EP4361531A1 - Pompe à chaleur à modulation étendue du dispositif d'expansion - Google Patents

Pompe à chaleur à modulation étendue du dispositif d'expansion Download PDF

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Publication number
EP4361531A1
EP4361531A1 EP23201646.9A EP23201646A EP4361531A1 EP 4361531 A1 EP4361531 A1 EP 4361531A1 EP 23201646 A EP23201646 A EP 23201646A EP 4361531 A1 EP4361531 A1 EP 4361531A1
Authority
EP
European Patent Office
Prior art keywords
opening area
aexv
max
expansion device
total opening
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
EP23201646.9A
Other languages
German (de)
English (en)
Inventor
Roberto Alessandrelli
Giorgia CAMMI
Marco Molteni
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 EP4361531A1 publication Critical patent/EP4361531A1/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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—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
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves

Definitions

  • the invention relates to a heat pump, for example for heating and/or cooling air and/or water, e.g., in a plant for heating and/or cooling rooms and/or water.
  • a heat pump comprises a circuit for the circulation of a refrigerant fluid, an evaporator (consisting of a first heat exchanger) placed in the circuit, a compressor placed in the circuit downstream of the evaporator, a condenser (consisting of a second heat exchanger) placed in the circuit downstream of the compressor, and an expansion valve placed in the circuit downstream of the condenser and upstream of the evaporator.
  • the indications "downstream” and “upstream” refer to the circulation direction of the refrigerant fluid in at least one operating mode.
  • the compressor is operable to take in the refrigerant fluid in the gaseous phase and at low pressure from the evaporator, compress the refrigerant fluid, and push it into the condenser.
  • the compressed refrigerant fluid releases heat and condensation at high pressure.
  • the refrigerant fluid passes through the expansion valve which decompresses it, bringing the refrigerant fluid into a depressurized liquid phase with a possibly lower amount of gaseous phase.
  • the depressurized liquid refrigerant fluid is conveyed into the evaporator where the refrigerant fluid absorbs heat and evaporates at low pressure, before being taken in and compressed again by the compressor.
  • the refrigerant fluid changes state inside the evaporator, switching from liquid to gaseous by absorbing heat, and inside the condenser, switching from gaseous to liquid by yielding heat.
  • the air or fluid in contact with the evaporator (or, in other words: the space where it is located) is thus cooled, whereas the air or fluid in contact with the condenser (or, in other words: the space where it is located) is heated.
  • a (four-way) switching valve which allows inverting the compression and circulation direction of the refrigerant fluid and thus switching the first heat exchanger from evaporator to condenser and the second heat exchanger from condenser to evaporator, allowing both cooling and heating the air or fluid in contact with the first and second heat exchangers (or the spaces in which they are located).
  • Known heat pumps can be used in a heating mode, e.g., in winter months, taking heat from the external air and bringing heat into a building.
  • the refrigerant fluid crosses the expansion valve and becomes a liquid-vapor mixture at low pressure, then enters into the evaporator, placed outside, where it absorbs heat until it becomes vapor at low temperature, which vapor is then taken in and compressed by the compressor with the consequent temperature increase, and the hot and compressed vapor is pushed from the compressor outlet into the condenser, which can for example be a fan coil unit placed inside the building (close to the boiler for example), and changes phase again from gas to liquid releasing the liquefaction heat.
  • the liquid refrigerant fluid returns to the expansion valve and the cycle is repeated.
  • the same heat pump can be used in a cooling mode, e.g., in the summer months, where the refrigerant fluid evaporates in the indoor fan coil unit and condenses in the outdoor heat exchange battery.
  • Heat pumps use greenhouse gas as a refrigerant fluid.
  • the reduction in global warming potential can be carried out using refrigerant fluids with low greenhouse effect properties, or by adopting technical solutions that reduce the mass of fluid required for the individual heat pump with equivalent thermal performance levels.
  • GWP global warming potential
  • flammable refrigerant fluids with low global warming potential are classified as flammable (e.g., R32, propane).
  • allowable amount limits are set or recommended in a heat pump present inside a house (or at least also extending thereto).
  • heat pumps known as splits (with units inside the house) which use flammable refrigerant fluids must thus operate with low charges of refrigerant fluid with respect for example to single-block heat pumps completely located outdoors.
  • heat pumps have to operate in a wide range of outdoor temperatures and water (or indoor) temperatures and it is known that a refrigerant fluid charge reduction in the same heat pump also reduces the operating temperature range.
  • a heat pump comprises:
  • this ratio (Aexv_max / Aexv_min) between the upper total opening area limit (Aexv_max) and the lower total opening area limit (Aexv_min) of the expansion device (8) is in the range from 22 to 26, or from 23 to 25, or 24.
