Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B13/00—Compression machines, plants or systems, with reversible cycle
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B39/00—Evaporators; Condensers
  • F25B39/04—Condensers
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F24—HEATING; RANGES; VENTILATING
  • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
  • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
  • F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
  • F24F1/46—Component arrangements in separate outdoor units
• • 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
  • F25B2313/003—Indoor unit with water as a heat sink or heat source
• • 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
  • F25B2313/004—Outdoor unit with water as a heat sink or heat source
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B2339/00—Details of evaporators; Details of condensers
  • F25B2339/04—Details of condensers
  • F25B2339/044—Condensers with an integrated receiver
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B2339/00—Details of evaporators; Details of condensers
  • F25B2339/04—Details of condensers
  • F25B2339/047—Water-cooled condensers
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B2400/00—Component parts or details not otherwise provided for in this subclass
  • F25B2400/06—Several compression cycles arranged in parallel

Definitions

• the present invention relates to a thermal installation of the type comprising: an external fluid flow and an internal fluid flow, distinct from one another; and a heat pump; said heat pump comprising: a first refrigerant circuit; and a first compressor, a condenser, a first external heat exchanger, a first internal heat exchanger, a first expansion valve and a first connection device, arranged on said first circuit; the heat pump being capable of imposing a higher pressure on the refrigerant of the first circuit downstream of the first compressor than upstream of said first compressor; each of the first external and internal heat exchangers allowing heat exchange between the refrigerant and, respectively, the external fluid flow and the internal fluid flow; the installation being configured such that, in a first configuration of the first connection device, the downstream of the first compressor is connected to the condenser, to allow the refrigerant of the first circuit to transfer energy to said condenser; and the first expansion valve is positioned upstream of the first external heat exchanger, to allow the refrigerant of the first circuit to
• the invention is particularly applicable to thermal installations for residential buildings.
• Heat pumps can reduce energy consumption by a factor of three to four compared to fossil fuel heating systems such as gas or oil boilers. Furthermore, using heat pumps reduces the building's carbon footprint.
• fluorinated refrigerant such as HFC-134a.
• HFC-134a fluorinated refrigerant
• GWP global warming potential
• the present invention aims to provide a thermal installation capable of performing several functions, such as domestic heating, air conditioning and domestic hot water heating, while requiring a reduced quantity of refrigerant.
• the invention relates to a thermal installation of the aforementioned type, in which: the heat pump further comprises: a second refrigerant circuit, separate from the first circuit; and a second compressor, a second external heat exchanger, a second internal heat exchanger, a second expansion valve and a second connection device, arranged on said second circuit; the heat pump being capable of imposing a higher pressure on the refrigerant of the second circuit downstream of the second compressor than upstream of said second compressor; each of the second external and internal heat exchangers allowing heat exchange between the refrigerant and, respectively, the external fluid flow and the internal fluid flow; and - the installation is configured so that, in a first configuration of the second connection device, the downstream of the second compressor is connected to the second external heat exchanger, to allow the refrigerant of the second circuit to transfer energy to the external fluid flow.
• the invention further relates to a first method of operating a thermal installation as described above, in which each of the first and second connection devices is in its first configuration.
• the flow of external fluid and a speed of the second compressor are regulated so that a temperature of the external fluid at the outlet of the second external heat exchanger is equal to a temperature of said external fluid at the inlet of the first external heat exchanger.
• a domestic hot water temperature setpoint is lowered and an indoor air temperature setpoint is raised during a night period, compared to setpoint values during a day period.
• the invention further relates to a second method of operating a thermal installation as described above, in which each of the first and second connection devices is in its second configuration.
• a domestic hot water temperature setpoint is raised and an indoor air temperature setpoint is lowered during a night period, compared to setpoint values during a day period.
• FIGS. 1 And 2 show a thermal installation 10 according to an embodiment of the invention.
• the thermal installation 10 is integrated into a building 12, for example a dwelling.
• the thermal installation 10 comprises: an external arrangement 14; an internal arrangement 16; a domestic hot water circuit 18; and a heat pump 20.
• the thermal installation 10 also includes an auxiliary electrical resistance 22.
• the external arrangement 14 is capable of generating a flow 24 of external fluid, flowing outside the building 12.
• the external fluid is the air outside the building 12; and the external arrangement 14 includes an external fan 26 capable of generating the flow 24 of outside air.
• the interior arrangement 16 is capable of generating an internal fluid flow 28, flowing inside the building 12.
• the internal fluid is the air inside the building 12; and the interior arrangement 16 includes an internal fan 30 capable of generating the internal air flow 28.
