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WO2015076331A1 - Appareil de conditionnement d'air - Google Patents

Appareil de conditionnement d'air Download PDF

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Publication number
WO2015076331A1
WO2015076331A1 PCT/JP2014/080759 JP2014080759W WO2015076331A1 WO 2015076331 A1 WO2015076331 A1 WO 2015076331A1 JP 2014080759 W JP2014080759 W JP 2014080759W WO 2015076331 A1 WO2015076331 A1 WO 2015076331A1
Authority
WO
WIPO (PCT)
Prior art keywords
condenser
valve
opening degree
oil return
compressor
Prior art date
Application number
PCT/JP2014/080759
Other languages
English (en)
Japanese (ja)
Inventor
山本　昌由
喜記 山野井
Original Assignee
ダイキン工業株式会社
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 ダイキン工業株式会社 filed Critical ダイキン工業株式会社
Publication of WO2015076331A1 publication Critical patent/WO2015076331A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B49/027—Condenser control arrangements
    • 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
    • F25B31/00—Compressor arrangements
    • F25B31/002—Lubrication
    • F25B31/004—Lubrication oil recirculating arrangements
    • 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
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0403—Refrigeration circuit bypassing means for the 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
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/021—Inverters therefor
    • 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
    • F25B2600/11—Fan speed control
    • F25B2600/111—Fan speed control of condenser fans
    • 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
    • F25B2600/17—Control issues by controlling the pressure of the 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2501—Bypass 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
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1931—Discharge pressures
    • 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
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1933—Suction pressures
    • 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
    • F25B2700/2106—Temperatures of fresh outdoor air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Definitions

  • the present invention relates to a cooling-only air conditioner used in a computer room, for example.
  • air conditioners used in, for example, computer rooms are known. Since this type of air conditioner performs cooling operation throughout the year, the air conditioner includes a cooling-only refrigerant circuit in which a compressor, a condenser, an expansion mechanism, and an evaporator are connected in this order (for example, Patent Document 1). In this type of refrigerant circuit, when the temperature of the outside air is low (for example, in winter), the capacity of the condenser may become excessive.
  • This bypass circuit is a circuit that has an electric valve capable of controlling the opening degree, and sends the refrigerant discharged from the compressor to the evaporator, bypassing the condenser.
  • This bypass circuit is a circuit that has an electric valve capable of controlling the opening degree, and sends the refrigerant discharged from the compressor to the evaporator, bypassing the condenser.
  • An object of the present invention is to effectively return the refrigeration oil accumulated in the condenser to the compressor in an air conditioner dedicated to cooling.
  • the air conditioner according to the present invention is an air conditioner dedicated to a refrigerant including a main refrigerant circuit, a bypass circuit, a fan, and a control unit.
  • the main refrigerant circuit includes a compressor, a condenser, a first valve capable of opening degree control, and an evaporator.
  • the bypass circuit has a second valve capable of opening control.
  • the bypass circuit is connected to the main refrigerant circuit so that the refrigerant discharged from the compressor bypasses the condenser and the first valve.
  • the fan creates an air flow to the condenser.
  • the control unit controls the compressor, the first valve, the second valve, and the fan.
  • the control unit performs a normal operation and an oil return operation of the condenser.
  • the condensation pressure is adjusted by adjusting at least one of the opening degree of the first valve, the opening degree of the second valve, and the air volume of the fan.
  • the oil return operation of the condenser when a predetermined condition is satisfied, at least one of control for increasing the opening degree of the first valve and control for reducing the opening degree of the second valve is performed.
  • the refrigerator oil in the condenser is returned to the compressor together with the refrigerant.
  • FIG. 1 is a schematic configuration diagram of an air conditioner according to an embodiment of the present invention. It is a control block diagram in the air conditioner according to the embodiment. It is a flowchart which shows the control example 1 of the air conditioner which concerns on the said embodiment. It is a flowchart which shows the control example 2 of the air conditioner which concerns on the said embodiment. It is a schematic block diagram of the air conditioner which concerns on the modification of the said embodiment.
  • (A) to (C) are graphs for explaining fluctuations in the differential pressure across the condenser in the oil return operation of the condenser.
  • the air conditioner 1 which concerns on this embodiment is an air conditioner only for a refrigerant
  • the air conditioner 1 includes a refrigerant circuit 10 and cools the room by performing a vapor compression refrigeration cycle operation.
  • the object of cooling is a computer room such as a server room, for example, the air conditioner 1 continuously performs a cooling operation for adjusting the room to a predetermined temperature range throughout the year.
  • An air conditioner 1 includes a heat source unit (outdoor unit) 2 installed outdoors, a utilization unit (indoor unit) 3 installed indoors, and a refrigerant communication tube 4 that connects these units. And 5.
  • the refrigerant circuit 10 includes a main refrigerant circuit 11 and a bypass circuit 12.
  • the main refrigerant circuit 11 includes a compressor 24, a condenser 25, a first valve 21 capable of controlling the opening degree, and an evaporator 26.
  • the main refrigerant circuit 11 is provided in the heat source unit 2 and forms a part of the main refrigerant circuit 11, and the heat source side main refrigerant circuit 11 a that forms a part of the main refrigerant circuit 11 and the use side that forms a part of the main refrigerant circuit 11 in the use unit 3.
