EP1734318B1 - Anlage und Verfahren für die Produktion von Kälte und für die Regelung der Lufttemperatur und Vorrichtung zum Wärmeaustausch für diese Anlage - Google Patents

Anlage und Verfahren für die Produktion von Kälte und für die Regelung der Lufttemperatur und Vorrichtung zum Wärmeaustausch für diese Anlage Download PDF

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Publication number
EP1734318B1
EP1734318B1 EP05425423A EP05425423A EP1734318B1 EP 1734318 B1 EP1734318 B1 EP 1734318B1 EP 05425423 A EP05425423 A EP 05425423A EP 05425423 A EP05425423 A EP 05425423A EP 1734318 B1 EP1734318 B1 EP 1734318B1
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EP
European Patent Office
Prior art keywords
thermal
unit
working fluid
installation
fluid
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Not-in-force
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EP05425423A
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English (en)
French (fr)
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EP1734318A1 (de
Inventor
Andrea Verondini
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Zanotti SpA
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Zanotti SpA
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Priority to DE602005014098T priority Critical patent/DE602005014098D1/de
Priority to AT05425423T priority patent/ATE429619T1/de
Priority to EP05425423A priority patent/EP1734318B1/de
Publication of EP1734318A1 publication Critical patent/EP1734318A1/de
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Publication of EP1734318B1 publication Critical patent/EP1734318B1/de
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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
    • 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
    • F25B39/00—Evaporators; Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0426—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with units having particular arrangement relative to the large body of fluid, e.g. with interleaved units or with adjacent heat exchange units in common air flow or with units extending at an angle to each other or with units arranged around a central element
    • F28D1/0435—Combination of units extending one behind the other
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/14—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally
    • F28F1/22—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally the means having portions engaging further tubular elements
    • 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
    • F25B2400/22—Refrigeration systems for supermarkets

Definitions

  • the present invention refers to a thermal installation for producing cold and adjusting air temperature of an environment, which has preferred, although not exclusive, use in environments where it is necessary to conserve deep frozen or frozen and/or fresh food.
  • the invention also refers to a thermal exchange device usable in the aforementioned thermal installation, and to a process for producing cold and for adjusting air temperature of an environment that can be carried out through such an installation.
  • the food can be fresh food, for example meat, fruit, vegetables, dairy products, soft drinks, desserts or gastronomic products etc., and dee ⁇ p-frozen or frozen food.
  • the conservation at a controlled temperature can, for example, be intended for the display and sale of food or for storage thereof.
  • a second requirement which is that of adjusting air temperature of the environment so as to make it comfortable for employees and customers or patrons to be in, both during the cold seasons and during the hot seasons.
  • suitable air-conditioning installations and/or heat pump installations are commonly used, that comprise one or more units suitable for adjusting air temperature through thermal exchange with a working fluid of such installations.
  • Such units can, for example, be "fan-coil" units or the like.
  • the possibility of setting up installations for producing cold and installations for adjusting air temperature can be restricted due to the low space available and/or due to building constraints. This can occur, for example, in the case of old buildings of historical town centres.
  • US patent N. 4,373,348 discloses a closed cycle refrigeration system, particularly for use in a store or a supermarket, constructed so as to improve operation efficiency and reduce power consumption.
  • a refrigeration system comprises a plurality of remotely located evaporators, associated, for example, with respective refrigerated display cases or cold rooms, a remote condenser and a heat recovery coil for extracting from the gaseous refrigerant heat that, during cold seasons, can be used for heating the building where the refrigeration system is located.
  • Patent Abstract of Japan vol. 1999, no. 02, 26 February 1999 (1999-02-26 ) - JP 10 300271 A discloses an outdoor heat exchanger for a heat pump type heating-cooling apparatus, which heat exchanger comprises an evaporator and a condenser provided at the lower edge part of the evaporator.
  • the evaporator end the condenser are embedded in a same fin assembly and are in thermal exchange relationship with each other so that the condenser can be used to heat the evaporator for preventing frost formation thereon.
  • the object of the present invention is to provide a thermal installation that allows the aforementioned requirements to be simultaneously met in an effective way and with the least possible number of components, so as to reduce the overall size and the extent of the interventions necessary to set up the installation.
  • the invention refers to a thermal installation having the features set forth in claim 1.
  • environment is used to generally indicate a limited portion of space and the term “outside” is used to generally indicate any space outside said environment, although possibly located indoors. More specifically, environment is used to indicate the commercial concern or the dining point where the installation is set up, irrespective of whether it comprises just one or many rooms.
  • the thermal installation of the invention advantageously allows the requirements of producing cold and of adjusting air temperature to be satisfied by sharing the closed circuit and many components, with a substantially reduced number of components with respect to those required by separate installations for producing cold and for adjusting air temperature.
  • both the overall size of the installation, and the interventions required for setting up the installation are reduced. This is particularly advantageous in the case of small environments and/or environments located in old buildings, where the possibility of carrying out structural interventions for setting up installations can be limited.
  • the use of a single installation for producing cold and for adjusting air temperature advantageously allows achieving a greater operating flexibility of the units intended to carry out such functions.
  • a thermal exchange device comprising a condensing portion and a selectively activatable evaporating portion at which the working fluid can at least partially absorb the heat released at the condensing portion allows the operation of the thermal installation to be improved, in particular during the cold seasons, when the at least one unit for adjusting air temperature is typically active to heat the environment.
  • the working fluid at the evaporating portion substantially absorbs the heat released at the condensing portion.
  • the at least one deep-frozen or frozen food conservation unit is a counter, cabinet or cold-storage room at a temperature between about -14°C and about -25°C.
  • a temperature is preferably between about -14°C and about -16°C in the case of conservation of frozen food, is preferably equal to or less than about - 18°C in the case of conservation of deep-frozen food and is preferably close to about -25°C in the case of conservation of industrial ice cream.
  • the at least one fresh food conservation unit is a counter, cabinet or cold-storage room at a temperature between about +10°C and about -1°C.
