EP0348771A2 - Procédé d'approvisionnement en froid d'un consommateur de froid - Google Patents

Procédé d'approvisionnement en froid d'un consommateur de froid Download PDF

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Publication number
EP0348771A2
EP0348771A2 EP89111056A EP89111056A EP0348771A2 EP 0348771 A2 EP0348771 A2 EP 0348771A2 EP 89111056 A EP89111056 A EP 89111056A EP 89111056 A EP89111056 A EP 89111056A EP 0348771 A2 EP0348771 A2 EP 0348771A2
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EP
European Patent Office
Prior art keywords
cold
cold water
consumer
water
ice
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Withdrawn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
EP89111056A
Other languages
German (de)
English (en)
Other versions
EP0348771A3 (fr
Inventor
Thomas Brunder
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.)
York Deutschland GmbH
Original Assignee
York International 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 York International GmbH filed Critical York International GmbH
Publication of EP0348771A2 publication Critical patent/EP0348771A2/fr
Publication of EP0348771A3 publication Critical patent/EP0348771A3/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Withdrawn legal-status Critical Current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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D16/00—Devices using a combination of a cooling mode associated with refrigerating machinery with a cooling mode not associated with refrigerating machinery
    • 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
    • F25D17/00—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces
    • F25D17/02—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating liquids, e.g. brine

