EP2791589B1 - Unité de pompe à chaleur et procédé permettant de refroidir et/ou de chauffer au moyen de ladite unité de pompe à chaleur - Google Patents

Unité de pompe à chaleur et procédé permettant de refroidir et/ou de chauffer au moyen de ladite unité de pompe à chaleur Download PDF

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EP2791589B1
EP2791589B1 EP12818604.6A EP12818604A EP2791589B1 EP 2791589 B1 EP2791589 B1 EP 2791589B1 EP 12818604 A EP12818604 A EP 12818604A EP 2791589 B1 EP2791589 B1 EP 2791589B1
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Prior art keywords
heat pump
heat
pump unit
hpcm
pump cycle
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German (de)
English (en)
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EP2791589A1 (fr
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Gianfranco Pellegrini
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Teon Srl
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Teon Srl
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D11/00—Central heating systems using heat accumulated in storage masses
    • F24D11/02—Central heating systems using heat accumulated in storage masses using heat pumps
    • 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
    • F25B29/006—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the sorption type system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D17/00—Domestic hot-water supply systems
    • F24D17/02—Domestic hot-water supply systems using heat pumps
    • 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
    • F25B30/00—Heat pumps
    • F25B30/04—Heat pumps of the sorption type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D2200/00—Heat sources or energy sources
    • F24D2200/12—Heat pump