  • a temperature is preferably between about +8°C and about +6°C in the case of conservation of fruit and vegetables, is preferably between about +5°C and about +3°C in the case of conservation of dairy products and cold pork and salami and is preferably between about +2°C and about 0°C in the case of conservation of meat and poultry.
  • the aforementioned environment is a commercial concern at least partially intended for the sale of food or a dining point.
  • the at least one of the deep-frozen or frozen food conservation unit and the fresh food conservation unit directly operate with the working fluid flowing in the closed circuit, and is hydraulically connected with the closed circuit of the thermal installation at the respective thermal user point.
  • the production of cold at such units takes place by direct expansion of the working fluid, with advantages for the simplification of the installation and the efficiency of the aforementioned units.
  • the at least one deep-frozen or frozen food conservation unit and/or the at least one fresh food conservation unit to operate with a thermal carrier fluid, preferably an unfreezable thermal carrier fluid, distinct from the working fluid and in thermal exchange relationship with it.
  • a thermal carrier fluid preferably an unfreezable thermal carrier fluid
  • such units are connected with one or more secondary circuits hydraulically separate from the closed circuit of the thermal installation and in thermal exchange relationship with it at one or more thermal exchange elements in said thermal user points.
  • the unit for adjusting air temperature embodiments may be foreseen in which such a unit operates directly with the working fluid. However, it is preferred that this unit operates with its own thermal carrier fluid, for example water, distinct from the working fluid and in thermal exchange relationship with it.
  • the at least one unit for adjusting air temperature is therefore preferably connected with a secondary circuit hydraulically separate from the closed circuit of the thermal installation and in thermal exchange relationship with it at one or more thermal exchange elements in a thermal user point.
  • the thermal carrier fluid flowing in the unit for adjusting air temperature can advantageously be kept at a positive temperature even when the unit is active to cool the environment. This substantially avoids the formation, at the thermal exchange bank of such a unit, of frost that, being thermally insulating, would hinder the thermal exchange with the air of the environment. Moreover, a more comfortable climate is achieved, since the temperature difference of the air emitted by the unit with respect to the temperature of the environment can be better controlled, therefore reducing the risk of people suffering from thermal shocks.
  • the thermal installation of the invention comprises means for switching between an operating mode wherein the at least one unit for adjusting air temperature cools the environment and an operating mode wherein the at least one unit for adjusting air temperature heats the environment.
  • the thermal installation of the invention can therefore be used for adjusting air temperature both during hot seasons and during cold seasons, substantially without jeopardising the operation of the at least one deep-frozen or frozen food conservation unit and/or of the at least one fresh food conservation unit.
  • the means for switching comprise a reversing cycle valve and means for intercepting portions of the closed circuit.
  • the condensing portion per se has a substantially analogous function to that of a condenser in a conventional refrigerating installation and allows the heat absorbed by the working fluid at the at least one deep-frozen or frozen food conservation unit, and/or at the at least one fresh food conservation unit and at the at least one unit for adjusting air temperature, when it is active to cool the environment, to be released to the outside of said environment.
  • the evaporating portion per se has a substantially analogous function to that of an evaporator in a conventional heat pump installation and allows the working fluid to absorb heat from the outside of the environment and to release it at the at least one unit for adjusting air temperature, when it is active to heat such an environment.
  • the heat released by the condensing portion is at least partially and preferably substantially used to heat the evaporating portion. Thanks to such heating, the evaporating portion can exchange heat also at lower outside temperatures with respect to those at which a conventional heat pump installation could operate. Such temperatures have indeed a lower limit determined by the formation, at the evaporator, of frost, which, being thermally insulating, hinders the heat exchange.
  • the condensing portion comprises at least one first fluid path and the evaporating portion comprises at least one second fluid path and these fluid paths comprise a plurality of ducts embedded in a same assembly of fins.
  • the heat exchange between condensing portion and evaporating portion can therefore advantageously take place both by convection of a fluid, preferably air, externally flowing in contact with the ducts, and by conduction through the fins.
  • the fluid paths of the condensing and evaporating portions of the heat exchange device are preferably coil-shaped.
  • the aforementioned thermal exchange device preferably further comprises means for forcedly circulating said fluid externally of the fluid paths of the condensing and evaporating portions of the thermal exchange device. This allows the efficiency of the convective thermal exchange to be increased and a preferential flow direction of the fluid through the device to be ensured, so that it firstly flows in contact with the condensing portion, heating up, and then in contact with the evaporating portion.
  • the aforementioned means for the forced circulation are of conventional type and can comprise, for example, one or more fans, typically electrically actuated.
  • the evaporating portion of the thermal exchange device comprises a plurality of second fluid paths connected in parallel and selectively interceptable through a corresponding plurality of interception means.
  • the condensing portion also preferably comprises a plurality of first fluid paths connected in parallel. However, in the case of the condensing portion it is preferred not to use interception means to intercept such fluid paths.
  • the thermal exchange at the condensing portion is preferably controlled by changing the flow rate of the fluid externally flowing in contact with such a portion, for example through the means for the forced circulation described above.
  • the thermal installation of the invention comprises a plurality of compressors defining a compression section of the working fluid, wherein a first group of compressors of said plurality of compressors has a refrigerating capacity suitable for ensuring the operation of said at least one deep-frozen or frozen food conservation unit and a second group of compressors of said plurality of compressors has a refrigerating capacity suitable for ensuring the operation of said at least one fresh food conservation unit and of said at least one unit for adjusting air temperature.
  • the operation of the at least one deep-frozen or frozen food conservation unit is thus ensured by a group of compressors exclusively dedicated to such a unit. It can thus be controlled, and, possibly, excluded from the closed circuit of the thermal installation, without substantially influencing the performance of the at least one fresh food conservation unit and of the at least one unit for adjusting air temperature.
  • the operation of these units is ensured by the same group of compressors. This allows, in the case of failure of one of the compressors in the group, the operation of the at least one fresh food conservation unit to be ensured, at least to a limited extent, partially limiting or totally excluding the air temperature adjustment function.
