EP4343233A1 - Procédé de gestion optimisé d'une pompe à chaleur écologique - Google Patents

Procédé de gestion optimisé d'une pompe à chaleur écologique Download PDF

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Publication number
EP4343233A1
EP4343233A1 EP23193672.5A EP23193672A EP4343233A1 EP 4343233 A1 EP4343233 A1 EP 4343233A1 EP 23193672 A EP23193672 A EP 23193672A EP 4343233 A1 EP4343233 A1 EP 4343233A1
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EP
European Patent Office
Prior art keywords
compressor
temperature
operating fluid
oil
refrigerant
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
EP23193672.5A
Other languages
German (de)
English (en)
Inventor
Milena Pia VARRIANO
Samuele AMBROSINI
Roberto Alessandrelli
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Ariston SpA
Original Assignee
Ariston SpA
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Ariston SpA filed Critical Ariston SpA
Publication of EP4343233A1 publication Critical patent/EP4343233A1/fr
Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/005—Arrangement or mounting of control or safety devices of safety devices
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/08—Exceeding a certain temperature value in a refrigeration component or 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
    • F25B2500/00—Problems to be solved
    • F25B2500/19—Calculation of parameters
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21155—Temperatures of a compressor or the drive means therefor of the oil
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2116—Temperatures of a condenser
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator

Definitions

  • the object of the present invention is a thermodynamic machine, for example a heat pump, of a conditioning apparatus of a residential and/or industrial environment, based on a compression/expansion thermodynamic cycle of a low environmental impact operating fluid and capable of ensuring optimal operating conditions and maximum efficiency and performance.
  • the object of the present invention is a management method or logic of said heat pump, able to ensure optimal operating and performance conditions and preserve the functionality of the mechanical components thereof, in particular of the compressor thereof.
  • the object of the present invention is a management method or logic of a heat pump able to optimising the temperature of a low environmental impact operating fluid at the compressor discharge (hereinafter referred to as the "delivery temperature" of the compressor), so as to ensure the maximum reliability thereof (i.e., eliminating any risk of breakage and malfunction) and ensuring the same operating range ( or envelope ) of said conditioning apparatus with refrigerants having a higher GWP.
  • the invention falls within the sector of heat pump conditioning apparatuses for residential and/or industrial environments (or similar scopes), where "conditioning” is indifferently referred to as “heating” or “cooling”, preferably made by electrical energy.
  • thermodynamic apparatuses and systems that comprise at least one thermodynamic machine configured to heat or cool a heat transfer fluid (e.g. water or air) intended to reach, through specific devices and/or distribution circuits, the various rooms of said building in order to release therein part of the heat energy thereof or draw it from the same.
  • a heat transfer fluid e.g. water or air
  • thermodynamic machines are, for example, the so-called heat pumps (hereinafter also abbreviated with the acronym HP) in which an operating fluid, that circulates in a refrigerant circuit, is evaporated at low temperature, brought to high pressure, condensed and finally brought back to the evaporation pressure.
  • HP heat pumps
  • Heat pumps where the cold well consists of air and the hot well consists of water are referred to as “air-water” (or vice versa “water-air”) heat pumps.
  • the refrigerant circuit of the aforementioned heat pump may be switched between a "cooling" and a “heating” operating mode (and vice versa) with said first and second heat exchanger that may therefore operate, if necessary, either as a condenser or as an evaporator.
  • Such regulation provides that by 2030 the "equivalent CO2" (a measure that expresses the impact on global warming of a certain amount of “greenhouse-gas” compared to the same amount of “carbon dioxide”) currently attributable to greenhouse or polluting refrigerant gases is reduced by 80%.
  • R32 (or similar/equivalent refrigerants) has the drawback, compared to the refrigerants (R410A) most commonly used so far with which, in the graph in figure, is compared, of significantly increasing the delivery temperature of the heat pump compressor (obviously, the same other operating conditions being equal such as, for example, the condensation and evaporation temperatures).
  • Such technology provides that some liquid refrigerant, extracted from the highpressure side of the refrigeration cycle, is by-passed towards the compressor by means of a conduit whereon at least one expansion valve and a heat exchanger, generally a plate heat exchanger, are inserted, that works as a sub-cooler or economiser.
  • liquid refrigerant switches to the form of overheated vapour to be injected into the compressor substantially in the middle of the compression process thereof (cycle not shown in the accompanying figures).
  • Document JP6594698 discloses, for example, an air refrigerating/conditioning device comprising a refrigerating cycle using refrigerant R32 and means for controlling the opening degree of the electronic expansion valve to have a predetermined overheating degree at the delivery of the compressor.
  • the compressor delivery temperature is excessively reduced, e.g. up to below the condensation temperature of the refrigerant, with the consequent condensation thereof in the oil inside the compressor.
  • this type of compressors is in fact characterised by one or more compression chambers C2 of the refrigerant, (in the example in figure two chambers), set in rotation, in opposing phase, by an electric motor C4 and completely immersed in the lubricating oil contained in the lower part of the compressor body C1, also known as oil sump C3.
  • the refrigerant discharged from one or more compression chambers C2 at the delivery temperature is therefore forced to lap and/or cross the lubricating oil before rising up the entire body C1 of the compressor C, cool the electric motor C4 and reach the outlet and connecting pipe C5 towards a heat exchanger placed downstream (the condenser of the refrigeration cycle). It is therefore clear that due to such direct interaction, the risk of dilution of the oil by the refrigerant is particularly high and harmful.
  • the purpose of the present invention is to provide an innovative control and management logic for a heat pump, for example of a conditioning apparatus in a residential and/or industrial environment, based on a compression/expansion thermodynamic cycle of a low environmental impact (GWP) operating fluid that obviates such kind of drawbacks.