  • the configuration of the expansion device and of the control system extends the total area range of the expansion device with respect to the adjustment of the opening area ranges of expansion devices during the operation of heat pumps of the prior art.
  • the expansion of the total opening area range of the expansion device, during its operation with the expansion valve open allows using a smaller amount of refrigerant fluid with substantially the same thermal and energy performance of the heat pump.
  • a heat pump comprises:
  • the configuration of the expansion device and the control system allows extending the total opening area range of the expansion device, with respect to the individual opening ranges of known and commercially available expansion valves. As will be explained hereinafter, the extension of the total opening area range of the expansion device allows using a smaller amount of refrigerant fluid with substantially the same thermal and energy performance of the heat pump.
  • the configuration of the expansion device and of the control system also allows a sufficiently fine adjustment within, and in particular at the margins, of the entire extended total opening area range, using known and commercially available expansion valves notwithstanding the known disadvantage of adjustable valves, according to which as the maximum opening area increases, the adjustment of the smaller opening areas becomes more approximate and less certain.
  • Figures 1 - 4 show typical operating ranges for a heat pump operated with R32 refrigerant, where operating points are observed in a heating mode ( figures 1 and 2 ) with high compression ratios CR (>8) at points of operation in a cooling mode ( figures 3 and 4 ) with low compression ratios CR (about 1).
  • the suction pressure of the compressor also depends on the refrigerant fluid charge, since an increase in the refrigerant fluid charge increases the amount of liquid phase in the evaporator and reduces the volume of the vapor phase that can be taken in by the compressor. Therefore, if the refrigerant charge increases, the suction pressure (absolute value) of the compressor also increases, whereas if the refrigerant charge decreases, the compressor suction pressure (absolute value) also decreases.
  • a desired decrease in the refrigerant fluid entails a decrease in the suction and delivery pressures of the compressor ( figure 5 ).
  • Figure 5 shows the results of simulations carried out by varying the R32 refrigerant charge in a heat pump operating with an example thermodynamic cycle, in a heating mode, with an outdoor air temperature of 7°C and a water temperature of 30°C.
  • Figure 6 shows the coefficient of performance (COP) values of the exemplary heat pump being simulated as the refrigerant fluid charge varies. Leaving the opening area of the expansion valve unchanged and decreasing the refrigerant charge to 80% of the nominal charge, a decrease in the COP coefficient of performance of more than 5% is observed compared to the simulation with the nominal refrigerant charge. It is also observed that, by increasing the opening area of the expansion valve (but keeping the refrigerant charge low) the COP coefficient of performance can be re-increased to 99% of the nominal COP.
  • COP coefficient of performance
  • a heat pump 1 comprises:
  • the expansion device 8 comprises a plurality of electric expansion valves 10, 11 (e.g., a first electric expansion valve 10 and a second electric expansion valve 11) placed in parallel in the circuit 2.
  • a plurality of electric expansion valves 10, 11 e.g., a first electric expansion valve 10 and a second electric expansion valve 11 placed in parallel in the circuit 2.
  • the electric expansion valves 10, 11 each have an individually adjustable opening area Aexv1, Aexv2 (e.g., the first electric expansion valve 10 has a first adjustable opening area Aexv1 and the second electric expansion valve 11 has a second adjustable opening area Aexv2) which together define a total opening area Aexv of the expansion device 8.
  • the control system 9 is configured to control the plurality of electric expansion valves 10, 11 in a total opening area range delimited by a lower total opening area limit Aexv_min and an upper total opening area limit Aexv_max, where the upper total opening area limit Aexv_max is greater than an upper individual opening area limit Aexv1_max, Aexv2_max of each of the electric expansion valves 10, 11.
  • control system 9 is configured to adjust the individual opening areas Aexv1, Aexv2 of the electric expansion valves 10, 11 to assume different values at the same instant of time. This makes it possible to adjust at least one of the plurality of expansion valves 10, 11 to a valve position with good adjustment resolution.
  • control system 9 is configured to completely close at least a first expansion valve 10 of the expansion valves 10, 11 and to adjust the individual opening area Aexv2 of at least a second expansion valve 11 of the electric expansion valves 10, 11 in a lower half of an individual opening area range of the second electric expansion valve 11.
  • the electronic control system (9) controls an upper total opening area limit (Aexv_max) of the expansion device (8) and a lower total opening area limit (Aexv_min) of the expansion device (8), where the electronic control system (9) and the expansion device (8) are configured so as to achieve a ratio (Aexv_max / Aexv_min) between the upper total opening area limit (Aexv_max) and the lower total opening area limit (Aexv_min) of the expansion device (8) greater than 15, or in the range from 22 to 70, or greater than 70.
