EP1746370B1 - Unité de chauffage et/ou de refroidissement - Google Patents

Unité de chauffage et/ou de refroidissement Download PDF

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Publication number
EP1746370B1
EP1746370B1 EP20060116924 EP06116924A EP1746370B1 EP 1746370 B1 EP1746370 B1 EP 1746370B1 EP 20060116924 EP20060116924 EP 20060116924 EP 06116924 A EP06116924 A EP 06116924A EP 1746370 B1 EP1746370 B1 EP 1746370B1
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EP
European Patent Office
Prior art keywords
exchanger
circuit
heating
heat
cooling unit
Prior art date
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Not-in-force
Application number
EP20060116924
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German (de)
English (en)
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EP1746370A3 (fr
EP1746370A2 (fr
Inventor
Severino Veggian
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Blue Box Group SRL
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Blue Box Group SRL
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Publication of EP1746370A2 publication Critical patent/EP1746370A2/fr
Publication of EP1746370A3 publication Critical patent/EP1746370A3/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D17/00—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces
    • F25D17/02—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating liquids, e.g. brine
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/04—Desuperheaters

Definitions

  • the present invention relates to a heating cooling unit.
  • the heating cooling unit object of the present invention in general relates to the field of conditioning systems, and more specifically to the field of systems to be installed on the building roofs, commonly called roof top systems.
  • the unit is suitable for meeting all the heating and cooling requirements normally present in the various rooms of a building for industrial, commercial and/or residential use.
  • the thermal requirements of a building essentially consist in heating the rooms in the cold season, in cooling the same in the hot season and in producing hot water for sanitary use.
  • thermo-hydraulic system provided with boiler that also ensures the production of sanitary water
  • cooling is obtained separately through a conditioning system, which normally consists of a chiller.
  • heating and cooling are preferably obtained by a single heating cooling system.
  • the system is based on a steam compression refrigeration circuit and can operate with cycle reversal as heat pump in the cold season and as chiller in the hot season.
  • the heating cooling unit respectively produces hot water or cold water for heating or cooling the various rooms of the building through localised devices, such as fan coils, or through distributed devices, such as floor or wall systems.
  • the production of hot sanitary water is carried out by a specially provided boiler.
  • a heating cooling unit suitable for alternately operating as heat pump and as a chiller is described, for example, in US patent 5088296 and in US patent 4909041 .
  • the heating cooling systems currently available on the market therefore exhibit the disadvantage of being little flexible from the operating point of view and of not allowing an integrated management of the thermal requirements of a building, with consequent disadvantages from the point of view of the overall energy efficiency.
  • the object of the present invention is to overcome the disadvantages of the mentioned prior art by providing a heating cooling unit which should allow an integrated management of the thermal requirements of a building or of a group of buildings.
  • a further object of the present invention is to provide a heating cooling unit which should allow recovering part of the heat of condensation for pre-heating hot sanitary water.
  • a further object of the present invention is to provide a heating cooling unit which should allow concurrently meeting cooling and heating requirements.
  • a further object of the present invention is to provide a heating cooling unit which should be constructively easy to make and operatively totally reliable.
  • FIG. 1 shows a diagram of the heating cooling unit according to the present invention, in accordance with a first and a second plant configuration
  • FIG. 2 shows the diagram of a refrigeration circuit used in the heating cooling unit of Figure 1 made in accordance with the first plant configuration
  • FIG. 3 shows the diagram of a refrigeration circuit used in the heating cooling unit of Figure 1 made in accordance with the second plant configuration
  • FIG. 4 shows the diagram of the heating cooling unit according to the present invention made in accordance with a third plant configuration
  • FIG. 5 shows the diagram of a refrigeration circuit used in the heating cooling unit shown in Figure 4 .
  • reference numeral 1 globally denotes the heating cooling unit according to the invention.
  • the heating cooling unit 1 is suitable for meeting all the heating and cooling requirements present in the different rooms of a building for commercial and/or residential use.
  • the heating cooling unit 1 is capable of concurrently meeting both the thermal requirements of rooms with large cubic volumes by generating conditioned air flows, and the thermal requirements of rooms with low cubic volume by feeding localised thermal devices, such as fan coils, or distributed devices, such as floor or wall systems.
  • Unit 1 further allows the production of hot water for sanitary use through a recovery of the energy that is dissipated during the operation of unit 1 itself.
  • the heating cooling unit 1 is a roof top system, that is, intended to be installed on the roof of a building. To this end, unit 1 is provided with a supporting structure (not shown in the figures) with a box shape, having an aluminium frame, a steel base and multilayer thermal insulation panels, inside which there are arranged all the operating elements of the same heating cooling unit 1.
  • the operating elements of the heating cooling unit 1 are: an air treatment station 10; a refrigeration circuit 20a, 20b, or 20c for producing a heat load and a cool load; a first and a second hydraulic circuit 30 and 40 suitable for thermally connecting the air treatment station 10 and the refrigeration circuit; a hot sanitary water production circuit 50; and a heat integration circuit 60.
  • the air treatment station 10 is suitable for generating an air flow for conditioning the main rooms of the building. To this end, station 10 is provided with special connections for the ducts conveying the air flow to the various rooms. Station 10 is capable of ensuring all the treatments normally envisaged for an air flow, that is, cooling, heating, filtering, dehumidification and humidification. In particular, it is provided with heat exchange means 11 and 12 which are suitable for regulating the temperature of said air flow and are thermally connected to the refrigeration circuit through the two hydraulic circuits 30 and 40.
  • such heat exchange means comprise a main heat exchanger 11 and a secondary heat exchanger 12, which is located downstream of the main one 11 relative to the air flow moving direction.
  • Both exchangers 11 and 12 are of the finned battery type.
  • the refrigeration circuit 20a, 20b, or 20c operates according to a steam compression cycle and is susceptible of generating a heat load for meeting the heating requirements and a cool load for meeting the cooling requirements.
  • the refrigeration circuit may be sided by the heat integration circuit 60 to meet especially high heating requirements and/or to produce hot sanitary water. Typically, this can happen in the cold season when especially low external temperatures can impair the refrigeration circuit.
  • Steam compression refrigeration cycle herein means a refrigeration cycle intended for transferring heat from a cold source to a hot source continuously treating a refrigerating fluid through an evaporation stage, a compression stage, a condensation stage and finally, a lamination stage.
  • Such cycle is carried out in a closed circuit provided with an evaporator, a compressor, a condenser, and lamination means, connected to one another in series.