Definitions

  • the present invention relates to the heat pump sector.
  • the invention relates to a heat pump adapted to be used for cooling and/or heating spaces and for producing sanitary hot water with high performance in terms of energy efficiency and flexibility of use.
  • Heat pumps are an increasingly more popular solution for satisfying the cooling/heating needs of spaces and/or fluids.
  • the reasons of such a success are mainly related to their high energy efficiency, to the possibility of using a single device for both cooling and heating (known as "reversible” heat pumps), to the flexibility in managing thermal users with different needs, and to the possibility, when used for heating, of drastically reducing the use of fossil fuel and consequently the emission of greenhouse gases which are harmful for the environment.
  • a known solution for improving energy efficiency consists in performing an undercooling of the operating fluid after its condensation and exploiting the undercooling heat power thus obtained for preheating the heat carrier fluid coming from a heat sink before sending it to the evaporator to determine the evaporation of the operating fluid.
  • Documents DE 3311505 A1 and WO 2011/045752 A1 describe the use of the aforesaid solution, in particular, in irreversible type two-stage heat pumps intended for heating.
  • An additional heat exchanger connected downstream of the condenser and upstream of the expansion means in the circuit of each stage is present in the two-stage heat pumps described in such documents.
  • the additional heat exchangers are further connected to a heat carrier fluid delivery line of a heat sink, upstream of the evaporator of the lower temperature stage. It is thus possible to preheat the heat carrier fluid coming from the heat sink before sending it to the lower temperature heat pump cycle evaporator by means of the heat power deriving from the undercooling of the operating fluids which perform the higher and lower temperature heat pump cycles.
  • High COP can be obtained with this solution, in particular either equal to or higher than 3, also in two-stage heat pumps.
  • the technical problem underlying the present invention is improving the energy efficiency of heat pumps for cooling, which may be either irreversible heat pumps intended for cooling only or reversible heat pumps capable of either cooling or heating.
  • a heat pump which can guarantee high EER (Energy Efficiency Ratio) values, in particular equal to or higher than 3, in a wide range of operating conditions, also in presence of thermal users with different needs in terms of refrigerating/heat power and/or required working temperatures.
  • EER Energy Efficiency Ratio
  • a first aspect of the invention thus relates to a heat pump unit comprising two circuits, wherein said two circuits comprise a first sub-circuit adapted to perform a higher temperature heat pump cycle with a respective operating fluid, and a second sub-circuit adapted to perform a lower temperature heat pump cycle with a respective operating fluid, wherein said first and second sub-circuits are in a cascading heat exchange relationship with each other so as to perform globally a two-stage heat pump cycle, said two circuits comprising:
  • the heat power subtracted from the operating fluid during its undercooling may be transferred to a second thermal user installation, and thus, in essence, disposed outside the heat pump unit without influencing the conditions of the heat carrier fluid in the external circuit which is connected to the evaporator of the heat pump unit, in particular in this case, the external circuit of a thermal cooling installation.
  • the undercooling of the operating fluid of the heat pump cycle results, in this case, into an increase of the evaporation enthalpy of the operating fluid in the heat pump cycle, i.e. of the performance in the case of an irreversible heat pump intended for cooling or of a reversible heat pump operating in cooling mode.
  • the EER of the heat pump unit increases as a whole.
  • the heat power deriving from an undercooling of the operating fluid is treated in the heat pumps of the invention in manner entirely different from that which occurs in the heat pump units of the aforesaid prior art, in which the increase of the performance is obtained by recovering the undercooling heat power of the heat pump unit and exploiting it for preheating the heat carrier fluid in a lower temperature heat sink, before sending it to the evaporator.
  • the heat pump unit of the invention allows to reach EER values equal to 3.5-4.0, with improvements in some cases even higher than 100% with respect to the performance of conventional heat pumps of equal type and power.
  • the heat pump unit of the invention is capable of providing an additional performance, again without any increase of electric compression power, with a further benefit of increasing the overall energy efficiency of the heat pump unit.
  • the technical features of the heat pump unit of the invention by means of which the aforesaid advantageous results can be obtained are compatible and easily integrated with the other technical solutions aimed at exploiting the undercooling thermal power of the operating fluid, in particular for the purpose of increasing energy efficiency also in a heating operating mode, when required, to the benefit for flexibility of use of the heat pump of the invention.
  • the presence of the aforesaid switching means allows to obtain a reversible heat pump capable of cooling and heating.
  • the choice of inverting the cycle by exchanging the external circuits of the thermal user(s) and of the heat sink with each other releases the switching of the two operating modes of the configuration specification of the heat pump unit.
  • Such configuration allows to make a two-stage heat pump cycle, which is particularly advantageous when the heat pump unit of the invention must be used for cooling in very hot or torrid climates.
