EP0148062A2 - Kälte und Wärme erzeugende Kühlanlage - Google Patents

Kälte und Wärme erzeugende Kühlanlage Download PDF

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Publication number
EP0148062A2
EP0148062A2 EP84402522A EP84402522A EP0148062A2 EP 0148062 A2 EP0148062 A2 EP 0148062A2 EP 84402522 A EP84402522 A EP 84402522A EP 84402522 A EP84402522 A EP 84402522A EP 0148062 A2 EP0148062 A2 EP 0148062A2
Authority
EP
European Patent Office
Prior art keywords
cold
condensers
heat
heated
refrigerated
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Withdrawn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
EP84402522A
Other languages
English (en)
French (fr)
Other versions
EP0148062A3 (de
Inventor
Adrien Laude-Bousquet
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.)
Bonnet SA
Original Assignee
Bonnet 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 Bonnet SA filed Critical Bonnet SA
Publication of EP0148062A2 publication Critical patent/EP0148062A2/de
Publication of EP0148062A3 publication Critical patent/EP0148062A3/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Withdrawn legal-status Critical Current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
    • 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
    • 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
    • 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
    • F25B6/02—Compression machines, plants or systems, with several condenser circuits 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
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—Component parts or details not otherwise provided for in this subclass
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/075—Details of compressors or related parts with parallel compressors

