EP1821050A2 - Kombiniertes Kühl- und Klimatisierungssystem - Google Patents

Kombiniertes Kühl- und Klimatisierungssystem Download PDF

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Publication number
EP1821050A2
EP1821050A2 EP07380048A EP07380048A EP1821050A2 EP 1821050 A2 EP1821050 A2 EP 1821050A2 EP 07380048 A EP07380048 A EP 07380048A EP 07380048 A EP07380048 A EP 07380048A EP 1821050 A2 EP1821050 A2 EP 1821050A2
Authority
EP
European Patent Office
Prior art keywords
exchanger
refrigerant
series
air conditioning
expansion valve
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Withdrawn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
EP07380048A
Other languages
English (en)
French (fr)
Other versions
EP1821050A3 (de
Inventor
Ramón Fernando Puente Varela
José Luis Fernandez Pazos
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.)
Aproalia SL
Original Assignee
Aproalia SL
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 Aproalia SL filed Critical Aproalia SL
Publication of EP1821050A2 publication Critical patent/EP1821050A2/de
Publication of EP1821050A3 publication Critical patent/EP1821050A3/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Withdrawn legal-status Critical Current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
    • F25B41/00—Fluid-circulation 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/24—Arrangement of shut-off valves for disconnecting a part of the refrigerant cycle, e.g. an outdoor part
    • 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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • 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
    • F25B2400/06—Several compression cycles 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—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
    • F25B2400/16—Receivers
    • 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
    • F25B2400/19—Pumping down refrigerant from one part of the cycle to another part of the cycle, e.g. when the cycle is changed from cooling to heating, or before a defrost cycle is started