  • said ratio (Aexv_max / Aexv_min) between the upper total opening area limit (Aexv_max) and the lower total opening area limit (Aexv_min) of the expansion device (8) is in the range from 22 to 26, or in the range from 23 to 25, or 24.
  • the upper total opening area limit Aexv_max of the expansion device 8 is greater than 2.5 mm 2 , preferably from 3.14 mm 2 to 11.45 mm 2 , for example 5.09 mm 2 , whereas the lower total opening area limit Aexv_min is less than 4% of the upper total opening area limit (Aexv_min ⁇ 0.04*Aexv_max), for example 0.21 mm 2 .
  • the upper total opening area limit (Aexv_max) of the expansion device (8) is in the range from 4.9 mm 2 to 5.2 mm 2 , or from 5.04 mm 2 to 5.13 mm 2 , or 5.09 mm 2 .
  • the total opening area range (Aexv_max - Aexv_min) expressed as the difference between the upper total opening area limit (Aexv_max) and the lower total opening area limit (Aexv_min) of the expansion device 8 is greater than 2.5 mm 2 , preferably between 4.83 mm 2 and 11 mm 2 , for example 4.88 mm 2 .
  • the total opening area range (Aexv_max - Aexv_min) expressed as the difference between the upper total opening area limit (Aexv_max) and the lower total opening area limit (Aexv_min) of the expansion device (8) opened and controlled by the electronic control system (9), is between 4.6 mm 2 and 5.18 mm 2 , or between 4.83 mm 2 and 4.93 mm 2 , or 4.88 mm 2 .
  • a ratio Aexv1_max / Aexv1_min, Aexv2_max / Aexv2_min between the upper individual opening area limit Aexv1_max, Aexv2_max and the lower individual opening area limit Aexv1_min, Aexv2_min of one or each of the electric expansion valves 10, 11 is in the range from 10.5 to 13.5, preferably from 11.5 to 12.5, for example 12.
  • the upper individual opening area limit Aexv1_max, Aexv2_max of one or each of the electric expansion valves 10, 11 is greater than 2.13 mm 2 , preferably from 2.54mm 2 to 4.52 mm 2 , for example 2.54 mm 2
  • the lower individual opening area limit Aexv1_min, Aexv2_min of one or each of the electric expansion valves 10, 11 is less than 0.25 mm 2 , preferably from 0.106 mm 2 to 0.25 mm 2 , for example 0.21 mm 2 .
  • the upper individual opening area limit (Aexv1_max, Aexv2_max) of one or each of the electric expansion valves (10, 11) is in the range from 2.4 mm 2 to 2.7 mm 2 , or from 2.5 mm 2 to 2.6 mm 2 , or 2.54 mm 2
  • the lower individual opening area limit (Aexv1_min, Aexv2_min) of one or each of the electric expansion valves (10, 11) is in the range from 0.20 mm 2 to 0.30 mm 2 , or from 0.207 mm 2 to 0.213 mm 2 , or 0.21 mm 2 .
  • the individual opening area range Aexv1_max - Aexv1_min, Aexv2_max - Aexv2_min expressed as the difference between the upper individual opening area limit Aexv1_max, Aexv2_max and the lower individual opening area limit Aexv1_min, Aexv2_min of one or each of the electric expansion valves 10, 11 is less than 5.27 mm 2 , preferably between 1.22 mm 2 and 2.9 mm 2 , for example 2.33 mm 2 .
  • the individual opening area range (Aexv1_max - Aexv1_min, Aexv2_max - Aexv2_min) expressed as the difference between the upper individual opening area limit (Aexv1_max, Aexv2_max) and the lower individual opening area limit (Aexv1_min, Aexv2_min) of one or each of the electric expansion valves (10, 11) is between 2.18 mm 2 and 2.48 mm 2 , preferably between 2.30 mm 2 and 2.36 mm 2 , for example 2.33 mm 2 .
  • a ratio Aexv1_max / Aexv1_min, Aexv2_max / Aexv2_min between the upper individual opening area limit Aexv1_max, Aexv2_max and the lower individual opening area limit Aexv1_min, Aexv2_min of one or each of the electric expansion valves 10, 11 is less than the ratio Aexv_max / Aexv_min between the upper total opening area limit Aexv_max and the lower total opening area limit Aexv_min of the expansion device 8, preferably the ratio Aexv_max / Aexv_min of the expansion device 8 is greater than or equal to 200 % of the ratio Aexv1_max / Aexv1_min , Aexv2_max / Aexv2_min of each of the single expansion valves 10, 11.
  • the individual opening area range Aexv1_max - Aexv1_min, Aexv2_max - Aexv2_min expressed as the difference between the upper individual opening area limit Aexv1_max, Aexv2_max and the lower individual opening area limit Aexv1_min, Aexv2_min of one or each of the electric expansion valves 10, 11 is less than the total opening area range Aexv_max - Aexv_min expressed as the difference between the upper total opening area limit Aexv_max and the lower total opening area limit Aexv_min of the expansion device 8, preferably the total opening area range Aexv_max - Aexv_min of the expansion device 8 is greater than or equal to 110% of the individual opening area range Aexv1_max - Aexv1_min , Aexv2_max - Aexv2_min of each of the single expansion valves 10, 11.
  • control system 9 is configured to control the compressor 5 and the expansion device 8 so that, in a heating mode (of the second heat exchanger 6 operating as a condenser 7), when the compression ratio CR of the compressor 5 is greater than 8, both the electric expansion valves 10, 11 are open and the total opening area Aexv of the expansion device 8 is greater than the upper individual opening area limit Aexv1_max, Aexv2_max of each of the expansion valves 10, 11.
  • the total opening area Aexv of the expansion device 8 does not depend only on the compression ratio CR but also on the frequency of the compressor 5 and on the pressure at the inlet of the compressor 5. For example, with the same compression ratio CR, if the frequency of the compressor 5 is reduced, a small total opening area Aexv is also sufficient to let through the flow of refrigerant required to obtain optimal performance. With the same compression ratio CR of the compressor 5 and the same frequency of the compressor 5, with a reduction of the pressure at the inlet of the compressor 5, the total opening area Aexv of the expansion device 8 required to let through the refrigerant flow rate required for optimal performance is also reduced.