Definitions

  • the present invention relates to a refrigeration installation producing cold and heat.
  • a refrigeration plant producing cold and heat works to give in summer for example cold to the products and the premises to be refrigerated, and in winter for example cold and hot simultaneously to maintain in respective temperatures the products and the rooms to be refrigerated and products and premises to be heated.
  • the present invention aiming to minimize these drawbacks, makes it possible to produce an economic refrigeration installation which, having a given power of compressor units determined to satisfy the maximum predetermined needs in cold, can compared to a known installation provided with the same power of compressors better meet the maximum simultaneous needs in cold and in heat.
  • the installation operates constantly at its optimum power.
  • a refrigeration installation producing cold and heat, respectively for cold stations, rooms to be refrigerated and heated having one or more motor-compressors in parallel, condensers in parallel, evaporators in parallel and a tank for liquid refrigerant, is characterized in that, to better meet the demand for cold and hot demand, it transports heat from the cold stations and / or rooms to be refrigerated, and transfers it to the external atmosphere during '' a request for cold alone, and it recovers heat from both the cold stations and / or rooms to be refrigerated, and from the outside atmosphere, and transports it to the rooms to be heated, during a simultaneous demand for cold and heat respectively for these cold stations and rooms to be refrigerated and heated.
  • a known refrigeration installation 1 schematically illustrated in FIG. 1, for producing both cold in furniture or cold stations 2 and / or rooms to be refrigerated 3, and heat in rooms to be heated 4, usually comprises one or more several motor-compressors in parallel 5, one or more evaporators in parallel 6, two or more condensers 7, 8 in parallel of which at least one 8 is mounted, exposed to the external atmosphere and the other 7 or others are installed at the inside the premises to be heated 4, two valves 9 and 10 arranged upstream of these condensers 7, 8 for direct the refrigerant vapor, compressed by the motor compressors 5, either to the condensers 8 exposed to the outside atmosphere or to the condensers 7 arranged in the premises to be heated, two non-return valves 11, 12 mounted downstream of these condensers 7 , 8 to prevent the return of the liquid refrigerant, and possibly a refrigerant tank 13.
  • the coolant coming from the reservoir 13 passes through a regulator (not shown) and expands in the evaporator (s) 6 to produce cold in the cold stations 2 or the premises to be refrigerated 3.
  • the motor-compressors 5 draw the vapor of expanded refrigerant in the evaporators 6, compress it and discharge it either through the valve 9 in the condensers 8 exposed to the external atmosphere, during the summer period or period when no space heating is required. 'is requested, the valve 10 being closed, or through the valve 10 in the condensers 7 arranged in the premises to be heated 4 when heating is required, the valve 9 being closed.
  • the installation 5 When the power of the compressors 5 is determined to satisfy the predetermined maximum heat requirements in the rooms to be heated 4, it turns out that when no heating needs are requested in the rooms 4, for example during the summer period, the installation 5 only operates with a small fraction of their power to correctly meet the maximum cooling needs alone in the cold stations 2 and / or rooms to be refrigerated 3.
  • the refrigeration installation 14 in order to better meet the demanded requirements for cold and heating with a given power of compressors determined to satisfy the maximum predetermined cooling requirements, the refrigeration installation 14, during a cold request alone for its cooling stations. cold where products to be cooled and / or for its premises to be refrigerated are stored, transports the heat there and transfers it to the outside atmosphere and during a maximum simultaneous cold request for its cold stations and / or rooms to be refrigerated and hot for its premises to be heated recovers heat found both in these cold and / or local stations to be refrigerated and in the outside atmosphere, and transports it to these rooms to be heated.
  • the refrigeration system -4 can thus better meet both the maximum predefined needs - cold in its cold rooms and / or rooms to be refrigerated - and the maximum predetermined needs for hot in its rooms to be heated, thanks to recovery of heat in the outer atrosphere which makes it possible to supplement that in its stations this cold and / or rooms to be refrigerated.
  • the installation 14, for producing cold in mables or cold stations 15 and / or rooms to be refrigerated 16 and hot in rooms to be heated 17, comprises in its refrigeration circuit a or several motor compressors 18 in parallel, one or more evaporators 19 in parallel, two or more condensers 20E 21, 22 in parallel of which at least one 20 is mounted, exposed to the external atmosphere 36, and the other 21 or others, 22 are installed inside the premises to be heated 17, two solenoid valves 23, 24 dispersed on the outlet of the common delivery manifold 32 of the motor compressors 18 and upstream of these condensers to direct the refrigerant vapor compressed by the motor compressors, either to the condenser or group of condensers 20 exposed to the external atmosphere 36 either towards the conden sor or group of condensers 21, 22 installed in the premises to be heated 17, two non-return valves 25, 26 mounted downstream of the condenser or group of condensers 20 exposed to the external atmosphere 36, and of the condenser or group
  • the refrigeration installation 14 comprises a solenoid valve 30 and a detector-regulator of known type mounted in series which connect the outlet 29 of the liquid refrigerant tank 27 and the outlet 37 of the condenser or group of condensers 20 exposed to the external atmosphere 36, upstream of the non-return valve 25.
  • the refrigeration installation 14 takes a downstream piloted solenoid valve 33 of known type which connects the inlet 34 of the condenser or group of condensers 20 exposed to the external atmosphere 36, to the common suction manifold 35 motor compressors 18.
  • the elec - n-ovannes 24, 30, 33 are closed, and the solenoid valve 23 is opened to let the refrigerant vapor compressed by the motor compressors 18 pass into the condenser or group of condensers 20, exposed to the external atmosphere 36, then through the non-return valve 25, into the liquid refrigerant tank coming from the tank 27, crosses the regulators not shown and expands in the evaporators 19 to produce cold in these cold stations 15 and / or premises to be refrigerated 16 in other words to recover heat there and transform into vapor.
  • the refractory manager vapor leaving these evaporators 19 is sucked through a common collector 35, by the motor compressors 18 which compress it and discharge it through the solenoid valve 23 into the condenser or group of condensers 20 exposed to the external atmosphere. 36.
  • the compressed refrigerant vapor gives up heat there before passing through the valve 25 and entering the reservoir 27 and starting a new operating cycle.
  • the refrigerant recovers heat in the cold stations 15 and / or rooms to be refrigerated 16, transports it into the condenser or group of condensers 20 exposed to the external atmosphere 36 and gives off heat.
  • the installation 14 thus responds efficiently and correctly to the cold requirements requested.
  • the solenoid valve 23 is closed and the solenoid valves 24, 30, 33 are open .
  • the refrigerant vapor compressed by the motor compressors 18 and discharged through the solenoid valve 24, in the condensers 21, 22 installed in the premises to be heated 17 yields heat therein to meet the maximum heat requirements required before passing through the non-return valve 26 in the liquid refrigerant tank 27.
  • the liquid refrigerant leaving the tank 27 is divided into two parts, one passes through the regulators not shown, expands in the evaporators 19 and recovers heat being in the cold stations 15 and / or rooms to be refrigerated 16, in other words produces cold there to meet the maximum demand for cold demand, the other passes through the solenoid valve 30 and the regulator regulator 31, expands in the condenser or group of condensers 20 exposed to the external atmosphere 36 which then operates in evaporators, and recovers heat being in the external atmosphere 36.
  • the refrigerant recovers heat both in the cold stations 15 and / or rooms to be refrigerated 16 and in the outside atmosphere 36, and transports it to the rooms to be heated 17.
  • the refrigeration installation 14 produced according to the invention can, thanks to additional heat recovery in the external atmosphere 36 respond correctly to the times the maximum demand for cold in the cold stations 15 and / or rooms to be refrigerated 16 and the maximum demand for hot in the rooms to be heated 17.
  • the downstream piloted solenoid valve 33 which closes at a pressure downstream, greater than a chosen or predetermined value of evaporation pressure of the refrigerant in the common suction manifold 35 of the motor-compressors 18, and opens at a downstream pressure, lower than this chosen or predetermined value of evaporation pressure of the refrigerant, allows, through good regulation of the evaporation pressure of the refrigerant at the inlet of the motor-compressors 18 to obtain an operation of the installation in a constant manner at its optimum power to correctly respond to the maximum cold and hot requirements.
  • the refrigeration installation 14 can be controlled by control systems of known types either fully automatically or semi-automatically.
  • the refrigeration installation 14 described above although it has a simple structure, proves to be efficient and excellently economical in the production of cold and heat, the frcid being intended to ensure the preservation of the products in the cold stations 15 and / or the temperature resistance of the premises to be refrigerated 16, and the hot contributing to ensuring the maintenance of temperatures of the premises to be heated 17 and of the products which are stored there.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
EP84402522A 1983-12-09 1984-12-06 Kälte und Wärme erzeugende Kühlanlage Withdrawn EP0148062A3 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8319768A FR2556456B1 (fr) 1983-12-09 1983-12-09 Installation frigorifique produisant du froid et du chaud
FR8319768 1983-12-09