  • the refrigeration circuit 20a, 20b, or 20c which shall be described in more detail hereinafter, uses as refrigerating fluid (coolant), for example, R407C or R410 (or any other "ecological" refrigerating fluid) and is provided with a first and a third heat exchanger 21a, b, c and 23a, b, c (preferably of the plate type) for exchanging heat respectively with the two hydraulic circuits 30 and 40, and is provided with a second heat exchanger 22a, b, c (preferably of the finned battery type) for exchanging heat directly with the external environment.
  • refrigerating fluid for example, R407C or R410 (or any other "ecological" refrigerating fluid) and is provided with a first and a third heat exchanger 21a, b, c and 23a, b, c (preferably of the plate type) for exchanging heat respectively with the two hydraulic circuits 30 and 40, and is provided with a second heat exchanger 22a, b, c
  • the refrigeration circuit is structured for operating without cycle reversal, whereas in other configurations, the refrigeration circuit is structured for operating with cycle reversal.
  • Cycle reversal means the possibility of operating the refrigeration circuit alternately as a chiller in the hot season for carrying out a heat transfer from the building to the external environment, and as a heat pump in the cold season for carrying out, instead, a heat transfer from the external environment to the building.
  • the first and the second hydraulic circuit 30 and 40 are suitable for thermally connecting, by a thermal carrier fluid circulating therein (preferably water), the refrigeration circuit 20a, 20b, or 20c with the heat exchange means 11 and 12 of the air treatment station 10.
  • a thermal carrier fluid circulating therein preferably water
  • the refrigeration circuit 20a, 20b, or 20c with the heat exchange means 11 and 12 of the air treatment station 10.
  • These two circuits 30 and 40 allow transferring the heat load and/or the cool load generated by the refrigeration circuit to the air flow that is treated in the air treatment station 10 so as to regulate the temperature of the latter.
  • the thermal carrier fluid circulating in the two hydraulic circuits 30 and 40 can be cold or hot according to the operating conditions of unit 1.
  • the two hydraulic circuits 30 and 40 can feed the thermal carrier fluid circulating therein to external conditioning devices (fan coils, floor or wall systems) located in the secondary rooms of the building.
  • external conditioning devices fan coils, floor or wall systems located in the secondary rooms of the building.
  • at least one between the two hydraulic circuits 30 and 40 is provided with a tank 31, 41 for allowing the storage of the thermal carrier fluid, with a delivery header 32, 42 for allowing the fluid bleeding and with a return header 33, 43 for allowing the return of the fluid itself into the circuit.
  • the hot sanitary water production circuit 50 is intended for being hydraulically connected to a water distribution network of the building and is thermally connected to one of the two hydraulic circuits 30 and 40. This circuit 50 allows partly or fully absorbing the heat load generated by the refrigeration circuit 20 in all the operating situations wherein such load is not used for conditioning the rooms and would therefore be alternatively dissipated in the environment outside the building.
  • total, “complete” or “integral transfer” of the heat load means the transfer of the heat load share available for the exchange, excluding (of course) that absorbed by all the unavoidable energy dissipations.
  • the hot sanitary water production circuit 50 comprises a pre-heating exchanger 51 and a heating exchanger 52 connected to each other in series. These two exchangers 51 and 52 preferably are of the plate type for dimension and weight reasons. Circuit 50 can be further provided with a third tank 53 for the storage of the hot sanitary water produced.
  • the heat integration circuit 60 is provided with a boiler 63 and is thermally connected, through two parallel branches, respectively to one of the two hydraulic circuits 30 and 40 and to the hot sanitary water production circuit 50.
  • This circuit 60 allows integrating the heat load of the refrigeration circuit 20a, 20b, or 20c in heating respectively the sanitary water and the thermal carrier fluid circulating in the two hydraulic circuits 30 and 40.
  • boiler 63 is of the condensation type (high efficiency) and is provided with a gas burner. The features of a condensation boiler are well known to a man skilled in the art and therefore shall not be described in detail.
  • the plant structure of the heating cooling unit 1 can be suitably calibrated on the specific thermal requirements of a building by choosing among different configurations the one that most suits the specific case.
  • the heating cooling unit 1 can be structured with plant configurations capable of meeting at the same time both heating requirements and cooling requirements. In these cases, the heating cooling unit 1 is more complex to the detriment of the weight and dimensions thereof. For buildings that over the year exhibit substantially even thermal requirements in all the rooms and that do not need concurrent cooling and heating capabilities, the heating cooling unit 1 can instead be structured with less complex plant configurations, which are characterised by smaller dimensions and lower weights.
  • the heating cooling unit 1 is structured for meeting cooling requirements or heating requirements.
  • unit 1 can produce hot sanitary water by actuating a partial recovery of the heat load generated by the refrigeration circuit 20a. Such recovery can only be carried out when unit 1 is operating in cooling mode.
  • the refrigeration circuit 20a illustrated in detail in Figure 2 , is structured for operating with cycle reversal, that is, for operating in chiller mode or in heat pump mode, and to this end it is provided with a four way valve 24a for managing the coolant circulation.
  • Circuit 20a comprises one or more compressors 25a arranged in parallel, lamination means 26a, a first 21a and a second heat exchanger 22a, susceptible of alternately operating as condenser and as evaporator, and a third exchanger 23a susceptible of operating as desuperheater.
  • the first exchanger 21a and the third exchanger 23a are both of the plate type and are thermally connected respectively to the first and the second hydraulic circuit 30 and 40.
  • the second exchanger 22a is of the finned battery type and is installed in the air treatment station 10.
  • the third exchanger 23a is located downstream of compressors 25a and is suitable for transferring only a part of the heat load to the second hydraulic circuit 40, cooling the coolant without condensing it, that is, operating in desuperheating mode. For this reason, the third exchanger 23a has a size, and therefore a weight and overall dimensions, smaller than those of the first exchanger 21a.
  • the transfer of the heat load or of the cool load from the refrigeration circuit 20a to the air treatment station 10 and to the external conditioning devices is carried out by the first hydraulic circuit 30, which as already said is thermally connected to the first exchanger 21a of the refrigeration circuit 20a.
  • the transfer of the heat load from the refrigeration circuit 20a to the air flow for post-heating and/or to the hot sanitary water for the pre-heating is instead carried out by the second hydraulic circuit 40, which as already said is thermally connected to the third exchanger 23a of the refrigeration circuit 20a.
