EP0340115A1 - Zentrale Kälteanlage zur Versorgung von Räumen mit wenigstens zwei verschiedenen Temperaturen und Abtauverfahren für eine derartige Zentralanlage - Google Patents

Zentrale Kälteanlage zur Versorgung von Räumen mit wenigstens zwei verschiedenen Temperaturen und Abtauverfahren für eine derartige Zentralanlage Download PDF

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Publication number
EP0340115A1
EP0340115A1 EP89401229A EP89401229A EP0340115A1 EP 0340115 A1 EP0340115 A1 EP 0340115A1 EP 89401229 A EP89401229 A EP 89401229A EP 89401229 A EP89401229 A EP 89401229A EP 0340115 A1 EP0340115 A1 EP 0340115A1
Authority
EP
European Patent Office
Prior art keywords
refrigeration
distribution
circuit
temperature
circuits
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Withdrawn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
EP89401229A
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English (en)
French (fr)
Inventor
Michel Debieuvre
Marc Schnaebele
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.)
Electrolux CR SA
Original Assignee
Electrolux CR SA
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 Electrolux CR SA filed Critical Electrolux CR SA
Publication of EP0340115A1 publication Critical patent/EP0340115A1/de
Withdrawn legal-status Critical Current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
    • 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
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D21/00—Defrosting; Preventing frosting; Removing condensed or defrost water
    • F25D21/06—Removing frost
    • 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