  • the number of compressors present in the compression section and their allotment to the aforementioned two groups are preferably selected based on the number and type of units an on the type of environment for which the thermal installation is intended.
  • the thermal installation of the invention comprises expansion means for expanding the working fluid preferably selected from thermostatic valves and capillaries.
  • the thermal installation comprises means for the separation and recovery of a lubricating fluid, typically oil coming from the compressors, dispersed in said working fluid.
  • a lubricating fluid typically oil coming from the compressors, dispersed in said working fluid.
  • the working fluid is a refrigerating fluid selected from the group comprising hydro-fluoro-carbons (HFC), hydro-chloro-fluoro-carbons (HCFC), carbon dioxide, propane and ammonia.
  • HFC hydro-fluoro-carbons
  • HCFC hydro-chloro-fluoro-carbons
  • carbon dioxide propane and ammonia.
  • said refrigerating fluid is one of the hydro-fluoro-carbons (HFC) known under the ASHRAE denomination R-507A or R-404A.
  • HFC hydro-fluoro-carbons
  • the thermal installation of the invention comprises a microprocessor control unit adapted to control the operation of the thermal installation according to the required thermal conditions at the at least one unit for adjusting air temperature and the at least one of the deep-frozen or frozen food conservation unit and the fresh food conservation unit.
  • each of the component elements of the thermal installation of the invention has a plan overall size not greater than 80 cm by 120 cm.
  • Such size is that of standard pallets typically used for the transportation of foodstuffs. Therefore it is advantageously ensured that the installation in disassembled condition can be easily introduced in any environment adapted to the entry of such pallets without the need for special provisions.
  • the present invention refers to a heat exchange device having the features set forth in claim 19.
  • Such a heat exchange device allows specific advantages to be achieved when used in the thermal installation of the present invention, as described above, but it can also have advantageous uses in other types of installation, and generally in all cases where one wishes to lower the minimum temperature at which it is possible to operate a heat pump.
  • the present invention refers to a thermodynamic process comprising the stepsset forth in claim 20.
  • thermal installation 1 for producing cold and adjusting air temperature in accordance with the invention is globally indicated with reference numeral 1.
  • the thermal installation 1 essentially comprises a closed circuit 2 for circulating a working fluid, comprising: a compression section 3 of the working fluid, a thermal exchange device 4, at which the working fluid is in thermal exchange relationship with the outside E of an environment A, means 6 and 172 for expanding the working fluid and a plurality of thermal user points 5.
  • the working fluid is a refrigerating fluid, for example one of the hydro-fluoro-carbons (HFC) known under the ASHRAE denomination R-507A or R-404A.
  • HFC hydro-fluoro-carbons
  • the thermal installation 1 is preferably employed in an environment A where it is necessary to conserve fresh and/or deep frozen/frozen food, for example for sale purposes, in retail or wholesale, or for dining purposes.
  • Such applications comprise commercial concerns such as mini or supermarkets, food sellers and the like, and dining points such as canteens, restaurants, snack bars and the like.
  • the working fluid is at a temperature suitable for being placed in thermal exchange relationship with a deep-frozen or frozen food conservation unit 7, with a fresh food conservation unit 8, and with a unit 9 for adjusting air temperature of environment A or of one or more rooms thereof.
  • the units 7 and 8 can, for example, be refrigerated counter or cabinets or cold-storage rooms.
  • the unit 9 can be, for example, a "fan coil” type unit.
  • the deep-frozen or frozen food conservation unit 7 and the fresh food conservation unit 8 are preferably hydraulically connected with the closed circuit 2 and operate through direct expansion of the working fluid.
  • Such units 7, 8 are preferably arranged on separate lines of the closed circuit 2, so that a failure or a maintenance intervention on one line does not at the same time jeopardise the operation of both units 7, 8.
  • the unit 9 for adjusting air temperature is instead preferably connected with a secondary circuit 91 hydraulically separate from the closed circuit 2, wherein a thermal carrier fluid, for example water, distinct from the working fluid of the closed circuit 2, is circulated.
  • a thermal carrier fluid for example water
  • the working fluid and the thermal carrier fluid are placed in thermal exchange relationship at a heat exchanger 10, preferably a countercurrent heat exchanger, shared by the closed circuit 2 and the secondary circuit 91.
  • thermal user points 5 there are three thermal user points 5, but it is clear that their number can vary according to the specific requirements and, in particular, can be greater if there are more deep-frozen or frozen food conservation units 7 or more fresh food conservation units 8. As far as the adjustment of the air temperature is concerned, more units 9 can be provided, preferably connected with the same or with more secondary circuits 91, or else directly in respective thermal user points 5 of the closed circuit 2.
  • the working fluid at the respective thermal user point 5 shall begin expanding at a temperature of between about -32°C and about -38°C.
  • the temperature at the fresh food conservation unit 8 is typically between about +10°C and about -1°C - in particular, between about +8°C and about +6°C for fruit and vegetables, between about +5°C and about +3°C for dairy products and cold pork and salami and between about +2°C and about 0°C for meat and poultry -, the working fluid at the respective thermal user point 5 shall begin expanding at a temperature of between about -6°C and about -15°C.
  • the air temperature of the environment A shall be allowed to be adjusted typically between about 16°C (when the environment A is heated during the winter period) and about 25°C (when the environment A is cooled during the summer period) the working fluid at the heat exchanger 10 shall have a temperature of between about +4°C and about +2°C.
  • the compression section 3 comprises five compressors 11 allotted to two groups of compressors 11a and 11b, respectively comprising two and three compressors.
  • Such compressors can, for example, be of the hermetic, semi-hermetic or open type, and, in relation to the way in which the compression is carried out, can be of the piston, screw or scroll type, and they are in any case known to those skilled in the art.
  • the refrigerating capacities of the compressors 11 can be the same for all of the compressors or different for some or all of them.
  • the intake of the compressors 11 of the group of compressors 11a is connected with the line of the thermal user point 5 associated with the operation of the deep-frozen or frozen food conservation unit 7, while the intake of the compressors 11 of the group of compressors 11b is connected with the line of the thermal user point 5 associated with the operation of the fresh food conservation unit 8 and with the line of the thermal user point 5 associated with the operation of the unit 9 for adjusting air temperature.