  • Condensation temperatures about 80 °C allow an easy disposal of the heat power released at the condenser of the higher temperature heat pump cycle also in case of external ambient temperatures of 50-60 °C, typical of torrid climates, without needing to use cooling towers or similar heat disposal systems.
  • the first sub-circuit comprises a second heat exchanger adapted to perform an undercooling of the operating fluid at the higher pressure of said higher temperature heat pump cycle after the condensation of the same and selectively connectable to the external circuit of said second thermal user installation to transfer heat power released during said undercooling by the operating fluid of said higher temperature heat pump cycle thereto.
  • a second heat exchanger adapted to perform an undercooling of the operating fluid at the higher pressure of said higher temperature heat pump cycle after the condensation of the same and selectively connectable to the external circuit of said second thermal user installation to transfer heat power released during said undercooling by the operating fluid of said higher temperature heat pump cycle thereto.
  • the further increase of the evaporation enthalpy in the second sub-circuit occurs without a further increase of a corresponding electric power expended for compressing the operating fluids in the higher and lower temperature heat pump cycles.
  • the mass flow increase in the second sub-circuit implies a proportional increase of the electric power expended for compressing the operating fluid in the lower temperature heat pump, but no increase of the electric power expended for compressing the operating fluid in the higher temperature heat pump cycle. A considerable increase of the total EER of the heat pump is globally obtained.
  • At least either said first heat exchanger or said second heat exchanger is further selectively connectable to the external circuit of said first heat sink so as to perform a preheating of a heat carrier fluid coming from said heat sink by means of heat power released by the operating fluid of at least either said lower temperature heat pump cycle or said higher temperature heat pump cycle during the respective undercooling.
  • both the first heat exchanger and the second heat exchanger are selectively connectable to the external circuit of the heat sink.
  • the selective connection is such that heat exchangers may perform the respective preheating in reciprocally independent manner.
  • the heat power recovery deriving from the undercooling of the operating fluid of the lower and/or higher temperature heat pump cycle for preheating the heat carrier fluid of the heat sink allows to increase the COP of the heat pump unit of the invention when heating.
  • the operating fluid of said heat pump cycle i.e. the operating fluids of said higher temperature heat pump cycle and of said lower temperature heat pump cycle, respectively, are selected from the group consisting of: (E)-2-butene, (Z)-2-butene, 1-butylene, dimethyl ketone, methylacetylene, methyl alcohol, methylpentane, methylpropene, n-hexane, R1270, R290, R600, R600a, R601, R601a, RE-170, tetramethylmethane or RC-270.
  • the aforesaid refrigerant fluids are characterized by H-p (specific enthalpy - pressure) diagram limit curves strongly inclined towards increasing enthalpies, with inclination increasing with pressure. This advantageously allows to perform also very extreme undercooling, which, as explained above, allows to enhance all the beneficial effects on total EER or COP of the heat pump unit obtainable by means of the embodiments described above.
  • the invention in a second aspect thereof, relates to a system for cooling/heating spaces and/or for the production of sanitary hot water comprising a heat pump unit having the features described above.
  • a heat pump unit in accordance with the invention is indicated by reference numeral 1 as a whole.
  • the heat pump unit 1 is shown as part of a system 100 for cooling/heating spaces and/or for producing sanitary hot water comprising an external circuit of a first thermal user installation 10, an external circuit of a heat sink 20 and an external circuit of a second thermal user installation 12, which are shown only diagrammatically.
  • the first thermal user installation 10 may be a system for cooling spaces and the second thermal user installation 12 may be a system for producing of medium/low temperature sanitary hot water.
  • the first thermal user installation 10 may be a first system for heating spaces, e.g. a high temperature heating system
  • the second thermal user installation 12 may be a system for producing medium/low temperature or even a second heating system, e.g. a low temperature heating system.
  • the heat sink 20 may be replaced by a further thermal user installation capable of using the heat or refrigerating power otherwise disposed of by such a heat sink.
  • Fig. 1 shows a heat pump unit 1, in particular in a cooling configuration, comprising a circuit 2 for performing a heat pump cycle HPCM with a respective operating fluid.
  • the circuit 2 comprises: an evaporator S8 adapted to perform the evaporation of the operating fluid at a lower pressure of said heat pump cycle HPCM and intended to be connected, by means of a line FL2, to an external circuit of a first thermal user installation 10 in a cooling operating mode of the heat pump unit 1; a condenser S4 adapted to perform the condensation of the operating fluid at a higher pressure of the heat pump cycle HPCM and intended to be connected, by means of a line FL1, to an external circuit of a first heat sink 20 in a cooling operating mode of said heat pump unit 1; a compressor C1 adapted to take the evaporated operating fluid to the pressure lower than the higher pressure of the heat pump cycle HPCM and expansion means L1 - e.g. a lamination valve or other functionally equivalent known device - adapted to expand the operating fluids at the pressure higher than the lower pressure of the heat pump cycle HPCM.