  • GWP low environmental impact
  • the object of the present invention is to provide, according to one or more variants, a management logic of said heat pump able to ensure optimal operating and performance conditions and to preserve the functionality and duration of the mechanical components thereof, in detail of the compressor thereof.
  • the object of the present invention is to indicate a management method for a heat pump able to optimise the temperature of a low environmental impact (GWP) operating fluid to the compressor discharge, without compromising the operating range ( or envelope ) of said heat pump and the reliability of the same compressor.
  • GWP low environmental impact
  • a further object of the present invention is to provide a method/logic for managing a thermodynamic machine, for example a heat pump, able to ensure optimum performance under any load condition of the same thermodynamic machine and/or rotation frequency of the compressor.
  • a heat pump of a conditioning apparatus management method/logic for a residential and/or industrial environment based on a thermodynamic compression/expansion cycle of a low environmental impact (GWP) operating fluid, in accordance with the provisions of the independent claims.
  • GWP low environmental impact
  • any dimensional and spatial term refers to the positions of the elements as shown in the annexed figures, without any limiting intent relative to the possible operating conditions.
  • conditioning apparatus is intended a thermodynamic machine set up for the heating and/or "cooling" of a residential, industrial or similar environment.
  • heat pumps preferably of the air-water type, although everything that will be said with reference thereto may be extended to any other type of heat pumps, e.g. of the water-water or air-air type, or similar/equivalent heat machines.
  • Fig. 5 therefore shows the diagram of a heat pump HP, preferably reversible for ambient cooling and/or heating (but for simplicity herein shown in heating mode), wherein an expansion/compression refrigeration cycle of an operating fluid, hereinafter simply referred to as "refrigerant", is realised.
  • refrigerant an expansion/compression refrigeration cycle of an operating fluid
  • said pump HP comprises, connected to each other by means of suitable pipes 10, at least:
  • Reference 15 also denotes a switch valve, e.g. "four-ways", that enables to convert the operation of the heat pump HP between a "cooling” mode and a “heating” mode (or vice versa).
  • the refrigerant When in "heating" mode, the refrigerant dissipates heat in the second exchanger, that therefore acts as a condenser 12, while it evaporates in the first exchanger that acts as an evaporator 11.
  • the aforementioned first heat exchanger is the condenser 11 of the refrigerant circuit, the second exchanger the relative evaporator 12.
  • the exchanger 12 is that where the heat transfer fluid intended for a user is heated or cooled, while the exchanger 11 is the one cooperating with the well where the heat yielded or subtracted from said user is absorbed or disposed of.
  • the refrigerant circuit is then completed by at least one fan 16 that moves the air F.f through the evaporator 11 while the compressor 13 may be equipped with an accumulator 17 placed upstream of the suction section thereof and adapted to prevent, as is known, refrigerant excesses, oil or impurities therein.
  • a second known refrigerant accumulator 18 (referred to as “liquid receiver ”) may be provided in the proximity of the expansion valve 14 in order to compensate for any differences or variations in the levels and quantities of said refrigerant between the condenser and the evaporator.
  • a plurality of temperature sensors is also present along the refrigeration circuit.
  • thermosensor T.f.c and T.f.f may also be provided for the measurement of the temperatures of hot well T.a and cold well T.w temperatures.
  • thermosensors at least those placed at the evaporator 11 and condenser 12, may be replaced by corresponding pressure sensors, given the known correlation between pressures and temperatures of a refrigerant fluid in phase-change.
  • the heat pump HP is configured and managed in such a way as to control the wet fraction (or percentage) of the refrigerant at the inlet of the compressor 13 by adjusting the evaporative power of the evaporator 11 and in such a way that the temperature difference between the lubricating oil of the compressor 13 and the operating fluid (refrigerant) at the delivery of the same compressor 13, is kept at least equal to or above a safety (or threshold) value such that there is no condensation of said operating fluid in said lubricant oil, thus avoiding as a consequence the dilution and the loss of the optimal chemical-physical properties thereof.
  • the temperature Toil of the lubricating oil should be always higher than the temperature Tm of the operating fluid at the delivery of the compressor 13 by at least one appropriate margin defined by a safety threshold OIL_SH; i.e. the following relationship is wished to be verified: Toil ⁇ Tm ⁇ OIL _ SH where said safety threshold OIL_SH (that shall be referred to over the course of the present description) is:
  • the wet fraction of the refrigerant at the compressor suction 13 is increased or decreased by regulating the opening degree of the expansion valve 14, placed upstream of the evaporator 11.