  • Main refrigerant circuit 11b In this embodiment, the condenser 25 and the first valve 21 are provided in the heat source side main refrigerant circuit 11a, and the compressor 24 and the evaporator 26 are provided in the use side main refrigerant circuit 11b.
  • the compressor 24 may be provided in the heat source side main refrigerant circuit 11a.
  • the bypass circuit 12 has a second valve 22 capable of opening control.
  • the bypass circuit 12 is connected to the main refrigerant circuit 11 (more specifically, the heat source side main refrigerant circuit 11a) so as to bypass the refrigerant discharged from the compressor 24 through the condenser 25 and the first valve 21.
  • one end of the bypass circuit 12 is connected to, for example, a refrigerant pipe connecting the discharge side of the compressor 24 and the condenser 25, and the other end of the bypass circuit 12 is connected to, for example, the first valve 21. It is connected to a refrigerant pipe connecting the evaporator 26. More specifically, as shown in FIG.
  • one end of the bypass circuit 12 is connected to a refrigerant pipe connecting the refrigerant communication pipe 4 and the condenser 25 in the heat source side main refrigerant circuit 11a.
  • the other end is connected to a refrigerant pipe connecting the first valve 21 and the refrigerant communication pipe 5 in the heat source side main refrigerant circuit 11a.
  • the compressor 24 has a function of sucking low-pressure refrigerant, compressing it, and discharging it as high-pressure refrigerant.
  • the compressor 24 is driven by a compressor motor 24M.
  • the compressor motor 24M is driven by receiving electric power via an inverter device.
  • the compressor 24 is a compressor whose operating capacity can be changed by changing the frequency (that is, the rotation speed) of the compressor motor 24M.
  • the suction side of the compressor 24 is connected to the outlet of the evaporator 26, and the discharge side of the compressor 24 is connected to the inlet of the condenser 25 via the refrigerant communication pipe 4.
  • the condenser 25 for example, a cross fin type heat exchanger constituted by a heat transfer tube and a large number of fins can be used, but is not limited thereto.
  • the condenser 25 has a function of condensing the high-pressure refrigerant using outdoor air as a heat source.
  • the outlet of the condenser 25 is connected to the utilization unit 3 (more specifically, the third valve 23) via the first valve 21, the refrigerant regulator 30, the supercooling heat exchanger 31, and the refrigerant communication pipe 5. Yes.
  • the inlet of the condenser 25 is connected to the utilization unit 3 (more specifically, the discharge side of the compressor 24) via the refrigerant communication pipe 4.
  • a cross fin type heat exchanger constituted by a heat transfer tube and a large number of fins can be used, but is not limited thereto.
  • the evaporator 26 has a function of evaporating the low-pressure refrigerant and cools indoor air.
  • the inlet of the evaporator 26 is connected to the third valve 23.
  • the outlet of the evaporator 26 is connected to the suction side of the compressor 24.
  • the first valve 21 is an electric valve (expansion valve) capable of opening control, but is not limited thereto.
  • the first valve 21 is mainly used when performing control (high pressure control) for maintaining the condensation pressure (high pressure) in a predetermined range.
  • the second valve 22 is an electric valve (expansion valve) capable of opening degree control, but is not limited thereto.
  • the second valve 22 is mainly used when performing the above-described high pressure control.
  • the main refrigerant circuit 11 has a third valve 23 capable of opening degree control.
  • the third valve 23 is an electronic expansion valve capable of opening degree control, but is not limited thereto.
  • the third valve 23 is mainly used when the refrigerant cooled in the condenser 25 of the heat source unit 2 is decompressed.
  • the third valve 23 is provided in the use side main refrigerant circuit 11 b and is connected to the heat source side main refrigerant circuit 11 a via the refrigerant communication pipe 5.
  • the main refrigerant circuit 11 includes a refrigerant regulator (receiver) 30, a supercooling heat exchanger 31, and an oil separator 32.
  • the refrigerant regulator 30 is provided on the downstream side of the condenser 25, and is configured by a container that absorbs fluctuations in the refrigerant amount in the evaporator 26 due to load fluctuations.
  • the supercooling heat exchanger 31 further cools the refrigerant liquefied in the condenser 25, and cools it below its saturation temperature.
  • the oil separator 32 is for separating a part of the refrigerating machine oil from the refrigerant discharged from the compressor 24.
  • a part of the refrigerating machine oil discharged together with the refrigerant from the compressor 24 is separated from the refrigerant in the oil separator 32 and returned to the suction side of the compressor 24 through the oil return circuit 13 provided with the capillary tube 33.
  • the third valve 23 and the oil separator 32 are provided in the use side main refrigerant circuit 11b, and the refrigerant regulator 30 and the supercooling heat exchanger 31 are provided in the heat source side main refrigerant circuit 11a.
  • the refrigerant regulator 30 and the supercooling heat exchanger 31 are provided in the heat source side main refrigerant circuit 11a.
  • the heat source unit 2 includes a heat source side fan 28 that forms an air flow to the condenser 25.
  • the heat source side fan 28 sucks outdoor air from the suction port into the heat source unit 2, exchanges heat with the refrigerant in the condenser 25 accommodated in the heat source unit 2, and then blows it out as outdoor air from the air outlet.
  • the air flow is formed.
  • the heat source side fan 28 is driven by a fan motor 28M.
  • the fan motor 28M is driven by receiving electric power via an inverter device.
  • the heat source side fan 28 can change the air volume by changing the frequency (that is, the rotation speed) of the fan motor 28M.