  • an evaporator S8 adapted to perform the evaporation of the operating fluid at a lower pressure of said heat pump
  • the circuit 2 further comprises a heat exchanger S6, connected downstream of the condenser S4 and upstream of the expansion means L1, adapted to perform an undercooling of the operating fluid at the higher pressure of the heat pump cycle after condensation of the same in the condenser S4.
  • downstream and upstream refer to the directions of circulation of the fluid indicated in the figures by means of arrows and determined, in general, either by the compressors, in the case of heat pump cycle circuits, or by the circulation pumps, in the case of external thermal user installation and heat sink circuits, respectively.
  • the heat exchanger S6 is additionally selectively connectable to the external circuit of the second thermal user installation 12 to transfer the heat power released by the operating fluid during said undercooling thereto.
  • valve V9 preferably a modulating solenoid valve, arranged in a line FL3 for connecting to the external circuit of the second user system 12.
  • the heat power subtracted from the operating fluid during the undercooling thereof may thus be disposed of outside the heat pump unit 1 without influencing the operating conditions of the first thermal user installation 10, thus obtaining a considerable increase of energy efficiency of the heat pump 1, in particular of its EER.
  • such an increase is due to an increase of the refrigerating performance, determined by an increase of the evaporation enthalpy that the operating fluid may achieve at the evaporator S8, obtainable with an increase of electric compression power and/or collateral effects which contrast such a performance.
  • Fig. 1A diagrammatically shows in an H-p (specific enthalpy-pressure) diagram how a heat pump cycle of a conventional heat pump (solid line), free from the heat exchanger S6 with the aforesaid features, is modified (dashed line) in the case of the heat pump unit 1 of the invention.
  • H-p specific enthalpy-pressure
  • the operating fluid undergoes, after the condensation C-D at the condenser S4, an undercooling D-E, performed in the heat exchanger S6.
  • an undercooling positively impacts the steps of evaporating F-B performed in the evaporator S8.
  • the evaporation enthalpy increases with respect to the conventional cycle by an amount (h A -h F ), corresponding to the enthalpy performed during the undercooling D-E.
  • a cooling and/or heating method can be implemented, which in a cooling operating mode of the heat pump unit 1 comprises the steps described below.
  • the operating fluid is evaporated at a lower pressure of the heat pump cycle HPCM, putting it into heat exchange relationship with the first thermal user installation 10, in particular a cooling system from which heat power is thus subtracted.
  • the operating fluid is condensed at a higher pressure of the heat pump cycle HPCM placing it in heat exchange relationship with the heat sink 20, to which the thermal condensation power is surrendered.
  • the operating fluid is subjected to an undercooling, preferably isobar.
  • Fig. 2 shows a heat pump unit 1, which differs from that of Fig. 1 for the type of circuit 2.
  • a circuit comprises a second sub-circuit 2a adapted to perform a higher temperature heat pump cycle HPCM_HT with a respective operating fluid and a second sub-circuit 2b adapted to perform a lower temperature heat pump cycle HPCM_LT with a respective operating fluid.
  • the first and second sub-circuit 2a, 2b are connected to each other in cascading heat exchange relationship so as to perform a two-stage heat exchange cycle HPCM as a whole.
  • the first sub-circuit 2a comprises the condenser S4 described above with reference to the embodiment shown in Fig. 1 , expansion means L2, a compressor C2 and an evaporator.
  • the second sub-circuit 2b comprises the evaporator S8, the heat exchanger S6, the compressor C1 and the evaporation means L1 described above with reference to the embodiment Fig. 1 , and a condenser in heat exchange relationship with the first sub-circuit 2a.
  • the condenser of the second sub-circuit 2b and the evaporator of the first sub-circuit 2a are preferably integrated in a single heat exchange device S7, for the purpose of greater constructive compactness and a better heat exchange efficiency.
  • Embodiments in which such components are separated and placed in heat exchange relationship by means of an intermediate circuit for the circulation of an appropriate heat carrier fluid are not excluded in any case.
  • a two-stage configuration of the heat pump unit 1 is particularly advantageous in the case of use for cooling in very hot or torrid climates regions. Indeed, the heat condensation temperatures obtainable in this case at the condenser S4 allow in all cases an easy disposal of the condensation heat power in the outside environment, without needing to increase the evaporation temperature in the evaporator S8 and thus limiting the cooling performance.
  • the heat exchanger S5 is adapted to perform an undercooling of the operating fluid of the higher temperature heat pump cycle HPCM_HT after condensation of the same and is connectable in selectable manner to the external circuit of the second thermal user installation 12 to transfer thereto the heat power released by the operating fluid during said undercooling.
  • the selective connection of the heat exchanger S5 to the external circuit of the second thermal user installation 12 is performed by means of a valve V12, preferably a modulating solenoid valve.
  • the undercooling of the operating fluid in the first sub-circuit 2a by means of the heat exchanger S5 advantageously contributes to a further increase of the enthalpy which can be implemented at the evaporator S8 and thus to improving the EER of the heat pump unit 1.
  • Fig. 2A diagrammatically shows in an H-p (specific enthalpy-pressure) diagram how a two-stage heat pump cycle of a conventional heat pump (solid line), free from the heat exchangers S6 and S5 with the aforesaid features, is modified (dashed line) in the case of the embodiment shown in Fig. 2 by the heat pump unit 1 of the invention.
