US20190017730A1 - Refrigerating machine and control method thereof - Google Patents

Refrigerating machine and control method thereof Download PDF

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Publication number
US20190017730A1
US20190017730A1 US16/065,918 US201716065918A US2019017730A1 US 20190017730 A1 US20190017730 A1 US 20190017730A1 US 201716065918 A US201716065918 A US 201716065918A US 2019017730 A1 US2019017730 A1 US 2019017730A1
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Prior art keywords
refrigerant
condenser
expansion valve
economizer
liquid refrigerant
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US16/065,918
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English (en)
Inventor
Noriyuki Matsukura
Yasushi Hasegawa
Jun Miyamoto
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Mitsubishi Heavy Industries Thermal Systems Ltd
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Mitsubishi Heavy Industries Thermal Systems Ltd
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Assigned to MITSUBISHI HEAVY INDUSTRIES THERMAL SYSTEMS, LTD. reassignment MITSUBISHI HEAVY INDUSTRIES THERMAL SYSTEMS, LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: HASEGAWA, YASUSHI, MATSUKURA, NORIYUKI, MIYAMOTO, JUN
Publication of US20190017730A1 publication Critical patent/US20190017730A1/en
Abandoned legal-status Critical Current

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    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • F25B1/053—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of turbine type
    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/022—Compressor 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/02—Details of evaporators
    • F25B2339/024—Evaporators with refrigerant in a vessel in which is situated a heat exchanger
    • F25B2339/0242—Evaporators with refrigerant in a vessel in which is situated a heat exchanger having tubular elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—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
    • F25B2400/0409—Refrigeration circuit bypassing means for the evaporator
    • 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
    • F25B2400/0411—Refrigeration circuit bypassing means for the expansion valve or capillary tube
    • 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
    • F25B2400/12—Inflammable refrigerants
    • F25B2400/121—Inflammable refrigerants using R1234
    • 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
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size
    • 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
    • F25B2600/022—Compressor control for multi-stage operation
    • 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
    • F25B2600/026—Compressor control by controlling unloaders
    • F25B2600/0261—Compressor control by controlling unloaders external to 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
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/027—Compressor control by controlling pressure
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2515—Flow 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
    • F25B2700/2115—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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2116—Temperatures of a condenser
    • F25B2700/21161—Temperatures of a condenser of the fluid heated by 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2116—Temperatures of a condenser
    • F25B2700/21163—Temperatures of a condenser of the refrigerant at the outlet 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21171—Temperatures of an evaporator of the fluid cooled by the evaporator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators

Definitions

  • the present invention relates to a refrigerator having an economizer which is a plate type heat exchanger and a control method thereof.
  • an economizer is a plate type heat exchanger. Accordingly, compared to a gas-liquid separation type economizer used in a two-stage compression subcooler two-stage expansion cycle, a refrigerant charge amount can be reduced.
  • the present invention is made in consideration of the above-described circumstances, and an object thereof is to provide a refrigerator capable of being appropriately operated against an increase of a refrigerant circulation amount generated in a case where a plate type heat exchanger is used as the economizer and a control method thereof.
  • a refrigerator and a control method thereof according to the present invention adopts the following means.
  • a refrigerator including: a compressor which compresses a refrigerant; a condenser which condenses the refrigerant compressed by the compressor; an economizer which is a plate type heat exchanger which performs heat exchange between a liquid refrigerant introduced from the condenser and a two-phase refrigerant obtained by expanding a portion of the liquid refrigerant introduced from the condenser by a sub-expansion valve; a main expansion valve which expands the liquid refrigerant introduced from the economizer; and an evaporator which expands the refrigerant introduced from the main expansion valve, in which the plate type heat exchanger is configured such that a width of a plate is 100 mm or more and 400 mm or less, a height of the plate is 300 mm or more and 1,000 mm or less, and the number of stacked plates is 80 or more.
  • the plate type heat exchanger is used as the economizer, the width of the stacked plates is 100 mm or more and 400 mm or less, the height of the stacked plates is 300 mm or more and 1,000 mm or less, and the number of the stacked plates is 80 or more. Accordingly, a pressure loss of the economizer can be 100 kPa or more, preferably, can be 150 kPa or more and 200 kPa or less. Therefore, even when a refrigerant circulation amount increases, a predetermined pressure loss can be secured, and thus, a refrigerant distribution in the economizer which is the plate type heat exchanger is appropriately performed, and it is possible to operate a refrigerator without damaging performance of the refrigerator.