  • the condition described above (CR > 8, Aexv > Aexv1_max, Aexv > Aexv2_max) is thus applicable to constant frequency f_comp and pressure on the suction side of the compressor 5.
  • control system 9 is configured to control the compressor 5 and the expansion device 8 so that, in a cooling mode (of the second heat exchanger 6 operating as an evaporator 4), when the compression ratio CR of the compressor 5 is less than 2, only one 10 of the electric expansion valves 10, 11 is open and the other electric expansion valves 11 are completely closed.
  • the electric expansion valves 10, 11 are exactly two in number.
  • all the electric expansion valves 10, 11 of the plurality of electric expansion valves 10, 11 are the same. This simplifies the control of the valves, reduces storage and assembly costs of the parts of the heat pump 1, and prevents assembly errors due to possible confusion between two different valves.
  • the compressor 5 can be connected in the circuit 2 by the interposition of a switching/reversing valve 12 which allows inverting the compression and circulation direction of the refrigerant fluid and thus switching the first heat exchanger 3 from evaporator 4 to condenser 7 and of the second heat exchanger 6 from condenser 7 to evaporator 4, allowing both cooling and heating the spaces in which the first and second heat exchangers are located (i.e., the fluid in contact with the first and second heat exchangers).
  • a switching/reversing valve 12 which allows inverting the compression and circulation direction of the refrigerant fluid and thus switching the first heat exchanger 3 from evaporator 4 to condenser 7 and of the second heat exchanger 6 from condenser 7 to evaporator 4, allowing both cooling and heating the spaces in which the first and second heat exchangers are located (i.e., the fluid in contact with the first and second heat exchangers).
  • the heat pump 1 further comprises, in a known manner, a refrigerant fluid storage vessel/reservoir 13, connected to the circuit 2, e.g., between the first heat exchanger 3 (e.g., external unit) and the compressor 5, or directly upstream of the compressor 5 ( figure 7 ).
  • a refrigerant fluid storage vessel/reservoir 13 connected to the circuit 2, e.g., between the first heat exchanger 3 (e.g., external unit) and the compressor 5, or directly upstream of the compressor 5 ( figure 7 ).
  • the electronic control system 9 also controls the speed of the blower associated with the first heat exchanger 3 and the speed of the water pump or the conveyor associated with the second heat exchanger 6.
  • the electronic control unit 9 controls the expansion device 8 also depending on the speed of the blower of the first heat exchanger 3 and of the conveyor of the second heat exchanger 6.
  • the values of the individual opening areas Aexv1, Aexv2 can be converted into step number signals for controlling electric stepper motors of the expansion valves 10 and 11.
  • the advantage obtainable by this criterion is an improved adjustment resolution.
  • both the first 10 and second 11 expansion valves are opened.
  • the advantage obtainable by this criterion is the extension of the total opening area to allow optimal operation of the heat pump with a small amount of refrigerant fluid.
  • the total opening area target value Aexv is greater than the first threshold value X and less than the second threshold value Y, only one or both of the first 10 and second 11 expansion valves are opened, but so as to position at least one of the expansion valves 10, 11 in an opening region with high adjustment resolution. This achieves the advantage of obtaining finer and more reliable adjustment of the expansion device 8 and, therefore, greater efficiency of the heat pump 1.
  • heat pumps of the prior art already implement algorithms for determining the opening area target value of the expansion valve.
  • control system 9 determines the total opening area target value Aexv of the expansion device 8 depending on a delivery temperature target value TD_target and a detected temperature value TD of the refrigerant fluid on the delivery side of the compressor 5.
  • the delivery temperature target value TD_target can be calculated according to the compression ratio CR, or depending on the compression ratio and the frequency of the compressor 5 and the heating or cooling operating mode.
  • control system 9 determines the total opening area target value Aexv of the expansion device 8 depending on a superheating target value SH_target of the refrigerant fluid vapor at the inlet of the compressor 5.
  • control system 9 determines the total opening area target value Aexv depending on:
  • FIG 8 shows a further embodiment of the heat pump 1, with an outdoor unit 14 intended to be positioned outdoors, an indoor unit 15 intended to be positioned inside a building, and with an application/usage 35, for example a heating/cooling system with a primary water circuit 16.
  • the outdoor unit 14 comprises (inside a housing):
  • the indoor unit 15 comprises (inside a housing):
  • the user/application 35 comprises a part of the primary water circuit 16 and a water vessel 36 and/or a plurality of heaters or radiators 36 for heating and cooling.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)
EP23201646.9A 2022-10-26 2023-10-04 Pompe à chaleur à modulation étendue du dispositif d'expansion Pending EP4361531A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
IT202200022080 2022-10-26