Definitions

  • the invention relates to a method for supplying a cold consumer with cold, in which the cold is taken from an ice store and a liquid cooler and fed to the cold consumer through a cold water circuit.
  • the ice store is charged by a refrigeration machine with the involvement of an intermediate circuit which contains glycol or brine as the coolant.
  • the cold given off by the chiller of the liquid cooler is given to the cold water circuit by a further intermediate circuit and transported by it to the cold consumer.
  • the respective activation of an intermediate circuit in the cold flow has the disadvantage that the temperature gradient required for the transmission of the cold results in a corresponding lowering of the evaporation temperature of the cold means required. This has the consequence that, provided the condensing temperature of the refrigerant remains unchanged, the coefficient of performance and thus the efficiency of the system deteriorate.
  • the object of the invention is therefore to develop the method of the type mentioned at the outset in such a way that the coefficient of performance is improved and, moreover, the effort is reduced.
  • a water cooler is used as the liquid cooler, the chiller of which only releases cold to the ice store during the nighttime break of the cold consumer, whereas cold only gives off to the cold water circuit by direct heat exchange during daily operation of the cold consumer.
  • the chiller or chiller of the water cooler is therefore used alternatively for charging the cold storage or for delivering cold to the cold water circuit.
  • This double utilization of the refrigeration machine considerably reduces the outlay for the method according to the invention. Since the charging of the ice storage and the heat transfer to the cold water circuit is carried out by direct evaporation of the refrigerant in the ice storage or by a direct evaporator inserted into the cold water circuit and intermediate circuits are thus avoided, a higher evaporation temperature of the refrigerant is possible than in the prior art, and it becomes achieved refrigeration with a good coefficient of performance and thus high efficiency.
  • the nominal output of the refrigeration machine can advantageously be selected to be lower than the nominal refrigeration requirement of the refrigeration consumer. This further reduces the effort required to carry out the method according to the invention.
  • a preferred development of the invention is that the cold water circuit is led through the ice store to absorb cold. This enables the ice storage to be discharged without switching on an intermediate circuit and therefore with high efficiency.
  • a chiller As a water cooler. Such a chiller combines high operational reliability with a compact structure.
  • the cold water of the cold water circuit is cooled to absorb cold by about 6 K, preferably from about 12 ° Celsius to about 6 ° Celsius.
  • the system shown in FIG. 1 has a water cooler 10, the compressor 12 of which is connected on the pressure side to the preferably air-cooled condenser 14.
  • a line 16 leads from the condenser to the evaporator 18 of the water cooler, a remote-operated shut-off device 20 and an expansion valve 22 being inserted into the line 16, as seen in the flow direction of the refrigerant.
  • the remote shut-off device 20 receives its opening or closing impulses from a control device, not shown in the drawing.
  • a line 24 leads from the evaporator 18 back to the compressor 12.
  • a line 28 is connected to the line 16 upstream of the remotely operated shut-off device 20 at point 26, into which a second remotely operated shut-off device 30 and a second expansion valve 32 are inserted and which leads to the storage tubes 34 of the ice store 36.
  • the second remotely operated shut-off device 30 is connected for control purposes to the control device not shown in FIG. 1 and already mentioned above.
  • a line 38 leads back to the compressor 12 and is connected upstream of the compressor 12 at the point 40 to the line 24.
  • the storage tubes 34 of the ice store are arranged in a storage space 42 which is filled with water. Since the present exemplary embodiment is an open ice store 36, the storage space 42 is connected to the outer space 44 and forms it a water level in the storage space 42, the surface 46 of which is indicated. The storage tubes 34 are arranged below the surface 46 and run at a mutual distance.
  • a line 48 with inserted circulation pump 50 leads from the lower area of the storage space 42 to the primary-side entrance of a surface heat exchanger 52.
  • a line 54 leads back from the exit of the surface heat exchanger to the upper area of the storage space 42.
  • a distribution valve 56 is inserted into line 54, the distribution line 58 of which leads to line 48 and is connected there downstream of the circulation pump 50.
  • a temperature sensor 62 is inserted into the line 48, which acts on the distribution valve 56 through a control line 64.
  • the secondary side of the surface heat exchanger 52 is inserted into the cold water circuit 66, which transports the cold to the schematically indicated cold consumer 68, for example in the form of a heat exchanger.
  • a pipe 70 leads from the surface heat exchanger 52 to a flow header 72, from which a cold water flow line 74 with inserted second circulation pump 76 leads to the cooling consumer 68.
  • a cold water return line 78 is returned to a return collector 80, which is connected to the secondary side of the surface heat exchanger 52 by a pipe 82 with an inserted third circulation pump 84 to close the cold water circuit 66.
  • a second distribution valve 86 is arranged in the pipeline 82 between the surface heat exchanger 52 and the third circulation pump 84, the distribution line 88 bypassing the surface heat exchanger 52 and at point 90 in the Pipe 70 opens, as can be clearly seen from FIG. 1.
  • a second temperature sensor 92 is arranged in the pipeline 70, the control line 94 of which acts on the distribution valve 86.
  • the evaporator 18 of the water cooler 10 is also designed as a surface heat exchanger, the secondary side of which is inserted into the cold water circuit 66 in parallel on the water side in parallel with the surface heat exchanger 52.
  • the evaporator 18 is connected to the return manifold 80 through the pipeline 96 with an inserted fourth circulation pump 98 and through the pipeline 100 to the flow manifold 72.
  • the flow collector 72 is connected to the return collector 80 by a bypass line 102, an overflow valve 104 being inserted into the bypass line 102 and opening at a predetermined differential pressure between the two collectors.
  • all the circulation pumps 76, 84, 98 of the cold water circuit 66 are switched off.
  • the first circulation pump 50 of the pipeline 48 is switched off, so that no water is circulated from the storage space 42 through the surface heat exchanger 52.
  • the water circuit which connects the storage space 42 of the ice store to the surface heat exchanger 52 is referred to here as an intermediate circuit 106 for the sake of simplicity.
  • the remote-operated shut-off valve 20 is closed, so that no refrigerant can get into the evaporator 18, that is to say the evaporator 18 is out of operation.
  • the compressor 12 of the water cooler now becomes lers put into operation, so that refrigerant passes through the opened second remote shut-off valve 30 and the second expansion valve 32 into the storage tubes 34 and evaporates there.
  • part of the water in the storage space freezes on the outside of the storage tubes 34 and forms an ice layer, which takes over the cold storage. Since the evaporation of the refrigerant takes place directly in the ice store, the difference between the evaporation temperature in the storage tubes 34 and the condensation temperature of the refrigerant in the outside air-cooled condenser 14 is small, so that the ice is stored with a good coefficient of performance and thus with a good efficiency.
  • the condenser 14 Since the condenser 14 is subjected to a relatively cold temperature by outside air during the nightly ice storage and thus the temperature difference between the evaporating and the condensed refrigerant is reduced, an improvement in the coefficient of performance and the efficiency of the system is additionally achieved.
  • the ice storage is now driven until the storage tubes 34 of the ice storage are covered with an ice layer of permissible thickness and the ice storage is thus charged. Then the compressor 12 is switched off.
  • the second remotely operated shut-off device 30 is closed and the first remotely operated shut-off device 20, on the other hand, is opened, so that the evaporator 18 of the water cooler through which the cold water of the cold water circuit 66 flows is acted upon on the refrigerant side.
  • all the circulation pumps 50, 76, 84, 98 are in operation, so that the following cold flow results:
  • the cold water flowing through the cold water circuit is at a temperature of un while the compressor 12 is running cooled 6 ° Celsius and then fed through the pipeline 100 to the flow collector 72.
  • the cold water is fed through the second circulation pump 76 and the flow line 74 to the cold consumer 68, in which the cold water releases cold with an increase in temperature to approximately 12 ° Celsius.
  • This heated cold water is then fed through the return line 78 to the return collector 80 and then through the fourth circulation pump 98 and the pipeline 96 to the evaporator 18 for renewed cooling.
  • the intermediate circuit 106 is in operation, so that water is cooled to approximately 1.5 ° C. by melting ice located in the storage space 42 and is then fed to the surface heat exchanger 52.
  • the temperature of the water is detected by the temperature sensor 62 and passed on through the control line 64 to the distribution valve 56, which influences the water circulation in the intermediate circuit 106 in such a way that the desired temperature of 1.5 ° Celsius in the line 48 is maintained.
  • the water of the intermediate circuit heats up to approximately 4 ° Celsius.
  • the cold supplied from the ice store 36 to the surface heat exchanger 52 is passed on to the cold water circuit 66.
  • cooled cold water flows from the return collector 80 under the action of the third circulation pump 84, and heated cold water flows from the return collector 80 through the pipeline 82 to the surface heat exchanger 52, in which it is cooled from approximately 12 ° Celsius to 6 ° Celsius.
  • the cooled cold water then flows through the line 70 to the flow collector 72.
  • the water flows coming from the surface heat exchanger 52 and from the evaporator 18 are combined in the flow collector 72 and then flow together through the flow line 74 to the cooling consumer 68.
  • bypass line 102 is provided, which is released at a presettable differential pressure between the flow collector 72 and the return collector 80 by automatically opening the overflow valve 104 so that an emergency circuit is released the cold water is maintained.
  • the cold water temperature in the pipeline 70 is detected by the second temperature sensor 92 and passed on through the control line to the second distribution valve 86, which the cold water flowing to the surface heat exchanger corresponds to the desired temperature conditions
  • Surface heat exchanger 52 and the distribution line 88 divides.
  • the cooling of the cold water in the evaporator 18 is advantageously carried out by influencing the refrigerant circuit, e.g. regulated by switching the compressor on and off, 12.
  • FIG. 2 shows an embodiment variant of the system according to FIG. 1. Individual parts of FIG. 1 recurring in FIG. 2 are provided with reference numbers in FIG. 2 only insofar as this is necessary for understanding, the individual parts of FIG. 1 recurring in FIG. 2 being provided with reference numbers that are equal to 100 have been expanded.