  • the usage unit 3 includes a usage-side fan 29 that forms an air flow to the evaporator 26.
  • the usage-side fan 29 sucks room air into the usage unit 3 from the suction port, exchanges heat with the refrigerant in the evaporator 26 accommodated in the usage unit 3, and then blows it out into the room as supply air from the blow-out port.
  • the air flow is formed.
  • the use side fan 29 is driven by a fan motor 29M.
  • the air conditioner 1 is provided with various sensors.
  • the heat source unit 2 is provided with an outdoor temperature sensor 41 that detects the temperature of outdoor air.
  • the utilization unit 3 is provided with a suction pressure sensor 42 for detecting the suction pressure of the compressor 24, a discharge pressure sensor 43 for detecting the discharge pressure of the compressor 24, and the like.
  • the air conditioner 1 includes a control unit 27 that controls the operation of the air conditioner 1.
  • the control unit 27 may be provided in the heat source unit 2, may be provided in the utilization unit 3, or may be provided in both of them.
  • the control unit 27 includes, for example, a microcomputer and a memory.
  • FIG. 2 is a control block diagram of the air conditioner 1 according to the present embodiment.
  • the control unit 27 can capture signals corresponding to state quantities (pressure value, temperature, etc.) detected by various sensors such as the sensors 41, 42, and 43. And the control part 27 controls operation
  • the control unit 27 performs a normal operation and an oil return operation of the condenser.
  • the air conditioner 1 may further perform an oil return operation of the gas pipe.
  • the normal operation and the oil return operation will be specifically described.
  • Normal operation In normal operation, the temperature of the indoor air that is the object of cooling is adjusted to a predetermined range, and the condensation pressure (high pressure) is adjusted to a predetermined range in order to maintain the reliability of the compressor 24. Specifically, in the normal operation, the control unit 27 determines that the condensing pressure is within a predetermined target high pressure range based on the high pressure in the refrigerant circuit 10 (for example, the discharge pressure of the compressor 24 detected by the discharge pressure sensor 43). The refrigerant circuit 10 is controlled to enter.
  • the refrigerant circuit 10 performs the following refrigeration cycle operation.
  • the low-pressure refrigerant is sucked into the compressor 24 of the usage unit 3 and compressed to become a high-pressure refrigerant.
  • the high-pressure refrigerant discharged from the compressor 24 is sent to the heat source unit 2 via the refrigerant communication pipe 4, and is cooled by exchanging heat with outdoor air supplied by the heat source side fan 28 in the condenser 25.
  • the high-pressure refrigerant cooled in the condenser 25 is sent to the utilization unit 3 via the first valve 21 and the refrigerant communication pipe 5.
  • the opening degree of the first valve 21 provided in the main refrigerant circuit 11 and the opening degree of the second valve 22 provided in the bypass circuit 12 are controlled as follows, for example.
  • the control unit 27 performs control to increase the opening degree of the first valve 21, reduce the opening degree of the second valve 22, or increase the air volume of the heat source side fan 28.
  • the opening degree of the first valve 21 is set to a fully open state
  • the opening degree of the second valve 22 is set to a fully closed state, for example. Not limited to this.
  • the control unit 27 performs control to reduce the opening degree of the first valve 21, increase the opening degree of the second valve 22, or reduce the air volume of the heat source side fan 28.
  • the opening degree of the first valve 21 can be reduced while the opening degree of the second valve 22 can be fully opened, but is not limited thereto. .
  • the high-pressure refrigerant sent to the usage unit 3 is reduced in pressure by the third valve 23 to become a low-pressure gas-liquid two-phase refrigerant and sent to the evaporator 26, and is supplied by the usage-side fan 29 in the evaporator 26. Heat is exchanged with air. As a result, the refrigerant evaporates into a low-pressure gas refrigerant. The low-pressure gas refrigerant heated in the evaporator 26 is again sucked into the compressor 24.
  • the oil return operation of the gas pipe for returning the refrigeration oil accumulated in the gas pipe to the compressor 24 and the refrigeration oil accumulated in the condenser 25 are returned to the compressor 24.
  • the oil return operation of the condenser is performed.
  • the operation capacity of the compressor 24 is increased and the flow rate of the refrigerant flowing through the refrigerant circuit 10 is increased. Thereby, a part or all of the refrigerating machine oil accumulated in the gas pipe can be returned to the compressor 24.
  • the control for increasing the opening degree of the first valve 21 and the second valve 22 At least one of the controls for reducing the opening is performed to increase the flow rate of the refrigerant flowing through the condenser 25.
  • the refrigerating machine oil can be returned to the compressor 24 together with the liquid refrigerant in the condenser 25.
  • the oil return operation of the gas pipe and the oil return operation of the condenser may be performed at different times or may be performed continuously. Specifically, a mode in which only the condenser oil return operation is performed independently as in Control Example 1 described later, and the oil in the condenser is immediately after the oil return operation of the gas pipe is performed as in Control Example 2 described later.
  • working can be illustrated, it is not restricted to these forms.
  • the air conditioner 1 continuously performs a cooling operation for adjusting a room to a predetermined temperature range throughout the year. Therefore, the operation of the compressor 24 is easy to be stabilized and it is easy to maintain a certain state. That is, since it is easy to maintain the state where the rotation speed of the compressor 24 is low, the refrigerating machine oil tends to accumulate particularly in the gas pipe and the condenser 25.