Publications (1)

Publication Number Publication Date
EP4361531A1 true EP4361531A1 (fr) 2024-05-01

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP23201646.9A Pending EP4361531A1 (fr) 2022-10-26 2023-10-04 Pompe à chaleur à modulation étendue du dispositif d'expansion

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EP (1) EP4361531A1 (fr)
CN (1) CN117928124A (fr)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09229495A (ja) * 1996-02-26 1997-09-05 Saginomiya Seisakusho Inc 電動膨張弁の制御装置及び制御方法
US20170167762A1 (en) * 2014-06-27 2017-06-15 Mitsubishi Electric Corporation Refrigeration cycle apparatus
EP3499148A1 (fr) * 2016-10-31 2019-06-19 Mitsubishi Heavy Industries Thermal Systems, Ltd. Dispositif de réfrigération, système de réfrigération
EP3633290A1 (fr) * 2017-05-31 2020-04-08 Daikin Industries, Ltd. Climatiseur
GB2588714A (en) * 2018-04-23 2021-05-05 Mitsubishi Electric Corp Refrigeration cycle device
WO2021223481A1 (fr) * 2020-05-25 2021-11-11 青岛海尔空调电子有限公司 Procédé de commande de retour d'huile pour système à divisions multiples

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09229495A (ja) * 1996-02-26 1997-09-05 Saginomiya Seisakusho Inc 電動膨張弁の制御装置及び制御方法
US20170167762A1 (en) * 2014-06-27 2017-06-15 Mitsubishi Electric Corporation Refrigeration cycle apparatus
EP3499148A1 (fr) * 2016-10-31 2019-06-19 Mitsubishi Heavy Industries Thermal Systems, Ltd. Dispositif de réfrigération, système de réfrigération
EP3633290A1 (fr) * 2017-05-31 2020-04-08 Daikin Industries, Ltd. Climatiseur
GB2588714A (en) * 2018-04-23 2021-05-05 Mitsubishi Electric Corp Refrigeration cycle device
WO2021223481A1 (fr) * 2020-05-25 2021-11-11 青岛海尔空调电子有限公司 Procédé de commande de retour d'huile pour système à divisions multiples

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