  • H-p specific enthalpy-pressure
  • the undercooling operations D'-E' and E-H, performed in the higher temperature heat pump cycle HPCM_HT by the heat exchanger S5 and in the lower temperature heat pump cycle HPCM_LT by the heat exchanger S6, determine an increase of the evaporation enthalpy performed at the evaporator S8 (G-B transformation) equal as a total to (h A -h G ) > (h A -h F ), where (h A -h F ) is the increase of the evaporation enthalpy which would be obtained by performing an undercooling only of the higher temperature heat pump cycle HPCM_HT.
  • such heat exchangers are preferably arranged so as to transfer the respective undercooling heat powers to the second thermal user installation 12 independently from each other, i.e. by operating in parallel on two different heat carrier fluid flows of the second thermal user installation 12.
  • compressors C1 and C2 are variable flow rate compressors, e.g. capacity step compressors or with inverter. This guarantees a better adaptability of the heat pump unit 1 to possible heat exchange imbalances between the higher temperature heat pump cycle HPCM_HT and the lower temperature heat pump cycle HPCM_LT which may occur as a result of the undercooling operations. Such a greater adaptability has a positive influence on the total energy efficiency of the heat pump unit 1, all other conditions being equal.
  • Fig. 3A and Fig. 3B show a first preferred embodiment of the heat pump unit 1 adapted for either cooling or heating, i.e. of the reversible type.
  • switching means are provided in this embodiment adapted to allow to exchange the external circuit connections of the first thermal user installation 10 and of the heat sink 20 with the evaporator S8 and the condenser S4, respectively.
  • switching means comprise two four-way valves V1 and V2, preferably solenoid valves, appropriately arranged in the lines for connecting the aforesaid external circuits to the evaporator S8 and the condenser S4.
  • the external circuit of the first thermal user installation 10 is connected to the evaporator S8, while the external circuit of the heat sink 20 is connected to the condenser S4, in manner similar to the previously described embodiments.
  • the external circuit of the first thermal user installation 10 is connected to the condenser S4, so as to provide the required heat power to such an installation, while the external circuit of the heat sink 20 is connected to the evaporator S8.
  • the heat exchanger S6 and/or the heat exchanger S5 are additionally selectively connectable to the external circuit of the heat sink 20 so as to perform, in the heating operating mode of the heat pump unit 1, a preheating of the heat carrier fluid coming from said heat sink 20 by means of the heat power released by the operating fluid of the lower temperature heat pump cycle HPCM_LT and/or of the higher temperature heat pump cycle HPCM_HT during the respective undercooling operations.
  • switching means are provided, in particular a three-way valve V8, preferably a solenoid valve, adapted to connect the aforesaid heat exchangers alternatively either to line FL3 or to line FL2.
  • both heat exchangers S6 and S5 are selectively connectable to the external circuit of the heat sink 20
  • the connections are arranged so that the heat exchangers may preheat the heat carrier fluid of the heat sink 20 independently from each other, i.e. working in parallel on two different flows of a heat carrier fluid of the heat sink 20.
  • the heat exchanger S5 is connected to a first branch FL2' of the line FL2 for connecting to the external circuit of the heat sink 20.
  • a valve V7 preferably a modulating solenoid valve, is present in the first branch FL2'.
  • a heat exchanger S6 is instead connected to a second branch FL2", in parallel with the first branch FL2', of the line FL2.
  • line FL2 also comprises, in this case, a first manifold M1 connected upstream of the heat exchanger S6 and S5 and a second manifold M2 connected upstream of the evaporator S8 and downstream of the valves V6 and V7.
  • Manifolds M1 and M2 are preferably connected by means of a bypass line BPL for bypassing the branches FL2' and FL2", provided with a valve V5, also preferably a modulating solenoid valve.
  • a modulation or closing of the valve V6 and/or of the valve V7 is compensated by means of a corresponding modulation or opening of the valve V5, in order to maintain a constant flow of the heat carrier fluid of the heat sink 20 in the evaporator S8.
  • valves V9 and V12 are either completely or partially open.
  • An adjustment of the degree of opening of the valves V9 and V12 allows to adjust the heat power transferred to the heat carrier fluid of the second thermal user installation 12, and consequently the entity of the undercooling carried out in the heat exchangers S6 and S5.
  • valves V6 and V7 are either completely or partially open.
  • An adjustment of the degree of opening of the valves V6 and V7 allows to adjust the heat power transferred to the heat carrier fluid 20 before it reaches the evaporator S8, and consequently the entity of the undercooling carried out in the heat exchangers S6 and S5.
  • each of such pairs may be replaced by a three-way valve arranged so as to perform the functions of the corresponding two-way valves described above.
  • Fig. 4A and Fig. 4B show a second preferred embodiment of the heat pump unit 1 which differs from that of Fig. 3A and Fig. 3B in that it can also serve in dedicated manner both in a cooling configuration ( Fig. 4A ) and a heating configuration ( Fig. 4B ), a further thermal user installation 13 for the production of sanitary hot water, in addition to the thermal user installations 10 and 12.
  • This embodiment allows in particular to serve a thermal user installation for the production of hot temperature sanitary hot water.