• the interior arrangement 16 includes a solid particle filter 32.
• the internal fluid is a water loop flowing inside building 12.
• the domestic hot water circuit 18 is intended to supply building 12 with domestic hot water.
• This circuit 18 includes, in particular: a domestic hot water storage tank 34; and a water inlet and outlet opening onto said tank.
• the auxiliary electric heating element 22 is in thermal contact with the water in the tank 34.
• the heat pump 20 is intended to provide both thermal regulation and domestic hot water heating for building 12.
• the heat pump 20 has a first 40 and a second 42 refrigerant circuits, separate from each other. More specifically, the heat pump 20 is configured so that the refrigerant in the first circuit 40 and the refrigerant in the second circuit 42 do not mix.
• the heat pump 20 further comprises: a first compressor 44, a condenser 46, a first external heat exchanger 48, a first internal heat exchanger 50, a first expansion valve 52 and a first connection device 54, arranged on said first circuit 40.
• the heat pump 20 also includes: a second compressor 56, a second external heat exchanger 58, a second internal heat exchanger 60, a second expansion valve 62 and a second connection device 64, arranged on the second circuit 42.
• the heat pump 20 also includes an electronic control module 66.
• the heat pump 20 also includes one or more temperature and/or pressure sensors (not shown), connected to said electronic module 66. Said sensors are notably located on the first 40 and second 42 circuits of refrigerant fluid and/or on the flows 24, 28 of external and internal fluid and/or in the domestic hot water tank 34.
• the first refrigerant circuit 40 comprises several branches connected by junctions.
• the first refrigerant circuit 40 includes a first 68 and a second 70 junctions known as "T-junctions".
• a T-junction is defined as a junction joining three branches of the first circuit 40.
• the first compressor 44 is capable of compressing the refrigerant of the first circuit 40, so as to determine a direction of circulation of said refrigerant.
• the first compressor 44 is considered to be located on the first circuit 40 between a first upstream point 72 and a first downstream point 74.
• low-pressure gaseous refrigerant enters said first compressor at the first upstream point 72 and exits at high pressure at the first downstream point 74.
• the first upstream point 72 i.e. the low pressure side of the first compressor 44, is connected to the first T-junction 68 of the first circuit 40.
• the first compressor 44 is a fixed speed compressor.
• the condenser 46 is positioned in thermal contact with the domestic hot water tank 34, so as to transfer heat to the domestic hot water.
• the condenser 46 is preferably designed with a reduced internal volume to require only a small quantity of refrigerant. For example, it is a condenser such as the one described in the document FR2963416 on behalf of the Plaintiff.
• one end of the condenser 46 is connected to the second T-junction 70.
• the first external heat exchanger 48 is located on the external fluid stream 24.
• the first external heat exchanger 48 is an air/refrigerant heat exchanger, located on the external air stream 24.
• the ends of the first external heat exchanger 48 are connected respectively to the first 68 and the second 70 T-junctions.
• the first internal heat exchanger 50 is located on the internal fluid stream 28.
• the first internal heat exchanger 50 is an air/refrigerant heat exchanger, located on the internal air stream 28.
• one end of the first internal heat exchanger 50 is connected to the second T-junction 70.
• each of the first external heat exchangers 48 and internal heat exchangers 50 is a reversible heat exchanger, capable of operating in condenser mode or evaporator mode.
• the first external heat exchangers 48 and internal heat exchangers 50 are designed with a reduced internal volume to require only a small amount of refrigerant.
• the first expansion valve 52 is located between the first external heat exchanger 48 and the second T-junction 70.
• the first connection device 54 includes a first four-way valve 76.
• the first connection device 54 also includes non-return valves 78, 80.
• the first four-way valve 76 is connected to the downstream 74 of the first compressor 44, to a second end of the condenser 46, to the first T-junction 68 and to a second end of the first internal heat exchanger 50.
• a first non-return valve 78 is arranged between the first end of the condenser 46 and the second T-junction 70.
• a second non-return valve 80 is arranged between the first end of the first internal heat exchanger 50 and the second T-junction 70. Each of the valves 78, 80 prevents the circulation of fluid from said second junction 70.
• the second compressor 56 is capable of compressing the refrigerant of the second circuit 42, so as to determine a direction of circulation of said refrigerant.
• the second compressor 56 is considered to be located on the second circuit 42 between a second upstream point 82 and a second downstream point 84.
• low-pressure gaseous refrigerant enters said second compressor at the second upstream point 82 and exits at high pressure at the second downstream point 84.