  • FIG. 3 is a flowchart showing a control example 1 of the air conditioner 1 according to the present embodiment. As shown in FIG. 3, in step 1, the control unit 27 controls the refrigerant circuit 10 so that a normal operation for adjusting the indoor air temperature to a predetermined temperature range is performed.
  • step S2 the control unit 27 determines whether or not a start condition for the oil return operation of the condenser is satisfied. If the start condition is not satisfied, the process returns to the process of step S1 and the normal operation is continued. If the start condition is satisfied, the process proceeds to the process of step S3 to change from the normal operation to the condenser. Switch to the oil return operation.
  • the conditions for starting the oil return operation of the condenser are conditions determined in advance in the air conditioner 1. Examples of the start condition include the following conditions (A), (B), (C), and (D), but are not limited to these, and other conditions may be employed.
  • the start condition for the oil return operation of the condenser may be, for example, one of the conditions (A), (B), (C), (D), and the conditions (A), (B) , (C), (D) may be combined.
  • (A) The amount of oil sump is equal to or greater than a predetermined reference amount
  • the opening degree of the first valve 21 is equal to or less than a predetermined reference opening degree (C)
  • the operating capacity of the compressor 24 is predetermined. The state of being below a predetermined reference value continues for a predetermined time (D)
  • the outdoor temperature is below a predetermined reference temperature
  • the reference amount of condition (A), the reference opening of condition (B), the reference value of condition (C), and the reference temperature of condition (D) are stored in the memory of the control unit 27. These criteria may be changeable by the user as needed.
  • the amount of oil pool is, for example, the amount of refrigerating machine oil contained in the refrigerant discharged from the compressor 24 and the refrigerant separated in the oil separator 32 and supplied to the compressor 24 through the oil return circuit 13. It can be obtained by integrating the returned oil return amount.
  • step S2 the control unit 27 determines whether or not the accumulated oil sum is equal to or greater than a reference value. When the oil sum is less than the reference value, the process returns to step S1 to continue normal operation. When the oil sum is equal to or greater than the reference value, the process proceeds to step S3 and the normal operation starts. Switch to condenser oil return operation.
  • step S2 the control unit 27 determines whether or not the opening degree of the first valve 21 is equal to or less than the reference opening degree. When the opening degree of the first valve 21 exceeds the reference opening degree, the process returns to step S1 to continue normal operation. When the opening degree of the first valve 21 is equal to or less than the reference opening degree, step S3 is performed. The process is switched to the normal operation and the condenser oil return operation. In addition, this condition (B) is good also as the state where the opening degree of the 1st valve 21 is below a predetermined reference opening degree continuing for the predetermined time. Thereby, the judgment precision of the necessity for oil return operation can be raised more.
  • step S2 the control unit 27 determines that the operating capacity of the compressor 24, specifically, the frequency (that is, the rotation speed) of the compressor motor 24M is equal to or less than a predetermined reference value. It is determined whether or not this state continues for a predetermined time. If the start condition is not satisfied, the process returns to the process of step S1 and the normal operation is continued. If the start condition is satisfied, the process proceeds to the process of step S3 and the condenser is changed from the normal operation to the condenser. Switch to the oil return operation.
  • step S2 the control unit 27 determines whether or not the outdoor temperature detected by the temperature sensor 41 is equal to or lower than a predetermined reference temperature. If the outdoor temperature exceeds a predetermined reference temperature, the process returns to step S1 to continue normal operation. If the outdoor temperature is equal to or lower than the predetermined reference temperature, the process of step S3 is performed. And switch from normal operation to condenser oil return operation. In addition, this condition (D) is good also as the state where the outdoor temperature is below a predetermined reference temperature for a predetermined time. Thereby, the judgment precision of the necessity for oil return operation can be raised more.
  • step S3 the control unit 27 performs the oil return operation of the condenser. Specifically, the control unit 27 returns the refrigeration oil in the condenser 25 to the compressor 24 together with the refrigerant, for example, the first valve 21 so that the opening degree of the first valve 21 is larger than that during normal operation.
  • the opening degree of the first valve 21 is not particularly limited as long as it is larger than that in the normal operation, but it is preferable that the first valve 21 is fully opened, for example.
  • FIG. 6A is a graph for explaining the fluctuation of the differential pressure across the condenser 25 in the oil return operation of the condenser.
  • step S3 as shown in FIG. 6A, when the opening of the first valve 21 is made larger than that during normal operation (for example, when the opening of the first valve 21 is fully opened), condensation occurs.
  • the amount of refrigerant flowing into the condenser 25 increases, and the refrigerant in the condenser 25 is pushed by the refrigerant that has flowed in, so the pressure HP near the inlet of the condenser 25 temporarily (instantaneously) increases.
  • the differential pressure ⁇ P across the condenser 25 that is, the difference ⁇ P between the pressure HP near the inlet of the condenser 25 and the pressure LP near the outlet of the condenser 25 temporarily increases. Since the refrigerant flow is promoted in the condenser 25 by such a differential pressure ⁇ P, the refrigerating machine oil accumulated in the condenser 25 is pushed out of the condenser 25 together with the refrigerant.
  • step S3 the opening degree of the second valve 22 in the oil return operation may be maintained as shown in FIG. 6A, and the opening degree of the second valve 22 in the normal operation may be maintained. ) May be changed so as to be smaller than the opening of the second valve 22 during normal operation.