  • the production of high temperature hot water, in particular higher than 60 °C, is required in all cases in which the possible occurrence of Legionella must be prevented (hospitals, swimming pools and sports centers, military quarters etc.).
  • Fig. 4A and Fig. 4B includes, by way of example, that the heat exchange with the thermal user installation 13 occurs indirectly at a thermal accumulator (boiler) 13a, but other solutions known to a person skilled in the art to connect the heat pump unit 1 to the external circuit of such a thermal user installation are also possible.
  • connections for an external circuit of the thermal user installation 13 and of the two three-way valves V11 and V3, preferably solenoid valves, are additionally provided in this case.
  • the three-way valve V11 is provided so as to allow, in the cooling operating configuration ( Fig. 4A ), to connect line FL1 to the external circuit of the thermal user installation 13. In this manner, it is possible to exploit the heat power released by the condenser S4 to produce high temperature sanitary hot water instead of dispersing such a power at the heat sink 20.
  • the three-way valve V3 is provided so as to allow, in the heating configuration ( Fig. 4B ), to connect line FL1 alternatively to the external circuit of the thermal user installation 10 or to the external circuit of the thermal user installation 13. In this manner, it is possible to use the heat power released at the condenser S4 alternatively either for heating or for producing high temperature sanitary hot water.
  • Fig. 5A and Fig. 5B show a third preferred embodiment of the heat pump unit 1, which, with respect to the embodiment shown in Fig. 4A and Fig. 4B , allows to satisfy low temperature sanitary hot water needs by means of the thermal user installation 13 in addition to the aforesaid production of sanitary hot water.
  • the embodiment in Fig. 5A and Fig. 5B differs from that of Fig. 4A and Fig. 4B in particular for the presence of a further three-way valve V4, preferably a solenoid valve.
  • the three-way valve V4 is set so as to allow to selectively also connect the lines FL2' and FL2", in which the heat exchangers S5 and S6 are connected, to the external circuit of the thermal user installation 13 for the production of sanitary hot water in order to create a closed circuit therewith.
  • the heat power released at the two heat exchangers S5 and S6 alternatively to produce sanitary hot water, and in cooling configuration ( Fig. 5A ) and in heating configuration ( Fig. 5B ), or for preheating the heat carrier fluid of the heat sink 20, in the heating configuration.
  • Such means preferably comprise a three-way valve V13, preferably a solenoid valve, arranged between the external circuit of the thermal user installation 10 and the external circuit of the thermal user installation 13.
  • the external three-way valve V13 in combination with the aforesaid three-way valve V11 of the heat pump unit 1, allows to connect the line FL1 to the external circuit of the thermal user installation 13 bypassing the external circuit of the thermal user installation 10.
  • the three-way valve V11 connects the line FL1 to the external circuit of the thermal user installation 13, while the external three-way valve V13 allows to bypass the external circuit of the thermal user installation 10. In this manner, it is possible to exploit the heat power released by the main condenser S4 to produce high temperature sanitary hot water instead of dispersing such a power at the heat sink 20.
  • This operation mode requires circuit FL1 to be a closed circuit.
  • the heat pump unit 1 preferably also comprises a programmable control unit (not shown in the figures).
  • a control unit may be appropriately programmed for controlling the opening/closing, the modulation or diversion of the valves, as well as the switching on/off, the capacity degree or rpm of the compressors present in each embodiment of the heat pump unit 1.
  • the operating fluids used in the heat pump cycles performed in the heat pump unit 1 may be reciprocally equal or different.
  • the first two features mentioned above are particularly relevant for embodiments or operating conditions in which extreme undercooling is used, while the third is particularly relevant for all other embodiments or operating conditions in which extreme overheating is used.
  • the following operating fluids have proven to be particularly advantageous to obtain the best performance of the heat pump unit 1: (E)-2-butene, (Z)-2-butene, 1-butylene, dimethyl ketone, methylacetylene, methyl alcohol, methylpentane, methylpropene, n-hexane, R1270, R290, R600, R600a, R601, R601a, RE-170, tetramethylmethane or RC-270.
  • these operating fluids have the advantage of being so-called "natural" refrigerants, i.e. not harmful for the environment in terms of negative effects on atmospheric ozone nor from the point of view of greenhouse effect.
  • the pump is preferably also provided with means for detecting and evacuating gas leaks.
  • Fig. 6 shows another embodiment of the heat pump unit 1 comprising a system for detecting and evacuating gas leaks.
  • the system for detecting and evacuating gas leaks comprises at least one gas detector 31, positioned as close to the bottom of the heat pump unit 1 as possible and ventilation means 32, activatable by the gas detector 31 and arranged so that their intake is also near the bottom of the heat pump unit 1, while their delivery is connected to a gas evacuation pipe in communication with the outside environment.
  • a specific control device 34 adapted to receive signals from the gas detector 31 and to control the ventilation means 32 as a consequence may be provided.
  • the control device 34 may also control acoustic and/or light warning means 35, if provided, and/or may be configured to send alarm signals to a possible external monitoring/supervising system (not shown).
  • the functions of the control device 34 may also be carried out by the programmable control unit of the heat pump unit 1.