  • the first hydraulic circuit 30 thermally connects the first heat exchanger 21a of the refrigeration circuit 20a to the main exchanger 11 of the air treatment station 10 for heating or cooling the air flow according to whether the first heat exchanger 21a operates as condenser or as evaporator.
  • the first hydraulic circuit 30 can also feed the above conditioning devices external to unit 1 and to this end it is provided with a first tank 31 for the storage of the thermal carrier fluid, as well as a first delivery header 32 and a first return header 33 for the thermal carrier fluid circulation outside the heating cooling unit 1.
  • the first tank 31 is located downstream of the first heat exchanger 21a.
  • the air flow conditioning for the main rooms of the building can be carried out as an alternative to the feeding of the conditioning devices installed in the secondary rooms.
  • the first circuit 30 is provided with a first by-pass 36 for excluding the main exchanger 11 of the air treatment station 10 from the circulation.
  • the opening the first by-pass 36 is regulated by a second three way valve 37 based on the temperature values that the air flow exhibits in input to and output from the air treatment station 10. It is understood that the second three way valve 37 can be used for regulating the inflow of thermal carrier fluid to the main exchanger 11 by a flow rate modulation.
  • the second hydraulic circuit 40 thermally connects the third exchanger 23a of the refrigeration circuit 20a, which operates as desuperheater, respectively to the secondary exchanger 12 of the air treatment station 10 for post-heating the air flow and to the pre-heating exchanger 51 of the hot sanitary water production circuit 50 for pre-heating the sanitary water.
  • the post-heating of the air flow and the pre-heating of the sanitary water can only be carried out when the refrigeration circuit 20a operates in the chiller mode, that is, when the first exchanger 21a operates as evaporator.
  • the second hydraulic circuit 40 is thermally connected to the pre-heating exchanger 51 through a closed circuit 44 which develops in parallel from a specially provided header 44a.
  • the post-heating of the air flow is preferably carried out as an alternative to the heat recovery for the production of hot sanitary water.
  • the second circuit 40 is provided with a second by-pass 46 for excluding the secondary exchanger 12 of the air treatment station 10 from the circulation.
  • the opening the second by-pass 46 is regulated by a third three way valve 47 based on the temperature values that the air flow exhibits in input to and output from the air treatment station 10. It is understood that the third three way valve 47 can be used for regulating the inflow of thermal carrier fluid to the secondary exchanger 12 by a flow rate modulation.
  • the heat integration circuit 60 uses water as circulating fluid and is hydraulically connected to the first tank 31 of the first hydraulic circuit 30 by a first branch 61 and to the heating exchanger 52 of the hot sanitary water production circuit 50 by a second branch 62. The latter is connected in parallel to the first branch 61.
  • the inflow of hot water coming from boiler 63 into the first branch 61 can be carried out as an alternative to the inflow into the second branch 62 and is regulated by a first three way valve 64 which is located at the point where the first and the second branch 61 and 62 join into the main circuit 60. It is understood that the inflow of hot water into the first branch 61 can be regulated by the first three way valve 64 so that is concurrent to the inflow into the second branch 62.
  • the thermal carrier fluid circulating into the first hydraulic circuit 30 is cold and the hot water coming from boiler 63 must never flow into the first branch 61 towards the first tank 31.
  • the heat integration circuit 60 can intervene only to integrate the pre-heating of the sanitary water carried out by the second hydraulic circuit 40.
  • the first three way valve 64 is therefore regulated so that the hot water coming from boiler 63 flows only into the second branch 62, towards the heating exchanger 52 of the hot sanitary water production circuit 50.
  • the thermal carrier fluid circulating into the first hydraulic circuit 30 is hot and the hot water coming from boiler 63 can flow also into the first branch 61.
  • the heat integration circuit 60 can intervene both to integrate the pre-heating of the sanitary water and to integrate the heating of the thermal carrier fluid of the first hydraulic circuit 30.
  • the heating of the thermal carrier fluid of the first hydraulic circuit 30 has priority over the heating of the sanitary water.
  • the opening of the first three way valve 64 is controlled by a temperature sensor 31t which is installed on the first tank 31 of the first circuit 30 and is suitable for sensing the temperature of the thermal carrier fluid contained into tank 31.
  • the first three way valve 64 allows the inflow of hot water into the second branch 62 towards the heating exchanger 52 only when sensor 31t senses a temperature of the thermal carrier fluid contained in tank 31 exceeding a predetermined threshold value.
  • the latter is set so that the thermal carrier fluid may ensure the heating of the air flow into the air treatment unit 10 and a suitable thermal feeding of the external conditioning devices.
  • the second branch 62 of the heat integration circuit 60 is provided with a third by-pass 66 for excluding the heating exchanger 52 from the circulation.
  • the opening of the third by-pass 66 is regulated by a fourth three way valve 67 based on the temperature value that the hot sanitary water exhibits in output from the heating exchanger 52.
  • the fourth three way valve 67 can be used for regulating the inflow of hot water coming from the boiler to the heating exchanger 52 by a flow rate modulation.
  • the opening of the above four three way valves 37, 47, 64 and 67 is coordinated by a logical control unit according to a predetermined operating logic based on the thermal requirements of the various building rooms.
  • the refrigeration circuit 20a is structured for operating with cycle reversal and to this end, it is provided with a four way valve 24a.
  • This valve connects four circuit lines to one another: a first line 28a which represents the delivery line of compressors 25a and wherein there is inserted the third exchanger (desuperheater) 23a; a second line 28b wherein there is inserted the second exchanger 22a; a third line 28c which represents the return line to compressors 25a; a fourth line 28d wherein there is inserted the first exchanger 21a.
  • the first exchanger 21a is connected to the second exchanger 22a by a fifth line 28e consisting of a first and a second branch 28e' and 28e" parallel to one another which join back the second exchanger 22a.
  • a third branch 28e' which connects to the second exchanger 22a by a distributor 29, branches from the second branch 28e".
  • Access to the third branch 28e'" is regulated by a first and a second solenoid valve 541 and 542 respectively inserted at the inlet of the third branch 28e'" and into the second branch 28e".
  • the lamination means 26a consist of a first thermostatic valve 26a', which is inserted into the second branch 28e" and allows the coolant flow only towards the first exchanger 21a, and of a second thermostatic valve 26a", which is inserted into the third branch 28e"' and allows the coolant flow only towards distributor 29.
  • a first and a second nonreturn valve 110 and 120 respectively inserted into the first branch 28e' and in the portion of the fifth line 28e which is comprised between the second exchanger 22a and the convergence point of the two branches 28e' and 28e".