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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)
  • Combustion & Propulsion (AREA)
  • Other Air-Conditioning Systems (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
EP19890111056 1988-06-29 1989-06-19 Procédé d'approvisionnement en froid d'un consommateur de froid Withdrawn EP0348771A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19883821910 DE3821910A1 (de) 1988-06-29 1988-06-29 Verfahren zur versorgung eines kaelteverbrauchers mit kaelte
DE3821910 1988-06-29

Publications (2)

Publication Number Publication Date
EP0348771A2 true EP0348771A2 (fr) 1990-01-03
EP0348771A3 EP0348771A3 (fr) 1991-03-27

Family

ID=6357508

Family Applications (1)

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EP19890111056 Withdrawn EP0348771A3 (fr) 1988-06-29 1989-06-19 Procédé d'approvisionnement en froid d'un consommateur de froid

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EP (1) EP0348771A3 (fr)
DE (1) DE3821910A1 (fr)

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE9404321U1 (de) * 1994-03-15 1994-05-05 Gesellschaft für Kältetechnik-Klimatechnik mbH, 50859 Köln Kälteerzeugungsanlage
DE9404320U1 (de) * 1994-03-15 1994-05-05 Gesellschaft für Kältetechnik-Klimatechnik mbH, 50859 Köln Verteil- und Steuervorrichtung für eine Kälteerzeugungsanlage
DE9404319U1 (de) * 1994-03-15 1994-05-19 Gesellschaft für Kältetechnik-Klimatechnik mbH, 50859 Köln Kälteerzeugungsanlage
EP0602911A1 (fr) * 1992-12-10 1994-06-22 Baltimore Aircoil Company, Inc. Système de refroidissement supplémentaire
EP0861406A4 (fr) * 1995-11-17 1998-12-30 Lennox Ind Inc Systeme de conditionnement d'air a accumulation d'energie thermique
WO1999002929A1 (fr) * 1997-07-10 1999-01-21 York International Corporation Systeme frigorifique de type compound pour refroidissement d'eau et stockage thermique
EP0927861A1 (fr) * 1997-10-31 1999-07-07 Fafco SA Appareil d'accumulation de froid avec stockage de glace
DE19907250A1 (de) * 1999-02-20 2000-08-24 Christian Liebetanz Kältemaschine
EP1085277A3 (fr) * 1999-09-17 2001-12-05 Hitachi Air Conditioning Systems Co., Ltd. Réfrigérateur utilisant de l'ammoniac
US6634182B2 (en) 1999-09-17 2003-10-21 Hitachi, Ltd. Ammonia refrigerator
WO2006021440A1 (fr) * 2004-08-26 2006-03-02 Thermo Electron (Karlsruhe) Gmbh Dispositif de regulation thermique
CN104110926A (zh) * 2014-07-18 2014-10-22 合肥美菱股份有限公司 一种冷凝器的散热结构及其电冰箱

