US20150168024A1 - Cooling apparatus - Google Patents

Cooling apparatus Download PDF

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Publication number
US20150168024A1
US20150168024A1 US14/567,001 US201414567001A US2015168024A1 US 20150168024 A1 US20150168024 A1 US 20150168024A1 US 201414567001 A US201414567001 A US 201414567001A US 2015168024 A1 US2015168024 A1 US 2015168024A1
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US
United States
Prior art keywords
refrigerant
evaporator
refrigerant circuit
cooling
ejector
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US14/567,001
Other languages
English (en)
Inventor
Byung moo Lee
Hee Moon Jeong
Seong Ho Kil
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Samsung Electronics Co Ltd
Original Assignee
Samsung Electronics Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Samsung Electronics Co Ltd filed Critical Samsung Electronics Co Ltd
Assigned to SAMSUNG ELECTRONICS CO., LTD. reassignment SAMSUNG ELECTRONICS CO., LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: JEONG, HEE MOON, KIL, SEONG HO, LEE, BYUNG MOO
Publication of US20150168024A1 publication Critical patent/US20150168024A1/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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control 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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • 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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/04—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in series
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D21/00—Defrosting; Preventing frosting; Removing condensed or defrost water
    • F25D21/002—Defroster control
    • F25D21/006—Defroster control with electronic control circuits
    • 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
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/001—Ejectors not being used as compression device
    • F25B2341/0011—Ejectors with the cooled primary flow at reduced or low 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
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/001—Ejectors not being used as compression device
    • F25B2341/0012—Ejectors with the cooled primary flow at high 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
    • 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
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • F25B2400/052—Compression system with heat exchange between particular parts of the system between the capillary tube and another part of the refrigeration cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • F25B2400/054—Compression system with heat exchange between particular parts of the system between the suction tube of the compressor and another part of the cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B2400/06—Several compression cycles arranged in parallel
    • 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
    • F25B2400/23—Separators
    • 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
    • F25B2500/06—Damage
    • 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
    • F25B2500/14—Problems to be solved the presence of moisture in a refrigeration component or cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/19—Calculation of parameters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/28—Means for preventing liquid refrigerant entering into 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
    • F25B2600/025—Compressor control by controlling speed
    • F25B2600/0251—Compressor control by controlling speed with on-off 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
    • F25B2600/025—Compressor control by controlling speed
    • F25B2600/0253—Compressor control by controlling speed with variable speed
    • 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
    • F25B2600/112—Fan speed control of evaporator 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
    • F25B2600/23—Time delays
    • 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
    • F25B2600/2507—Flow-diverting 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
    • F25B2600/2519—On-off 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
    • F25B2700/02—Humidity
    • 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
    • F25B2700/2104—Temperatures of an indoor room or compartment
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/385—Dispositions with two or more expansion means arranged in parallel on a refrigerant line leading to the same 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D21/00—Defrosting; Preventing frosting; Removing condensed or defrost water
    • F25D21/06—Removing frost
    • F25D21/08—Removing frost by electric heating
    • 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

