EP0325163A1 - Procédé de fonctionnement d'une installation frigorifique et installation frigorifique pour la mise en oeuvre du procédé - Google Patents

Procédé de fonctionnement d'une installation frigorifique et installation frigorifique pour la mise en oeuvre du procédé Download PDF

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Publication number
EP0325163A1
EP0325163A1 EP89100468A EP89100468A EP0325163A1 EP 0325163 A1 EP0325163 A1 EP 0325163A1 EP 89100468 A EP89100468 A EP 89100468A EP 89100468 A EP89100468 A EP 89100468A EP 0325163 A1 EP0325163 A1 EP 0325163A1
Authority
EP
European Patent Office
Prior art keywords
refrigerant
temperature
pressure
refrigeration system
expansion
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Withdrawn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
EP89100468A
Other languages
German (de)
English (en)
Inventor
Franz Gruber
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.)
Linde GmbH
Original Assignee
Linde 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 Linde GmbH filed Critical Linde GmbH
Publication of EP0325163A1 publication Critical patent/EP0325163A1/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Withdrawn legal-status Critical Current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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/027—Condenser control arrangements
    • 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
    • F25B2600/00—Control issues
    • F25B2600/19—Refrigerant outlet condenser temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B40/00—Subcoolers, desuperheaters or superheaters

Definitions

  • the invention relates to a method for operating a refrigeration system and a refrigeration system for carrying out the method with a refrigerant circuit in which a refrigerant compresses, liquefies, expands, evaporates and is then fed back to the compression.
  • Refrigeration systems are used where the temperature in a room has to be kept at a lower level than in the environment, e.g. for refrigeration units in supermarkets or for cold rooms in warehouses.
  • the gaseous refrigerant is compressed in a compressor and then condensed in a condenser.
  • outside air is used to remove the heat of condensation.
  • the pressure in the condenser is set so that the corresponding condensing temperature of the refrigerant is higher than the temperature of the air used for cooling.
  • the refrigerant In order to ensure a trouble-free refrigerant circuit, the refrigerant must be undercooled prior to expansion, ie it must be in a liquid state.
  • the throughput of a commonly used expansion valve is in fact not sufficient to maintain sufficient cooling capacity if part of the refrigerant is in vapor form before the expansion.
  • refrigeration systems In order to ensure that the refrigerant is always in a liquid state between liquefaction and expansion, refrigeration systems have previously been operated at relatively high pressures, which correspond, for example, to liquefaction temperatures of 20 to 27 ° C (when using R12, R22 or R502 as refrigerant). As a rule, the condensing temperature of the refrigerant is then higher than the temperatures of the rooms through which the refrigerant lines are laid.
  • the present invention has for its object to develop a method for operating a refrigeration system that works economically, in particular by saving work in compression.
  • This object is achieved in that the temperature and pressure of the refrigerant are measured before the expansion and that, depending on this measurement, the pressure of the refrigerant before the expansion is adjusted by regulating the power during liquefaction so that the refrigerant is in a liquid state before expansion is present.
  • the condensing pressure can be reduced to surprisingly low values, corresponding to a condensing temperature of, for example, -10 ° C., without disturbances in the refrigerant circulation. With correspondingly low outside temperatures, very little energy is required for compression. If the pressure during the liquefaction is smoothly adapted to the outside temperatures, a refrigeration system operated according to the method of the invention works extremely economically.
  • the cooling capacity is the ratio of the cooling capacity Q0 to the drive power P supplied during compression. The smaller the difference between the temperatures during liquefaction and evaporation, the better the cooling capacity e k .
  • the sliding adjustment of the temperature during the liquefaction to the outside air temperature which is possible with the method according to the invention, also makes economic operation possible by the fact that the cooling capacity Q0 increases as the outside air temperature falls and at the same time the drive power P supplied decreases and the cooling capacity coefficient e k increases.
  • the refrigerant has a temperature before the expansion which is slightly below the condensing temperature.
  • the slight subcooling ensures that the refrigerant remains liquid before the expansion process and that the refrigerant circulation is not disturbed.
  • the invention also relates to a refrigeration system for carrying out the method according to the invention, which is characterized by a measuring device for pressure and temperature of the refrigerant attached to the pipe in front of the expansion device, a control device connected to it and a control line which connects the control device and the liquefaction device.
  • the refrigeration system shown in the figure contains a refrigeration unit, consisting of a compressor 6, an air-cooled condenser 7 and a refrigerant collector 10, and a cooling device, consisting of a heat exchanger 13, an expansion valve 14 and an evaporator 12.
  • the refrigeration unit is installed outdoors, while the cooling device in or on the cooled space, for example a refrigerator.
  • the refrigeration device and the cooling device are connected by a liquid line 3 and a suction line 4, which generally lead through heated rooms.
  • the two lines 3, 4 are insulated against condensation.
  • R22 or R502 is preferably used as the refrigerant.
  • the refrigerant in the liquid line 3 can heat up considerably.
  • the refrigerant in the evaporator 12 also has a relatively high temperature. Therefore, the performance of the heat exchanger 13 is not sufficient to ensure subcooling of the refrigerant upstream of the expansion valve 14. The refrigerant thus boils upstream of the expansion valve 14.
  • the pressure in the condenser can be set to a condensing temperature t c of approximately 2K.
  • the condensed refrigerant for example, has a temperature of 0 ° C and is thus subcooled by 2K. In continuous operation, this subcooling and the cooling in the heat exchanger 13 are generally sufficient to keep the liquid free of bubbles up to the expansion valve 14. However, during an interruption in operation or when starting up for the first time, the refrigerant can heat up well above the condensing temperature t c , in extreme cases up to room temperature.
  • the throughput of the expansion valve 14 is then, however, much too small to supply the evaporator with sufficient refrigerant in the event of a larger vapor content.
  • the pressure in the evaporator drops and the compressor 6 is switched off by the usual suction pressure control (not shown in the figure) and the refrigeration is thereby interrupted.
  • the pressure in the liquid line 4 drops further, so that the condensing temperature t c .
  • the compressor 6 is switched on and off again and again until finally a steady state is reached after a long time.
  • the refrigeration system outlined in the figure has sensors 18 for the temperature and pressure of the refrigerant upstream of the expansion valve 14 and a control device 16, which is connected to the condenser 7 via a control line 17.
  • the supercooling of the refrigerant is maintained by these devices: as soon as the temperature of the refrigerant exceeds a certain limit value t 1 below the condensing temperature t c of the refrigerant at the measured pressure, the control device 16 throttles the performance during the liquefaction 7. This increases the pressure in the liquid line 3. As soon as the pressure in front of the expansion valve 14 has risen to such an extent that the condensing temperature t c of the refrigerant has reached a further limit value t 2, the performance during the condensing 7 is increased again.
  • t c depends on the vapor pressure curve on the pressure of the refrigerant, which is measured together with the temperature of the refrigerant.
EP89100468A 1988-01-21 1989-01-12 Procédé de fonctionnement d'une installation frigorifique et installation frigorifique pour la mise en oeuvre du procédé Withdrawn EP0325163A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19883801711 DE3801711A1 (de) 1988-01-21 1988-01-21 Verfahren zum betreiben einer kaelteanlage und kaelteanlage zur durchfuehrung des verfahrens
DE3801711 1988-01-21