  • the first exchanger 21a operates as evaporator and transfers the cool load (evaporation heat) to the thermal carrier fluid of the first hydraulic circuit 30, whereas the second exchanger 22a operates as condenser and dissipates the heat load (heat of condensation) to the external environment.
  • the third exchanger (desuperheater) 23a is upstream of the second exchanger 22a and can recover about 20% of the heat load transferring it to the thermal carrier fluid circulating into the second hydraulic circuit 40.
  • the residual 80% of the heat load is dissipated to the environment through the second exchanger 22a.
  • the four way valve 24a is regulated so that the coolant in output from the third exchanger (desuperheater) 23a proceeds towards the second exchanger 22a along the second line 28b.
  • the coolant gets into the second branch in parallel 28e" (deviated by the first nonreturn valve 110).
  • the first solenoid valve 541 is closed, whereas the second one 542 is open.
  • the coolant flows through the first thermostatic valve 26a' to reach the first exchanger 21a. From the latter, following the fourth line 28d, the coolant reaches the four way valve 24a and then returns to compressors 25a following the third line 28c.
  • the first exchanger 21a When the refrigeration circuit 20a operates as heat pump, typically in the cold season, the first exchanger 21a operates as condenser and transfers the heat load to the thermal carrier fluid of the first hydraulic circuit 30, whereas the second exchanger 22a operates as evaporator and transfers the cool load to the external environment.
  • the third exchanger (desuperheater) 23a In this operating mode, the third exchanger 23a is upstream of the first exchanger 21a. In this case, the heat load is used for heating the rooms and therefore cannot be used for producing hot sanitary water.
  • the third exchanger 23a is thus deactivated, interrupting the circulation of the thermal carrier fluid into the second hydraulic circuit 40.
  • the four way valve 24a is regulated so that the coolant in output from the third exchanger 23a (deactivated) proceeds towards the first exchanger 21a along the fourth line 28d.
  • the coolant gets into the first branch in parallel 28e' (deviated by the first thermostatic valve 26a') and proceeds through the second branch 28e" (deviated by the second nonreturn valve 120).
  • the second solenoid valve 542 is closed, whereas the first one 541 is open.
  • the coolant flows through the third branch 28e'" flowing through the second thermostatic valve 26a" and then enters into the second exchanger 22a through distributor 29. From the second exchanger 22a, following the second line 28d, the coolant reaches the four way valve 24a and then returns to compressors 25a following the third line 28c.
  • the heating cooling unit 1 is structured for meeting only cooling requirements or only heating requirements, similarly to what envisaged in the first configuration.
  • unit 1 can fully recover the heat load generated by the refrigeration circuit and, above all, it can carry out such recovery both when it is operating in heating (heat pump operating mode) and when it is operating in cooling (chiller operating mode).
  • the second configuration differs from the first one only in the refrigeration circuit, which is globally denoted with reference numeral 20b.
  • the remaining operating elements are totally similar to those envisaged in the first configuration and are illustrated in the same Figure 1 .
  • the description of this second configuration shall therefore focus on the refrigeration circuit 20b and shall highlight only the differences existing between the two configurations from an operating point of view. Elements in common between the two configurations shall therefore be referred to with the same alphanumerical references.
  • the refrigeration circuit 20b of this second configuration is suitable for operating with cycle reversal, that is, as chiller or as heat pump, and to this end, similarly to the first configuration, it is provided with a four way valve 24a.
  • Circuit 20b comprises one or more compressors 25a arranged in parallel, lamination means 26a, a first 21b and a second heat exchanger 22b, susceptible of alternately operating as condenser and as evaporator, and a third exchanger 23b which is susceptible of operating as condenser as an alternative to the first or second exchanger 21b and 22b.
  • the first exchanger and the third exchanger 21b and 22b are both of the plate type and are thermally connected respectively to the first and the second hydraulic circuit 30 and 40.
  • the second exchanger 22b preferably is of the finned battery type and is installed in the air treatment station 10.
  • the third exchanger 23b must not carry out the desuperheating of the coolant only, but the complete condensing thereof, and therefore has a suitable size, with dimensions and weight comparable to those of the first exchanger 21b.
  • the refrigeration circuit 20b is structured differently from that of the first configuration and comprises a parallel line 200 wherein there is inserted the third exchanger 23b.
  • the third exchanger 23b can operate as an alternative to the other two exchangers 21b and 22b or it can be excluded from the circulation.
  • the refrigeration circuit 20b is substantially identical to the refrigeration circuit 20a of the first configuration and therefore, in the following description the same alphanumerical references shall be used for the elements in common.
  • the parallel line 200 branches from the first line 28a of circuit 20b in a point comprised between compressors 25a and the four way valve 24a and reconnects to the circuit at the first branch 28e' of the above fifth line 28e, downstream of the second exchanger 22b.
  • the coolant deviation towards the parallel line 200 or towards the four way valve 24a is regulated by a third and a fourth solenoid valve 310 and 320 respectively inserted at the input of the parallel line 200 and of the four way valve 24b.
  • the parallel line 200 is further provided, at the final end thereof, with a third nonreturn valve 130 which is inserted downstream of the third exchanger 23b.
  • the first exchanger 21b operates as evaporator and transfers the cool load (evaporation heat) to the thermal carrier fluid of the first hydraulic circuit 30.
  • the second and the third exchanger 22b and 23b both operate as condensers, alternating each other.
  • the heat load heat of condensation
  • the third exchanger 23b is activated, the heat load is integrally transferred to the thermal carrier fluid circulating into the second hydraulic circuit 40.
  • the third exchanger 23b can recover all the heat load for pre-heating the hot sanitary water and/or post-heating the air flow treated into the air treatment station 10.
  • the third exchanger 23b substantially has the same size as the first exchanger 21b to carry out a complete recovery of the heat load.
  • the pre-heating of the sanitary water can be carried out also concurrently to the post-heating of the air flow.
  • the coolant in output from compressors 25a finds the third solenoid valve 310 closed and the fourth one 320 open and is therefore deviated towards the four way valve 24a.
  • the latter is regulated so that the coolant proceeds towards the second exchanger 22b along the second line 28b.
  • the coolant gets into the second branch in parallel 28e".
  • the first solenoid valve 541 is closed, whereas the second one 542 is open.
  • the coolant flows through the first thermostatic valve 26a' and reaches the first exchanger 21b. From the latter, following the fourth line 28d, the coolant reaches the four way valve 24a and then returns to compressors 25a following the third line 28c.
