektiv schaltbar ist, während die übrigen Einheiten noch während der Kühlung betriebbar sind.
  7. System nach Anspruch 1, worin wenigstens ein Kühlkompressor (12) parallel zu einem oder mehreren Kompressoren schaltbar ist, so dass er zeitweise als Enteisungskompressor (20) betriebbar ist.
EP02747250A 2001-06-13 2002-06-11 Abtauen von kaskadenkühlanlagen mittels co2-heissgas Expired - Lifetime EP1409936B1 (de)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DK200100921 2001-06-13
DKPA200100921 2001-06-13
DKPA200101068 2001-07-06
DK200101068 2001-07-06
PCT/DK2002/000391 WO2002101305A1 (en) 2001-06-13 2002-06-11 Co2 hot gas defrosting of cascade refrigeration plants

Publications (2)

Publication Number Publication Date
EP1409936A1 EP1409936A1 (de) 2004-04-21
EP1409936B1 true EP1409936B1 (de) 2006-12-13

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP02747250A Expired - Lifetime EP1409936B1 (de) 2001-06-13 2002-06-11 Abtauen von kaskadenkühlanlagen mittels co2-heissgas

Country Status (5)

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EP (1) EP1409936B1 (de)
AT (1) ATE348301T1 (de)
DE (1) DE60216764T2 (de)
DK (1) DK1409936T3 (de)
WO (1) WO2002101305A1 (de)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1422487A3 (de) * 2002-11-21 2008-02-13 York Refrigeration APS Heissgasabtau für Kälteanlagen
DE10332859A1 (de) * 2003-07-18 2005-02-10 Linde Kältetechnik GmbH & Co. KG Heißgasabtauverfahren für Kälteanlagen
EP1775531A1 (de) * 2005-10-12 2007-04-18 GTI Koudetechnik B.V. Gerät und System zum Kühlen und/oder Gefrieren und zum Abtauen
WO2008112568A2 (en) * 2007-03-09 2008-09-18 Johnson Controls Technology Company Compressor with multiple inlets

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3766745A (en) * 1970-03-16 1973-10-23 L Quick Refrigeration system with plural evaporator means
US4184341A (en) * 1978-04-03 1980-01-22 Pet Incorporated Suction pressure control system
US4437317A (en) * 1982-02-26 1984-03-20 Tyler Refrigeration Corporation Head pressure maintenance for gas defrost
SE439831C (sv) * 1984-03-21 1987-01-26 Olson Hans E E Forfarande och anordning for avfrostning av flera forangare
JP3082560B2 (ja) * 1994-03-09 2000-08-28 ダイキン工業株式会社 二元冷却装置
NO20005575D0 (no) * 2000-09-01 2000-11-03 Sinvent As Metode og arrangement for avriming av kulde-/varmepumpeanlegg
DK174257B1 (da) * 2001-02-23 2002-10-21 Teknologisk Inst Anlæg samt fremgangsmåde, hvor CO2 anvendes som kølemiddel og som arbejdsmedie ved afrimning

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ATE348301T1 (de) 2007-01-15
DE60216764D1 (de) 2007-01-25
EP1409936A1 (de) 2004-04-21
DE60216764T2 (de) 2007-10-04
DK1409936T3 (da) 2007-04-23
WO2002101305A1 (en) 2002-12-19

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