  • the opening of the first valve 21 is reduced in the normal operation of step S1, while the second valve 22 The opening is fully open.
  • the opening degree of the first valve 21 is, for example, fully open while the opening degree of the second valve 22 is maintained, for example, in a fully open state. Is done.
  • the fluctuation range of the pressure in the condenser 25 is increased, The pressure fluctuation of the entire refrigerant circuit 10 can be suppressed.
  • the opening degree of the first valve 21 is changed to be larger than the opening degree of the first valve 21 in the normal operation step S1.
  • the opening degree of the second valve 22 is changed to be smaller than the opening degree of the second valve 22 during the normal operation in step S1 (for example, when the opening degree of the second valve 22 is fully closed).
  • the control for increasing the opening degree of the first valve 21 and the control for decreasing the opening degree of the second valve 22 may be slightly different in time, but preferably Should be done at the same time.
  • step S3 the opening degree of the second valve 22 is made smaller than that in the normal operation, while the opening degree of the first valve 21 is maintained in the normal operation state. May be.
  • the opening degree of the second valve 22 is not particularly limited as long as it is smaller than that in the normal operation.
  • the second valve 22 is fully closed, and the first valve 21 is opened. The degree is not at least fully closed.
  • step S3 when the opening degree of the second valve 22 is made smaller than that during normal operation (for example, when the opening degree of the second valve 22 is fully closed), Since the refrigerant in the condenser 25 is pushed temporarily (instantaneously), the pressure HP near the inlet of the condenser 25 temporarily (instantaneously) increases. As a result, the differential pressure ⁇ P across the condenser 25, that is, the difference ⁇ P between the pressure HP near the inlet of the condenser 25 and the pressure LP near the outlet of the condenser 25 temporarily increases. Since the refrigerant flow is promoted in the condenser 25 by such a differential pressure ⁇ P, the refrigerating machine oil accumulated in the condenser 25 is pushed out of the condenser 25 together with the refrigerant.
  • the air volume of the heat source side fan 28 in the oil return operation may be maintained so that the air volume of the heat source side fan 28 during the normal operation may be maintained, and may be changed to be smaller than the air volume of the heat source side fan 28 during the normal operation. Also good. That is, in the oil return operation of the condenser, the frequency (rotation speed) of the fan motor 28M may be changed to be smaller than the frequency (rotation speed) during normal operation.
  • the condensation pressure can be increased, so that the air volume in the normal operation is maintained. In comparison with this, a larger fluctuation of the condensation pressure can be caused. Thereby, the refrigerating machine oil accumulated in the condenser 25 can be pushed out of the condenser 25 more effectively.
  • step S3 the timing for reducing the air volume of the heat source side fan 28 may be before the opening degree of the first valve 21 or after the opening degree of the first valve 21 is increased. However, when the opening degree of the first valve 21 is increased, a larger fluctuation of the condensation pressure can be caused.
  • step S ⁇ b> 3 the timing for reducing the air volume of the heat source side fan 28 may be before the opening of the second valve 22 is reduced, or when the opening of the second valve 22 is reduced. However, when the opening degree of the second valve 22 is decreased, a larger fluctuation of the condensation pressure can be caused.
  • step S4 the control unit 27 determines whether or not an end condition for the oil return operation of the condenser is satisfied. If the end condition is not satisfied, the process returns to step S3 and the oil return operation is continued. If the end condition is satisfied, the process returns to step S1 and the normal operation from the oil return operation is resumed. Switch to operation.
  • the end condition of the oil return operation of the condenser is a condition predetermined in the air conditioner 1.
  • Examples of the end condition include a condition that the elapsed time from the start of the oil return operation in step S3 reaches a predetermined time, but is not limited to this, and other conditions can also be adopted.
  • FIG. 4 is a flowchart showing a control example 2 of the air conditioner 1 according to the present embodiment.
  • This control example 2 is different from the control example 1 in that not only the condenser oil return operation but also the gas pipe oil return operation is performed.
  • step S11 is the same as step S1 in the control example 1.
  • the control unit 27 determines whether a start condition for the oil return operation of the gas pipe is satisfied. If the start condition is not satisfied, the process returns to step S11 to continue the normal operation. If the start condition is satisfied, the process proceeds to step S13 and the normal operation is changed to the gas pipe. Switch to the oil return operation.
  • the start condition of the oil return operation of the gas pipe in step S12 is a condition determined in advance in the air conditioner 1.
  • Examples of conditions for starting the oil return operation of the gas pipe include the conditions (A), (B), (C), and (D) in Control Example 1, but are not limited to these, and other conditions are adopted. You can also
  • the start condition of the oil return operation of the gas pipe may be one of the conditions (A), (B), (C), (D), and the conditions (A), (B), A condition combining a plurality of (C) and (D) may be used.
  • step S13 the control unit 27 performs the oil return operation of the gas pipe.
  • the control unit 27 performs control to increase the operating capacity of the compressor 24 compared to that during normal operation in order to return the refrigeration oil in the gas pipe to the compressor 24.
  • the compressor motor 24M is driven so that the frequency (that is, the rotation speed) of the compressor motor 24M is larger than that in the normal operation.
  • the amount of refrigerant circulating in the refrigerant circuit 10 increases, so that part or all of the refrigerating machine oil adhering to the inner surface of the gas pipe is returned to the compressor 24.