  • the coolant in output from compressors 25a finds the first solenoid valve 310 open and the second one 320 closed and is therefore deviated into the parallel line 200.
  • the coolant flows into the first branch in parallel 28e' and then flows into the second branch in parallel 28e" (deviated by the first and the third nonreturn valve 110 and 130) to flow towards the first thermostatic valve 26a' and towards the first exchanger 21b.
  • the first exchanger 21b operates as condenser and transfers the heat load to the thermal carrier fluid of the first hydraulic circuit 30, whereas the second exchanger 22b operates as evaporator and transfers the cool load to the external environment.
  • the third exchanger 23b still operates as condenser, but as an alternative to the first exchanger 21b.
  • the heating of the thermal carrier fluid of the first hydraulic circuit 30 has priority over the heating of the sanitary water.
  • the coolant condensation can move from the first exchanger 21b to the third exchanger 23b when the temperature of the thermal carrier fluid, which is contained into the first tank 31 of the first hydraulic circuit 30, exceeds the above threshold temperature i.e when the thermal carrier fluid has such temperature as to ensure the heating of the air flow into the air treatment station 10 and a suitable thermal feeding of the external conditioning devices.
  • the coolant in output from compressors 25a finds the third solenoid valve 310 closed and the fourth one 320 open and is therefore deviated towards the four way valve 24a.
  • the latter is regulated so that the coolant proceeds towards the first exchanger 21b along the fourth line 28d.
  • the coolant gets into the first branch in parallel 28e" (deviated by the first thermostatic valve 26a') and proceeds through the second branch 28e" (deviated by the third and the second nonreturn valve 130 and 120).
  • the second solenoid valve 542 is closed, whereas the first one 541 is open.
  • the coolant flows through the third branch 28e'" flowing through the second thermostatic valve 26a" and then enters into the second exchanger 22b through distributor 29. From the second exchanger 22a, following the second line 28b, the coolant reaches the four way valve 24a and then returns to compressors 25a following the third line 28c.
  • the coolant in output from compressors 25a finds the first solenoid valve 310 open and the second one 320 closed and is therefore deviated into the parallel line 200.
  • the coolant flows into the first branch in parallel 28e', flows into the second branch in parallel 28e" (deviated by the first and the second nonreturn valve 110 and 120) and then into the third branch 28e'" to flow towards the first thermostatic valve 26a" and the second exchanger 22b.
  • the heating cooling unit 1 is capable of concurrently meeting cooling requirements and heating requirements of a building, totally recovering the heat load generated by the refrigeration circuit 20c in any operating situation.
  • the heating cooling unit 1 offers the highest operating flexibility. In fact, it can operate at the same time for cooling and for heating, or for cooling only and heating only. The production of hot sanitary water with recovery of the heat load can take place in all the three operating modes.
  • the refrigeration circuit 20c illustrated in detail in Figure 5 , unlike the other two configurations, operates without cycle reversal.
  • the refrigeration circuit 20c comprises one or more compressors 25a arranged in parallel, lamination means 26a, a first and a third heat exchanger 21c and 23c, susceptible of respectively operating only as evaporator and only as condenser, and a second exchanger 22c which is susceptible of operating as evaporator or as condenser as an alternative respectively to the first and the third exchanger 21c and 23c.
  • the third exchanger 23c has a size suitable for carrying out the coolant condensation.
  • the second exchanger 22c is of the finned battery type and is installed in the air treatment station 10.
  • the lamination means 26a comprise a first and a second thermostatic valve 26a' and 26a".
  • the first hydraulic circuit 30 is devoted only for transferring the cool load from the refrigeration circuit 20c to the air flow and/or to the external conditioning devices and therefore operates in cooling mode only. Therefore, the thermal carrier fluid circulating into the first hydraulic circuit 30 can only be cold.
  • the second hydraulic circuit 40 is devoted only for transferring the heat load from the refrigeration circuit 20c to the air flow and/or to the external conditioning devices and therefore operates in heating mode only.
  • the second hydraulic circuit 40 can also transfer the heat load to the sanitary water for pre-heating it. Therefore, in this third configuration, the thermal carrier fluid circulating into the second hydraulic circuit 40 can only be hot.
  • the first hydraulic circuit 30 thermally connects the first exchanger 21c (evaporator) of the refrigeration circuit 20c to the main exchanger 11 of the air treatment station 10 for allowing the air flow cooling.
  • the first hydraulic circuit 30 is provided with a first tank 31 for allowing the storage of the thermal carrier fluid, as well as with a first delivery header 32 and with a first return header 33 for allowing the circulation of the cold thermal carrier fluid outside the heating cooling unit 1.
  • the second hydraulic circuit 40 thermally connects the third exchanger 23c (condenser) of the refrigeration circuit 20c respectively to the secondary exchanger 12 of the air treatment station 10 for allowing the post-heating of the air flow and to the pre-heating exchanger 51 of the hot sanitary water production circuit 50 for allowing the pre-heating of the sanitary water.
  • the second circuit 40 is provided with a second tank 41 for allowing the storage of the thermal carrier fluid, as well as with a second delivery header 42 and with a second return header 43 for allowing the circulation of the hot thermal carrier fluid outside the heating cooling unit 1.
  • the second hydraulic circuit 40 can thermally connect the third exchanger 23c of the refrigeration circuit 20c to the main exchanger 11 of the air treatment station 10 for allowing the air flow heating.
  • the air flow heating must be carried out in the main exchanger 11 of the air treatment station 10, since it is provided with a larger heat exchange surface than the secondary exchanger 12.
  • the second hydraulic circuit 40 is hydraulically connected to the first hydraulic circuit 30 by means of a delivery by-pass 45a and by means of a return by-pass 45b, respectively upstream and downstream of the main exchanger 11 of the air treatment station 10.
  • Access to the delivery by-pass 45a and to the return by-pass 45b is respectively regulated by a first three way valve 451 and by a second three way valve 452.
  • the air flow conditioning for the main rooms of the building can be carried out also as an alternative to the feeding of the conditioning devices installed in the secondary rooms.
  • the first circuit 30 is provided with a first by-pass 36 for excluding the main exchanger 11 of the air treatment station 10 from the circulation.
  • the opening the first by-pass 36 is regulated by a third three way valve 37 based on the temperature values that the air flow exhibits in input to and output from the air treatment station 10.
  • the second circuit 40 is provided with a second by-pass 46 for excluding the secondary exchanger 12 of the air treatment station 10 from the circulation.