  • the value of the delivery temperature Tm thereof depends directly on the percentage of the wet fraction at the inlet of the compressor 13.
  • said "delivery temperature” is the temperature "read/measured” at point B, B' ; B i of the refrigeration cycle (see Figures 1-3 attached to the description), i.e. at the outlet of one or more compression chambers of the compressor 13 (see, for example, Fig. 6 ).
  • the delivery temperature Tm of the compressor 13 is therefore regulated and determined by regulating the wet fraction of the refrigerant to be compressed.
  • the heat pump HP of the invention is configured to control the percentage of wet fraction of the refrigerant entering the compressor 13 in such a way as to make the aforementioned delivery temperature Tm equal to an "optimal" delivery temperature, hereinafter referred to as "target delivery temperature or Tm_target”.
  • Said delivery temperature Tm_target that, as shall be seen, is determined for every operating condition of the heat pump HP, is that temperature that, even when using a low environmental impact refrigerant (e.g. the aforementioned R32), ensures:
  • the expansion valve 14 of the heat pump HP is preferably an electromechanical valve and the opening degree thereof is suitably piloted and regulated, for example by means of a feedback control system, as long as the delivery temperature Tm of the compressor 13 does not approximate and/or reach the aforementioned target delivery temperature Tm_target.
  • said control of the expansion valve 14 is, without any limiting intent, a control of the Proportional-Integral-Derivative type (hereinafter also briefly referred to as "PID control").
  • PID control a control of the Proportional-Integral-Derivative type
  • an "optimal" percentage of the wet fraction of the refrigerant at the compressor suction 13 corresponds to a delivery temperature Tm equal to a target delivery temperature Tm_target the value thereof is substantially determined as a function "f1" of at least:
  • said first pair of parameters preferably comprises:
  • Tm _ target ⁇ 1 SDT , SST , k , OIL _ SH
  • Tm_target may be equal to the sum between the aforementioned condensation temperature SDT, the value OIL_SH and a correction " f2 " that, in turn, is determined according to the model and technical features of the compressor 13 and of the operating conditions of the heat pump.
  • said correction f2 takes into account the heat exchange coefficients:
  • the correction coefficient k may be between 0.05 ⁇ k ⁇ 0.35, with values that are as lower as more effectively the compressor 13 of said heat pump HP is thermally insulated.
  • k may preferably be equal to 0.15, that may be possibly raised to 0.25 for safety reasons.
  • the expansion valve 14 of the heat pump HP is piloted, preferably by means of a control PID, to regulate the opening degree thereof so as to ensure a refrigerant temperature Tm at the delivery of the compressor 13 equal to Tm_target as defined above.
  • the value of the target delivery temperature of the compressor Tm target to be reached at the following instant tn+1 by operating the expansion valve 14 is therefore obtained and calculated, the constants OIL_SH, OIL_SH opt and k being known.
  • the heat pump HP is operating in a steady state, in particular if the temperatures T.f, T.c of the cold and hot well remain substantially constant, for example because there is a continuous consumption of water that subtracts from the hot well (e.g. from one of its tanks) a thermal power substantially equal to that introduced by the heat pump HP, at a certain instant tn+1 there is obtained that:
  • the subsequent values of the Tm_target provided by the logic of the invention calculated on the basis of the values of the condensation and evaporation temperatures SDT, SST read in the immediately preceding instant converge to a constant and time invariant value Tm target.
  • a heating element C7 may therefore be provided, preferably an electrical resistance C7, placed externally to the oil sump C3 of the compressor 13 (see Fig. 7 ).
  • OIL _ SH Tm ⁇ SDT * 1 + k + k * SST / 1 + k and the electrical resistance C7 will be activated if said calculated value of OIL_SH is lower than the aforementioned OIL SH min, obviously taking into account an appropriate hysteresis; in formula:
  • said minimum threshold value OIL SH min indicative for the activation or not of the electrical resistance C7, is a value lower than the safety threshold OIL_SH_opt to be ensured and maintained during the regulation of the previously described opening degree of the expansion valve 14.
  • the minimum threshold value OIL SH min for the switching on/off of said electrical resistance C7 may be set substantially equal to 5°C.
  • control and regulation of the expansion valve 14 may be associated in a synergistic and joint way with the control on the activation of the electrical resistance C7 of the compressor 13.
  • the electrical resistance C7 is first turned on to quickly heat the oil and bring the difference between the temperature thereof and that of the refrigerant to values higher than OIL_SH_min, then, once deactivated, the aforementioned regulation of the expansion valve 14 is carried out.