  • a plurality of conventional check valves 12 and means for the separation and recovery of oil from the compressors 11 dispersed in the working fluid are also provided.
  • Such means also conventional and known to those skilled in the art, comprise an oil separator 13, a filter 14 and a line 15 (in figures 1-3 represented as a dotted line) that takes the separated and filtered oil back to the compressors 11.
  • an oil accumulation reservoir (not shown) placed between the oil separator 13 and the filter 14.
  • the thermal exchange device 4 preferably consists of an assembly arranged at the outside E of the environment A where the deep-frozen or frozen food conservation unit 7, the fresh food conservation unit 8 and the unit 9 for adjusting air temperature are active, preferably outside the building comprising environment A.
  • the thermal exchange device 4 allows the thermal exchange of the working fluid with air or other fluid available outside E, such as water (e.g., according to availability and/or requirements, thermal water, river water, ground water, waste water) or another suitable fluid.
  • the thermal exchange device 4 comprises a condensing portion 16 and an evaporating portion 17.
  • the evaporating portion 17 is connected with the closed circuit 2 so that, when active (see figure 3 described hereafter), the working fluid reaches it after flowing through the condensing portion 16.
  • the condensing portion 16 and the evaporating portion 17 comprise ducts defining respective fluid paths 160 and 170.
  • the fluid paths 160 and 170 are preferably coil-shaped and are embedded in the same assembly of fins 18.
  • the fins 18 are substantially planar and arranged substantially perpendicular to the ducts of the fluid paths 160 and 170.
  • the ducts of the fluid paths 160 and 170 are preferably made of copper; alternatively, the ducts of the fluid paths 160 and 170 could be made of steel.
  • the fins 18 are preferably made of aluminium, possibly surface treated through painting or oxidation or other known processes; alternatively, the fins 18 could be made of copper or iron, possibly surface treated.
  • Both the condensing portion 16 and the evaporating portion 17 preferably comprise a plurality of respective fluid paths 160 and 170.
  • just two fluid paths are represented for each portion 16, 17, for the sake of simplicity.
  • the condensing portion 16 is diagrammatically represented without specifying in detail the number of fluid paths 160, while the evaporating portion 17 is represented as a group of four fluid paths 170.
  • Each of the fluid paths 170 of the evaporating portion 17 can be selectively intercepted through conventional interception means 171, for example solenoid valves. In embodiments not shown some of the interception means 171 could be left out.
  • Each fluid path 170 of the evaporating portion also has associated with it a respective conventional means 172 for expanding the working fluid, preferably selected from a thermostatic valve and a capillary, more preferably a thermostatic valve, which allows the working fluid flow rate in the respective fluid path 170 to be adjusted.
  • a respective conventional means 172 for expanding the working fluid preferably selected from a thermostatic valve and a capillary, more preferably a thermostatic valve, which allows the working fluid flow rate in the respective fluid path 170 to be adjusted.
  • the heat exchange device 4 also preferably comprises conventional means 162 for forcedly circulating air or another fluid available outside, such as one or more fans, for example of the helical or centrifugal type, typically electrically actuated.
  • Such means 162 are provided so as to increase the air flow through the thermal exchange device 4 in a preferred direction, indicated by arrows 22. This preferred direction is such that the air crosses the thermal exchange device 4 flowing firstly in contact with the fluid paths 160 of the condensing portion 16 and the respective portions of the fins 18 and then in contact with the fluid paths 170 of the evaporating portion 17 and the respective portions of the fins 18.
  • Further interception means 19, 20 and 21, again of the conventional type, for example solenoid valves, are suitably provided in the closed circuit 2, so that the insertion or exclusion of portions thereof is possible both during normal operation, for example to change operating mode, as better described hereafter, and in conditions of failure or of partial stop of the thermal installation 1.
  • Means for expanding the working fluid are also arranged in the closed circuit 2 at the thermal user points 5.
  • Figures 1-3 show expansion means 6 at the thermal user point 5 associated with the operation of the unit 9 for adjusting air temperature.
  • the expansion of the working fluid typically takes place at the units 7, 8 themselves and therefore the expansion means 6 are not shown.
  • a reversing cycle valve 23 is arranged in the closed circuit 2 to allow switching between different operating modes, as better described hereafter.
  • the closed circuit 2 there are preferably also an accumulation reservoir 24 of the working fluid and a portion defining a double riser 25, which comprises a siphon 251, also known to those skilled in the art under the term "oil trap". Since part of oil from the compressors 11 remains dispersed in the working fluid in the absence of the oil separator 13, but also when it is present, the double riser 25 allows the oil dispersed to be dragged together with the working fluid, and therefore to be returned - through the units 7 and/or 8 - to the compressors 11, substantially in every allowed working fluid flow rate condition in the closed circuit 2, and in particular at minimum flow rates.
  • Each of the component elements of the thermal installation 1 described above is preferably designed so as to have a plan overall size not greater than 80 cm by 120 cm, so that the installation 1 can be distributed on one or more standard pallets.
  • the thermal exchange device 4 could also have a larger plan size, if one foresees to install it outside the building.
  • the connection pipelines are preferably made of flexible material and equipped with screwed joints, so as to avoid as far as possible the need for welding in loco, thus easing the assembly operations.
  • thermodynamic process of the invention shall now be described, according to a preferred embodiment of the thermodynamic process of the invention.
  • circuit portions active in an operating mode are indicated with a solid line, while the portions not active are indicated with a dashed line.
  • the arrows indicate the path of the working fluid in the closed circuit 2 in each operating mode.
  • the thermal installation 1 is active only for producing cold at the deep-frozen or frozen food conservation unit 7 and at the fresh food conservation unit 8.
  • the reversing cycle valve 23 is in a first operating configuration, which allows the delivery of the compressors 11 to be connected directly with the condensing portion 16 of the thermal exchange device 4 through the double riser 25.