Definitions

  • the present invention relates to a refrigeration plant supplying enclosures at at least two temperatures of the type used in large food distribution areas. It also relates to a defrosting process for this plant.
  • This type of known refrigeration plant has a significant drawback due to the thermal inertia of the heat exchangers or refrigerators of the points to be refrigerated supplied by the distribution circuit. This significantly increases the time necessary for defrosting especially refrigerators at negative temperature due to the large volume of cryogenic liquid circulating in the refrigeration distribution circuit.
  • the object of the present invention is to remedy these drawbacks by proposing a new refrigeration plant operating on this principle and supplying chambers at at least two different temperatures, as well as a method for defrosting such a plant.
  • the object of the present invention is a refrigeration plant supplying chambers at at least two different temperatures of the type comprising, for each temperature, a refrigeration unit consisting of a cold production stage, the evaporator of which is connected by an exchanger to a refrigeration distribution circuit, which comprises at least one refrigerator, circuit in which a cryogenic fluid circulates, the refrigeration units being connected to each other, according to the temperatures decreasing res at which they operate, via an exchanger between the refrigeration distribution circuit of the refrigeration unit at the highest temperature and the condenser of the cold production stage of the refrigeration unit at the lowest temperature, refrigeration plant characterized in that the refrigeration distribution circuit of a first refrigeration unit is connected to the refrigeration distribution circuit of a second refrigeration unit by means of pipes making it possible to short-circuit the cold production stage of the second refrigeration unit.
  • the means making it possible to short-circuit the refrigeration production stage of the second refrigeration unit are constituted by two valves mounted respectively on the outward and return pipes for interconnection of the refrigeration distribution circuits and by two conical valves. controlling the circulation of the cryogenic liquid in the distribution circuits, respectively in the exchanger of the refrigeration distribution circuit of the first refrigeration unit in heat exchange with the condenser of the second refrigeration production stage and in the exchanger of the refrigeration distribution circuit of the second assembly refrigeration in heat exchange with the evaporator of the second refrigeration production stage.
  • the present invention also relates to a defrosting process of a refrigeration plant comprising at least two stages of cold production supplying by refrigeration exchangers refrigeration distribution circuits at different temperatures, characterized in that one proceeds successively when defrosting the refrigeration distribution circuits, starting with the one at the highest temperature, the defrosting of the other circuits being carried out at least partially by circulating the cryogenic fluid of the distribution circuits simultaneously in the refrigerators of this circuit and in those of the circuits to higher temperatures.
  • the return to refrigeration operation comprises the following steps: - putting the two refrigeration distribution circuits into communication, stops the circulation of the fluid in the refrigerators of the first refrigeration distribution circuit and forced start of the first refrigeration production stage until the return temperature of the circulating cryogenic fluid in the first refrigeration distribution circuit reaches a negative temperature; - stopping the communication between the two refrigeration distribution circuits and re-regulating all of the refrigerators and the second refrigeration production stage, then - re-regulation of the first refrigeration production stage than.
  • the communication between the two refrigeration distribution circuits and the stopping of the circulation of the fluid in the refrigerators of the first refrigeration distribution circuit makes it possible, at the start, to cool the cryogenic fluid circulating in the second refrigeration distribution circuit. , that is to say the cryogenic fluid which must be brought to the lowest temperature. This therefore makes it possible to speed up the return to refrigeration operation of the second refrigeration unit.
  • the first refrigeration unit operates in controlled refrigeration.
  • the refrigeration unit essentially comprises two refrigeration units 1 and 2, the first refrigeration unit producing a temperature average refrigeration temperature of -4 ° C while the second refrigeration unit produces an average refrigeration temperature of -27 ° C.
  • the first refrigeration unit 1 consists of a cold production stage A of conventional type connected by an evaporator / exchanger device 15 to a circuit B of refrigeration distribution.
  • the stage A for producing cold comprises a compressor 10 passing the gaseous refrigerant from its low pressure state at the inlet to the high pressure fluid state at the outlet, a condenser 11 in which the high pressure fluid liquefies, a liquid accumulator bottle 12, and a pressure reducer 13 which lets the liquid refrigerant pass from the bottle 12 to the evaporator 16 of the evaporator / exchanger device 15.
  • This cold production stage is traversed by a halogenated refrigerant type "freon 12" as is well known to those skilled in the art.
  • This refrigeration production stage is brought via the evaporator / exchanger device 15 to cool the cryogenic fluid circulating in the refrigeration distribution circuit B.
  • the refrigeration distribution circuit B therefore comprises an exchanger 17 forming part of the device 15, a pump 18 for circulation of the cryogenic fluid, a refrigeration distribution circuit discharge valve 19 and, mounted in parallel between the outgoing pipe 29 and the return pipe 30, three assemblies, in the embodiment shown, each consisting of a valve 20, 22, 24 and a refrigerator 21, 23, 25.
  • the circuit B of the refrigeration distribution of the first refrigeration unit 1 is connected to the cold production stage C of the second refrigeration unit 2 by means of a device 27 comprising an exchanger 28 forming part of the refrigeration distribution circuit B and a condenser 31 forming part of the cold production stage C .
  • the exchanger 28 is connected via a valve 26 on the outgoing pipe 29 and directly on the return pipe 30.
  • This first refrigeration unit 1 makes it possible to obtain at the level of the refrigerators 21, 23 or 25 an average temperature of the atmosphere of -4 ° C.
  • the cryogenic fluid circulating in this refrigeration distribution circuit consists of a non-polluting fluid of the brine type.
  • stage C for producing cold comprising a compressor 32, a condenser 31, an accumulator bottle of liquid 33, a pressure reducer 34 and an evaporator 36 forming part of an evaporator / exchanger device 37.
  • the refrigeration distribution circuit D also consists of an exchanger 38, a fluid circulation pump 40, a relief valve 41 and three assemblies mounted in parallel constituted by valves 42, 44 and 46 and refrigerators 43, 45, 47. These three assemblies are connected between the outgoing line 48 and the return line 49.
  • the two distribution circuits B and D are connected together via pipes 50, 51 making it possible to short-circuit the stage C of produc Refrigeration of the second refrigeration unit 2. More specifically, the outward pipe 29 of the refrigeration production circuit B is connected by the pipe 50 provided with the valve 52 to the outward pipe 48 of the second refrigeration distribution circuit D. Similarly, the return pipe 49 of the second refrigeration distribution circuit D is connected via the pipe 51 provided with the valve 53 to the return pipe 30 of the first refrigeration distribution circuit B. On the other hand, a valve 39 is provided having the exchanger 38 of the second refrigeration distribution circuit D. The role of valves 26 and 39, as well as valves 53 and 52 will be explained in more detail below.
  • the valves 26 and 39 are open while the valves 53 and 52 are closed.
  • the operation in defrosting we start by defrosting the refrigeration distribution circuit B in which the cryogenic fluid circulates at an average temperature of -4 ° C. To do this, the compressor 10 of the refrigeration production stage A is stopped, then the pump 18 is forced on and the valves 20, 22, 24 are forced to open. In this case, the distribution circuit B is subjected to a supply of heat produced in particular by the exchanger 28 which is in a heat exchange state with the evaporator 31 of the stage C for producing cold which continues to operate.
  • a cryogenic fluid is therefore sent to approximately + 3 ° C in circuit D, which causes an increase in the temperature of the refrigerant circulating in this circuit.
  • the valves 53 and 52 are closed and the valves 26 and 39 are opened again.
  • the circuits B and D are disconnected .
  • the refrigeration production stage C is then operated in reverse so as to heat the cryogenic fluid circulating in the refrigeration distribution circuit D.
  • the first refrigeration unit can again operate in refrigeration if necessary.
  • valves 53 and 52 are opened, putting the two refrigeration distribution circuits B and D into communication while the valves 26 and 39 are closed, as well as the valves 20, 22 and 24 connected to the refrigerators. 21, 23 and 25.
  • the compressor 10 is then forced into operation.
  • the cryogenic fluid circulating in circuit D is therefore rapidly cooled.
  • T3 in general chosen equal to -14 ° C
  • the valves 53 and 52 are closed, thereby disconnecting the two circuits B and D of refrigeration distribution and the valves 26 and 39 are opened.
  • the valves 20, 22 are brought back into regulation.
  • the refrigeration plant described above therefore has many advantages.
  • the power of the second stage C of refrigeration production can be lower than that of conventional stages, which leads to a reduction in costs and a reduction in energy consumption even if the compressor 10 must be oversized.
  • the cost price of the instal lation in operation is less than in current installations. It is obvious to those skilled in the art that the above description has been given by way of illustration and that the installation must also include devices well known to those skilled in the art such as thermostats with dots. setpoint, programmable thermometers or the like.