  • the opening the second by-pass 46 is regulated by a fourth three way valve 47 based on the temperature values that the air flow exhibits in input to and output from the air treatment station 10.
  • third and the fourth three way valve 37 and 47 can be used for regulating the inflow of thermal carrier fluid to the main exchanger 11 and to the secondary exchanger 12 by a flow rate modulation.
  • the heat integration circuit 60 is hydraulically connected by a first branch 61 to the second tank 41 of the second hydraulic circuit 40, and not to the first tank 31 of the first circuit 30 anymore.
  • the heat integration circuit 60 is further hydraulically connected to the heating exchanger 52 of the hot sanitary water production circuit 50 by a second branch 62, which is connected in parallel to the first one. Access to the second branch 62 is regulated by a fifth three way valve 455 located at the inlet of the second branch 62 itself.
  • the opening of the above five three way valves 451, 452, 37, 47 and 455 is coordinated by a logical control unit according to a predetermined operating logic based on the thermal requirements of the various building rooms.
  • the refrigeration circuit 20c is structured for operating without cycle reversal.
  • the refrigeration circuit 20c consists of a main loop 400, wherein there are inserted in series the first exchanger 21c (evaporator), compressors 25a, the third exchanger 23c (condenser) and the first thermostatic valve 26a', and of a secondary loop 500, which can be excluded from the circulation and wherein there are inserted the second heat exchanger 22c (condenser or evaporator) and the second thermostatic valve 26a".
  • the secondary loop 500 comprises a first branch 510, which develops in parallel to the main loop 400 downstream of the third exchanger 23c, a by-pass 520, which connects the first branch 510 directly to the compressor intake, and a second branch 530, which is connected to the second exchanger 22c by a distributor 29 and which allows excluding the first thermostatic valve 26a' and the first exchanger 21c from the circulation.
  • the second thermostatic valve 26a" is inserted in this second branch 530.
  • access to the first branch 510 is regulated by a first solenoid valve 511 inserted just after the inlet of the first branch 510 and by a second solenoid valve 512 inserted in the main loop 400.
  • the first branch 510 is provided with a nonreturn valve 513 arranged in the proximity of the point at which the first branch 510 reconnects to the main loop 400.
  • Access to by-pass 520 is regulated by a third solenoid valve 521 inserted in the by-pass itself.
  • Access to the second branch 530 is regulated by a fourth solenoid valve 531, which is inserted just after the inlet of the second branch, and by a fifth solenoid valve 541, which is inserted in the main loop upstream of the first thermostatic valve 26a'.
  • the coolant circulates only in the main loop 400.
  • the secondary loop 500 is excluded from the circulation and the second exchanger 22c is deactivated.
  • This operating mode occurs not only in the intermediates seasons, when there may be rooms in the building with opposite thermal requirements, but also in the hot season, when even if the thermal requirements of all the rooms in a building are even, in any case there may be the need of producing hot sanitary water and thus the possibility of recovering the heat load with a pre-heating, or the need of regulating the temperature of the conditioned air flow with a post-heating.
  • the third heat exchanger 23c is deactivated interrupting the circulation of the thermal carrier fluid in the second hydraulic circuit 40.
  • the heat load heat of condensation
  • the coolant in output from compressors 25a flows through the third exchanger 23c (deactivated).
  • the first solenoid valve 511 is open, whereas the second solenoid valve 512 is closed, so that the coolant flows into the first branch 510 of the secondary loop 500.
  • the coolant After dissipating the heat load to the environment through the second exchanger 22c, the coolant returns into the main loop 500 for flowing towards the first thermostatic valve 26a' and the first exchanger 21c (evaporator).
  • the third and the fourth solenoid valve 521 and 531 are closed and access to by-pass 520 and to the second branch 520 of the secondary loop 500 is therefore prevented.
  • the heating cooling unit 1 When the heating cooling unit 1 operates in heating only, for example during the cold season, the cool load cannot be used and must be yielded to the external environment. In this case, the first heat exchanger 21c is excluded from the circulation and the evaporation stage of the refrigeration cycle is carried out in the second heat exchanger 22c.
  • the coolant in output from compressors 25a yields the heat load to the thermal carrier fluid of the second hydraulic circuit 30 into the third exchanger 23c (condenser).
  • the first solenoid valve 511 is closed, whereas the second solenoid valve 512 is open.
  • the coolant continues to flow into the main loop 400 until it meets with the second branch 530 of the secondary loop 500.
  • the fourth solenoid valve 531 is open, whereas the fifth solenoid valve 541 is closed.
  • the coolant can thus flow through the second thermostatic valve 26a" and get into the second exchanger 22c (evaporator) thanks to distributor 29.
  • the coolant flows through the by-pass 520 and then returns to compressors 25a.
  • the heating cooling unit 1 cannot concurrently meet heating and cooling requirements of the building rooms. Moreover, the heat load recovery for the production of hot sanitary water is partial and limited to some special operating situations. However, unit 1 is less complex and heavy and is easier to install on a building roof. In fact, the third heat exchanger 23a has a reduced size with reduction of the overall dimensions and of the weight and the second circuit is not provided with tank and with the two headers for feeding the conditioning devices external to unit 1.
  • the heating cooling unit 1 cannot concurrently meet heating and cooling requirements of the building rooms, but the heat load recovery for the production of hot sanitary water is total and can be carried out in a greater number of operating situations.
  • unit 1 is slightly more complex and heavy, in particular due to the fact that the third heat exchanger 23b has a larger size for allowing a total recovery of the heat load and the refrigeration circuit 20b consequently is more complex.
  • the heating cooling unit 1 can meet any thermal requirements with the possibility of recovering the heat load in any operating situation.
  • unit 1 is more complex from a plant point of view, but especially heavier than the other two configurations. This can make its installation more difficult.
  • both hydraulic circuits are provided with tank and with the two headers for feeding the conditioning devices external to unit 1.