• the second compressor 56 is a variable speed compressor, in particular an inverter type compressor.
• the second external heat exchanger 58 is located on the external fluid stream 24.
• the second external heat exchanger 58 is an air/refrigerant heat exchanger, located on the external air stream 24.
• the first 48 and second 58 external heat exchangers are arranged in series. More preferably, the second external heat exchanger 58 is arranged downstream of the first external heat exchanger 48.
• the second internal heat exchanger 60 is located on the internal fluid stream 28.
• the second internal heat exchanger 60 is an air/refrigerant heat exchanger, located on the internal air stream 28.
• the first 50 and second 60 internal heat exchangers are arranged in series with respect to the internal airflow 28. Such an arrangement allows for maximum utilization of the two compressors 44 and 56.
• the second indoor heat exchanger 60 is arranged upstream of the first indoor heat exchanger 50. In an alternative not shown, the second indoor heat exchanger 60 is arranged downstream of the first indoor heat exchanger 50.
• filter 32 is positioned upstream of the first 50 and second 60 internal heat exchangers, relative to the internal air flow 28.
• each of the second external heat exchangers 58 and internal heat exchangers 60 is a reversible heat exchanger, capable of operating in condenser mode or evaporator mode.
• the second external heat exchangers 58 and internal heat exchangers 60 are designed with a reduced internal volume to require only a small amount of refrigerant.
• the second expansion valve 62 is located between the second external heat exchanger 58 and the second internal heat exchanger 60.
• the second connection device 64 includes a second four-way valve 86. This second valve 86 is connected to the upstream 82 and downstream 84 of the second compressor 56 and to the second external 58 and internal 60 heat exchangers.
• the electronic control module 66 is in communication with the outdoor fan 26 and indoor fan 30, with the first 44 and second 56 compressors and with the first 76 and second 86 four-way valves.
• the second expansion valve 62 is an electronic expansion valve, also communicating with the electronic control module 66.
• Such an electronic expansion valve allows for better adaptation to power variations in the second circuit 42, induced by the second variable-speed compressor 56.
• the first four-way valve 76 is in a first position. In said first position of the first valve 76, the downstream 74 of the first compressor 44 is connected to the second end of the condenser 46; and the first T-junction 68 is connected to the first internal heat exchanger 50.
• the first four-way valve 76 is in a second position. In said second position of the first valve 76, the downstream 74 of the first compressor 44 is connected to the first internal heat exchanger 50; and the second end of the condenser 46 is connected to the first T-junction 68.
• the second four-way valve 86 is in a first position. In said first position of the second valve 86, the downstream 84 of the second compressor 56 is connected to the second external heat exchanger 58; and the second internal heat exchanger 60 is connected to the upstream 82 of said second compressor 56.
• the second four-way valve 86 is in a second position. In said second position of the second valve 86, the downstream 84 of the second compressor 56 is connected to the second internal heat exchanger 60; and the second external heat exchanger 58 is connected to the upstream 82 of said second compressor 56.
• FIG. 3 represents a preferred embodiment of the first 48 and second 58 external heat exchangers.
• the heat pump 20 includes an exchanger block 90.
• An orthonormal basis (X, Y, Z) is considered associated with said exchanger block 90.
• the exchanger block 90 is an air/refrigerant exchanger, intended to be traversed by the flow 24 of outside air, said flow 24 moving parallel to the direction X.
• the heat exchanger block 90 comprises a first 92 and a second 94 refrigerant circuits. These first 92 and second 94 circuits are arranged respectively on the first 40 and second 42 refrigerant circuits.
• the heat exchanger block 90 thus forms the first 48 and second 58 external heat exchangers, configured as a single unit.
• the heat exchanger block 90 is configured so that the second network 94 is located downstream of the first network 92 with respect to the outside air flow 24. As indicated above, the second outdoor heat exchanger 58 is located downstream of the first outdoor heat exchanger 48 with respect to said flow 24.
• the exchanger block 90 comprises: a plurality of fins 96; a plurality of first 98 and second 99 tubes; and a plurality of first 100 and second 101 connections.
• the fins 96 are configured to facilitate heat exchange with the outside airflow 24.
• the fins 96 are parallel to each other and arranged in (X, Z) planes. Only one fin 96 is visible in the cross-sectional view of the figure 3 .
• Each tube 98, 99 passes through the fins 96 and extends between two ends.
• the tubes 98, 99 are parallel to each other and to the Y direction.
• Each tube 98, 99 is configured to receive circulating refrigerant.