  • the interception means 19 and 171 intercept the respective circuit portions, preventing the working fluid from entering the heat exchanger 10 and the evaporating portion 17 of the thermal exchange device 4.
  • the working fluid is compressed in the compression section 3 and sent - through the reversing cycle valve 23 and the double riser 25 - to the condensing portion 16, where it condenses releasing heat. Thereafter, the working fluid reaches the accumulation reservoir 24 to be sent to the thermal user points 5 where the deep-frozen or frozen food conservation unit 7 and the fresh food conservation unit 8 are connected.
  • the working fluid undergoes a substantially adiabatic expansion and evaporates, absorbing heat from the surroundings and therefore keeping the aforementioned units 7, 8 at the required low temperatures.
  • Such temperatures are typically between about -14°C and about -25°C in the case of the deep-frozen or frozen food conservation unit 7, and between about +10°C and about -1°C in the case of the fresh food conservation unit 8.
  • the flow rate of working fluid circulated in the deep-frozen or frozen food conservation unit 7 is then sent to the intake of the compressors 11 of the group of compressors 11a, while the flow rate of working fluid circulated in the fresh food conservation unit 8 is sent to the intake of the compressors 11 of the group of compressors 11b, thus completing the refrigerating cycle.
  • the thermal installation 1 is active both for producing cold at the deep-frozen or frozen food conservation unit 7 and at the fresh food conservation unit 8, and for cooling the air of one or more rooms of the environment A through the unit 9 for adjusting air temperature.
  • the reversing cycle valve 23 is still in its first operating configuration.
  • the interception means 20 and 171 again intercept the respective circuit portions, preventing the working fluid respectively from by-passing the heat exchanger 10 and from entering the evaporating portion 17 of the thermal exchange device 4.
  • the interception means 19 and 21 are instead open and allow the passage of the working fluid at the thermal user point 5 associated with the operation of the unit 9 for adjusting air temperature, that is through the heat exchanger 10.
  • the working fluid is compressed in the compression section 3 and sent, through the reversing cycle valve 23, to the condensing portion 16, where it condenses releasing heat. Thereafter, a first flow rate of the working fluid, through the accumulation reservoir 24, reaches the deep-frozen or frozen food conservation unit 7 and the fresh food conservation unit 8. At these units it undergoes a substantially adiabatic expansion and an evaporation producing cold, and then returns to the compressors 11 completing the refrigerating cycle, as already described with reference to the first operating mode. A second flow rate of the working fluid, thanks to the interception means 19 and 21 being open, flows through the expansion means 6 and reaches the heat exchanger 10.
  • the unit 9 for adjusting air temperature is thus active for cooling environment A.
  • the flow rate of working fluid coming out from the heat exchanger 10 is then sent, again through the reversing cycle valve 23, to the intake of the compressors 11 of the group of compressors 11b, completing the refrigerating cycle.
  • the thermal installation 1 is active both for producing cold at the deep-frozen or frozen food conservation unit 7 and at the fresh food conservation unit 8, and for heating one or more rooms of the environment A through the unit 9 for adjusting air temperature.
  • the reversing cycle valve 23 is in a second operating configuration, which allows the delivery of the compressors 11 to be directly connected with the thermal user point 5 associated with the air unit 9, that is with the heat exchanger 10.
  • the interception means 19 and 21 intercept the relative circuit portions, respectively preventing the working fluid from passing from the heat exchanger 10 directly to the accumulation reservoir 24 and from the reversing cycle valve 23 directly to the intake of the compressors 11.
  • the interception means 20 and at least one of the interception means 171 are open.
  • the working fluid is compressed in the compression section 3 and sent, through the reversing cycle valve 23, to the heat exchanger 10, where it can release sensible superheat and, moreover, partially or totally condense, releasing a first amount of latent heat to the thermal carrier fluid circulating in the secondary circuit 91 associated with the unit 9 for adjusting air temperature.
  • the unit 9 is thus active to heat environment A.
  • the working fluid is sent to the condensing portion 16, where it possibly completes the condensation releasing a second amount of latent heat.
  • a first flow rate of the working fluid, flowing through the accumulation reservoir 24, reaches the deep-frozen or frozen food conservation unit 7 and the fresh food conservation unit 8.
  • a second flow rate of working fluid reaches the evaporating portion 17 of the thermal exchange device 4. Based on the number of open interception means 171, this second flow rate flows through one or more of the fluid paths 170, evaporating after having undergone a substantially adiabatic expansion in the respective expansion means 172. The second flow rate of the working fluid coming out from the evaporating portion 17 is then sent to the intake of the compressors 11 of the group of compressors 11b, also in this case substantially completing a heat pump thermal cycle.
  • the amount of heat released by the working fluid during condensation at the condensing portion 16 can be at least partially, and preferably substantially, transferred to the evaporating portion 17 by forced convection of the air and conduction through the fins 18.
  • This contributes both to evaporate the working fluid within the evaporating portion 17, and to delay the possible formation of frost at the fluid paths 170 and at the fins 18.
  • frost which is thermally insulating, would hinder the heat exchange with the air of the outside E and therefore would limit to higher values the minimum outside temperature at which the evaporating portion 17 can be active, thus reducing the working range of the thermal installation 1.
  • the thermal installation 1 is therefore still active both for producing cold at the aforementioned units 7 and 8, and for heating environment A through the unit 9 for adjusting air temperature, but with a reduced heating capacity.
  • the amount of heat that the working fluid can release to environment A upon condensation is related to the demand of cold at the units 7 and 8 only.
  • This variant of the third operative mode can advantageously be used in all those situations where there is reduced need to heat the environment, as for example can happen at the end of winter or in late autumn.
  • a greater heating capacity it is possible to switch to the third operative mode described above by partially or totally activating the evaporating portion 17.
  • the addition of this thermal load increases the demand of cold in the thermal installation 1 and consequently increases the amount of heat that the working fluid can release upon condensation at the thermal user point 5 associated with the operation of the unit 9 for adjusting air temperature.
  • Both the changes in operating mode and the adjustment of the thermal installation 1 in each operating mode are preferably actuated through a microprocessor control unit (not shown in the figures).