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  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
  • Steam Or Hot-Water Central Heating Systems (AREA)

Claims (6)

  1. Unité de pompe à chaleur (1) comprenant deux circuits (2a, 2b), dans laquelle lesdits deux circuits (2a, 2b) comprennent un premier sous-circuit (2a) conçu pour effectuer un cycle de pompe à chaleur à température plus haute (HPCM_HT) avec un fluide de fonctionnement respectif, et un deuxième sous-circuit (2b) conçu pour effectuer un cycle de pompe à chaleur à température plus basse (HPCM_LT) avec un fluide de fonctionnement respectif, dans laquelle lesdits premier et deuxième sous-circuits sont en relation d'échange de chaleur en cascade l'un avec l'autre de manière à effectuer globalement un cycle de pompe à chaleur en deux phases, lesdits deux circuits comprenant :
    - un évaporateur (S8) conçu pour effectuer l'évaporation du fluide de fonctionnement à une pression plus basse du cycle de pompe à chaleur à température plus basse (HPCM_LT) et destiné à être raccordé à un circuit externe d'une première installation d'utilisateur thermique (10) dans un mode de fonctionnement de refroidissement de ladite unité de pompe à chaleur (1) ;
    - un condensateur (S4) conçu pour effectuer la condensation du fluide de fonctionnement à une pression plus haute du cycle de pompe à chaleur à température plus haute (HPCM_HT) et destiné à être raccordé à un circuit externe d'un premier dissipateur de chaleur (20) dans un mode de fonctionnement de refroidissement de ladite unité de pompe à chaleur (1) ; et
    - un premier échangeur de chaleur (S6), conçu pour effectuer un sous-refroidissement du fluide de fonctionnement à la pression plus haute du cycle de pompe à chaleur à température plus haute (HPCM_HT) après la condensation de ce dernier,
    caractérisée en ce que
    ledit premier échangeur de chaleur (S6) est sélectivement raccordable à un circuit externe d'une deuxième installation d'utilisateur thermique (12) pour transférer à ce dernier de la puissance thermique libérée par ledit fluide de fonctionnement pendant ledit sous-refroidissement, ladite unité de pompe à chaleur (1) comprenant un moyen de commutation (V1, V2), conçu pour permettre un échange de raccordements des circuits externes de ladite première installation d'utilisateur thermique (10) et dudit premier dissipateur de chaleur (20) avec ledit évaporateur (S8) et avec ledit condensateur (S4), respectivement.
  2. Unité de pompe à chaleur (1) selon la revendication 1, dans laquelle ledit premier sous-circuit (2a) comprend un deuxième échangeur de chaleur (S5) conçu pour effectuer un sous-refroidissement du fluide de fonctionnement à la pression plus haute dudit cycle de pompe à chaleur à température plus haute (HPCM_HT) après la condensation de ce dernier et sélectivement raccordable au circuit externe de ladite deuxième installation d'utilisateur thermique (12) pour transférer à ce dernier de la puissance thermique libérée pendant ledit sous-refroidissement par le fluide de fonctionnement dudit cycle de pompe à chaleur à température plus élevée (HPCM_HT).
  3. Unité de pompe à chaleur (1) selon la revendication 1, dans laquelle au moins un dudit premier échangeur de chaleur (S6) et dudit deuxième échangeur de chaleur (S5) dans un mode de fonctionnement de chauffage de ladite unité de pompe à chaleur (1) est en outre sélectivement raccordable au circuit externe dudit premier dissipateur de chaleur (20) de manière à effectuer un préchauffage d'un fluide caloporteur provenant dudit dissipateur de chaleur (20) au moyen de la puissance thermique libérée par le fluide de fonctionnement d'au moins un dudit cycle de pompe à chaleur à température plus basse (HPCM_LT) et dudit cycle de pompe à chaleur à température plus haute (HPCM_HT) pendant le sous-refroidissement respectif.
  4. Unité de pompe à chaleur (1) selon l'une quelconque des revendications précédentes, dans laquelle le fluide de fonctionnement dudit cycle de pompe à chaleur (HPCM), ou les fluides de fonctionnement dudit cycle de pompe à chaleur à température plus haute (HPCM_HT) et dudit cycle de pompe à chaleur à température plus basse (HPCM_LT) respectivement, sont sélectionnés dans le groupe composé de : (E)-2-butène, (Z)-2-butène, 1-butylène, diméthylcétone, méthylacétylène, alcool méthylique, méthylpentane, méthylpropène, n-hexane, R1270, R290, R600, R600a, R601, R601a, RE-170, tétraméthylméthane ou RC-270.
  5. Unité de pompe à chaleur (1) selon l'une quelconque des revendications précédentes, comprenant des moyens (31, 32, 33, 34) pour détecter et évacuer des fuites de gaz.
  6. Système (100) pour refroidir/chauffer des environnements et/ou pour produire de l'eau chaude sanitaire, comprenant une unité de pompe à chaleur (1) selon l'une quelconque des revendications précédentes.
EP12818604.6A 2011-12-12 2012-12-12 Unité de pompe à chaleur et procédé permettant de refroidir et/ou de chauffer au moyen de ladite unité de pompe à chaleur Active EP2791589B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IT001134A ITTO20111134A1 (it) 2011-12-12 2011-12-12 Unita' a pompa di calore e procedimento per raffrescare e/o riscaldare tramite tale unita' a pompa di calore
PCT/IB2012/057221 WO2013088358A1 (fr) 2011-12-12 2012-12-12 Unité de pompe à chaleur et procédé permettant de refroidir et/ou de chauffer au moyen de ladite unité de pompe à chaleur