  • HFC-134a is appropriately used, or HFO-1234ze(E), HFO-1233zd(E), or HFO-1233zd(Z) may be used.
  • a refrigerator including: a compressor which compresses a refrigerant; a condenser which condenses the refrigerant compressed by the compressor; an economizer which is a plate type heat exchanger which performs heat exchange between a liquid refrigerant introduced from the condenser and a two-phase refrigerant obtained by expanding a portion of the liquid refrigerant introduced from the condenser by a sub-expansion valve; a main expansion valve which expands the liquid refrigerant introduced from the economizer; an evaporator which evaporates the refrigerant introduced from the main expansion valve; a bypass path which bypasses the economizer and through which the liquid refrigerant from the condenser is introduced to an upstream side of the main expansion valve; a bypass valve which is provided in the bypass path; and a controller which controls an opening degree of the bypass valve.
  • the bypass valve is opened by a command of the controller, and a flow rate of the refrigerant flowing through the bypass path increases. Accordingly, it is possible to decrease a flow rate of the liquid refrigerant which flows into the economizer. Therefore, even in a case where the refrigerant circulation amount increases, it is possible to prevent the liquid refrigerant from excessively flowing into the economizer. Accordingly, it is possible to suppress occurrence of a failure of the refrigerant distribution in the economizer which is the plate type heat exchanger.
  • a refrigerator including: a compressor which compresses a refrigerant; a condenser which condenses the refrigerant compressed by the compressor; an economizer which is a plate type heat exchanger which performs heat exchange between a liquid refrigerant introduced from the condenser and a two-phase refrigerant obtained by expanding a portion of the liquid refrigerant introduced from the condenser by a sub-expansion valve; a main expansion valve which expands the liquid refrigerant introduced from the economizer; an evaporator which evaporates the refrigerant introduced from the main expansion valve; a bypass path which bypasses the economizer and through which the liquid refrigerant from the condenser is introduced to a cooled-medium inlet side of the evaporator; a bypass valve which is provided in the bypass path; and a controller which controls an opening degree of the bypass valve.
  • the bypass valve is opened by a command of the controller, and a flow rate of the refrigerant flowing through the bypass path increases. Accordingly, it is possible to decrease a flow rate of the liquid refrigerant which flows into the economizer. Therefore, even in a case where the refrigerant circulation amount increases, it is possible to prevent the liquid refrigerant from excessively flowing into the economizer. Accordingly, it is possible to suppress occurrence of a failure of the refrigerant distribution in the economizer which is the plate type heat exchanger.
  • the main expansion valve can be bypassed, and thus, it is not necessary to adopt an expansion valve having a large diameter in anticipation of an increase of the refrigerant circulation amount, and there is no possibility that control accuracy of the expansion valve deteriorates.
  • the liquid refrigerant is introduced to the cooled-medium (for example, cold water) inlet side of the evaporator via the bypass path. Accordingly, the refrigerant can be introduced to the cooled-medium inlet side which is a region in which a heat exchange amount is large, the refrigerant is evaporated, and thus, dry-out easily occurs. Therefore, the dry-out in this region is suppressed, and it is possible to improve a heat transfer coefficient in the evaporator.
  • the cooled-medium for example, cold water
  • the controller increases the opening degree of the bypass valve.
  • the difference between the pressure in the condenser and the pressure in the evaporator is equal to or less than the predetermined value or the opening degree of the main expansion valve is equal to or more than the predetermined value, it is determined that the refrigerant circulation amount is excessive, and thus, the opening degree of the bypass valve increases. Accordingly, it is possible to suppress occurrence of the failure of the refrigerant distribution in the economizer which is the plate type heat exchanger.