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH688784A5 (de) * 1993-03-05 1998-03-13 Escher Wyss Gmbh Kuehleinrichtung.
DE102007031335B4 (de) 2007-07-05 2018-03-22 Kälte-Eckert GmbH Kocheinrichtung und Verfahren zum Kühlen einer Kocheinrichtung
DE102012208941A1 (de) * 2012-05-29 2013-12-19 Fraunhofer-Gesellschaft zur Förderung der angewandten Forschung e.V. Eisspeicher mit verbessertem Wärmetauscher

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2246401A (en) * 1933-10-03 1941-06-17 Carrier Corp Method and means for providing refrigeration
DE3409480A1 (de) * 1984-03-15 1985-09-26 Meyer, Rud. Otto, 2000 Hamburg Verfahren zur kaelteerzeugung mit zwischengeschaltetem kaeltespeicher zur versorgung lufttechnischer anlagen od. dgl. und anlagen zur durchfuehrung des verfahrens
DE3428713A1 (de) * 1984-05-26 1985-11-28 Hilbers, Heinrich, Dipl.-Ing., 5205 St Augustin Verfahren und vorrichtung eines geschlossenen eisspeichers fuer die kaelteversorgung der raumlufttechnischen klimaanlage
US4565069A (en) * 1984-11-05 1986-01-21 Maccracken Calvin D Method of cyclic air conditioning with cogeneration of ice

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0602911A1 (fr) * 1992-12-10 1994-06-22 Baltimore Aircoil Company, Inc. Système de refroidissement supplémentaire
DE9404321U1 (de) * 1994-03-15 1994-05-05 Gesellschaft für Kältetechnik-Klimatechnik mbH, 50859 Köln Kälteerzeugungsanlage
DE9404320U1 (de) * 1994-03-15 1994-05-05 Gesellschaft für Kältetechnik-Klimatechnik mbH, 50859 Köln Verteil- und Steuervorrichtung für eine Kälteerzeugungsanlage
DE9404319U1 (de) * 1994-03-15 1994-05-19 Gesellschaft für Kältetechnik-Klimatechnik mbH, 50859 Köln Kälteerzeugungsanlage
EP0861406A4 (fr) * 1995-11-17 1998-12-30 Lennox Ind Inc Systeme de conditionnement d'air a accumulation d'energie thermique
US5894739A (en) * 1997-07-10 1999-04-20 York International Corporation Compound refrigeration system for water chilling and thermal storage
WO1999002929A1 (fr) * 1997-07-10 1999-01-21 York International Corporation Systeme frigorifique de type compound pour refroidissement d'eau et stockage thermique
EP0927861A1 (fr) * 1997-10-31 1999-07-07 Fafco SA Appareil d'accumulation de froid avec stockage de glace
US6053006A (en) * 1997-10-31 2000-04-25 Delroc Sa Cold-storing installation having an ice storage reservoir
DE19907250A1 (de) * 1999-02-20 2000-08-24 Christian Liebetanz Kältemaschine
EP1085277A3 (fr) * 1999-09-17 2001-12-05 Hitachi Air Conditioning Systems Co., Ltd. Réfrigérateur utilisant de l'ammoniac
US6634182B2 (en) 1999-09-17 2003-10-21 Hitachi, Ltd. Ammonia refrigerator
WO2006021440A1 (fr) * 2004-08-26 2006-03-02 Thermo Electron (Karlsruhe) Gmbh Dispositif de regulation thermique
CN104110926A (zh) * 2014-07-18 2014-10-22 合肥美菱股份有限公司 一种冷凝器的散热结构及其电冰箱

Also Published As

Publication number Publication date
DE3821910C2 (fr) 1990-04-12
DE3821910A1 (de) 1990-01-04
EP0348771A3 (fr) 1991-03-27

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