Publications (2)

Publication Number Publication Date
EP0148062A2 true EP0148062A2 (de) 1985-07-10
EP0148062A3 EP0148062A3 (de) 1985-08-07

Family

ID=9295043

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84402522A Withdrawn EP0148062A3 (de) 1983-12-09 1984-12-06 Kälte und Wärme erzeugende Kühlanlage

Country Status (2)

Country Link
EP (1) EP0148062A3 (de)
FR (1) FR2556456B1 (de)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2422653A (en) * 2005-01-10 2006-08-02 Arctic Circle Ltd Refrigeration apparatus having a heating capability during cold weather
EP1921401A3 (de) * 2006-11-13 2009-12-16 "Arneg" Kühlmöbel und Ladeneinrichtungen Produktions- u. Handelsgesellschaft m.b.H. Verfahren zur Wärmerückgewinnung
ITBO20110022A1 (it) * 2011-01-24 2012-07-25 Rivacold S R L Impianto frigorifero multi-utenza
EP3002529A1 (de) * 2014-10-01 2016-04-06 Rivacold S.R.L. Kühlanlage für kühl- und klimaanlagen
EP3470748A1 (de) * 2017-05-12 2019-04-17 Artik-A Klimaanlage

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2162245A (en) * 1937-10-23 1939-06-13 Stator Corp Heating and cooling system
GB634574A (en) * 1945-10-25 1950-03-22 Harold Selby Craddock Improvements relating to refrigeration and heating apparatus
US2700279A (en) * 1952-06-12 1955-01-25 Gen Motors Corp Refrigerating apparatus and water heater
US2934913A (en) * 1958-01-17 1960-05-03 Gen Electric Combination kitchen appliances
DE2337746A1 (de) * 1973-07-25 1975-02-06 Peter Schmidt Einrichtung zur waermerueckgewinnung aus dem abwasser fuer ein hallenbad
DE2407047A1 (de) * 1974-02-14 1975-08-28 Hartmut Wick Waermepumpen-speichersystem
US4196595A (en) * 1976-01-29 1980-04-08 Dunham-Bush, Inc. Integrated thermal solar heat pump system
FR2339813A1 (fr) * 1976-01-29 1977-08-26 Paul Mayens Production calorifique par " pompes a chaleur "
IT1160889B (it) * 1978-10-26 1987-03-11 Berti Furic Impianto di essiccazione particolarmente per legname
FI60439C (fi) * 1979-04-05 1982-01-11 Asko Upo Oy Kompressor-vaermepumpsystem

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2422653A (en) * 2005-01-10 2006-08-02 Arctic Circle Ltd Refrigeration apparatus having a heating capability during cold weather
GB2422653B (en) * 2005-01-10 2011-03-02 Arctic Circle Ltd Refrigeration apparatus having a heating capability during cold weather
EP1921401A3 (de) * 2006-11-13 2009-12-16 "Arneg" Kühlmöbel und Ladeneinrichtungen Produktions- u. Handelsgesellschaft m.b.H. Verfahren zur Wärmerückgewinnung
ITBO20110022A1 (it) * 2011-01-24 2012-07-25 Rivacold S R L Impianto frigorifero multi-utenza
EP2479518A3 (de) * 2011-01-24 2012-12-05 Rivacold S.r.l. Gefrieranlage für mehrere Benutzer
EP3002529A1 (de) * 2014-10-01 2016-04-06 Rivacold S.R.L. Kühlanlage für kühl- und klimaanlagen
EP3470748A1 (de) * 2017-05-12 2019-04-17 Artik-A Klimaanlage

Also Published As

Publication number Publication date
FR2556456A1 (fr) 1985-06-14
FR2556456B1 (fr) 1986-05-16
EP0148062A3 (de) 1985-08-07

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Inventor name: LAUDE-BOUSQUET, ADRIEN