Publications (1)

Publication Number Publication Date
EP0325163A1 true EP0325163A1 (fr) 1989-07-26

Family

ID=6345730

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89100468A Withdrawn EP0325163A1 (fr) 1988-01-21 1989-01-12 Procédé de fonctionnement d'une installation frigorifique et installation frigorifique pour la mise en oeuvre du procédé

Country Status (2)

Country Link
EP (1) EP0325163A1 (fr)
DE (1) DE3801711A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL1000899C2 (en) * 1994-12-09 1996-08-28 Kempen Koudetechniek B V Van Cooling system e.g. for refrigerated storage - uses under-cooled refrigerant whose pressure is held constant by regulating pump and valves irrespective of ambient temperature and pressure
EP0762064A1 (fr) * 1995-09-08 1997-03-12 Fritz Ing. Weider Réglage d'écoulement du réfrigérant d'une pompe à chaleur et procédé
FR2748799A1 (fr) * 1996-05-17 1997-11-21 Mc International Procede de regulation d'un condenseur d'installation frigorifique pour economiser l'energie
EP0866291A1 (fr) * 1997-03-18 1998-09-23 Andreas Bangheri Pompe de chaleur à compression ou machine de refroidissement à compression et sa méthode de régulation
WO2005073645A1 (fr) * 2004-01-28 2005-08-11 Bms-Energietechnik Ag Evaporation a haut rendement dans des dispositifs frigorifiques et procede correspondant d'obtention de conditions stables avec des differences de temperature minimales et/ou requises des produits a refroidir par rapport a la temperature d'evaporation
US9759468B2 (en) 2014-03-21 2017-09-12 Lennox Industries Inc. System for controlling operation of an HVAC system having tandem compressors

