EP2642221A2 - Kälteanlage - Google Patents

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Publication number
EP2642221A2
EP2642221A2 EP13160512.3A EP13160512A EP2642221A2 EP 2642221 A2 EP2642221 A2 EP 2642221A2 EP 13160512 A EP13160512 A EP 13160512A EP 2642221 A2 EP2642221 A2 EP 2642221A2
Authority
EP
European Patent Office
Prior art keywords
heat
chamber
outlet
carrying fluid
refrigerator assembly
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Withdrawn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
EP13160512.3A
Other languages
English (en)
French (fr)
Other versions
EP2642221A3 (de
Inventor
Alessandro Zen
Michele Vio
Marco Pozzati
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.)
IRSAP SpA
Original Assignee
IRSAP SpA
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 IRSAP SpA filed Critical IRSAP SpA
Publication of EP2642221A2 publication Critical patent/EP2642221A2/de
Publication of EP2642221A3 publication Critical patent/EP2642221A3/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Withdrawn legal-status Critical Current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
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
    • 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
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/38—Expansion means; Dispositions thereof specially adapted for reversible cycles, e.g. bidirectional expansion restrictors
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • 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
    • F25B2400/06—Several compression cycles arranged in parallel

Definitions

  • the present invention relates to a refrigerator assembly.
  • the present invention can be applied advantageously, but not exclusively, to any type of refrigerator assembly suitable to be used in an air conditioning system comprising radiant devices and/or ambient air treatment devices, to which the description below will specifically refer, without loss of generality.
  • the definition refrigerator assembly must be intended in its broadest sense, i.e. a machine comprising at least one refrigeration circuit through which a refrigeration cycle is carried out so as to transfer heat from a first fluid at a lower temperature to a second fluid at higher temperature. Therefore, a heat pump also falls within the definition of refrigerator assembly used in this document.
  • An air conditioning system comprises in general a plurality of system terminals, which comprise, for example, fan coils and/or radiators and are supplied with a heat carrying fluid essentially composed of water, a heat generator for cooling or heating the heat carrying fluid and a transport circuit of the fluid to deliver the cooled or heated fluid to the system terminals.
  • the heat generator is composed of a refrigerator machine or assembly, as this latter is very versatile and allows the generation of cold and heat (heat pump).
  • a refrigerator machine comprises at least one refrigeration circuit, which essentially comprises a compressor, an evaporator, an expansion valve and a condenser so as to carry out a refrigeration cycle on a refrigerant fluid circulating in the circuit.
  • the pumping power required is substantially proportional to the cube of the flow rate of the heat carrying fluid in the transport circuit.
  • the flow rate of the fluid is proportional to the ratio between the thermal power required by the air conditioning system and the thermal gradient delivered by the refrigerator assembly, i.e. the difference between the delivery temperature and the return temperature of the heat carrying fluid, then the pumping power varies, in proportion to the dimensions of the transport circuit, in a manner inversely proportional to the cube of the thermal gradient. Therefore, it is easy to understand how important it is for a refrigerator assembly to have a high thermal gradient.
  • Refrigerator assemblies available on the market normally ensure a thermal gradient of around 5 °C. With suitable sizing of the heat exchangers of the evaporator and of the condenser, the thermal gradient can be increased up to 7 °C.
  • some air conditioning systems comprise fan coils and radiant devices, these latter consisting, for example, of radiant ceilings or beams; in summer operating mode, the fan coils are supplied with water at low temperature, such as 7 °C, while the radiant devices are supplied with water at intermediate temperature, such as 12 °C; in winter operating mode the fan coils are supplied with water at a high temperature, such as 52 °C, while the radiant devices are supplied with water at a lower temperature, such as 40 °C. Normally, the water is delivered at a first return temperature and is mixed with the water at the return temperature to obtain water at a second delivery temperature of intermediate value. As can easily be understood, this mixing causes a loss of output.