• the fins 96 and the tubes 98, 99 are designed to facilitate heat exchange between said refrigerant and the outside air flow 24.
• the first tubes 98 are included in the first network 92 and the second tubes 99 are included in the second network 94. In the embodiment shown, the first tubes 98 are arranged upstream of the second tubes 99 with respect to the outside air flow 24.
• the first connections 100 are arranged at the ends of the first tubes 98, so as to form the first network 92.
• the first tubes 98 are connected in series and/or in parallel by the first connections 100.
• the first network 92 has three parallel branches, arranged on the first refrigerant circuit 40 and forming the first external heat exchanger 48.
• the second connections 101 are arranged at the ends of the second pipes 99, so as to form the second network 94.
• the second pipes 99 are connected in series and/or in parallel by the second connections 101.
• the second network 94 has two parallel branches, arranged on the second refrigerant circuit 42 and forming the second external heat exchanger 58.
• the first 50 and second 60 internal heat exchangers are formed as a single unit, by an exchanger block similar to the exchanger block 90.
• an exchanger block allows the formation of heat exchangers with a reduced internal volume, requiring only a small quantity of refrigerant.
• a first operating mode of the first circuit 40 allows the production of domestic hot water by extracting heat from the outside air of the building 12.
• the first four-way valve 76 is in the first position of the figure 1 .
• the first operating compressor 44 sends gaseous refrigerant, under high pressure, towards the first four-way valve 76.
• Said first valve directs said refrigerant to the condenser 46.
• Said refrigerant then releases heat to the water in the tank 34 by condensing into a liquid state.
• the refrigerant then reaches the first expansion valve 52 via the second junction 70, and its pressure drops.
• the fluid then passes through the first external heat exchanger 48.
• This first heat exchanger operates in evaporative mode, with the refrigerant absorbing heat from the outside air as it changes to a gaseous state.
• the fluid in a low-pressure gaseous state then joins the upstream 72 of the first compressor 44 via the first junction 68.
• the first internal heat exchanger 50 is subjected to the low pressure of the first compressor 44 via the first junction 68.
• the residual refrigerant in the first internal heat exchanger 50 is therefore in a gaseous state, which minimizes its quantity.
• a second operating mode of the first circuit 40 of the heat pump 20 allows the interior air of the building 12 to be heated by extracting heat from the outside air.
• the first four-way valve 76 is in the second position of the figure 2 .
• the high-pressure gaseous refrigerant is directed to the first indoor heat exchanger 50 by the first four-way valve 76.
• This first indoor heat exchanger 50 operates in condenser mode, with the refrigerant transferring heat to the indoor airflow 28 while condensing.
• the refrigerant then passes through the second junction 70 and is sent to the first expansion valve 52, where its pressure drops. It then passes through the first external heat exchanger 48 in evaporative mode. The refrigerant evaporates, absorbing heat from the outside air stream 24. The low-pressure gaseous refrigerant then returns to the upstream side 72 of the first compressor 44 by passing through the first junction 68.
• the condenser 46 is subjected to the low pressure of the first compressor 44 via the first junction 68.
• the residual refrigerant in the condenser 46 is therefore in a gaseous state, which minimizes its quantity.
• Each operating mode of the first refrigerant circuit 40 thus allows the unused part of said first circuit to be isolated and emptied via the check valves 78, 80 and by the appropriate position of the four-way valve 76.
• a first operating mode of the second circuit 42 of the heat pump 20 allows the indoor air of the building 12 to be cooled by transferring heat to the outdoor air.
• the second four-way valve 86 is in the first position of the figure 1 .
• the second compressor 56 when running, sends gaseous refrigerant under high pressure to the second four-way valve 86.
• This second valve directs the refrigerant to the second outdoor heat exchanger 58 in condensing mode.
• the refrigerant in the second circuit 42 condenses, releasing heat to the outside air stream 24.
• the refrigerant is then sent to the second expansion valve 62, where its pressure drops, and then it passes through the second internal heat exchanger 60.
• This second heat exchanger then operates in evaporative mode, with the refrigerant absorbing heat from the internal air stream 28 while evaporating.
• the low-pressure gaseous refrigerant then enters the upstream side 82 of the second compressor 56 via the second four-way valve 86.
• a second operating mode of the second circuit 42 of the heat pump 20 allows the interior air of the building 12 to be heated by extracting heat from the outside air.
• the second four-way valve 86 is in the second position of the figure 2 .
• the high-pressure gaseous refrigerant is directed to the second indoor heat exchanger 60 by the second four-way valve 86.