  • the refrigerator includes a compressor which compresses a refrigerant, a condenser which condenses the refrigerant compressed by the compressor, an economizer which is a plate type heat exchanger which performs heat exchange between a liquid refrigerant introduced from the condenser and a two-phase refrigerant obtained by expanding a portion of the liquid refrigerant introduced from the condenser by a sub-expansion valve, a main expansion valve which expands the liquid refrigerant introduced from the economizer, an evaporator which evaporates the refrigerant introduced from the main expansion valve, a bypass path which bypasses the economizer and introduces the liquid refrigerant from the condenser to an upstream side of the main expansion valve, and a bypass valve which is provided in the bypass path, the control method including: increasing the opening degree of the bypass valve in a case where a difference between a pressure in
  • the bypass valve is opened and a flow rate of the refrigerant flowing through the bypass path increases. Accordingly, it is possible to decrease a flow rate of the liquid refrigerant which flows into the economizer. Therefore, even in a case where the refrigerant circulation amount increases, it is possible to prevent the liquid refrigerant from excessively flowing into the economizer. Accordingly, it is possible to suppress occurrence of a failure of the refrigerant distribution in the economizer which is the plate type heat exchanger.
  • the refrigerator includes a compressor which compresses a refrigerant, a condenser which condenses the refrigerant compressed by the compressor, an economizer which is a plate type heat exchanger which performs heat exchange between a liquid refrigerant introduced from the condenser and a two-phase refrigerant obtained by expanding a portion of the liquid refrigerant introduced from the condenser by a sub-expansion valve, a main expansion valve which expands the liquid refrigerant introduced from the economizer, an evaporator which evaporates the refrigerant introduced from the main expansion valve, a bypass path which bypasses the economizer and through which the liquid refrigerant from the condenser is introduced to a cooled-medium inlet side of the evaporator, and a bypass valve which is provided in the bypass path, the control method including: increasing the opening degree of the bypass valve in a case
  • the bypass valve is opened and a flow rate of the refrigerant flowing through the bypass path increases. Accordingly, it is possible to decrease a flow rate of the liquid refrigerant which flows into the economizer. Therefore, even in a case where the refrigerant circulation amount increases, it is possible to prevent the liquid refrigerant from excessively flowing into the economizer. Accordingly, it is possible to suppress occurrence of a failure of the refrigerant distribution in the economizer which is the plate type heat exchanger.
  • the main expansion valve can be bypassed, and thus, it is not necessary to adopt an expansion valve having a large diameter in anticipation of an increase of the refrigerant circulation amount, and there is no possibility that control accuracy of the expansion valve deteriorates.
  • the liquid refrigerant is introduced to the cooled-medium (for example, cold water) inlet side of the evaporator via the bypass path. Accordingly, the refrigerant can be introduced to the cooled-medium inlet side which is a region in which the heat exchange amount is large, the refrigerant is evaporated, and thus, dry-out easily occurs. Therefore, the dry-out in this region is suppressed, and it is possible to improve a heat transfer coefficient in the evaporator.
  • the cooled-medium for example, cold water
  • the width, the height, and the number of the stacked plates it is possible to secure a predetermined pressure loss even when the refrigerant circulation amount increases. Accordingly, the refrigerant distribution in the economizer which is the plate type heat exchanger is appropriately performed, and it is possible to operate a refrigerator without damaging performance of the refrigerator.
  • FIG. 1 is a schematic configuration diagram showing a turbo refrigerator according to a first embodiment of the present invention.
  • FIG. 2 is a longitudinal sectional diagram showing a schematic configuration of an economizer of FIG. 1 .
  • FIG. 3 is a diagram showing a result of thermography of an economizer according to the first embodiment.
  • FIG. 4 is a diagram showing a result of thermography of an economizer according to a reference example.
  • FIG. 5 is a schematic configuration diagram showing a turbo refrigerator according to a second embodiment of the present invention.
  • FIG. 6 is a schematic configuration diagram showing a turbo refrigerator according to a third embodiment of the present invention.
  • FIG. 7 is a longitudinal sectional diagram schematically showing an evaporator of FIG. 6 .
  • a turbo refrigerator (refrigerator) 1 includes a turbo compressor (compressor) 2 , a condenser 3 , an economizer 4 , a main expansion valve 5 , an evaporator 7 , and a controller (not shown).
  • the turbo compressor 2 is a centrifugal compressor which is driven by an inverter motor 9 and includes an intermediate intake port 2 C provided between a first impeller (not shown) and a second impeller (not shown) in addition to an intake port 2 A and a discharge port 2 B.
  • a low-pressure gas refrigerant sucked from the intake port 2 A is compressed in two stages by rotations of the first impeller and the second impeller, and the compressed high-pressure gas refrigerant is discharged from the discharge port 2 B.