Definitions

  • the present invention relates to a combined refrigeration and air conditioning system which allows improving the efficiency of cold energy conversion in installations requiring air conditioning, either providing cold or heat, and the refrigeration of chambers, displays or any other object or medium at least temporarily.
  • the system can particularly be used in a refrigerator installation of premises that are also provided with a comfort air conditioning system such as for example a refrigeration unit with one or more displays of goods in a store with an air conditioning system.
  • a comfort air conditioning system such as for example a refrigeration unit with one or more displays of goods in a store with an air conditioning system.
  • the invention belongs to the sector of the art of air conditioning and refrigeration.
  • the premises in which perishable products are stored or sold to the public always have two thermal systems, independent from one another, working in an independent and isolated manner.
  • the industrial cold installation most frequently comprises a conventional mechanical compression refrigeration system, and the air conditioning systems of the premises are provided with air-air heat pumps.
  • a basic mechanical compression and refrigeration cycle by direct expansion consists of four elements or steps: compressor, condenser, expansion valve and evaporator.
  • the refrigerant evaporates and absorbs heat from the space that it is cooling and from its content.
  • the refrigerant vapor then passes to a compressor increasing its pressure, which increases its temperature.
  • This high pressure overheated gas is subsequently transformed into a liquid in a condenser that is refrigerated by air or water.
  • the liquid passes through an expansion valve, where its pressure and temperature are reduced until reaching the conditions existing in the evaporator inlet, the cycle being closed.
  • the present invention relates to a complete and unique refrigeration and air conditioning system currently comprising two independent subsystems, which are the industrial cold system and the air conditioning system for the premises (the latter can heat or cool according to the comfort needs).
  • This system offers energy saving as the condensation phases of the compressors and the complete compression systems of cold and air conditioning installations are optimized. This saving occurs in heating the premises in winter and in taking advantage of the efficiency of higher capacity equipment in summer.
  • the process allows improving the safety and reliability of the main power systems and compressors of the main system because, by the grouping thereof, backups are obtained when any of them fails.
  • the air conditioning systems will mainly back industrial cold systems, given that their operation is the top priority so that refrigerated or frozen products do not spoil.
  • the present invention therefore relates to the combination of industrial cold and air conditioning systems in a single system.
  • the residual energy of one of them generally the industrial cold system, is used to carry out the air conditioning of the premises by means of the heat pump formed.
  • the proposed system is formed by a traditional refrigeration system, which could be completed with an additional subsystem such as controlled electronic injection or liquid pump for greater energy saving.
  • this hot spot will correspond to the premises during the period in which it must be heated (denominated winter herein, regardless of the season in which it occurs and of its duration) through the air conditioning system.
  • the heat generated by all or part of the condensers of the industrial cold installation, which was previously degraded, is taken advantage of in the air conditioning of the premises.
  • this heat source will be accompanied by other sources such as electric resistances, hot water, steam, solar energy or another energy source.
  • the main cold power system will be used for the two subsystems as a traditional installation, but taking advantage of the combination of the two systems to seek a higher efficiency, using higher capacity equipment.
  • the negative cold subsystem cools up to a temperature that is lower than that of positive cold; between -10°C and -35°C for example.
  • the negative cold subsystem can be used to preserve frozen products
  • the positive cold subsystem can be used for refrigerated products (butter, fish, meat, etc.)
  • Both subsystems may share elements, but they are generally provided independently for safety reasons due to possible leakages.
  • the system of the invention comprises two compressors, or two pluralities of compressors in series or in parallel, denominated first and second compressor, the outlet of compressed refrigerant of which is at a common point.
  • the flow of refrigerant from this common point to the inlet of the compressors will vary according to the operation mode such that:
  • a first heat exchanger In the summer operation mode, a first heat exchanger carries out refrigerant condensation functions after the common point, and will pour the condensed refrigerant in two parallel branches, each of which comprises an expansion valve, either of the electronic, mechanic or constant overheating type or of any other type, and a heat exchanger acting as an evaporator.
  • the refrigerant traverses a first expansion valve and a second heat exchanger, which will remove heat from the medium which is to be cooled by means of the industrial cold system.
  • the refrigerant will traverse a second expansion valve and a third heat exchanger which exchanges heat with the premises or installation which is to be cooled, in this case by cooling it.
  • the second and third exchanger After the second and third exchanger, it returns to the suction inlets of the compressors, which inlets can be connected so that one compressor backs the other in the event of failure.
  • the refrigerant will follow a first branch from the common point reaching the third heat exchanger, which in this case will condense the refrigerant and will provide the extracted heat to the premises or installation to be conditioned and at the outlet of which the first expansion valve and the second exchanger are arranged, which second exchanger continues working as an evaporator and removing heat from the medium object of the industrial cold.
  • a second branch starting at the common point and following the first heat exchanger, which will condense the refrigerant, can be created. From this point and through a section which can optionally comprise a liquid pump or a tank, the refrigerant enters the first expansion valve. The negative calories of the industrial cold system can thus be increased without affecting the air conditioning system.
  • the refrigerant can be drawn from outlet of the third exchanger to a third expansion valve followed by a fourth exchanger evaporating the refrigerant, removing heat from an element outside both air conditioning and industrial cold systems.
  • the refrigerant will finally return to a compressor, for example the second compressor.
  • Two series of valves the opening and closing of which defines the operation mode of the system (summer or winter), can be advantageously arranged to change from one operation mode to another.
  • These valves can be manually actuated by servomotors controlled by an automaton, or by any other means.
  • Another variant is to use the fourth exchanger, which according to the described operation only acts in winter, as a condenser in summer. To that end, the third expansion valve must be bridged.
  • the system is self-regulated by the temperatures detected in each of the objects, premises and installations which are to be cooled or air conditioned, such as for example perishable product displays, refrigeration chambers and sale rooms.