• This second indoor heat exchanger 60 then operates in condenser mode, with the refrigerant transferring heat to the indoor airflow 28 while condensing.
• the refrigerant is then sent to the second expansion valve 62, where its pressure decreases. It then passes through the second external heat exchanger 58 in evaporative mode. The refrigerant evaporates, absorbing heat from the outside air stream 24. The low-pressure gaseous refrigerant then enters the upstream side 82 of the second compressor 56 via the second four-way valve 86.
• a first operating method for the installation 10 will now be described.
• the first method cools the indoor air of the building 12 while simultaneously producing domestic hot water.
• each of the first 40 and second The 42 circuits of the 20-unit heat pump are in their first operating mode described above. More specifically, each of the first 76 and second 86 four-way valves is in its first position of the figure 1 .
• FIG. 3 schematically shows a temperature variation of the outside air flow 24 in the context of the first process.
• the outside air flow 24 arrives at the inlet of the first external heat exchanger 48 in evaporator mode.
• the outside air transfers energy to the refrigerant of the first circuit 40; the outside air flow 24 exits said first external heat exchanger 48 with a temperature Tmin , lower than T1 .
• the flow 24 continues its path by passing through the second external heat exchanger 58 in condenser mode.
• the outside air receives energy from the refrigerant of the second circuit 42; the outside air flow 24 exits said second external heat exchanger 58 with a temperature T2 , greater than Tmin .
• the second circuit 42 benefits from outdoor air cooled by the first circuit 40, which improves the performance of the heat pump 20.
• the electronic module 66 regulates the speeds of the outdoor fan 26 and the second variable-speed compressor 56, so that T2 equals T1 .
• the energy extracted from the outside air by the heat pump 20 is therefore zero. In other words, the energy used to produce the domestic hot water for the system 10 is entirely extracted from the indoor airflow 28 of the building 12, which is thus cooled.
• the electronic module 66 promotes the production of domestic hot water during the day, in order to cool the indoor air of building 12 by means of cooled outdoor air as described above.
• a domestic hot water temperature setpoint is lowered and an indoor air temperature setpoint is raised during a night period as defined in said electronic module 66.
• the production of domestic hot water and the cooling of the indoor air are thus favoured during the day.
• Each of the first 40 and second 42 circuits of the heat pump 20 is in its second operating mode described above. More specifically, each of the first 76 and second 86 four-way valves is in its second position of the figure 2 .
• the first 48 and second 58 external heat exchangers are arranged in series to extract heat from the outside air flow 24.
• the first 50 and second 60 internal heat exchangers are arranged in series to transfer heat to the inside air flow 28.
• the second process provides significant heating power, allowing the indoor air to quickly reach the desired heating temperature.
• the second variable-speed compressor 56 regulates the heating power according to demand.
• the electronic module 66 promotes the production of domestic hot water during the night, so as to leave the first compressor 44 available during the day for heating the indoor air.
• a domestic hot water temperature setpoint is raised and an indoor air temperature setpoint is lowered during the night period as defined in said electronic module 66.
• the production of domestic hot water is thus favoured during the night.
• a third operating method for the installation 10 will now be described.
• such a method is implemented temporarily, in the event of a failure of the second circuit 42 and/or the second compressor 56.
• the heating of the indoor airflow 28 is provided by the first circuit 40, in its second operating mode described above. Furthermore, domestic hot water production is provided by the auxiliary electric heating element 22.
• the third process ensures a minimum acceptable temperature for the indoor air flow 28, without a shortage of domestic hot water.
• system 10 minimizes the amount of refrigerant required for its operation.
• system 10 can be sized to operate with a propane (R290) charge of 150 g or less per circuit 40, 42. Therefore, a building 12 can be equipped with system 10 without any constraints regarding the building's surface area or ventilation, and with a low environmental impact.
• R290 propane
• installation 10 allows combining an air conditioning function with heating and domestic hot water functions, for better thermal comfort of building 12.

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• Engineering & Computer Science (AREA)
• Physics & Mathematics (AREA)
• Mechanical Engineering (AREA)
• Thermal Sciences (AREA)
• General Engineering & Computer Science (AREA)
• Heat-Pump Type And Storage Water Heaters (AREA)
• Other Air-Conditioning Systems (AREA)

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Citations (5)

• 2024
  • 2024-04-29 FR FR2404460A patent/FR3161727A1/fr active Pending
• 2025
  • 2025-04-29 EP EP25173071.9A patent/EP4644801A1/de active Pending

Patent Citations (5)

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