  • the object of the present invention is to produce a refrigerator assembly with high thermal gradient, which allows the problems described above to be solved and which is, at the same time, easy and economical to produce.
  • the number 1 generically indicates, as a whole, an air conditioning system comprising a plurality of thermal loads 2, which comprise, for example, fan coils and/or radiators, a transport circuit 3 for supplying a heat carrying fluid to the thermal loads, and a refrigerator assembly 4 produced in accordance with the present invention.
  • the refrigerator assembly 4 has a return inlet 4a to receive the heat carrying fluid from a return branch 3a of the transport circuit at a return temperature TR and a delivery outlet 4a to deliver the heat carrying fluid to a delivery branch 3b of the transport circuit 3 at a delivery temperature TD.
  • the heat carrying fluid is essentially composed of a water and glycol mixture to prevent freezing.
  • the refrigerator assembly 4 of the invention comprises two independent refrigeration circuits 5 and 6.
  • Each refrigeration circuit 5, 6 comprises a respective compressor 7, 8, a heat exchanger 9, 10 operating as evaporator, a respective expansion valve 11, 12 and a further heat exchanger 13, 14 operating as condenser.
  • the two refrigeration circuits 5, 6 carry out two independent refrigeration cycles on respective refrigerant fluids.
  • the refrigerator assembly 4 of the example of embodiment of Fig. 1 is of the type suited to cool the heat carrying fluid that circulates in the thermal loads.
  • Each of the heat exchangers 9 and 10 is a surface heat exchanger, in which a heat exchange surface physically separates one side of the heat exchanger 9, 10, through which the related refrigerant fluid flows, from another side of the heat exchanger 9, 10 through which the heat carrying fluid flows.
  • each heat exchanger 9, 10 comprises a respective chamber 15, 16 thermally coupled to a respective duct 5a, 6a of the related refrigeration circuit 5, 6, this duct 5a, 6a being arranged between the expansion valve 11, 12 and the compressor 7, 8.
  • the direction of flow of the refrigerant fluid in each refrigeration circuit is defined by the respective compressor 7, 8.
  • the chambers 15 and 16 communicate with one another so that, in use, the heat carrying fluid flows through them so that this latter transfers heat to both refrigerant fluids, which consequently evaporate inside the related duct 5a, 6a.
  • the chamber 15 comprises an inlet, which substantially coincides with, i.e.
  • the chamber 16 comprises an inlet 16a, which is connected to the outlet 15a, and an outlet, which substantially coincides with, i.e. is directly connected to, the outlet 4b of the refrigerator assembly 4.
  • the two heat exchangers 9 and 10 are connected to one another in series on the side of the heat carrying fluid.
  • the heat carrying fluid flows through the chambers 15 and 16 one after the other, from the inlet 4a to the outlet 4b, thus transferring heat first to the refrigerant fluid in the refrigeration circuit 5 and then to the refrigerant fluid in the refrigerating circuit 6.
  • Each chamber 15, 16 has a shape that depends on the specific type of surface heat exchanger used for the heat exchangers 9, 10.
  • the chamber 15, 16 is in the shape of a rectilinear duct, or of a coil shaped duct, or of a tube bundle.
  • the refrigerator assembly 4 described above allows heat carrying fluid to be delivered at a delivery temperature TD of 5 °C, i.e. allows a thermal gradient of 10 °C to be easily obtained. If the two refrigeration circuits 5 and 6 deliver the same power in terms of frigories and the two heat exchangers 9 and 10 are analogous, the intermediate temperature T1 of the heat carrying fluid at the outlet 15a, or at the inlet 16b, is substantially the same as the average of the two return TR and delivery TD temperatures, i.e. 10 °C.
  • the refrigeration circuits 5 and 6 operate as two independent heat pumps, i.e. the two compressors 7 and 8 cause the two refrigerant fluids to circulate in opposite direction with respect to the refrigerator assembly 4 of Fig. 1 and therefore the two heat exchangers 9 and 10, which exchange heat with the heat carrying fluid, operate as condensers and the other two heat exchangers 13 and 14 operate, necessarily, as evaporators.