  • a back up system can be provided for the air conditioning system in winter periods by means of electric resistances, batteries for hot water, boilers or other means, in which periods it is necessary to heat the building even more to carry out sales in the center either due to extremely low temperatures or due to a failure of the compression system.
  • Refrigerant flow control equipment will be installed to carry out power changes in either direction, either refrigeration or air conditioning. This equipment will be formed by:
  • Any type of equipment required by a refrigeration installation such- as safety valves against overpressure, manometers, bleed valves, refrigerant tanks, etc. will also be installed.
  • the combined refrigeration and air conditioning system consists of an air conditioning system which can refrigerate or heat the environmental air of a premises, and an industrial cold system, which can in turn be divided into an independent positive cold subsystem and a negative cold subsystem or with common elements.
  • the air conditioning system recovers part of the energy which the industrial cold system was previously going to waste, operating in two different modes.
  • the operation must be separated into two modes, one will be denominated summer, in which the air conditioning must cool the environment, and the other will be denominated winter, in which the air conditioning must heat the premises.
  • the industrial cold system will comprise a first compressor (10), a first heat exchanger (11) acting as a condenser, a first expansion valve (12) and a second heat exchanger (13) acting as an evaporator.
  • the air conditioning system will comprise a second compressor (20), a second expansion valve (22) and two heat exchangers, one of them evaporating and the other one condensing.
  • Each of the mentioned equipment can actually correspond to a plurality of equipment placed in series or in parallel.
  • the summer operation mode is less complex, given that the refrigerant is common for both systems (where appropriate, between one or both positive or negative cold subsystems, generally the former and the air conditioning system). Both systems are further placed in parallel, such that the refrigerant traverses the first exchanger (11). It is convenient to place at least two exchangers in parallel to better adjust the power and if necessary, to be able to disconnect one of the two exchangers in order to carry out the maintenance, to repair the other exchanger, or even when the one of the two exchangers has the sufficient capacity, to condense all the refrigerant by itself.
  • the flow lines are separated in two branches, a first flow line traversing the first expansion valve (12) and the second exchanger (13) acting as an evaporator in the industrial cold system, before returning to the first compressor (10), whereas the second flow line traverses the second expansion valve (22) and a third exchanger (23) (acting as an evaporator of the air conditioning system, and cooling the premises) and returns to the second compressor (20).
  • valves are opened and closed so that the schematic arrangement changes to that corresponding to Figure 2.
  • FIG. 2 shows both compressors (10, 20) arranged in a manner similar to the previous one, but with an important variation in the arrangement of the exchangers (11,13,23).
  • a first branch (1) takes the compressed refrigerant to the third exchanger (23) or air conditioning battery, acting as a condenser instead of an evaporator, providing heat to the premises instead of cooling it.
  • This heating method can be supplemented by other heat sources such as electric resistances, hot water, steam, solar energy or any other energy source.
  • the fluid traverses the first expansion valve (12) and the second exchanger (13), which continue to carry out the same functions as in the summer mode, to return to the first compressor (10).
  • both a condenser and an evaporator are heat exchangers and can operate in either manner according to the temperature of the fluids exchanging heat, it being possible for one fluid to condense while the other fluid evaporates.
  • the flow is divided from the common point located at the outlet of both compressors (10, 20), the refrigerant being able to go through two different branches (1, 2) instead of only one.
  • the second branch (2) takes part of the refrigerant to the first exchanger (11), which continues to carry out the condensation. From this point, the condensed refrigerant reaches the first expansion valve (12), where it is pooled with the rest of the refrigerant. In this manner, some of the refrigerant which has not condensed in the air conditioning system evaporates in the industrial cold system, in a manner similar to the summer mode. To that end, the lower section (3) must be traversed in the example shown in the figures.
  • the refrigerant flow through this second branch (2) can be taken to a point such that no condensation is carried out in the third exchanger (23) when the temperature of the premises is suitable for sales and does not require air conditioning (mode between seasons).
  • the refrigerant flow passing through the third exchanger (23) is increased and the refrigerant is divided, part of the refrigerant reaching the first expansion valve (12) and the second exchanger (13), whereas the rest of the refrigerant reaches a third expansion valve (32) and a fourth exchanger (33) through the lower section (3), which exchanger evaporates the refrigerant, using the negative calories for something other than the industrial cold system (or discarding them).
  • the following variant uses the fourth exchanger better: changing the operation of the fourth exchanger (33), making it condense the refrigerant in parallel with the first exchanger (11) in the summer operation.
  • a small change must be made in the connections of the elements of the invention which are considered to be evident for a person skilled in the art (placing a bypass of the third expansion valve (32) which may or may not be activated and the circuits and valves necessary to reorient the flow).
  • the tank (40) in which the refrigerant passing through the combined refrigeration system and the aforementioned liquid pump (41) is stored can optionally be placed in this lower section (3).
  • Figure 3 shows an installation scheme according to the invention showing, in a simplified manner, all the elements of the invention, and two series of preferably automatic valves (50, 51) which allow selecting the operation mode.
  • the summer operation occurs when the first series of valves (50) is closed and the second series of valves (51) is opened.
  • the winter operation occurs if the first series of valves (50) is opened and the second series of valves (51) is closed.
  • a connection can be installed between the suction inlets of the compressors (10, 20) so that one can back the other in the event of a hypothetic failure of one of the two systems.
  • the cycle condensation means may comprise one or more condensers cooled by air, water, evaporative condensers or condensers of any other type, outside the premises with an axial type fan or inside the premises with a centrifugal type fan, or any other equipment compatible with the precise energy source for condensation, designed to a great extent for positive cold and air conditioning systems in one of them and negative cold systems for the other.
  • This equipment is standard equipment which is normally installed in these installations.
  • each of the elements of the system can be substituted by a plurality of elements of the same type placed in series or in parallel.
  • This process can be carried out with any known refrigerant, refrigerants R404a, R507 or R134a for example.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Other Air-Conditioning Systems (AREA)
EP07380048A 2006-02-21 2007-02-21 Kombiniertes Kühl- und Klimatisierungssystem Withdrawn EP1821050A3 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
ES200600412A ES2318941B1 (es) 2006-02-21 2006-02-21 Sistema combinado de refrigeracion y climatizacion.

