EP4379288A1 - Dampfkompressionskühlzyklusvorrichtung - Google Patents

Dampfkompressionskühlzyklusvorrichtung Download PDF

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Publication number
EP4379288A1
EP4379288A1 EP23212226.7A EP23212226A EP4379288A1 EP 4379288 A1 EP4379288 A1 EP 4379288A1 EP 23212226 A EP23212226 A EP 23212226A EP 4379288 A1 EP4379288 A1 EP 4379288A1
Authority
EP
European Patent Office
Prior art keywords
compressor
refrigerant
heat exchanger
side heat
expansion device
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
EP23212226.7A
Other languages
English (en)
French (fr)
Inventor
Tsuneko Imagawa
Yuki YAMAOKA
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.)
Panasonic Intellectual Property Management Co Ltd
Original Assignee
Panasonic Intellectual Property Management Co Ltd
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 Panasonic Intellectual Property Management Co Ltd filed Critical Panasonic Intellectual Property Management Co Ltd
Publication of EP4379288A1 publication Critical patent/EP4379288A1/de
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
    • 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
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/031—Sensor arrangements
    • F25B2313/0314—Temperature sensors near the indoor heat exchanger
    • 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—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • 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
    • F25B2500/26—Problems to be solved characterised by the startup of the refrigeration 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2509—Economiser 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
    • 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
    • F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction 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
    • F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor

Definitions

  • the present invention relates to a vapor compression refrigeration cycle device.
  • patent document 1 by controlling compressor operation frequency in accordance with discharge temperature, foaming phenomenon is reduced by abrupt reduction of low pressure, and discharging amount of lubricant oil of the compressor to outside of the compressor which is caused by this foaming phenomenon is reduced.
  • patent document 1 proposes a protection control device of an air conditioner capable of securing reliability of the compressor.
  • a vapor compression refrigeration cycle device of the present invention described in claim 1 includes a main refrigerant circuit 10 formed by sequentially connecting a compressor 11, a use-side heat exchanger 12, an intermediate heat exchanger 13, a first expansion device 14 and a heat source-side heat exchanger 15 to one another through a refrigerant pipe 16; a bypass refrigerant circuit 20 which branches off from the refrigerant pipe 16 located between the use-side heat exchanger 12 and the first expansion device 14, and which is formed by sequentially connecting a second expansion device 21, the intermediate heat exchanger 13 and a compression midstream of the compressor 11 to one another; and a control device 50 which controls valve opening degrees of the first expansion device 14 and the second expansion device 21, wherein the control device 50 includes a compressor actuation mode, in the compressor actuation mode, the control device 50 controls the first expansion device 14 and the second expansion device 21 such that refrigerant flows through both the main refrigerant circuit 10 and the bypass refrigerant circuit 20 for a predetermined period after operation of the compressor 11 is started.
  • a flow rate of use-side heat medium which flows through the use-side heat exchanger 12 is set to a predetermined value or lower, or the use-side heat medium does not flow through the use-side heat exchanger 12.
  • a flow rate of use-side heat medium which flows through the use-side heat exchanger 12 is set to a predetermined value or lower, or the use-side heat medium does not flow through the use-side heat exchanger 12.
  • control device 50 carries out the compressor actuation mode when temperature of the compressor 11 is lower than set temperature.
  • the control device 50 terminates the compressor actuation mode if discharge superheat of the compressor 11 becomes equal to or higher than a predetermined value, or if suction superheat of the compressor 11 becomes equal to or lower than a predetermined value, or if suction pressure of the compressor 11 becomes positive pressure.
  • an amount of work of the compressor is increased by increasing an amount of refrigerant which flows into the compressor, and the discharge temperature can be increased within a short time.
  • the discharge temperature By increasing the discharge temperature, the melting amount of refrigerant into oil can be reduced. Therefore, viscosity of the oil is not reduced, friction of a machine in the compressor can be suppressed, and reliability of the compressor can be secured. Further, the discharge amount of oil from the compressor can be reduced, and deterioration of heat exchange efficiency of a heat exchanger can be prevented.
  • a control device includes a compressor actuation mode.
  • a first expansion device and a second expansion device are controlled such that refrigerant flows through both a main refrigerant circuit and a bypass refrigerant circuit for a predetermined period after operation of a compressor is started.
  • the first expansion device is brought into an opened state and according to this, suction density of the compressor rises, and an inflow amount of refrigerant into the compressor is increased.
  • the second expansion device By bringing the second expansion device into an opened state, an inflow amount of refrigerant which is injected into the compressor is increased.
  • the second expansion device in the vapor compression refrigeration cycle device of the first embodiment, in the compressor actuation mode, the second expansion device is controlled such that dryness of the refrigerant on an exit side of the intermediate heat exchanger in the bypass refrigerant circuit becomes equal to or greater than a predetermined value.
  • temperature of refrigerant which is injected into the compressor can be increased, and it is possible to increase, within a short time, the discharge temperature of refrigerant which is discharged from the compressor.
  • a flow rate of use-side heat medium which flows through the use-side heat exchanger is set to a predetermined value or lower, or the use-side heat medium does not flow through the use-side heat exchanger.
  • temperature of refrigerant which flows out from the use-side heat exchanger is not lowered. According to this, it is possible to increase the temperature of refrigerant which is sucked into the compressor, and to also increase temperature of injected refrigerant, and it is possible to increase, within a short time, the discharge temperature of refrigerant which is discharged from the compressor.
  • the control device carries out the compressor actuation mode when temperature of the compressor is lower than set temperature.
  • the compressor actuation mode can be carried out in a state where a melting amount of refrigerant into oil is large.
  • the control device terminates the compressor actuation mode if discharge superheat of the compressor becomes equal to or higher than a predetermined value, or if suction superheat of the compressor becomes equal to or lower than a predetermined value, or if suction pressure of the compressor becomes positive pressure.
  • the compressor actuation mode can be concluded in a state where the melting amount of refrigerant into oil is reduced.
  • Fig. 1 is a block diagram of a vapor compression refrigeration cycle device according to the embodiment.
  • the vapor compression refrigeration cycle device is composed of a main refrigerant circuit 10 and a bypass refrigerant circuit 20.
  • the main refrigerant circuit 10 is formed by sequentially connecting, to one another through a refrigerant pipe 16, a compressor 11 which compresses refrigerant, a use-side heat exchanger 12 which functions as a radiator, an intermediate heat exchanger 13 which functions as an economizer, a first expansion device 14 which is a main expansion valve, and a heat source-side heat exchanger 15 which functions as an evaporator.
  • the vapor compression refrigeration cycle device may include a four-way valve 17 between the compressor 11 and the use-side heat exchanger 12.