  • the heat carrying fluid flowing through the chambers 15 and 16 from the inlet 4a to the outlet 4b, is heated absorbing heat first from the refrigerant fluid of the refrigeration circuit 5 and then from the refrigerant fluid of the refrigeration circuit 6, thus causing the refrigerant fluids to condense inside the related ducts 5a and 6a.
  • TR return temperature
  • the expansion valves 11 and 12 are of reversible type and the refrigerator assembly 4 comprises members for diverting the flow of the refrigerant fluids so as to simultaneously reverse the two refrigeration cycles of the refrigeration circuits 5 and 6, which therefore operate as two reversible heat pumps.
  • the heat exchangers 9 and 10 cause the two refrigerant fluids to evaporate or condense and, analogously, the heat exchangers 13 and 14 cause the two refrigerant fluids to condense or evaporate so as to cool or heat the heat carrying fluid that circulates in the thermal loads 2 according to the common direction of the two refrigeration cycles 5 and 6.
  • the refrigerator assembly 4 comprises, in place of the heat exchangers 9 and 10 of Fig. 1 , a single heat exchanger 17, which comprises a chamber 18 thermally coupled to both ducts 5a and 6a so as to allow the heat carrying fluid to transfer heat to both refrigerant fluids.
  • the chamber 18 comprises an inlet, which in practice coincides with the inlet 4a of the refrigerator assembly 4, and an outlet, which in practice coincides with the outlet 4b of the refrigerator assembly 4.
  • the chamber 18 has a shape analogous to that described for the chambers 16 and 15 of Fig. 1 .
  • the chamber 18 comprises a first portion 18a, which is thermally coupled, so as to exchange heat, only to the duct 5a, and a second portion 18b, which is thermally coupled, so as to exchange heat, only with the duct 6a.
  • the two portions 18a and 18b are consecutive to one another with respect to the direction of circulation of the heat carrying fluid inside the chamber 18.
  • the heat exchanger 17 is a surface heat exchanger.
  • the refrigerator assembly 4 is of the type suited to cool the heat carrying fluid that flows through the heat exchangers 9 and 10 and to heat a further heat carrying fluid that flows through the heat exchangers 13 and 14.
  • the further heat carrying fluid is essentially composed of water.
  • Each of the heat exchangers 13 and 14 is of the same type as the heat exchangers 9 and 10.
  • each heat exchanger 13, 14 comprises a respective chamber 19, 20 thermally coupled to a respective duct 5b, 6b of the related refrigeration circuit 5, 6, this duct 5b, 6b being arranged, following the direction of circulation of the respective refrigerant fluid, between the compressor 7, 8 and the expansion valve 11, 12.
  • the chambers 19 and 20 are analogous to and connected in the same way as the chambers 15 and 16. In other words, the two heat exchangers are connected to one another in series on the side of the heat carrying fluid.
  • the chambers 19 and 20 communicate with one another so that, in use, a further heat carrying fluid flows through them, one after the other, so that this latter absorbs heat first from the refrigerant fluid of the refrigeration circuit 5 and then from the refrigerant fluid of the refrigeration circuit 6.
  • the two refrigerant fluids thus condense inside the related duct 5b, 6b.
  • the chamber 19 comprises an inlet, which substantially coincides with, i.e. is directly connected to, a second return inlet 4c of the refrigerator assembly 4, and an outlet 19a.
  • the chamber 20 comprises an inlet 20a, which is connected to the outlet 19a, and an outlet, which substantially coincides with, or is directly connected to, a second delivery outlet 4d of the refrigerator assembly 4.
  • the refrigerator assembly 4 of Fig. 4 allows a heat carrying fluid to be delivered at the outlet 4b (cold outlet) at a delivery temperature TD of 5 °C and the further heat carrying fluid to be delivered at a delivery temperature TD2 of 52 °C at the outlet 4d (hot outlet).
  • the intermediate temperature TI of the heat carrying fluid at the outlet 15a is substantially 10 °C and the intermediate temperature T12 of the further heat carrying fluid at the outlet 19a is substantially 42 °C.
  • the refrigerator assembly 4 of Fig. 3 can be used as multipurpose refrigerator assembly with the inlet 4a and the outlet 4b connected to the return branch and, respectively, the delivery branch of a further transport circuit (not illustrated) of the air conditioning system 1 for heating and supplying the further heat carrying fluid to a further plurality of thermal loads.