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3293876A (en) * 1964-10-28 1966-12-27 Carrier Corp Refrigeration system including control arrangement for maintaining head pressure
DE1912613A1 (de) * 1969-03-12 1970-09-24 Sueddeutsche Kuehler Behr Vorrichtung zur selbsttaetigen Regelung von Geblaesen zur zwanglaeufigen Belueftung von Waermetauschern
DE2451361A1 (de) * 1974-10-29 1976-05-06 Jakob Verfahren zum regeln einer kompressorkuehlanlage
US3958429A (en) * 1975-01-17 1976-05-25 Dravo Corporation Air-cooled condenser pressure control at low ambient temperatures
US4136528A (en) * 1977-01-13 1979-01-30 Mcquay-Perfex Inc. Refrigeration system subcooling control
US4193781A (en) * 1978-04-28 1980-03-18 Mcquay-Perfex Inc. Head pressure control for heat reclaim refrigeration systems
US4434625A (en) * 1983-04-20 1984-03-06 Control Data Corporation Computer cooling system
GB2150273A (en) * 1983-10-03 1985-06-26 Emhart Ind Refrigeration systems
US4660387A (en) * 1985-01-22 1987-04-28 Diesel Kiki Co., Ltd. Controls for refrigerating or air-conditioning units

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3147700A1 (de) * 1981-12-02 1983-06-09 Buderus Ag, 6330 Wetzlar Verfahren und vorrichtung zur regelung der antriebsleistung von waermepumpen
DE3220420A1 (de) * 1982-05-29 1983-12-15 Vereinigte Elektrizitätswerke Westfalen AG, 4600 Dortmund Verfahren zur regelung eines elektrisch ansteuerbaren expansionsventils

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3293876A (en) * 1964-10-28 1966-12-27 Carrier Corp Refrigeration system including control arrangement for maintaining head pressure
DE1912613A1 (de) * 1969-03-12 1970-09-24 Sueddeutsche Kuehler Behr Vorrichtung zur selbsttaetigen Regelung von Geblaesen zur zwanglaeufigen Belueftung von Waermetauschern
DE2451361A1 (de) * 1974-10-29 1976-05-06 Jakob Verfahren zum regeln einer kompressorkuehlanlage
US3958429A (en) * 1975-01-17 1976-05-25 Dravo Corporation Air-cooled condenser pressure control at low ambient temperatures
US4136528A (en) * 1977-01-13 1979-01-30 Mcquay-Perfex Inc. Refrigeration system subcooling control
US4193781A (en) * 1978-04-28 1980-03-18 Mcquay-Perfex Inc. Head pressure control for heat reclaim refrigeration systems
US4434625A (en) * 1983-04-20 1984-03-06 Control Data Corporation Computer cooling system
GB2150273A (en) * 1983-10-03 1985-06-26 Emhart Ind Refrigeration systems
US4660387A (en) * 1985-01-22 1987-04-28 Diesel Kiki Co., Ltd. Controls for refrigerating or air-conditioning units

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL1000899C2 (en) * 1994-12-09 1996-08-28 Kempen Koudetechniek B V Van Cooling system e.g. for refrigerated storage - uses under-cooled refrigerant whose pressure is held constant by regulating pump and valves irrespective of ambient temperature and pressure
EP0762064A1 (fr) * 1995-09-08 1997-03-12 Fritz Ing. Weider Réglage d'écoulement du réfrigérant d'une pompe à chaleur et procédé
FR2748799A1 (fr) * 1996-05-17 1997-11-21 Mc International Procede de regulation d'un condenseur d'installation frigorifique pour economiser l'energie
EP0866291A1 (fr) * 1997-03-18 1998-09-23 Andreas Bangheri Pompe de chaleur à compression ou machine de refroidissement à compression et sa méthode de régulation
WO2005073645A1 (fr) * 2004-01-28 2005-08-11 Bms-Energietechnik Ag Evaporation a haut rendement dans des dispositifs frigorifiques et procede correspondant d'obtention de conditions stables avec des differences de temperature minimales et/ou requises des produits a refroidir par rapport a la temperature d'evaporation
EP2063201A2 (fr) * 2004-01-28 2009-05-27 BMS-Energietechnik AG Procédé de fonctionnement d'un système frigorifique
EP2063201A3 (fr) * 2004-01-28 2009-10-14 BMS-Energietechnik AG Procédé de fonctionnement d'un système frigorifique
US9010136B2 (en) 2004-01-28 2015-04-21 Bms-Energietechnik Ag Method of obtaining stable conditions for the evaporation temperature of a media to be cooled through evaporation in a refrigerating installation
US9759468B2 (en) 2014-03-21 2017-09-12 Lennox Industries Inc. System for controlling operation of an HVAC system having tandem compressors

Also Published As

Publication number Publication date
DE3801711A1 (de) 1989-07-27

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