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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)
  • Defrosting Systems (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
EP89401229A 1988-04-28 1989-04-28 Zentrale Kälteanlage zur Versorgung von Räumen mit wenigstens zwei verschiedenen Temperaturen und Abtauverfahren für eine derartige Zentralanlage Withdrawn EP0340115A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8805680A FR2630816B1 (fr) 1988-04-28 1988-04-28 Centrale frigorifique alimentant des enceintes a au moins deux temperatures et procede de degivrage d'une telle centrale
FR8805680 1988-04-28

Publications (1)

Publication Number Publication Date
EP0340115A1 true EP0340115A1 (de) 1989-11-02

Family

ID=9365784

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89401229A Withdrawn EP0340115A1 (de) 1988-04-28 1989-04-28 Zentrale Kälteanlage zur Versorgung von Räumen mit wenigstens zwei verschiedenen Temperaturen und Abtauverfahren für eine derartige Zentralanlage

Country Status (3)

Country Link
EP (1) EP0340115A1 (de)
FR (1) FR2630816B1 (de)
SE (1) SE463277B (de)

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0483161B1 (de) * 1989-05-24 1994-06-29 Vp Energisystem I Pitea Ab Kühl- und gefrieranlage
EP0766051A1 (de) * 1995-05-19 1997-04-02 Zwahlen, Urs F. Kälteanlage
US5743102A (en) * 1996-04-15 1998-04-28 Hussmann Corporation Strategic modular secondary refrigeration
US5921092A (en) * 1998-03-16 1999-07-13 Hussmann Corporation Fluid defrost system and method for secondary refrigeration systems
EP1072850A3 (de) * 1999-07-30 2001-10-10 BKT Bonnet Kältetechnik GmbH Kälteanlage
EP1072849A3 (de) * 1999-07-30 2001-10-10 BKT Bonnet Kältetechnik GmbH Kälteanlage
US20110061419A1 (en) * 2007-11-13 2011-03-17 Hill Phoenix, Inc. Refrigeration system
US20110167847A1 (en) * 2008-04-22 2011-07-14 Hill Phoenix, Inc. Free cooling cascade arrangement for refrigeration system
EP2581691A1 (de) * 2011-10-12 2013-04-17 Thermocold Costruzioni SrL Optimierte Wärmepumpe für den Betrieb von Kaskadenkühlzyklen und für Sommerbetrieb
WO2013088358A1 (en) * 2011-12-12 2013-06-20 Innovation Factory S.R.L. Heat pump unit and method for cooling and/or heating by means of said heat pump unit
CN105135777A (zh) * 2015-08-07 2015-12-09 中国中元国际工程有限公司 工厂循环冷却系统及其冷却水再利用系统
DE112009001461B4 (de) * 2008-08-29 2018-05-09 Mitsubishi Heavy Industries Thermal Systems, Ltd. Wärmequellensystem mit einer Wärmepumpe und Steuerverfahren

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR461020A (fr) * 1913-08-01 1913-12-17 Societe Des Moteurs A Gaz Et D Industrie Mecanique Procédé de dégivrage des appareils frigorifères dans les installations frigorifiques à circulation de liquide réfrigérant
US1951447A (en) * 1930-04-18 1934-03-20 Schwarz August Process of and apparatus for refrigeration
DE674404C (de) * 1938-01-26 1939-04-19 Bbc Brown Boveri & Cie Kaelteanlage
US3520146A (en) * 1968-07-01 1970-07-14 Carrier Corp Refrigeration system
FR2114419A5 (de) * 1970-11-19 1972-06-30 Clark Equipment Co
FR2296829A1 (fr) * 1974-12-31 1976-07-30 Vignal Maurice Systeme thermique du genre pompe a chaleur ou refrigerateur
DE2620133A1 (de) * 1976-05-07 1977-11-24 Bosch Gmbh Robert Einrichtung zum beheizen oder kuehlen von raeumen
US4253309A (en) * 1978-12-28 1981-03-03 Thore Abrahamsson Heat pump arrangement
EP0076763A1 (de) * 1981-10-06 1983-04-13 Fsb Kühlanlage mit unterschiedlichen Verdampfungstemperaturen
FR2520853A1 (fr) * 1982-01-29 1983-08-05 Cem Comp Electro Mec Systeme de recuperation, avec elevation du niveau d'energie, des calories dissipees par une machine electrique refroidie par un fluide