  • the refrigerator assembly 4 of Fig. 3 can be used in an air conditioning system 1 that switches between heating and cooling modes through a reversal on the system, which is obtained by means of a suitable hydraulic switching system, known per se and therefore not illustrated, which connects the return and delivery branches 3a and 3b of the transport circuit to the cold side (inlet 4a, outlet 4b) or, alternatively, to the hot side (inlet 4c, outlet 4d) of the refrigerator assembly 4.
  • a suitable hydraulic switching system known per se and therefore not illustrated, which connects the return and delivery branches 3a and 3b of the transport circuit to the cold side (inlet 4a, outlet 4b) or, alternatively, to the hot side (inlet 4c, outlet 4d) of the refrigerator assembly 4.
  • Fig. 4 illustrates a further embodiment of the present invention.
  • the air conditioning system 1 comprises a first plurality of thermal loads composed of fan coils 21 and a second plurality of thermal loads composed of radiant devices 22 arranged so as to define, for example, radiant ceilings or beams.
  • the refrigerator assembly 4 comprises a node 23, which comprises an inlet connected to the outlet 15a, an outlet connected to the inlet 16a, and a further outlet defining a further delivery outlet 4e of the refrigerator assembly 4 so as to deliver heat carrying fluid at a delivery temperature TD3 different from the delivery temperature TD of the heat carrying fluid delivered at the outlet 4b.
  • the node is composed of a three-way valve.
  • the heat carrying fluid received from the inlet 4a flows through the chamber 15, thus transferring heat to the refrigerant fluid in the refrigeration circuit 5, and then, at the node 23, separates into a first part, which immediately reaches the outlet 4e at the delivery temperature TD3, and a second part, which also flows through the second chamber, thus transferring heat to the refrigerant fluid 6, and reaches the outlet 4b at the delivery temperature TD, which is lower than the delivery temperature TD3.
  • the outlet 4b delivers the heat carrying fluid at the temperature TD to the fan coils 22 through the delivery branch 3b and the outlet 4e delivers the heat carrying fluid at the temperature TD3 to the radiant devices 22 through a second delivery branch 3e of the transport circuit 3.
  • the heat carrying fluid delivered by the fan coils 21 and by the radiant devices 22 returns to the inlet 4a through the return branch 3a.
  • the refrigerator assembly 4 of Fig. 4 allows heat carrying fluid to be delivered at the delivery temperature TD of 7 °C from the outlet 4b and at the delivery temperature TD3 of 12 °C from the outlet 4e.
  • the refrigeration circuits 5 and 6 operate as two independent heat pumps, i.e. the two heat exchangers 9 and 10 operate as condensers and the other two heat exchangers 13 and 14 operate, necessarily, as evaporators.
  • the heat carrying fluid entering through the inlet 4a flows, in use, through the chamber 15 and is then separated into a first part that flows out from the outlet 4e and into a second part that flows through the chamber 16 to the outlet 4b, thus absorbing heat first from the refrigerant fluid in the refrigeration circuit 5 and then from the refrigerant fluid in the refrigeration circuit 6. Therefore, the delivery temperature TD will be higher than the delivery temperature TD3.
  • a delivery temperature TD of 52 °C suitable for supplying the fan coils 21, and a delivery temperature TD3 of 40 °C, suitable for supplying the radiant devices 22.
  • TR return temperature
  • TD3 delivery temperature
  • the invention refers in particular to the examples of embodiment described and illustrated above, it should not be considered limited to these examples of embodiment, and the scope of the invention includes all variants, modifications or simplifications that are obvious to a person skilled in the art, such as the use of different refrigerant fluids and/or of different compressors 7 and 8 for the two refrigeration circuits 5 and 6, or the use of heat carrying fluids other than water, or the use of more than two different delivery temperatures.
  • the main advantage of the refrigerator assembly 4 in the various embodiments described above is that of delivering a high thermal gradient, regardless of whether it is obtained to heat or cool the heat carrying fluid, at the same time guaranteeing a high output. Moreover, the refrigerator assembly 4 allows the delivery of heat carrying fluid at least at two different delivery temperatures without reductions in output.