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Claims (13)

  1. Unité thermo-frigorifique, destinée à satisfaire les exigences thermiques qu'un édifice, comprenant une structure portante en forme de caisson, laquelle est destinée à être installée sur la couverture dudit édifice et à l'intérieur de laquelle sont contenus :
    - une centrale de traitement d'air (10) pour traiter un flux d'air destiné à climatiser un ou plusieurs locaux principaux dudit édifice, ladite centrale de traitement d'air (10) comprenant des moyens d'échange thermique (11 ; 12) adaptés pour réguler la température dudit flux d' air ;
    - un circuit frigorifique (20a ; 20b ; 20c), fonctionnant suivant un cycle à compression de vapeur, lequel est en mesure de fournir une charge thermique générée à partir d'un stade de condensation et une charge frigorifique générée à partir d'un stade d'évaporation ; caractérisée en ce qu'il comprend en outre :
    - un premier (30) et un deuxième circuit hydraulique (40), lesquels sont adaptés relier thermiquement, par le biais d'un fluide caloporteur circulant dans ceux-ci, ledit circuit frigorifique (20) avec les moyens d'échange thermique (11 ; 12) de ladite centrale de traitement d'air (10) pour réguler la température dudit flux d'air au moyen de la charge thermique et/ou de la charge frigorifique fournies par ledit circuit frigorifique (20), au moins un parmi lesdits deux circuits hydrauliques (30 ; 40) étant équipé d'un réservoir (31 ; 41) pour permettre l'accumulation dudit fluide caloporteur, ainsi que d'un collecteur de refoulement (32 ; 42) et d'un collecteur de retour (33 ; 43) pour permettre une circulation dudit fluide caloporteur à l'extérieur de ladite unité thermo-frigorifique (1) et alimenter des dispositifs de climatisation situés dans des locaux secondaires dudit édifice ;
    - un circuit de production d'eau chaude sanitaire (50) qui est relié thermiquement à un desdits deux circuits hydrauliques (30) et (40) pour absorber au moins en partie la charge thermique dudit circuit frigorifique (20a ; 20b ; 20c) et est destiné à être relié hydrauliquement à un réseau de distribution de l'eau dudit édifice ; et
    - un circuit d'intégration thermique (60), équipé d'une chaudière (63), laquelle peut être reliée thermiquement en parallèle avec un desdits deux circuits hydrauliques (30 ; 40) et audit circuit de production d'eau chaude sanitaire (50) pour intégrer la charge thermique dudit circuit frigorifique (20) dans le chauffage respectivement dudit fluide caloporteur et de ladite eau sanitaire.
  2. Unité thermo-frigorifique selon la revendication 1, dans laquelle les moyens d'échange thermique (11 ; 12) de ladite centrale de traitement d'air (10) comprennent un échangeur de chaleur principale (11) et un échangeur de chaleur secondaire (12) placé en aval de celui principal (11) par rapport à la direction de déplacement dudit flux d'air, et dans lequel ledit circuit de production d'eau chaude sanitaire (50) comprend un échangeur de préchauffage (51) et un échangeur de chauffage (52) reliés entre eux en série.
  3. Unité thermo-frigorifique selon la revendication 2, dans laquelle :
    - ledit circuit frigorifique (20a) est adapté pour fonctionner avec inversion de cycle et comprend une vanne à quatre voies (24a), au moins un compresseur (25a), des moyens d'étranglement (26a), un premier (21a) et un deuxième échangeur de chaleur (22a), en mesures de fonctionner alternativement comme condenseur et comme évaporateur, et un troisième échangeur de chaleur (23a) qui est placé en aval dudit au moins un compresseur (25a) et est en mesure de fonctionner comme désurchauffeur ;
    - ledit premier circuit hydraulique (30) est en mesure de relier thermiquement le premier échangeur de chaleur (21a) dudit circuit frigorifique (20a) avec l'échangeur principal (11) de ladite centrale de traitement d'air (10) pour réchauffer ou pour refroidir ledit flux d'air selon que ledit premier échangeur de chaleur (21a) fonctionne comme condenseur ou comme évaporateur, ledit premier circuit (30) étant équipé d'un premier réservoir (31), ainsi que d'un premier collecteur de refoulement (32) et d'un premier collecteur de retour (33) ;
    - ledit deuxième circuit hydraulique (40) est en mesure de relier thermiquement le troisième échangeur de chaleur (23a) dudit circuit frigorifique (20a) respectivement avec l'échangeur secondaire (12) de ladite centrale de traitement d'air (10) pour post-chauffer ledit flux d'air et avec l'échangeur de préchauffage (51) dudit circuit de production d'eau chaude sanitaire (50) pour préchauffer l'eau sanitaire ; et
    - ledit circuit d'intégration thermique (60) est relié hydrauliquement au premier réservoir (31) dudit premier circuit hydraulique (30) par l'intermédiaire d'une première branche (61) et à l'échangeur de chauffage (52) dudit circuit de production d'eau chaude sanitaire (50) par l'intermédiaire d'une deuxième branche (62), connectée en parallèle avec la première.
  4. Unité thermo-frigorifique selon la revendication 3, dans laquelle ledit troisième échangeur de chaleur (23a) est activé quand ledit premier échangeur (21a) fonctionne comme évaporateur et ledit deuxième échangeur (22a) fonctionne comme condenseur.
  5. Unité thermo-frigorifique selon la revendication 2, dans laquelle :
    - ledit circuit frigorifique (20b) est adapté pour fonctionner avec inversion de cycle et comprend une vanne à quatre voies (24a), au moins un compresseur (25a), des moyens d'étranglement (26a), un premier (21b) et un deuxième échangeur de chaleur (22b), en mesures de fonctionner alternativement comme condenseur et comme évaporateur, et un troisième échangeur (23b), lequel est en mesure de fonctionner comme condenseur en alternative par rapport audit premier (21b) ou audit deuxième échangeur (22b) ;
    - ledit premier circuit hydraulique (30) est en mesure de relier thermiquement le premier échangeur de chaleur (21b) dudit circuit frigorifique (20b) avec l'échangeur principal (11) de ladite centrale de traitement d'air (10) pour réchauffer ou pour refroidir ledit flux d'air selon que ledit premier échangeur de chaleur (21b) fonctionne comme condenseur ou comme évaporateur, ledit premier circuit (30) étant équipé d'un premier réservoir (31), ainsi que d'un premier collecteur de refoulement (32) et d'un premier collecteur de retour (33) ;
    - ledit deuxième circuit hydraulique (40) est en mesure de relier thermiquement le troisième échangeur (23b) dudit circuit frigorifique (20b) respectivement avec l'échangeur secondaire (12) de ladite centrale de traitement d'air (10) pour post-chauffer ledit flux d'air et avec l'échangeur de préchauffage (51) dudit circuit de production d'eau chaude sanitaire (50) pour préchauffer l'eau sanitaire ; et
    - ledit circuit d'intégration thermique (60) est relié hydrauliquement au premier réservoir (31) dudit premier circuit hydraulique (30) par l'intermédiaire d'une première branche (61) et à l'échangeur de chauffage (52) dudit circuit de production d'eau chaude sanitaire (50) par l'intermédiaire d'une deuxième branche (62), connectée en parallèle avec la première.