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR461020A (fr) * 1913-08-01 1913-12-17 Societe Des Moteurs A Gaz Et D Industrie Mecanique Procédé de dégivrage des appareils frigorifères dans les installations frigorifiques à circulation de liquide réfrigérant
US1951447A (en) * 1930-04-18 1934-03-20 Schwarz August Process of and apparatus for refrigeration
DE674404C (de) * 1938-01-26 1939-04-19 Bbc Brown Boveri & Cie Kaelteanlage
US3520146A (en) * 1968-07-01 1970-07-14 Carrier Corp Refrigeration system
FR2114419A5 (de) * 1970-11-19 1972-06-30 Clark Equipment Co
FR2296829A1 (fr) * 1974-12-31 1976-07-30 Vignal Maurice Systeme thermique du genre pompe a chaleur ou refrigerateur
DE2620133A1 (de) * 1976-05-07 1977-11-24 Bosch Gmbh Robert Einrichtung zum beheizen oder kuehlen von raeumen
US4253309A (en) * 1978-12-28 1981-03-03 Thore Abrahamsson Heat pump arrangement
EP0076763A1 (de) * 1981-10-06 1983-04-13 Fsb Kühlanlage mit unterschiedlichen Verdampfungstemperaturen
FR2520853A1 (fr) * 1982-01-29 1983-08-05 Cem Comp Electro Mec Systeme de recuperation, avec elevation du niveau d'energie, des calories dissipees par une machine electrique refroidie par un fluide

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0483161B1 (de) * 1989-05-24 1994-06-29 Vp Energisystem I Pitea Ab Kühl- und gefrieranlage
EP0766051A1 (de) * 1995-05-19 1997-04-02 Zwahlen, Urs F. Kälteanlage
US5743102A (en) * 1996-04-15 1998-04-28 Hussmann Corporation Strategic modular secondary refrigeration
US5921092A (en) * 1998-03-16 1999-07-13 Hussmann Corporation Fluid defrost system and method for secondary refrigeration systems
EP1072850A3 (de) * 1999-07-30 2001-10-10 BKT Bonnet Kältetechnik GmbH Kälteanlage
EP1072849A3 (de) * 1999-07-30 2001-10-10 BKT Bonnet Kältetechnik GmbH Kälteanlage
US20110061419A1 (en) * 2007-11-13 2011-03-17 Hill Phoenix, Inc. Refrigeration system
US8844308B2 (en) 2007-11-13 2014-09-30 Hill Phoenix, Inc. Cascade refrigeration system with secondary chiller loops
US20110167847A1 (en) * 2008-04-22 2011-07-14 Hill Phoenix, Inc. Free cooling cascade arrangement for refrigeration system
US9151521B2 (en) * 2008-04-22 2015-10-06 Hill Phoenix, Inc. Free cooling cascade arrangement for refrigeration system
DE112009001461B4 (de) * 2008-08-29 2018-05-09 Mitsubishi Heavy Industries Thermal Systems, Ltd. Wärmequellensystem mit einer Wärmepumpe und Steuerverfahren
EP2581691A1 (de) * 2011-10-12 2013-04-17 Thermocold Costruzioni SrL Optimierte Wärmepumpe für den Betrieb von Kaskadenkühlzyklen und für Sommerbetrieb
WO2013088358A1 (en) * 2011-12-12 2013-06-20 Innovation Factory S.R.L. Heat pump unit and method for cooling and/or heating by means of said heat pump unit
CN105135777A (zh) * 2015-08-07 2015-12-09 中国中元国际工程有限公司 工厂循环冷却系统及其冷却水再利用系统
CN105135777B (zh) * 2015-08-07 2018-01-09 中国中元国际工程有限公司 冷却水再利用系统

Also Published As

Publication number Publication date
SE463277B (sv) 1990-10-29
FR2630816B1 (fr) 1991-01-11
SE8903325D0 (sv) 1989-10-10
FR2630816A1 (fr) 1989-11-03

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