  • step S14 the control part 27 determines whether the completion
  • the end condition of the oil return operation of the gas pipe is a condition determined in advance in the air conditioner 1.
  • Examples of the end condition include a condition that the elapsed time from the start of the oil return operation in step S13 reaches a predetermined time, but is not limited to this, and other conditions can also be adopted.
  • step S15 the control unit 27 performs the oil return operation of the condenser.
  • the operation capacity of the compressor 24 in the oil return operation of the condenser in step S15 may be changed from the operation capacity of the compressor 24 in the oil return operation of the gas pipe in step S13, but the compression in the oil return operation of the gas pipe The operating capacity of the machine 24 is preferably maintained.
  • Step S15 of Control Example 2 the oil return operation of the condenser is performed in the same manner as Step S3 of Control Example 1.
  • Step S16 of Control Example 2 is the same as Step S4 of Control Example 1, detailed description thereof is omitted.
  • the condensation pressure may fluctuate from the condensation pressure during the normal operation. Therefore, the oil return operation of the condenser is preferably completed in a short time. Therefore, when the condition that the elapsed time from the start of the oil return operation reaches a predetermined time is adopted as the end condition of the oil return operation of the condenser in step S16, the operation of the oil return operation of the condenser is adopted.
  • the time is preferably set shorter than the operation time of the oil return operation of the gas pipe.
  • the condensation pressure in normal operation, is adjusted to a predetermined value by adjusting at least one of the opening degree of the first valve 21, the opening degree of the second valve 22, and the air volume of the fan 28. Can be adjusted to range. Further, for example, when the temperature of the outside air is low, such as in winter, the capacity of the condenser may become excessive. In this case, in normal operation, for example, the opening degree of the first valve 21 may be reduced, The capacity of the condenser 25 is reduced by increasing the opening degree of the two valves 22 or by reducing the air volume of the fan 28, and the liquid refrigerant is stored in the condenser 25. Thereby, the condensation pressure can be adjusted to a predetermined range.
  • the refrigeration oil is accumulated in the condenser 25 in a state of being dissolved in the liquid refrigerant accumulated in the condenser 25.
  • the differential pressure across the condenser 25 the difference between the pressure near the inlet of the condenser 25 and the pressure near the outlet of the condenser 25
  • the refrigerant and the refrigerating machine oil do not circulate and accumulate in the flow path.
  • control unit 27 controls the first valve 21 so that the opening degree of the first valve 21 is fully opened in the oil return operation of the condenser.
  • the control unit 27 controls the first valve 21 so that the opening degree of the first valve 21 is fully opened in the oil return operation of the condenser.
  • the control unit 27 performs an oil return operation of the gas pipe that increases the operating capacity of the compressor 24 and returns the refrigeration oil accumulated in the gas pipe of the main refrigerant circuit 11 to the compressor 24.
  • the refrigeration oil may adhere to the inner surface of the gas pipe and accumulate, but by performing an oil return operation of the gas pipe that increases the operating capacity of the compressor 24, The refrigerating machine oil accumulated in can be returned to the compressor 24.
  • control unit 27 performs the oil return operation of the condenser while maintaining the operation capacity of the compressor 24 after performing the oil return operation of the gas pipe.
  • the operation capacity of the compressor 24 raised in the oil return operation of the gas pipe is maintained, that is, the refrigerant circulation amount in the refrigerant circuit is increased, the oil return operation of the condenser is performed.
  • the amount of refrigerant flowing through the condenser 25 in the oil return operation of the vessel can be increased. Thereby, the refrigerating machine oil accumulated in the condenser 25 can be pushed out of the condenser 25 more effectively.
  • the opening degree control of the first valve 21 and the second valve 22 may be performed.
  • the condensation pressure can be increased. Therefore, in the configuration in which the opening degree control of at least one of the first valve 21 and the second valve 22 and the air volume control of the fan 28 are performed, a larger variation in the condensation pressure occurs than in the case where only the valve opening degree control is performed. Can be made. Thereby, the refrigerating machine oil accumulated in the condenser 25 can be pushed out of the condenser 25 more effectively.
  • the condenser 25 is a heat exchanger that exchanges heat between the refrigerant and the outdoor air. It may be a heat exchanger of the type. That is, as shown in FIG. 5, the water-cooled condenser 25 includes a refrigerant passage and a water passage. Circulating water (cooling water) that flows into the water passage through the water pipe 25a is configured to flow out into the water pipe 25b after exchanging heat with the refrigerant.
  • the control unit 27 may perform control to reduce the flow rate of the cooling water flowing into the condenser 25.
  • control which enlarges the opening degree of the 1st valve 21 was illustrated so that the opening degree of the 1st valve 21 might be in a fully open state in the oil return operation
  • movement of a condenser it is not restricted to this.
  • control may be performed to increase the opening degree of the first valve 21 so that the opening degree of the first valve 21 is smaller than the fully opened state.
  • the oil return operation of the condenser is performed in a state where the operation capacity of the compressor 24 is maintained, but the present invention is not limited to this.
  • the oil return operation of the condenser may be performed after the operation capacity of the compressor 24 is changed after the oil return operation of the gas pipe. Further, the oil return operation of the gas pipe may be performed after the oil return operation of the condenser.