Publications (2)

Publication Number Publication Date
EP2791589A1 EP2791589A1 (fr) 2014-10-22
EP2791589B1 true EP2791589B1 (fr) 2019-11-20

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EP12818604.6A Active EP2791589B1 (fr) 2011-12-12 2012-12-12 Unité de pompe à chaleur et procédé permettant de refroidir et/ou de chauffer au moyen de ladite unité de pompe à chaleur

Country Status (4)

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US (1) US20140338377A1 (fr)
EP (1) EP2791589B1 (fr)
IT (1) ITTO20111134A1 (fr)
WO (1) WO2013088358A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016213680A1 (de) 2016-07-26 2018-02-01 Efficient Energy Gmbh Wärmepumpensystem mit CO2 als erstem Wärmepumpenmedium und Wasser als zweitem Wärmepumpenmedium
DE102016213679A1 (de) 2016-07-26 2018-02-01 Efficient Energy Gmbh Wärmepumpensystem mit eingangsseitig und ausgangsseitig gekoppelten Wärmepumpenanordnungen

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Publication number Priority date Publication date Assignee Title
DE3311505A1 (de) 1983-03-26 1984-09-27 Peter 2351 Hasenkrug Koch Waermepumpen-einrichtung
JPS61149759A (ja) * 1984-12-21 1986-07-08 Mitsubishi Electric Corp ヒ−トポンプ式給湯装置
FR2630816B1 (fr) * 1988-04-28 1991-01-11 Electrolux Cr Sa Centrale frigorifique alimentant des enceintes a au moins deux temperatures et procede de degivrage d'une telle centrale
US5727393A (en) * 1996-04-12 1998-03-17 Hussmann Corporation Multi-stage cooling system for commerical refrigeration
US5921092A (en) * 1998-03-16 1999-07-13 Hussmann Corporation Fluid defrost system and method for secondary refrigeration systems
US6094925A (en) * 1999-01-29 2000-08-01 Delaware Capital Formation, Inc. Crossover warm liquid defrost refrigeration system
IT1396440B1 (it) 2009-10-14 2012-11-23 Innovation Factory Scarl Dispositivo di riscaldamento a ciclo termodinamico irreversibile per impianti di riscaldamento ad alta temperatura di mandata.

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None *

Also Published As

Publication number Publication date
EP2791589A1 (fr) 2014-10-22
ITTO20111134A1 (it) 2013-06-13
US20140338377A1 (en) 2014-11-20
WO2013088358A1 (fr) 2013-06-20

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