  • the four-way valve 17 can change a direction of refrigerant which flows through the main refrigerant circuit 10. That is, by switching the four-way valve 17, refrigerant which is discharged from the compressor 11 flows through the heat source-side heat exchanger 15, the first expansion device 14, the intermediate heat exchanger 13 and the use-side heat exchanger 12 in this order, and the refrigerant is sucked into the compressor 11.
  • the heat source-side heat exchanger 15 functions as a radiator
  • the use-side heat exchanger 12 functions as an evaporator.
  • the bypass refrigerant circuit 20 branches off from the refrigerant pipe 16 between the use-side heat exchanger 12 and the first expansion device 14, and the bypass refrigerant circuit 20 is connected to a compression chamber which is located in the middle of a compression stroke of the compressor 11.
  • the bypass refrigerant circuit 20 is provided with a second expansion device 21.
  • a portion of high pressure refrigerant after it passes through the use-side heat exchanger 12, or a portion of high pressure refrigerant after it passes through the intermediate heat exchanger 13 is decompressed by the second expansion device 21, and this high pressure refrigerant becomes intermediate pressure refrigerant.
  • the intermediate pressure refrigerant exchanges heat in the intermediate heat exchanger 13 with high pressure refrigerant which flows through the main refrigerant circuit 10, and is injected into the compressor 11.
  • the refrigerant which is injected into the compressor 11 joins up with refrigerant which is in the middle of compression stroke of the compressor 11.
  • refrigerant which is injected and refrigerant which is in the middle of compression stroke join up with each other and recompression is carried out.
  • the use-side heat medium circuit 30 is formed by connecting the use-side heat exchanger 12, a transportation pump 31, a heating terminal (not shown) and a hot water tank (not shown) to one another through a heat medium pipe 32. Water or antifreeze liquid can be used as the use-side heat medium which flows through the use-side heat medium circuit 30.
  • the use-side heat exchanger 12 heats the use-side heat medium by refrigerant which is discharged from the compressor 11.
  • the use-side heat medium heated by the use-side heat exchanger 12 radiates heat in the heating terminal and the heat medium is utilized for heating a room, and the use-side heat medium which radiates heat in the heating terminal and whose temperature becomes low is again heated by the use-side heat exchanger 12.
  • the use-side heat medium heated by the use-side heat exchanger 12 is introduced into the hot water tank from an upper portion of the hot water tank, low temperature use-side heat medium flows out from a lower portion of the hot water tank and is heated by the use-side heat exchanger 12.
  • High pressure refrigerant discharged from the compressor 11 radiates heat in the use-side heat exchanger 12. Thereafter, the high pressure refrigerant branches off from the main refrigerant circuit 10, and is decompressed to intermediate pressure by the second expansion device 21 and the refrigerant becomes intermediate pressure refrigerant, and the intermediate pressure refrigerant exchanges heat in the intermediate heat exchanger 13.
  • High pressure refrigerant which flows through the main refrigerant circuit 10 after the refrigerant radiates heat in the use-side heat exchanger 12 is cooled by intermediate pressure refrigerant which flows through the bypass refrigerant circuit 20, and the high pressure refrigerant is decompressed in the first expansion device 14 in a state where its enthalpy is reduced.
  • Dryness (weight ratio occupied by gas phase component in entire refrigerant) of refrigerant decompressed by the first expansion device 14 when the refrigerant flows into the heat source-side heat exchanger 15 is reduced, liquid component of the refrigerant is increased, the refrigerant evaporates in the heat source-side heat exchanger 15, and the refrigerant returns to a suction side of the compressor 11.
  • intermediate pressure refrigerant which is decompressed to intermediate pressure by the second expansion device 21 is heated in the intermediate heat exchanger 13 by high pressure refrigerant which flows through the main refrigerant circuit 10, and the intermediate pressure refrigerant joins up with refrigerant which is in the middle of compression stroke of the compressor 11 in a state where its enthalpy is increased.
  • the compressor 11 is provided with a compressor temperature sensor 41 for detecting temperature of the compressor 11.
  • the refrigerant pipe 16 on the discharge side of the compressor 11 is provided with a refrigerant discharge temperature sensor 42.
  • the refrigerant discharge temperature sensor 42 detects discharge temperature of refrigerant which is discharged from the compressor 11.
  • the refrigerant pipe 16 on the suction side of the compressor 11 is provided with refrigerant suction pressure detecting means 43.
  • the refrigerant suction pressure detecting means 43 detects suction pressure of refrigerant which is sucked into the compressor 11.
  • a bypass pipe 22 on the exit side of the intermediate heat exchanger 13 in the bypass refrigerant circuit 20 is provided with an injection refrigerant temperature sensor 44.
  • the injection refrigerant temperature sensor 44 detects temperature of refrigerant which is injected into the compressor 11.
  • the vapor compression refrigeration cycle device of the embodiment includes a control device 50 which controls valve opening degrees of the first expansion device 14 and the second expansion device 21. Further, the control device 50 controls the number of rotations of the transportation pump 31. By controlling the number of rotations of the transportation pump 31, it is possible to change a flow rate of use-side heat medium which flows through the use-side heat exchanger 12.
  • the control device 50 includes a compressor actuation mode.
  • the first expansion device 14 and the second expansion device 21 are controlled such that refrigerant flows through both the main refrigerant circuit 10 and the bypass refrigerant circuit 20 for a predetermined period after operation of the compressor 11 is started.
  • the control device 50 carries out the compressor actuation mode.
  • the compressor actuation mode By carrying out the compressor actuation mode in this manner when the temperature of the compressor 11 is lower than the set temperature Ts, the compressor actuation mode can be carried out in a state where a melting amount of refrigerant into oil is large.