  • HFC-134a As a refrigerant, HFC-134a is used. However, HFO-1234ze(E), HFO-1233zd(E), or HFO-1233zd(Z) may be used.
  • the high-pressure gas refrigerant discharged from the discharge port 2 B of the turbo compressor 2 is introduced to an oil mist separation tank 10 , and oil in the refrigerant is centrifugally separated.
  • the high-pressure cooling gas from which the oil is centrifugally separated is introduced from the oil mist separation tank 10 to the condenser 3 .
  • the condenser 3 is a shell and tube type heat exchanger and performs heat exchange between the high-pressure gas refrigerant supplied via the oil mist separation tank 10 from the turbo compressor 2 and cooling water which circulates a cooling water circuit 11 , and thus, the high-pressure cooling gas is condensed and liquefied.
  • the cooling water circuit 11 is connected to a cooling tower (not shown) and the cooling water is cooled to a predetermined temperature by the cooling tower.
  • the flow of the cooling water supplied by a cooling water pump 12 and the flow of the high-pressure gas refrigerant are made to flow countercurrently.
  • a plate type heat exchanger may be used as the condenser 3 .
  • the economizer 4 is the plate type heat exchanger which performs heat exchange between a liquid refrigerant which flows through a main circuit of a refrigeration cycle 8 and is introduced from the condenser 3 and a two-phase refrigerant which branches off from the main circuit and is decompressed by the sub-expansion valve 13 and supercools the liquid refrigerant flowing through the main circuit by evaporation latent heat of the refrigerant.
  • a gas circuit 14 through which a gas refrigerant (intermediate-pressure refrigerant) which is evaporated by supercooling the liquid refrigerant is injected into a compressed refrigerant having an intermediate pressure from the intermediate intake port 2 C of the turbo compressor 2 is connected to the economizer 4 .
  • the refrigerant supercooled via the economizer 4 passes through the main expansion valve 5 to be expanded and is supplied to the evaporator 7 .
  • the evaporator 7 is the shell and tube type heat exchanger and performs heat exchange between the refrigerant introduced from the main expansion valve 5 and the cold water (cooled medium) which circulates via a cold water circuit 15 , evaporates the refrigerant, and cools the cold water by the evaporation latent heat.
  • the flow of the cold water supplied by the cold water pump 16 and the flow of the refrigerant are made to flow countercurrently.
  • a plate type heat exchanger may be used as the evaporator 7 .
  • the refrigeration cycle 8 includes a hot gas bypass circuit 17 which bypasses a portion of the high-pressure gas refrigerant in which the oil is separated by the oil mist separation tank 10 from between the condenser 3 and the turbo compressor 2 .
  • a hot gas bypass valve 18 is provided in the hot gas bypass circuit 17 , and the hot gas bypass valve 18 adjusts a flow rate of the high-pressure gas refrigerant introduced from the hot gas bypass circuit 17 to the turbo compressor 2 .
  • thermometers 31 , 32 , and 33 are provided in the intake port 2 A of the turbo compressor 2 , the discharge port 2 B, and the intermediate intake port 2 C, and thermometers 35 , 36 , 37 , and 38 are respectively provided in an inlet and an outlet of the cooling water circuit 11 and an inlet and an outlet of the cold water circuit 15 , and the thermometer 34 is provided in the inlet of the main expansion valve 5 .
  • the turbo refrigerator 1 is controlled by the controller (not shown).
  • the controller includes a Central Processing Unit (CPU), a Random Access Memory (RAM), a Read Only Memory (ROM), a computer readable storage medium, or the like.
  • CPU Central Processing Unit
  • RAM Random Access Memory
  • ROM Read Only Memory
  • a series of processing for realizing various functions is stored in the storage medium or the like as a program form, and the CPU reads the program to a RAM or the like and executes information processing/calculation processing to realize the various functions.
  • the program may be installed in the ROM or other storage mediums in advance, may be supplied in a form stored in a computer readable storage medium, or may be distributed via wired or wireless communication means.
  • the computer readable storage medium is a magnetic disk, a magneto-optical disk, a CD-ROM, a DVD-ROM, a semiconductor memory, or the like.
  • FIG. 2 shows a schematic configuration of the economizer 4 .