  6. Unité thermo-frigorifique selon la revendication 3 ou 5, dans laquelle ledit deuxième circuit hydraulique (40) est équipé d'un collecteur (44a) et est relié thermiquement avec ledit échangeur de préchauffage (51) par l'intermédiaire d'un circuit parallèle (44) qui s'étend à partir dudit collecteur (44a).
  7. Unité thermo-frigorifique selon la revendication 3 ou 5, dans laquelle le premier réservoir (31) dudit premier circuit hydraulique (30) est placé en aval dudit premier échangeur de chaleur (21 a ; 21b).
  8. Unité thermo-frigorifique selon la revendication 3 ou 5, dans laquelle le premier réservoir (31) dudit premier circuit hydraulique (30) est muni d'un capteur de température (31t) adapté pour évaluer la température du fluide caloporteur contenu dans ledit premier réservoir (31) et dans laquelle ledit circuit d'intégration thermique (60) utilise de l'eau comme fluide circulant et est muni d'une première vanne à trois voies (64) qui règle l'accès dudit fluide circulant provenant de ladite chaudière (63) alternativement à ladite première branche (61) et à ladite deuxième branche (62), l'ouverture de ladite première vanne à trois voies (64) étant contrôlée en fonction de la valeur de température mesurée par ledit capteur (31t).
  9. Unité thermo-frigorifique selon la revendication 2, dans laquelle :
    - ledit circuit frigorifique (20c) comprend au moins un compresseur (25a), des moyens d'étranglement (26a), un premier (21c) et un troisième échangeur (23c), lesquels sont en mesure de fonctionner respectivement comme évaporateur et comme condenseur, et un deuxième échangeur de chaleur (22c) qui est en mesure de fonctionner comme évaporateur ou comme condenseur en alternative respectivement par rapport audit premier (21c) et audit troisième échangeur (23c) ;
    - ledit premier circuit hydraulique (30) est en mesure de relier thermiquement le premier échangeur (21c) dudit circuit frigorifique (20c) avec l'échangeur principale (11) de ladite centrale de traitement d'air (10) pour refroidir ledit flux d'air, ledit premier circuit (30) étant équipé d'un premier réservoir (31), ainsi que d'un premier collecteur de refoulement (32) et d'un premier collecteur de retour (33) ;
    - ledit deuxième circuit hydraulique (40) est équipé d'un deuxième réservoir 41, ainsi que d'un deuxième collecteur de refoulement (42) et d'un deuxième collecteur de retour (43), et est en mesure de relier thermiquement le troisième échangeur (23c) dudit circuit frigorifique (20c) respectivement avec l'échangeur secondaire (12) de ladite centrale de traitement d'air (10) pour post-réchauffer ledit flux d'air et avec l'échangeur de préchauffage (51) dudit circuit de production d'eau chaude sanitaire (50) pour préchauffer l'eau sanitaire, ledit deuxième circuit hydraulique (40) étant en mesure de se relier hydrauliquement avec ledit premier circuit hydraulique (30) par l'intermédiaire d'une dérivation de refoulement (45a) et d'une dérivation de retour (45b) afin de relier thermiquement le troisième échangeur (23c) dudit circuit frigorifique (20c) avec l'échangeur principale (12) de ladite centrale de traitement d'air (10) de manière à pouvoir réchauffer ledit flux d' air ;
    - ledit circuit d'intégration thermique (60) est relié hydrauliquement par l'intermédiaire d'une première branche (61) au deuxième réservoir (41) dudit deuxième circuit hydraulique (40) et par l'intermédiaire d'une deuxième branche (62), connectée en parallèle avec la première, à l'échangeur de chauffage (52) dudit circuit de production d'eau chaude sanitaire (50).
  10. Unité thermo-frigorifique selon la revendication 9, dans laquelle ledit deuxième circuit hydraulique (40) est relié thermiquement avec ledit échangeur de préchauffage (51) par l'intermédiaire d'un circuit parallèle (44) qui s'étend à partir dudit deuxième réservoir (41).
  11. Unité thermo-frigorifique selon la revendication 3, 5 ou 9, dans laquelle le deuxième échangeur de chaleur (22a ; 22b ; 22c) dudit circuit frigorifique (20a ; 20b ; 20c) est un échangeur à batterie à ailettes et est installé dans ladite centrale de traitement d'air (10) pour échanger de la chaleur avec l'air extérieur dudit édifice.
  12. Unité thermo-frigorifique selon la revendication 3, 5 ou 9, dans laquelle le premier (21a ; 21b ; 21c) et le troisième échangeur de chaleur (23a ; 23b ; 23c) dudit circuit frigorifique (20a ; 20b ; 20c) sont des échangeurs à plaques.
  13. Unité thermo-frigorifique selon l'une quelconque des revendications précédentes, dans laquelle ledit circuit de production d'eau chaude sanitaire (50) est équipé d'un troisième réservoir (53) pour l'accumulation de ladite eau chaude sanitaire.
EP20060116924 2005-07-18 2006-07-10 Unité de chauffage et/ou de refroidissement Not-in-force EP1746370B1 (fr)

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US20130256423A1 (en) 2011-11-18 2013-10-03 Richard G. Lord Heating System Including A Refrigerant Boiler

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US4111259A (en) * 1976-03-12 1978-09-05 Ecosol, Ltd. Energy conservation system
US4199955A (en) * 1976-10-27 1980-04-29 Sun-Econ, Inc. Heat extraction or reclamation apparatus for refrigerating and air conditioning systems
US4457358A (en) * 1981-03-31 1984-07-03 Engineering Design And Management Inc. Heating and cooling system
US4513580A (en) * 1982-10-21 1985-04-30 Cooper Donald C Combined refrigeration and heating circuits
US4909041A (en) * 1984-07-27 1990-03-20 Uhr Corporation Residential heating, cooling and energy management system
US4633676A (en) * 1984-11-19 1987-01-06 Dittell Edward W Cooling and heating apparatus
AU1399988A (en) * 1987-11-03 1989-06-01 Edward W. Dittell Heat energy storage and transfer apparatus
JPH02150672A (ja) 1988-11-30 1990-06-08 Toshiba Corp 空気調和機
DE10142779A1 (de) * 2001-08-31 2003-03-27 Viessmann Werke Kg Kompaktheizgerät

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