  • control unit receives the following input signals:
  • the control unit determines the thermal load at the deep-frozen or frozen food conservation unit 7 and, if necessary, acts on the number of compressors 11 active in the group of compressors 11a.
  • the control unit determines the thermal load at the fresh food conservation unit 8 and at the unit 9 for adjusting air temperature when operating in cooling mode, and, if necessary, acts on the number of compressors 11 active in the group of compressors 11b. Based on this signal the control unit can also, in case of thermal load peaks, limit the air cooling function to continue ensuring the correct cooling at the fresh food conservation unit 8.
  • the control unit Based on the pressure signal at the delivery of the compression section 3, the control unit keeps the condensation of the working fluid within predetermined values for optimal operation of the thermal installation 1, for example by acting on the means 162 for forcedly circulating air at the thermal exchange device 4 (changing the number of active fans or the number of revolutions thereof).
  • the control unit determines whether the unit 9 for adjusting air temperature must be active in cooling mode, in heating mode, or else does not have to be active. This, in particular, can involve switching the reversing cycle valve 23 and opening/closing the interception means 19 and 21 to switch between the aforementioned modes, and possibly opening/closing the interception means 171, to totally or partially include or exclude the evaporating portion 17 of the thermal exchange device 4 into/from the closed circuit 2.
  • control unit Based on the temperature signal of the thermal carrier fluid of the secondary circuit 91 coming out from the heat exchanger 10 and on the required temperature signal of environment A, the control unit adjusts the operation of the unit 9 for adjusting air temperature with respect to the required temperature, for example changing or excluding the thermal carrier fluid flow rate circulating in the respective secondary circuit.
  • This last control could, on the other hand, be carried out directly by a control unit of the unit 9 for adjusting air temperature, especially when there are a plurality of units 9 connected with a single secondary circuit 91. In such a case, it is not necessary for the control unit of the installation 1 to receive as an input the temperature signal of the thermal carrier fluid of the secondary circuit 91 at the output of the heat exchanger 10.
  • the embodiment of the thermal installation 1 described above can undergo various modifications, which shall not be described here in detail, but in any case fall within the scope of the invention.
  • Such modifications can, for example, comprise: eliminating some or all of the check valves 12; eliminating the means for the separation and recovery of oil from the compressors (oil separator 13, filter 14, line 15); arranging the heat exchange device 4 so that the condensing portion 16 carries out a thermal exchange with air and the evaporating portion 17 with a different fluid, for example water as described above, or vice-versa; actuating the expansion at the evaporating portion 17 by means of a single expansion means 172; arranging the means 162 for forcedly circulating air so as to define a preferred direction of the air flow through the thermal exchange device 4 that is different from and, at the extreme, opposite to that indicated in the figures through the arrows 22, although to the detriment of the performance; leaving out the deep-frozen or frozen food conservation unit 7, the respective thermal user point 5 and the group of compressors 11a, or else leaving out the
  • the thermal installation 1 shall in general be marketed without the thermal users (units 7, 8, 9), even if, of course, the operation of the thermal installation 1 requires them to be connected at least at some of the thermal user points 5.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
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  • Devices That Are Associated With Refrigeration Equipment (AREA)
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Claims (27)

  1. Thermische Anlage (1) mit einem geschlossenen Kreislauf (2), in dem ein Arbeitsfluid einen thermodynamischen Kreisprozess ausführt, wobei der geschlossene Kreislauf (2) mehrere thermische Nutzerschnittstellen (5) umfasst, an denen das Arbeitsfluid eine Temperatur aufweist, welche zum Wärmeaustausch mit wenigstens einer Einheit (9) zum Einstellen der Lufttemperatur einer Umgebung (A) sowie einer Einheit (7) zum Aufbewahren tiefgekühlter oder gekühlter Lebensmittel und/oder einer Einheit (8) zum Aufbewahren frischer Lebensmittel geeignet ist, sowie mit einer Wärmetauschervorrichtung (4), an welcher das Arbeitsfluid in einer Wärmeaustauschbeziehung mit der Außenseite (E) der Umgebung (A) steht, wobei die Wärmetauschervorrichtung (4) einen Kondensationsteil (16) umfasst, an welchem das Arbeitsfluid Wärme abgibt, dadurch gekennzeichnet, dass die Wärmetauschervorrichtung (4) ferner einen wahlweise aktivierbaren Verdampfungsteil (17) umfasst, an welchem das Arbeitsfluid wenigstens teilweise die an dem Kondensationsteil (16) abgegebene Wärme aufnimmt.
  2. Thermische Anlage (1) nach Anspruch 1, bei der das Arbeitsfluid an dem Verdampfungsteil (17) einen wesentlichen Teil der an dem Kondensationsteil abgegebenen Wärme aufnimmt.
  3. Thermische Anlage (1) nach Anspruch 1 oder 2, bei der die wenigstens eine Einheit (7) zum Aufbewahren tiefgekühlter oder gekühlter Lebensmittel ein Schalter, ein Schrank oder ein Kälteraum bei einer Temperatur zwischen ungefähr -14°C und ungefähr -25°C ist.
  4. Thermische Anlage (1) nach einem der vorangehenden Ansprüche, bei der die wenigstens eine Einheit (8) zum Aufbewahren frischer Lebensmittel ein Schalter, ein Schrank oder ein Kälteraum bei einer Temperatur zwischen ungefähr +10°C und ungefähr -1°C ist.
  5. Thermische Anlage (1) nach einem der vorangehenden Ansprüche, bei der die Umgebung (A) ein Wirtschaftsuntemehmen, welches wenigstens teilweise für den Verkauf von Lebensmitteln bestimmt ist, oder eine Verzehrstelle ist.
  6. Thermische Anlage (1) nach einem der vorangehenden Ansprüche, wobei die Einheit (7) zum Aufbewahren tiefgekühlter oder gekühlter Lebensmittel und/oder die Einheit (8) zum Aufbewahren frischer Lebensmittel unmittelbar mit dem Arbeitsfluid betrieben ist.