  • the economizer 4 is the plate type heat exchanger in which the plurality of stacked plates 40 are stacked to form a plurality of flow paths adjacent to each other in parallel.
  • only six flow paths 42 a and 42 b are shown in FIG. 2 .
  • this is merely an example, and actually, 80 flow paths or more may be formed.
  • the flow paths 42 a of the liquid refrigerant which are introduced from the condenser 3 (indicated by “CON” in the drawing) and the flow paths 42 b of the two-phase refrigerant which branch from the condenser 3 and are introduced after passing through the sub-expansion valve are alternately provided and are made to flow countercurrently.
  • the liquid refrigerant from the condenser 3 passes through the flow paths 42 a from the upper side in the drawing toward the lower side in the drawing to pass through the economizer 4 .
  • the liquid refrigerant which has flowed through the economizer 4 is throttled by the main expansion valve 5 and, thereafter, is introduced to the evaporator 7 (indicated by “EVA” in the drawing).
  • a portion of the liquid refrigerant branching from the condenser 3 is throttled by the sub-expansion valve 13 so as to be the two-phase refrigerant, and thereafter, flows into each of the flow paths 42 b of the economizer 4 , and flows from the upper side in the drawing to the lower side.
  • a distributor 44 which applies a predetermined pressure loss is provided on the upstream side of each of the flow paths 42 b.
  • the two-phase refrigerant can be uniformly distributed to each of the flow paths 42 b by the distributor 44 .
  • the gas refrigerant which is changed from the two-phase refrigerant to the gas refrigerant while passing through the economizer 4 , flows from the intermediate intake port 2 C of the turbo compressor 2 (indicated by “COMP” in the drawing).
  • the liquid refrigerant which is introduced from the condenser 3 and flows through the flow paths 42 a from the upper side to the lower side in the drawing is cooled by the evaporation latent heat of the adjacent two-phase refrigerant so as to be a supercooled refrigerant, and the two-phase refrigerant which is introduced from the sub-expansion valve 13 and flows through the flow path 42 b from the lower side to the upper side in FIG. 1 acquires the evaporation latent heat from the adjacent liquid refrigerant and is changed to the gas refrigerant.
  • the width of the stacked plates 40 is 100 mm or more and 400 mm or less, the height of the stacked plates 40 is 300 mm or more and 1000 mm or less, and the number of the stacked plates 40 is 80 or more and 400 or less. Accordingly, the pressure loss of the economizer 4 can be 100 kPa or more, and, preferably, can be 150 kPa or more and 200 kPa or less. In addition, it is possible to suppress the failure in the refrigerant distribution of the flow path 42 b of the two-phase refrigerant.
  • the pressure loss of the economizer 4 which is the plate type heat exchanger is adjusted by increasing or decreasing the number of the stacked plates 40 . Specifically, a total cross-sectional area of the flow path is increased by increasing the number of the stacked plates, a flow rate decreases, and thus, the pressure loss decreases. In addition, the total cross-sectional area of the flow path is decreased by decreasing the number of stacked plates, the flow rate increases, and thus, the pressure loss increases.
  • FIGS. 3 and 4 show a state of the refrigerant distribution in the economizer 4 .
  • FIG. 3 shows the economizer 4 according to the present embodiment, and the number of the stacked plates is 86.
  • the refrigerant HFC-134a is used.
  • FIG. 3 shows a result of thermography when the economizer 4 is viewed from the front surface as shown in FIG. 2 . That is, a right-left direction in the drawings is a stacking direction, the two-phase refrigerant flow from the lower side toward the upper side, and the liquid refrigerant flows from the upper side toward the lower side. It can be understood from FIG. 3 that a temperature difference in the right-left direction is not large. This means that the refrigerant distribution is good. In the case of FIG. 3 , the pressure loss is 100 kPa or more.
  • FIG. 4 is a reference example and shows the result of the thermography similar to FIG. 3 .
  • FIG. 4 is different from FIG. 3 in that the number of the stacked plates is 212 .
  • the temperature difference in the right-left direction (stacking direction) is large and the refrigerant distribution is not good.
  • the pressure loss is 10 to 20 kPa. In this way, if the number of the stacked plates increases according to the increase of the refrigerant circulation amount, the pressure loss in the economizer decreases, and thus, it can be understood that the failure in the refrigerant distribution occurs.