  • said difference OIL_SH between oil and refrigerant may be determined according to the delivery Tm, condensation SDT and evaporation SST temperatures of the heat pump HP that, as seen, vary at each regulation of the opening degree of the expansion valve 14, and by the aforementioned correction coefficient k for the heat losses to the compressor 13.
  • At least one temperature sensor may be provided for the detection of said temperature Toil of the oil of the compressor 13 adapted to the lubrication of at least the moving parts thereof (for example, as seen, for at least one or more compression chambers C2), said sensor being able to be placed, for example, in contact with the sump C3 of said compressor 13.
  • thermodynamic machine e.g., a heat pump HP
  • GWP low environmental impact refrigerant
  • the method for the management and control of a thermodynamic machine e.g., a heat pump HP
  • GWP low environmental impact refrigerant
  • the suction and compression to the compressor 13 of said refrigerant in a "wet" state i.e., characterised by an optimal percentage of liquid fraction, by suitably acting on the opening degree of the expansion valve 14 thereof (for example, by means of a feedback control).
  • the aim of the method of the invention is therefore to regulate the wet fraction of the refrigerant so as to approximate the delivery temperature Tm of the compressor 13 to a value Tm_target value, referred to as "target delivery temperature", that represents that temperature ensuring optimal performance of the machine HP and eliminates the risk of the condensation of the refrigerant in the oil of said compressor 13.
  • Tm target SDT + OIL _ SH + k * SDT + OIL _ SH ⁇ SST , where,
  • thermodynamic machines for example on heat pumps HP
  • the implementation of the method for the management and control of the invention on thermodynamic machines guarantees maximum performance and efficiency when the compressor 13 thereof, e.g. of rotary type, operates at high rotation frequency, for example at high load and/or in nominal operating conditions.
  • thermodynamic machine HP for the heating and/or cooling may operate with variable rotation frequencies, so as to adapt to the power required according to specific environmental and/or operating conditions.
  • the SEER index represents the ratio between the annual energy requirement for cooling and the consumption of electrical energy intended thereto, while SCOP identifies the seasonal performance coefficient relating to heating, indicated as the ratio between the heating annual requirement and related electrical consumption.
  • such indices are parameters that allow determining both the energy performance of the machine HP and the environmental impact thereof.
  • the aforementioned target delivery temperature Tm_target is furthermore a function of at least the rotation frequency of the compressor 13. More precisely, a "correction" factor f3, that takes into account the impact of the actual rotation frequency of the compressor 13 on the delivery temperature Tm thereof, is preferably added to said target delivery temperature Tm target.
  • said correction factor f3 makes it possible to optimise and ensure high efficiency and performance of the thermodynamic machine HP even when it operates under partial load conditions and/or with reduced rotation frequencies of the same compressor 13 with respect to a full load operation.
  • said correction factor f3 is preferably a function of at least:
  • said correction factor f3 enables to "correct" the target delivery temperature according to the low operating rotation frequencies of a compressor 13 and in a manner relative, for example, to the nominal one.
  • the coefficient k3 may be a constant, suitably predefined, or, alternatively, a function of at least:
  • the correction factor f3 may assume a negative value and therefore like Tm target opt may be lower than the Tm_target as defined in accordance with the first variant of the invention (Tm_target opt ⁇ Tm_target).
  • Tm_target opt ⁇ Tm_target.
  • optimised target temperature Tm_target_opt is recursive; that is, in accordance with what has already been seen with reference to the first variant of the invention, even in such case each regulation of said expansion valve 14, in addition to a variation of the delivery temperature Tm actually measured at the outlet of the compressor 13, there also correspond new values of the condensing SDT and evaporation SST temperatures, and of any parameters and coefficients depending on them, and therefore of the same Tm_target_opt.
EP23193672.5A 2022-09-20 2023-08-28 Procédé de gestion optimisé d'une pompe à chaleur écologique Pending EP4343233A1 (fr)

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Application Number Priority Date Filing Date Title
IT202200019236 2022-09-20

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EP4343233A1 true EP4343233A1 (fr) 2024-03-27

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001227822A (ja) * 2000-02-17 2001-08-24 Mitsubishi Electric Corp 冷凍空調装置
JP6594698B2 (ja) 2015-08-10 2019-10-23 三菱重工サーマルシステムズ株式会社 冷凍・空調装置
US20220146165A1 (en) * 2019-03-26 2022-05-12 Fujitsu General Limited Air conditioning apparatus

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001227822A (ja) * 2000-02-17 2001-08-24 Mitsubishi Electric Corp 冷凍空調装置
JP6594698B2 (ja) 2015-08-10 2019-10-23 三菱重工サーマルシステムズ株式会社 冷凍・空調装置
US20220146165A1 (en) * 2019-03-26 2022-05-12 Fujitsu General Limited Air conditioning apparatus

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