  • the air conditioner 1 may include a plurality of refrigerant circuit systems. That is, the present invention can be applied to an air conditioner including a plurality of vapor compression refrigerant circuit systems each having a compressor, a condenser, an expansion mechanism, and an evaporator.
  • the refrigerant circuit 10 may be provided with a plurality of compressors.
  • the air conditioner 1 is a so-called remote condenser type in which the compressor 24 is provided in the use unit 3, but may be a type in which the compressor 24 is provided in the heat source unit 2.
  • the air conditioner of the present embodiment is a dedicated refrigerant air conditioner including a main refrigerant circuit, a bypass circuit, a fan, and a control unit.
  • the main refrigerant circuit includes a compressor, a condenser, a first valve capable of opening degree control, and an evaporator.
  • the bypass circuit has a second valve capable of opening control.
  • the bypass circuit is connected to the main refrigerant circuit so that the refrigerant discharged from the compressor bypasses the condenser and the first valve.
  • the fan creates an air flow to the condenser.
  • the control unit controls the compressor, the first valve, the second valve, and the fan.
  • the control unit performs a normal operation and an oil return operation of the condenser.
  • the condensation pressure is adjusted by adjusting at least one of the opening degree of the first valve, the opening degree of the second valve, and the air volume of the fan.
  • the oil return operation of the condenser when a predetermined condition is satisfied, at least one of control for increasing the opening degree of the first valve and control for reducing the opening degree of the second valve is performed.
  • the refrigerator oil in the condenser is returned to the compressor together with the refrigerant.
  • the condensation pressure in normal operation, at least one of the opening degree of the first valve, the opening degree of the second valve, and the air volume of the fan is adjusted to condense pressure (pressure on the high pressure side in the refrigerant circuit.
  • high pressure pressure pressure on the high pressure side in the refrigerant circuit.
  • the condensation pressure can be adjusted to a predetermined range.
  • the opening degree of the first valve is reduced or the second valve is opened.
  • the capacity of the condenser is reduced by increasing the opening of the valve or reducing the air volume of the fan, and liquid refrigerant is stored in the condenser.
  • the condensation pressure can be adjusted to a predetermined range (a range of a predetermined target high pressure).
  • the refrigerating machine oil is accumulated in the liquid refrigerant accumulated in the condenser. Even if the refrigeration oil accumulates in the condenser in this way, at least one of control for increasing the opening degree of the first valve and control for reducing the opening degree of the second valve if a predetermined condition is satisfied.
  • An oil return operation of the condenser is performed in which the refrigerating machine oil accumulated in the condenser is returned to the compressor together with the refrigerant.
  • the control unit controls the first valve so that the opening degree of the first valve is fully opened in the oil return operation of the condenser.
  • the control unit controls the first valve so that the opening degree of the first valve is fully opened in the oil return operation of the condenser.
  • the control unit preferably performs an oil return operation of the gas pipe that increases the operating capacity of the compressor and returns the refrigeration oil accumulated in the gas pipe of the main refrigerant circuit to the compressor.
  • refrigeration oil may adhere to the inner surface of the gas pipe and accumulate, but by performing an oil return operation of the gas pipe that increases the operating capacity of the compressor, The accumulated refrigeration oil can be returned to the compressor.
  • the control unit preferably performs the oil return operation of the condenser in a state where the operation capacity of the compressor is maintained after performing the oil return operation of the gas pipe.
  • the oil return operation of the condenser is performed in a state in which the operating capacity of the compressor raised in the oil return operation of the gas pipe is maintained, that is, in a state where the refrigerant circulation amount in the refrigerant circuit is increased.
  • the amount of refrigerant flowing through the condenser can be increased. Thereby, the refrigerating machine oil collected in the condenser can be pushed out of the condenser more effectively.
  • the predetermined condition includes, for example, a condition that an oil sump amount is equal to or more than a predetermined reference amount.
  • the amount of oil sump and the degree of refrigeration oil shortage in the compressor are related to each other. Therefore, the oil return operation of the condenser is more reliably performed when the oil return is required by determining whether or not the oil return operation is necessary based on the above-mentioned condition regarding the oil sump amount as in this configuration. Can do.
  • the predetermined condition includes, for example, a condition that an opening degree of the first valve is equal to or less than a predetermined reference opening degree.
  • a predetermined reference opening degree When the opening degree of the first valve is equal to or less than a predetermined reference opening degree, the refrigerating machine oil tends to accumulate in the condenser. Further, when the opening degree of the first valve is equal to or less than a predetermined reference opening degree, the fluctuation range (the opening degree increase amount) of the first valve can be increased in the oil return operation of the condenser. .
  • the oil return operation of the condenser is more reliably performed when the oil return is required by determining whether or not the oil return operation is necessary based on the above-described condition relating to the opening degree of the first valve as in this configuration.
  • the predetermined condition includes, for example, a condition that an outdoor temperature is equal to or lower than a predetermined reference temperature.
  • a predetermined reference temperature When the temperature of the outside air is low, the refrigerant is stored in the condenser during normal operation and the condensation pressure is adjusted to a predetermined range, so that the amount of oil pool increases. Therefore, the oil return operation of the condenser is more reliably executed when the oil return is required by determining whether or not the oil return operation is necessary based on the above-described conditions relating to the outdoor air temperature as in this configuration. Can do.
  • the predetermined condition includes, for example, a condition that a state where the operation capacity of the compressor is equal to or less than a predetermined reference value continues for a predetermined time.