  7. Thermische Anlage (1) nach einem der vorangehenden Ansprüche, wobei die wenigstens eine Einheit (9) zum Einstellen der Lufttemperatur mit einem thermischen Trägerfluid betrieben ist, welches von dem Arbeitsfluid verschieden ist und an der entsprechenden thermischen Nutzerschnittstelle (5) in einer Wärmeaustauschbeziehung mit ihm steht.
  8. Thermische Anlage (1) nach einem der vorangehenden Ansprüche mit Schaltmitteln (23, 19, 21, 171) zum Schalten zwischen einem Betriebszustand, in dem die wenigstens eine Einheit (9) zum Einstellen einer Lufttemperatur die Umgebung (A) kühlt, und einem Betriebszustand, in dem die wenigstens eine Einheit (9) zum Einstellen einer Lufttemperatur die Umgebung (A) heizt.
  9. Thermische Anlage (1) nach Anspruch 8, bei der die Schaltmittel (23, 19, 21, 171) ein Umschaltventil (23) und Mittel (19, 21, 171) zum Absperren von Teilen des geschlossenen Kreislaufs (2) umfassen.
  10. Thermische Anlage (1) nach einem der vorangehenden Ansprüche, bei der der Kondensationsteil (16) wenigstens einen ersten Fluidpfad (160) umfasst und der Verdampfungsteil wenigstens einen zweiten Fluidpfad (170) umfasst, wobei der erste Fluidpfad (160) und der zweite Fluidpfad (170) mehrere Kanäle umfassen, welche in einer gemeinsamen Lamellenanordnung (18) eingebettet sind.
  11. Thermische Anlage (1) nach Anspruch 10, bei der die Wärmetauschervorrichtung (4) Mittel (162) zum Zirkulieren eines Fluids, vorzugsweise Luft, außerhalb des ersten Fluidpfads (160) und des zweiten Fluidpfads (170) umfasst.
  12. Thermische Anlage (1) nach Anspruch 10 oder 11, bei der das Verdampfungsteil (17) mehrere zweite Fluidpfade (170) umfasst, welche in Parallelschaltung verbunden und durch eine entsprechende Anzahl von Absperrmitteln (171) wahlweise absperrbar sind.
  13. Thermische Anlage (1) nach einem der vorangehenden Ansprüche mit mehreren Kompressoren (11), welche einen Kompressionsabschnitt (3) des Arbeitsfluids bilden, wobei eine erste Gruppe von Kompressoren (11a) der mehreren Kompressoren (11) eine Kühlleistung aufweist, welche geeignet ist, den Betrieb der wenigstens einen Einheit (7) zum Aufbewahren von tiefgekühlten oder gekühlten Lebensmitteln sicherzustellen, und eine zweite Gruppe von Kompressoren (11b) der mehreren Kompressoren (11) eine Kühlleistung aufweist, welche geeignet ist, den Betrieb der wenigstens einen Einheit (8) zum Aufbewahren frischer Lebensmittel und der wenigstens einen Einheit (9) zum Einstellen der Lufttemperatur sicherzustellen.
  14. Thermische Anlage (1) nach einem der vorangehenden Ansprüche mit Ausdehnungsmitteln (6, 172) zum Expandieren des Arbeitsfluids, welche thermostatische Ventile und/oder Kapillargefäße umfassen.
  15. Thermische Anlage (1) nach einem der vorangehenden Ansprüche, bei der das Arbeitsfluid ein Kühlfluid ist, welches aus einer Fluorkohlenwasserstoffe (hydro-fluoro-carbons, HFC), Fluorchlorkohlenwasserstoffe (hydro-chloro-fluoro-carbons, HCFC), Kohlenstoffdioxide, Propan und Ammoniak umfassenden Gruppe ausgewählt ist.
  16. Thermische Anlage (1) nach Anspruch 15, bei der das Kühlfluid ein Fluorkohlenwasserstoff (hydro-fluoro-carbon, HFC) aus einer R-507A und R-404A umfassenden Gruppe ist.
  17. Thermische Anlage (1) nach einem der vorangehenden Ansprüche mit einer Mikroprozessorsteuereinheit, welche dazu eingerichtet ist, den Betrieb der thermischen Anlage (1) gemäß den erforderlichen Betriebsbedingungen an der wenigstens einen Einheit (9) zum Einstellen der Lufttemperatur sowie an der Einheit (7) zum Aufbewahren tiefgekühlter oder gekühlter Lebensmittel und/oder der Einheit (8) zum Aufbewahren frischer Lebensmittel zu regeln.
  18. Thermische Anlage (1) nach einem der vorangehenden Ansprüche, bei der jede ihrer Baugruppen einen Gesamtgrundriss von nicht mehr als 80 cm x 120 cm aufweist.
  19. Wärmeaustauschvorrichtung (4) mit einem Kondensationsteil (16), an welchem ein Arbeitsfluid Wärme abgibt, und einem Verdampfungsteil (17), wobei das Kondensationsteil (16) wenigstens einen ersten Fluidpfad (160) aufweist und das Verdampfungsteil (17) wenigstens einen zweiten Fluidpfad (170) aufweist und der wenigstens eine erste Fluidpfad (160) und der wenigstens eine zweite Fluidpfad (170) in eine gemeinsame Lamellenanordnung (18) eingebettet sind, dadurch gekennzeichnet, dass der Verdampfungsteil (17) wahlweise aktivierbar ist und mit Bezug auf einen Luftstrom (22) stromabwärts des Kondensationsteils (16) angeordnet ist, so dass das Arbeitsfluid zu wesentlichen Teilen die an dem Kondensationsteil (16) abgegebene Wärme aufnimmt.