Publications (2)

Publication Number Publication Date
EP1821050A2 true EP1821050A2 (de) 2007-08-22
EP1821050A3 EP1821050A3 (de) 2009-12-23

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EP07380048A Withdrawn EP1821050A3 (de) 2006-02-21 2007-02-21 Kombiniertes Kühl- und Klimatisierungssystem

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EP (1) EP1821050A3 (de)
ES (1) ES2318941B1 (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL2003228C2 (nl) * 2009-07-17 2011-01-18 Erney Errol Pinas Werkwijze voor het koppelen van een primair warmtepompsysteem bestemd voor het verwarmen van een gebouw en/of voor het verwarmen van tapwater aan een of meerdere secundaire warmtepompsystemen bestemd voor het verlagen van de temperatuur in een afgesloten ruimte en inrichting voor het uitvoeren van de werkwijze.
WO2018074370A1 (ja) * 2016-10-19 2018-04-26 パナソニックＩｐマネジメント株式会社 冷凍システムおよび室内ユニット

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2241317A (en) * 1990-02-14 1991-08-28 Toshiba Kk Air conditioning apparatus; defrosting a heat exchanger
GB2248494A (en) * 1990-08-10 1992-04-08 Hitachi Ltd Multi-airconditioner
EP0668474A2 (de) * 1994-02-18 1995-08-23 Sanyo Electric Co. Ltd Klimaanlage für mehrere Räume und Steuerverfahren hierfür
US20040112082A1 (en) * 2002-01-24 2004-06-17 Kenji Tanimoto Regfrigerating device
EP1498668A1 (de) * 2002-03-29 2005-01-19 Daikin Industries, Ltd. Wärmequelleneinheit von klimaanlage und klimaanlage

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4157649A (en) * 1978-03-24 1979-06-12 Carrier Corporation Multiple compressor heat pump with coordinated defrost
US4394816A (en) * 1981-11-02 1983-07-26 Carrier Corporation Heat pump system
GB9426207D0 (en) * 1994-12-23 1995-02-22 British Tech Group Usa Vapour compression system
US20060010907A1 (en) * 2004-07-15 2006-01-19 Taras Michael F Refrigerant system with tandem compressors and reheat function
US7272948B2 (en) * 2004-09-16 2007-09-25 Carrier Corporation Heat pump with reheat and economizer functions

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2241317A (en) * 1990-02-14 1991-08-28 Toshiba Kk Air conditioning apparatus; defrosting a heat exchanger
GB2248494A (en) * 1990-08-10 1992-04-08 Hitachi Ltd Multi-airconditioner
EP0668474A2 (de) * 1994-02-18 1995-08-23 Sanyo Electric Co. Ltd Klimaanlage für mehrere Räume und Steuerverfahren hierfür
US20040112082A1 (en) * 2002-01-24 2004-06-17 Kenji Tanimoto Regfrigerating device
EP1498668A1 (de) * 2002-03-29 2005-01-19 Daikin Industries, Ltd. Wärmequelleneinheit von klimaanlage und klimaanlage

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL2003228C2 (nl) * 2009-07-17 2011-01-18 Erney Errol Pinas Werkwijze voor het koppelen van een primair warmtepompsysteem bestemd voor het verwarmen van een gebouw en/of voor het verwarmen van tapwater aan een of meerdere secundaire warmtepompsystemen bestemd voor het verlagen van de temperatuur in een afgesloten ruimte en inrichting voor het uitvoeren van de werkwijze.
WO2011008089A1 (en) 2009-07-17 2011-01-20 Erney Errol Pinas Method for coupling of a primary heat pump system intended for heating a building and/or heating of tap water to one or more secondary heat pump systems intended for lower the temperature in an enclosed space and device for carrying out the method
WO2018074370A1 (ja) * 2016-10-19 2018-04-26 パナソニックＩｐマネジメント株式会社 冷凍システムおよび室内ユニット

Also Published As

Publication number Publication date
ES2318941A1 (es) 2009-05-01
ES2318941B1 (es) 2010-01-21
EP1821050A3 (de) 2009-12-23

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