  • the plate type heat exchanger is used as the economizer 4 , the width of the stacked plates 40 is 100 mm or more and 400 mm or less, the height of the stacked plates 40 is 300 mm or more and 1,000 mm or less, and the number of the stacked plates 40 is 80 or more. Accordingly, the pressure loss of the economizer 4 can be 100 kPa or more, preferably, can be 150 kPa or more and 200 kPa or less. Therefore, even when the refrigerant circulation amount increases, a predetermined pressure loss can be secured, and thus, a refrigerant distribution in the economizer 4 which is the plate type heat exchanger is appropriately performed, and it is possible to operate a refrigerator without damaging performance of the refrigerator.
  • the present embodiment is different from the first embodiment in that a bypass path is provided, and other portions are similar to each other. Accordingly, the same reference numerals are assigned to the same configurations, and descriptions thereof are omitted.
  • a bypass path 50 which bypasses the economizer 4 and through which the liquid refrigerant from the condenser 3 is introduced to the upstream side of the main expansion valve 5 , is provided.
  • An upstream end of the bypass path 50 is provided on a downstream side of a branch point A from which branches to the sub-expansion valve 13 .
  • a bypass valve 52 is provided in the bypass path 50 .
  • the bypass valve 52 an electrical ball valve capable of adjusting an opening degree is used.
  • a solenoid valve which is simply opened or closed may be used.
  • a command of the opening degree of the bypass valve 52 is performed by the controller (not shown).
  • the controller determines that the refrigerant circulation amount is excessive, and the controller increases the opening degree of the bypass valve 52 .
  • the bypass valve 52 is opened by the command of the controller to increase the flow rate of the refrigerant flowing through the bypass path 50 . Accordingly, it is possible to decrease the flow rate of the liquid refrigerant flowing into the economizer 4 . Accordingly, even in a case where the refrigerant circulation amount increases, it is possible to prevent the liquid refrigerant from excessively flowing into the economizer 4 . Accordingly, it is possible to suppress occurrence of a failure of the refrigerant distribution in the economizer 4 which is the plate type heat exchanger.
  • the plate type heat exchanger having the configuration shown in the first embodiment may not be used as the economizer 4 . That is, an economizer may be used in which the pressure loss is adjusted such that a desired refrigerant distribution is performed on the flow rate of the refrigerant which flows into the economizer 4 when the liquid refrigerant is bypassed through the bypass path 50 .
  • the present embodiment is different from the first embodiment in that the bypass path is provided, and other portions are similar to each other. Accordingly, the same reference numerals are assigned to the same configurations, and descriptions thereof are omitted.
  • a bypass path 60 which bypasses the economizer 4 and through which the liquid refrigerant from the condenser 3 is introduced to the cold water (cooled-medium) inlet side of the evaporator 7 , is provided.
  • An upstream end of the bypass path 60 is provided on a downstream side of a branch point A from which branches to the sub-expansion valve 13 .
  • a bypass valve 62 is provided in the bypass path 60 .
  • the bypass valve 62 an electrical ball valve capable of adjusting an opening degree is used. However, a solenoid valve which is simply opened or closed may be used.
  • a command of the opening degree of the bypass valve 62 is performed by the controller (not shown). In a case where the difference between the pressure in the condenser 3 and the pressure in the evaporator 7 is equal to or less than a predetermined value, or in a case where the opening degree of the main expansion valve 5 is equal or more than a predetermined value, the controller determines that the refrigerant circulation amount is excessive, and the controller increases the opening degree of the bypass valve 62 .
  • FIG. 7 shows a schematic configuration of the evaporator 7 .
  • the evaporator 7 is a shell and tube type evaporator and a cylindrical container which has an approximately circular cross section and a horizontal axis line.
  • Water chambers to which the cold water is introduced are provided on both end portions of the evaporator 7 , and a space which is interposed between the water chambers 45 and 46 becomes an evaporation chamber 47 in which the refrigerant introduced from the economizer 4 exists.
  • Pipe plates 48 are partitioned between the water chambers 45 and 46 and the evaporation chamber 47 .
  • a plurality of heat transfer pipe 49 are connected to each other between the water chambers 45 and 46 .
  • the heat transfer pipes 49 configures the plurality of pipe groups (not shown).