  • the motor of the compressor is operated at a low frequency (number of rotations)
  • the amount of refrigerant circulating through the refrigerant circuit is small, so that the refrigerating machine oil is difficult to be pushed out of the condenser and tends to accumulate in the condenser. Therefore, the oil return operation of the condenser is more reliably executed when the oil return is required by determining whether or not the oil return operation is necessary based on the above-described conditions regarding the operation capacity of the compressor as in this configuration. can do.
  • the control unit may perform control to reduce the air volume of the fan in the oil return operation of the condenser.
  • the control unit may perform control to reduce the air volume of the fan in the oil return operation of the condenser.
  • the opening control of the first valve and the second valve not only the opening control of the first valve and the second valve but also the control for reducing the air volume of the fan is performed.
  • the condensation pressure can be increased by reducing the fan air volume. Therefore, in the configuration in which the opening degree control of at least one of the first valve and the second valve and the air volume control of the fan are performed, a larger fluctuation of the condensation pressure can be generated than in the case of performing only the opening degree control of the valve. it can. Thereby, the refrigerating machine oil collected in the condenser can be pushed out of the condenser more effectively.
  • the condenser may be a water-cooled heat exchanger, and the control unit may perform control to reduce a flow rate of water flowing into the condenser in an oil return operation of the condenser. .
  • the control unit may perform control to reduce a flow rate of water flowing into the condenser in an oil return operation of the condenser.
  • the control unit may perform control to reduce a flow rate of water flowing into the condenser in an oil return operation of the condenser.
  • the condensation pressure can be increased by reducing the flow rate of the water flowing into the condenser. Therefore, in the configuration in which the opening degree control of at least one of the first valve and the second valve and the flow rate control of water are performed, a larger fluctuation of the condensation pressure can be generated than in the case of performing only the opening degree control of the valve. it can. Thereby, the refrigerating machine oil collected in the condenser can be pushed out of the condenser more effectively.

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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)

Abstract

La présente invention concerne un appareil de conditionnement d'air (1) qui est un appareil de conditionnement d'air dédié au refroidissement. Un dispositif de commande (27) de l'appareil de conditionnement d'air (1) effectue : une opération normale lors de laquelle la pression de condensation est ajustée par l'ajustement d'au moins une caractéristique parmi le degré d'ouverture d'un premier clapet (21), le degré d'ouverture d'un second clapet (22) et l'écoulement d'air d'une soufflante (28) ; et une opération de retour d'huile de condenseur lors de laquelle une huile de réfrigération à l'intérieur d'un condenseur (25) est ramenée avec un fluide frigorigène jusqu'à un compresseur (24) par la réalisation d'au moins une commande parmi une commande pour augmenter le degré d'ouverture du premier clapet (21) et une commande pour réduire le degré d'ouverture du second clapet (22), quand une condition prédéfinie est satisfaite.
PCT/JP2014/080759 2013-11-22 2014-11-20 Appareil de conditionnement d'air WO2015076331A1 (fr)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2019020093A (ja) * 2017-07-21 2019-02-07 パナソニックＩｐマネジメント株式会社 空気調和機
EP3998434A4 (fr) * 2019-07-09 2022-07-13 NEC Corporation Système de refroidissement, dispositif de prévention de génération de surtension, procédé de prévention de génération de surtension et programme de prévention de génération de surtension

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE112015006774T5 (de) * 2015-08-04 2018-04-26 Mitsubishi Electric Corporation Kühlgerät und Verfahren zum Betrieb des Kühlgeräts
CN110131840B (zh) * 2019-05-15 2021-05-14 宁波奥克斯电气股份有限公司 一种变频空调回油控制方法和变频空调
CN115342571B (zh) * 2022-06-30 2023-08-04 河北工程大学 一种温度可调的冰温贮藏保温设备

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06193981A (ja) * 1992-12-22 1994-07-15 Hitachi Ltd 冷凍装置
JP2000046419A (ja) * 1998-07-27 2000-02-18 Daikin Ind Ltd 冷凍装置
JP2008076001A (ja) * 2006-09-22 2008-04-03 Daikin Ind Ltd 空気調和装置
JP2008241065A (ja) * 2007-03-26 2008-10-09 Daikin Ind Ltd 冷凍装置及び冷凍装置の油戻し方法
JP2013024538A (ja) * 2011-07-26 2013-02-04 Hitachi Appliances Inc 冷凍装置

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06193981A (ja) * 1992-12-22 1994-07-15 Hitachi Ltd 冷凍装置
JP2000046419A (ja) * 1998-07-27 2000-02-18 Daikin Ind Ltd 冷凍装置
JP2008076001A (ja) * 2006-09-22 2008-04-03 Daikin Ind Ltd 空気調和装置
JP2008241065A (ja) * 2007-03-26 2008-10-09 Daikin Ind Ltd 冷凍装置及び冷凍装置の油戻し方法
JP2013024538A (ja) * 2011-07-26 2013-02-04 Hitachi Appliances Inc 冷凍装置

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2019020093A (ja) * 2017-07-21 2019-02-07 パナソニックＩｐマネジメント株式会社 空気調和機
EP3998434A4 (fr) * 2019-07-09 2022-07-13 NEC Corporation Système de refroidissement, dispositif de prévention de génération de surtension, procédé de prévention de génération de surtension et programme de prévention de génération de surtension

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