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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)
  • Transition And Organic Metals Composition Catalysts For Addition Polymerization (AREA)
  • Defrosting Systems (AREA)
EP13160512.3A 2012-03-21 2013-03-21 Kälteanlage Withdrawn EP2642221A3 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
IT000152A ITBO20120152A1 (it) 2012-03-21 2012-03-21 Gruppo frigorifero

Publications (2)

Publication Number Publication Date
EP2642221A2 true EP2642221A2 (de) 2013-09-25
EP2642221A3 EP2642221A3 (de) 2014-02-19

Family

ID=45992697

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13160512.3A Withdrawn EP2642221A3 (de) 2012-03-21 2013-03-21 Kälteanlage

Country Status (2)

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EP (1) EP2642221A3 (de)
IT (1) ITBO20120152A1 (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3051229A1 (de) * 2015-01-30 2016-08-03 Rolls-Royce Corporation Wärmeregelungssystem zur steuerung dynamischer und kontinuierlicher thermischer beharrungslastzustände
FR3047301A1 (fr) * 2016-01-29 2017-08-04 Stephane Boulet Dispositif d’optimisation des performances d’une installation de chauffage par pompe a chaleur par l’adjonction d’une pompe a chaleur auxiliaire captant l’energie thermique dans un milieu rechargeable
US10132529B2 (en) 2013-03-14 2018-11-20 Rolls-Royce Corporation Thermal management system controlling dynamic and steady state thermal loads

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ATE494516T1 (de) * 2007-05-10 2011-01-15 Carrier Corp Kühlsystem und verfahren zur steuerung von kompressoranlagen in solch einem kühlsystem
US7900467B2 (en) * 2007-07-23 2011-03-08 Hussmann Corporation Combined receiver and heat exchanger for a secondary refrigerant
US20090120117A1 (en) * 2007-11-13 2009-05-14 Dover Systems, Inc. Refrigeration system
US8132420B2 (en) * 2008-11-07 2012-03-13 Trane International Inc. Variable evaporator water flow compensation for leaving water temperature control

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10132529B2 (en) 2013-03-14 2018-11-20 Rolls-Royce Corporation Thermal management system controlling dynamic and steady state thermal loads
US11448432B2 (en) 2013-03-14 2022-09-20 Rolls-Royce Corporation Adaptive trans-critical CO2 cooling system
EP3051229A1 (de) * 2015-01-30 2016-08-03 Rolls-Royce Corporation Wärmeregelungssystem zur steuerung dynamischer und kontinuierlicher thermischer beharrungslastzustände
FR3047301A1 (fr) * 2016-01-29 2017-08-04 Stephane Boulet Dispositif d’optimisation des performances d’une installation de chauffage par pompe a chaleur par l’adjonction d’une pompe a chaleur auxiliaire captant l’energie thermique dans un milieu rechargeable

Also Published As

Publication number Publication date
ITBO20120152A1 (it) 2013-09-22
EP2642221A3 (de) 2014-02-19

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