  • the control device 50 estimates dryness of refrigerant on the exit side of the intermediate heat exchanger 13 in the bypass refrigerant circuit 20 from refrigerant temperature Ti which is detected by the injection refrigerant temperature sensor 44, and the control device 50 controls the second expansion device 21 such that the dryness becomes equal to or higher than a predetermined value. Therefore, temperature of refrigerant which is injected into the compressor 11 can be increased, and discharge temperature of refrigerant which is discharged from the compressor 11 can be increased within a short time.
  • the control device 50 controls the number of rotations of the transportation pump 31. According to this, a flow rate of the use-side heat medium which flows through the use-side heat exchanger 12 is set to the predetermined value or lower, or the use-side heat medium is not allowed to flow to the use-side heat exchanger. Therefore, since temperature of refrigerant which flows out from the use-side heat exchanger 12 is not lowered, temperature of refrigerant which is sucked into the compressor 11 can be increased, temperature of refrigerant which is injected can be increased, and discharge temperature of refrigerant which is discharged from the compressor 11 can be increased within a short time.
  • the control device 50 terminates the compressor actuation mode if discharge superheat of the compressor 11 becomes equal to or higher than a predetermined value, or if suction superheat of the compressor 11 becomes equal to or lower than the predetermined value, or if suction pressure of the compressor 11 detected by the refrigerant suction pressure detecting means 43 becomes positive pressure from discharge temperature of refrigerant detected by the refrigerant discharge temperature sensor 42. Therefore, the compressor actuation mode can be terminated in a state where a melting amount of refrigerant into oil is reduced.
  • Fig. 2 is a control flowchart of the vapor compression refrigeration cycle device of the embodiment.
  • control device 50 If temperature of the compressor 11 detected by the compressor temperature sensor 41 is lower than the set temperature Ts (Yes in S1), the control device 50 carries out the compressor actuation mode.
  • the valve opening degree of the second expansion device 21 is increased (S2), thereby flowing refrigerant to both the main refrigerant circuit 10 and the bypass refrigerant circuit 20.
  • the control device 50 does not carry out the compressor actuation mode.
  • control device 50 further increases the valve opening degree of the second expansion device 21 (S4).
  • the control device 50 reduces the valve opening degree of the second expansion device 21 (S5).
  • the control device 50 brings the valve opening degree of the second expansion device 21 to zero, i.e., the control device 50 closes the second expansion device 21 (S7), and the control device 50 terminates the compressor actuation mode.
  • the control device 50 controls the valve opening degree of the second expansion device 21 such that the predetermined injection superheat is secured (S4, S5).
  • the compressor actuation mode can be terminated based on a condition that the discharge superheat of the compressor 11 becomes equal to or higher than a predetermined value.
  • the compressor actuation mode can be terminated based on a condition that suction superheat of the compressor 11 becomes equal to or lower than the predetermined value.
  • Fig. 3(a) is a graph showing a relation between an injection amount of refrigerant and injection temperature
  • Fig. 3(b) is a graph showing a relation between the injection amount and discharge temperature of refrigerant, and injection superheat.
  • discharge temperature of refrigerant discharged from the compressor 11 rises during a period when the injection amount is small, but if the injection amount is increased (injection rate is increased), the injection amount is increased and the discharge temperature of refrigerant is lowered.
  • Fig. 4 is a graph showing a relation between temperature and pressure of oil and solubility of refrigerant.
  • Fig. 4 shows a relation between temperature and pressure of oil when solubility of refrigerant is 10%, 20%, 30% and 100%.
  • Solubility 100% means a saturated state of refrigerant. As shown in Fig. 4 , if temperature of oil is lowered, a melting amount of refrigerant into oil is increased. Therefore, if the temperature of oil is increased, solubility of refrigerant into oil is reduced. That is, if discharge superheat is increased, the melting amount of refrigerant into oil can be reduced.
  • Figs. 5 show a state of a compressor after it is actuated in a state where the compressor is cold when outside air temperature is low and the operation of the compressor is stopped for a long time.
  • Fig. 5(a) shows a melting amount of refrigerant into lubricant oil of the compressor 11, and shows that solubility is high when the compressor is actuated.
  • Fig. 5(b) shows a state of discharge pressure and suction pressure when the compressor 11 is actuated in a state where the solubility is high. As shown in Fig. 5(b) , in a state where refrigerant is melted in the lubricant oil of the compressor, suction pressure is negative pressure.
  • Fig. 5(c) shows states of discharge temperature and suction temperature when the compressor 11 is actuated in a state where the solubility is high. As shown in Fig. 5(c) , the suction temperature does not rise soon, and it also takes time to rise the discharge temperature.
  • Fig. 5(d) shows a state of suction superheat of the compressor 11 when the compressor 11 is actuated in a state where the solubility is high. As shown in Fig. 5(d) , if solubility is high, the suction superheat abruptly rises immediately after the compressor 11 is actuated, but as the temperature of the compressor 11 rises, if the solubility is reduced and refrigerant is melted out, the suction superheat is lowered.
  • suction density of the compressor 11 is increased and the inflow amount of refrigerant into the compressor 11 is increased, and by opening the second expansion device 21, the inflow amount of refrigerant injected into the compressor 11 is increased.
  • an amount of refrigerant which flows into the compressor 11 is increased, thereby increasing an amount of work of the compressor 11, and the discharge temperature can be increased within a short time.
  • a melting amount of refrigerant into oil can be reduced. Therefore, reliability of the compressor 11 can be enhanced. Further, a discharge amount of oil from the compressor 11 is reduced, and it is possible to prevent heat exchange efficiency of the heat exchanger from being deteriorated.