  20. Thermodynamisches Verfahren mit dem Schritt eines Ausführens eines thermodynamischen Kreisprozesses, bei dem ein Arbeitsfluid an mehreren thermischen Nutzerschnittstellen (5) mehrere Temperaturen annimmt, welche für den Betrieb wenigstens einer Einheit (9) zum Einstellen einer Lufttemperatur einer Umgebung (A) sowie einer Einheit (7) zum Aufbewahren tiefgekühlter oder gekühlter Lebensmittel und/oder einer Einheit (8) zum Aufbewahren frischer Lebensmittel geeignet sind, wobei der Schritt des Ausführens eines thermodynamischen Kreisprozesses in einem Heizbetriebmodus der wenigstens einen Einheit (9) zum Einstellen einer Lufttemperatur die folgenden Schritte umfasst:
    (a) Komprimieren des Arbeitsfluids;
    (b) Überführen des Arbeitsfluids in eine Wärmeaustauschbeziehung mit der wenigstens einen Einheit (9) zum Einstellen einer Lufttemperatur und Hervorrufen seiner teilweisen Kondensation;
    (c) im Wesentlichen Abschließen der Kondensation des Arbeitsfluids in einer Wärmeaustauschbeziehung mit der Außenseite (E) der Umgebung (A); und
    (d) Ausdehnen und Verdampfen des Arbeitsfluids,
    dadurch gekennzeichnet, dass in Schritt d) in Wärmeaustauschbeziehung mit der Außenseite (E) der Umgebung (A) wenigstens ein Teil des Arbeitsfluids ausgedehnt und verdampft wird und dass in Schritt d) das Arbeitsfluid wenigstens teilweise die in Schritt c) abgegebene Wärme aufnimmt.
  21. Verfahren nach Anspruch 20, bei dem das Arbeitsfluid in Schritt d) zu wesentlichen Teilen die in Schritt c) abgegebene Wärme aufnimmt.
  22. Verfahren nach Anspruch 20 oder 21, bei dem der Schritt c) in einem Kondensationsteil (16) einer Wärmetauschervorrichtung (4) ausgeführt wird und der Schritt d) an einem Verdampfungsteil (17) der Wärmetauschervorrichtung (4) ausgeführt wird, wobei der Kondensationsteil (16) wenigstens einen ersten Fluidpfad (160) umfasst und der Verdampfungsteil (17) wenigstens einen zweiten Fluidpfad (170) umfasst und der wenigstens eine erste Fluidpfad (160) und der wenigstens eine zweite Fluidpfad (170) in eine gemeinsame Lamellenanordnung (18) eingebettet sind.
  23. Verfahren nach einem der Ansprüche 20 bis 22, bei dem der Betrieb der wenigstens einen Einheit (9) zum Einstellen der Lufttemperatur wahlweise deaktivierbar ist.
  24. Verfahren nach einem der Ansprüche 20 bis 22, bei dem in einem weiteren Betriebsmodus der Betrieb der wenigstens einen Einheit (9) zum Einstellen der Lufttemperatur zum Kühlen der Lufttemperatur ausgelegt ist.
  25. Verfahren nach einem der Ansprüche 20 bis 24 mit einem Schritt des Erzeugens einer Strömung eines Fluids, vorzugsweise Luft, zum Steigern der Absorption der in Schritt c) abgegebenen Wärme in Schritt d).
  26. Verfahren nach einem der Ansprüche 20 bis 25, bei dem der Schritt des Ausführens eines thermodynamischen Kreisprozesses einen Schritt des Komprimierens einer ersten Strömungsrate des Arbeitsfluids umfasst, welcher dazu geeignet ist, den Betrieb der wenigstens einen Einheit (7) zum Aufbewahren tiefgekühlter oder gekühlter Lebensmittel sicherzustellen, und einen Schritt des Komprimierens einer zweiten Strömungsrate des Arbeitsfluids umfasst, welcher dazu geeignet ist, den Betrieb der wenigstens einen Einheit (8) zum Aufbewahren frischer Lebensmittel und der wenigstens einen Einheit (9) zum Einstellen der Lufttemperatur sicherzustellen.
  27. Verfahren nach Anspruch 26, bei dem der Betrieb der wenigstens einen Einheit (9) zum Einstellen der Lufttemperatur dem ordnungsgemäßen Betrieb der wenigstens einen Einheit (8) zum Aufbewahren frischer Lebensmittel untergeordnet wird.
EP05425423A 2005-06-13 2005-06-13 Anlage und Verfahren für die Produktion von Kälte und für die Regelung der Lufttemperatur und Vorrichtung zum Wärmeaustausch für diese Anlage Not-in-force EP1734318B1 (de)

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DE602005014098T DE602005014098D1 (de) 2005-06-13 2005-06-13 Anlage und Verfahren für die Produktion von Kälte und für die Regelung der Lufttemperatur und Vorrichtung zum Wärmeaustausch für diese Anlage
AT05425423T ATE429619T1 (de) 2005-06-13 2005-06-13 Anlage und verfahren für die produktion von kälte und für die regelung der lufttemperatur und vorrichtung zum wärmeaustausch für diese anlage
EP05425423A EP1734318B1 (de) 2005-06-13 2005-06-13 Anlage und Verfahren für die Produktion von Kälte und für die Regelung der Lufttemperatur und Vorrichtung zum Wärmeaustausch für diese Anlage

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EP2211125A1 (de) * 2009-01-27 2010-07-28 Zanotti S.p.A. Anlage und Verfahren zur Herstellung von kaltem und heißem Wasser, das an einen oder mehrere Wärmebenutzer geliefert wird
WO2013114071A2 (en) * 2012-01-31 2013-08-08 Clean Thermodynamic Energy Conversion Ltd Steam generation
US9746209B2 (en) 2014-03-14 2017-08-29 Hussman Corporation Modular low charge hydrocarbon refrigeration system and method of operation

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US3905202A (en) * 1974-01-08 1975-09-16 Emhart Corp Refrigeration system
US4373348A (en) * 1979-07-13 1983-02-15 Tyler Refrigeration Corporation Energy saving refrigeration system
JPH10300271A (ja) * 1997-04-30 1998-11-13 Nippon Light Metal Co Ltd ヒートポンプ式冷暖房機の室外用熱交換器
KR100473823B1 (ko) * 2002-08-06 2005-03-08 삼성전자주식회사 냉수 및 온수 제조 장치를 구비한 공기 조화기

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