  • a liquid distribution structure 68 which is a porous plate for distributing the two-phase refrigerant flowing into the evaporator 7 is provided below the heat transfer pipe 49 .
  • one water chamber 45 partitions a chamber for the cold water inlet and a chamber for a cold water outlet.
  • a refrigerant pipe 53 into which the refrigerant introduced via the main expansion valve 5 from the economizer 4 is introduced is connected to an approximately center position in the horizontal axis line below the evaporator 7 .
  • a suction pipe 64 through which the refrigerant gas evaporated in the evaporator 7 is introduced to the intake port 2 A of the turbo compressor 2 is connected to an upper portion of the evaporator 7 .
  • a gas-liquid separation structure 66 which is a porous plate so as to separate a gas and a liquid is provided in the vicinity of an upstream side of a position at which the suction pipe 64 is connected.
  • a hot gas bypass pipe 65 is connected to an end portion of an upper portion of the evaporator 7 .
  • bypass path 60 is connected to the cold water inlet side (the left side in the drawing) from the center position in a horizontal axial direction of the evaporator 7 . Accordingly, the refrigerant passing through the bypass valve 62 is introduced to the vicinity of the heat transfer pipe 49 through which the cold water on the cold water inlet side of the evaporator 7 flows.
  • the bypass valve 62 is opened by the command of the controller to increase the flow rate of the refrigerant flowing through the bypass path 60 . Accordingly, it is possible to decrease the flow rate of the liquid refrigerant flowing into the economizer 4 . Accordingly, even in a case where the refrigerant circulation amount increases, it is possible to prevent the liquid refrigerant from excessively flowing into the economizer 4 . Accordingly, it is possible to suppress occurrence of a failure of the refrigerant distribution in the economizer 4 which is the plate type heat exchanger.
  • the main expansion valve 5 can be bypassed, and thus, it is not necessary to adopt an expansion valve having a large diameter in anticipation of an increase of the refrigerant circulation amount, and there is no possibility that control accuracy of the expansion valve deteriorates.
  • the refrigerant is introduced to the inlet side of the cold water of the evaporator 7 via the bypass path 60 . Accordingly, the refrigerant can be introduced to the inlet side of the cold water which is a region in which the heat exchange amount is large, the refrigerant is evaporated, and thus, dry-out easily occurs. Therefore, the dry-out in this region is suppressed, and it is possible to improve a heat transfer coefficient in the evaporator.
  • the plate type heat exchanger having the configuration shown in the first embodiment may not be used as the economizer 4 . That is, an economizer may be used in which the pressure loss is adjusted such that a desired refrigerant distribution is performed on the flow rate of the refrigerant which flows into the economizer 4 when the liquid refrigerant is bypassed through the bypass path 60 .

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10578342B1 (en) * 2018-10-25 2020-03-03 Ricardo Hiyagon Moromisato Enhanced compression refrigeration cycle with turbo-compressor
CN113294925A (zh) * 2021-05-21 2021-08-24 浙江国祥股份有限公司 一种带复合式经济器的蒸发冷凝式冷水机组
US11162723B2 (en) * 2019-03-29 2021-11-02 Trane International Inc. Methods and systems for controlling working fluid in HVACR systems
US20220381485A1 (en) * 2019-10-07 2022-12-01 Shinwa Controls Co., Ltd Hydrogen cooling apparatus, hydrogen supply system, and refrigerator
EP4137759A1 (fr) * 2021-08-20 2023-02-22 Carrier Corporation Système de contrôle de dilatation d'un dispositif frigorifique centrifuge avec un sous-refroidisseur intégré