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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)
EP23212226.7A 2022-11-29 2023-11-27 Dampfkompressionskühlzyklusvorrichtung Pending EP4379288A1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2022190325A JP2024078026A (ja) 2022-11-29 2022-11-29 蒸気圧縮式冷凍サイクル装置

Publications (1)

Publication Number Publication Date
EP4379288A1 true EP4379288A1 (de) 2024-06-05

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP23212226.7A Pending EP4379288A1 (de) 2022-11-29 2023-11-27 Dampfkompressionskühlzyklusvorrichtung

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EP (1) EP4379288A1 (de)
JP (1) JP2024078026A (de)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH07190509A (ja) 1993-12-27 1995-07-28 Matsushita Electric Ind Co Ltd 周波数制御式空気調和機の保護制御装置
EP2075517A1 (de) * 2007-12-24 2009-07-01 LG Electronics Inc. Klimaanlagensystem
EP2290304A1 (de) * 2008-03-31 2011-03-02 Mitsubishi Electric Corporation Klimaanlage
US20160097568A1 (en) * 2014-10-03 2016-04-07 Mitsubishi Electric Corporation Air-conditioning apparatus

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH07190509A (ja) 1993-12-27 1995-07-28 Matsushita Electric Ind Co Ltd 周波数制御式空気調和機の保護制御装置
EP2075517A1 (de) * 2007-12-24 2009-07-01 LG Electronics Inc. Klimaanlagensystem
EP2290304A1 (de) * 2008-03-31 2011-03-02 Mitsubishi Electric Corporation Klimaanlage
US20160097568A1 (en) * 2014-10-03 2016-04-07 Mitsubishi Electric Corporation Air-conditioning apparatus

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