US20230296243A1 (en) * 2021-06-16 2023-09-21 Colorado State University Research Foundation Air source heat pump system and method of use for industrial steam generation

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6878550B2 (ja) * 2019-10-31 2021-05-26 三菱重工サーマルシステムズ株式会社 冷凍装置
EP3879207B1 (fr) * 2020-03-10 2023-09-06 Trane International Inc. Appareils de réfrigération et procédé pour leur opération
JP2022085386A (ja) * 2020-11-27 2022-06-08 三菱重工サーマルシステムズ株式会社 冷凍機
CN113048667B (zh) * 2021-03-22 2022-04-05 西安交通大学 一种低温保存箱快速启动的混合工质制冷系统及控制方法

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4832068A (en) * 1987-12-21 1989-05-23 American Standard Inc. Liquid/gas bypass
US20060207753A1 (en) * 2005-03-18 2006-09-21 Homayoun Sanatgar Intank oil cooler
US20130025306A1 (en) * 2010-09-30 2013-01-31 Mitsubishi Heavy Industries, Ltd. Turbo refrigeration unit, control device therefor, and control method therefor
US20160236538A1 (en) * 2013-09-18 2016-08-18 Sanden Holdings Corporation Vehicular air conditioner

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000193390A (ja) * 1998-12-25 2000-07-14 Daikin Ind Ltd プレ―ト式熱交換器
SE524176C2 (sv) * 2002-11-01 2004-07-06 Ep Technology Ab Värmeväxlare med förstärkningsorgan
US7114349B2 (en) * 2004-12-10 2006-10-03 Carrier Corporation Refrigerant system with common economizer and liquid-suction heat exchanger
CN101886852B (zh) * 2009-05-15 2012-07-25 珠海格力电器股份有限公司 应用过冷器的空调系统的制冷剂流量的控制方法
JP5155953B2 (ja) * 2009-06-19 2013-03-06 荏原冷熱システム株式会社 ターボ冷凍機
JP6176470B2 (ja) * 2011-02-04 2017-08-09 三菱重工サーマルシステムズ株式会社 冷凍機
WO2013183113A1 (fr) * 2012-06-05 2013-12-12 三菱電機株式会社 Échangeur de chaleur du type à plaques et dispositif à cycle frigorifique le comprenant
JP6028221B2 (ja) * 2012-07-12 2016-11-16 パナソニックＩｐマネジメント株式会社 熱交換器ユニットおよびそれを備えたヒートポンプ温水暖房装置
JP6105972B2 (ja) * 2013-02-27 2017-03-29 荏原冷熱システム株式会社 ターボ冷凍機
JP2015194301A (ja) * 2014-03-31 2015-11-05 荏原冷熱システム株式会社 ターボ冷凍機
EP3171096A4 (fr) * 2014-07-16 2018-03-14 Mitsubishi Electric Corporation Dispositif de réfrigération et de climatisation
JP6433709B2 (ja) * 2014-07-30 2018-12-05 三菱重工サーマルシステムズ株式会社 ターボ冷凍機及びその制御装置並びにその制御方法

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4832068A (en) * 1987-12-21 1989-05-23 American Standard Inc. Liquid/gas bypass
US20060207753A1 (en) * 2005-03-18 2006-09-21 Homayoun Sanatgar Intank oil cooler
US20130025306A1 (en) * 2010-09-30 2013-01-31 Mitsubishi Heavy Industries, Ltd. Turbo refrigeration unit, control device therefor, and control method therefor
US20160236538A1 (en) * 2013-09-18 2016-08-18 Sanden Holdings Corporation Vehicular air conditioner
JP6271195B2 (ja) * 2013-09-18 2018-01-31 サンデンホールディングス株式会社 車両用空気調和装置

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10578342B1 (en) * 2018-10-25 2020-03-03 Ricardo Hiyagon Moromisato Enhanced compression refrigeration cycle with turbo-compressor
US11162723B2 (en) * 2019-03-29 2021-11-02 Trane International Inc. Methods and systems for controlling working fluid in HVACR systems
US20220049886A1 (en) * 2019-03-29 2022-02-17 Trane International Inc. Methods and systems for controlling working fluid in hvacr systems
US20220381485A1 (en) * 2019-10-07 2022-12-01 Shinwa Controls Co., Ltd Hydrogen cooling apparatus, hydrogen supply system, and refrigerator
CN113294925A (zh) * 2021-05-21 2021-08-24 浙江国祥股份有限公司 一种带复合式经济器的蒸发冷凝式冷水机组
US20230296243A1 (en) * 2021-06-16 2023-09-21 Colorado State University Research Foundation Air source heat pump system and method of use for industrial steam generation
EP4137759A1 (fr) * 2021-08-20 2023-02-22 Carrier Corporation Système de contrôle de dilatation d'un dispositif frigorifique centrifuge avec un sous-refroidisseur intégré
US12007149B2 (en) 2021-08-20 2024-06-11 Carrier Corporation Expansion control system on a centrifugal chiller with an integral subcooler

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