  • Embodiments of the present disclosure relate to a cooling apparatus, more particularly a cooling apparatus having improved Coefficient of Performance (COP).
  • COP Coefficient of Performance
  • a cooling apparatus having at least two cooling chambers separated by a center partition is provided so that each cooling chamber is opened/closed by a door.
  • each cooling chamber may have an evaporator generating cooling air and a fan blowing the cooling air in to each chamber. All cooling chambers may be independently refrigerated by each evaporator and each fan, which is referred as a separate-cooling type.
  • a representative cooling apparatus having the separate-cooling type may be a refrigerator provided with a refrigerating compartment and a freezing compartment.
  • the freezing compartment is to store frozen food, and a proper temperature thereof may be about ⁇ 18° C.
  • the refrigerating compartment is store general food, which is stored at a cool temperature without requiring freezing, and a proper temperature thereof may be about 3° C.
  • evaporation temperatures of a first evaporator and a second evaporator in conventional refrigerators are the same. Because of this, a fan of the freezing compartment is rotated continuously and a fan of the refrigerating compartment is rotated intermittently as needed to blow cool air to the refrigerating compartment so that a temperature of the refrigerating compartment may be prevented from being lowered.
  • a load of a compressor may be increased unnecessarily since a refrigerant is compressed corresponding to the evaporation temperature required by the second evaporator.
  • a cooling apparatus includes a first refrigerant circuit configured to allow a refrigerant discharged from a compressor to flow to a suction side of the compressor by passing through a condenser, an ejector, and a vapor liquid separator; a second refrigerant circuit configured to allow the refrigerant to be sucked into an inlet of the ejector to be circulated by passing through the ejector, the vapor liquid separator, a first expansion device, a first evaporator and a second evaporator; and a third refrigerant circuit configured to allow the refrigerant passing through the vapor liquid separator to be sucked into an inlet of the ejector by passing through a second expansion device and the second evaporator to bypass the first expansion device and the first evaporator, wherein the ejector may mix a refrigerant, which is discharged from the condenser in the first refrigerant circuit, and a
  • the cooling apparatus may include a flow path switching device installed on a portion of a discharge side of the vapor liquid separator to allow a liquid refrigerant passing through the vapor liquid separator to flow through at least one of the second refrigerant circuit and the third refrigerant circuit.
  • the cooling apparatus may include a control unit configured to control a refrigerant flow by selectively opening or closing the flow path switching device, wherein the control unit may control the flow path switching so that a refrigerant may flow in the second refrigerant circuit when power supply is started and a refrigerant may flow in the third refrigerant circuit when cooling through the second refrigerant circuit is completed.
  • a control unit configured to control a refrigerant flow by selectively opening or closing the flow path switching device, wherein the control unit may control the flow path switching so that a refrigerant may flow in the second refrigerant circuit when power supply is started and a refrigerant may flow in the third refrigerant circuit when cooling through the second refrigerant circuit is completed.
  • the second refrigerant circuit may be configured to allow a refrigerant passing through the first evaporator to pass through the second evaporator.
  • the ejector may increase pressure of a refrigerant discharged from the condenser and a refrigerant discharged from the second evaporator, and discharge to the vapor liquid separator.
  • the vapor liquid separator may separate a refrigerant discharged from the ejector into a vapor refrigerant and a liquid refrigerant, may discharge the vapor refrigerant to the first refrigerant circuit, and may discharge the liquid refrigerant to the second refrigerant circuit or the third refrigerant circuit
  • the ejector may include a nozzle configured to decompress and expand a refrigerant discharged from the condenser, a suction unit configured to suction a refrigerant discharged from the second evaporator, a mixing unit configured to mix a refrigerant introduced to the nozzle and a refrigerant introduced to the suction unit, and a diffuser configured to raise a pressure of a refrigerant mixed in the mixing unit.
  • the compressor may include an inverter compressor configured to control the amount of a refrigerant flow by controlling a rotation.
  • the expansion device may include at least one of a capillary, an electronic expansion valve and a capillary tube.
  • the cooling apparatus may further include a third expansion device provided on a discharge unit of the condenser to increase a humidity of a refrigerant introduced to the ejector.
  • the cooling apparatus may further include a Suction Line Heat Exchanger (SLHX) configured to exchange heat between the third expansion device and the suction unit of the compressor.
  • SSHX Suction Line Heat Exchanger
  • the first refrigerant circuit may further include a heat exchanger configured to exchange heat between the discharge unit of the condenser and the suction unit of the compressor.
  • the second refrigerant circuit may include an intermediate expansion device provided on a discharge unit of the first evaporator to decompress a refrigerant flowing in the second evaporator.
  • An internal diameter of the intermediate expansion device may be smaller than an internal diameter of a refrigerant pipe disposed on a suction side of the compressor.
  • a cooling apparatus includes a main refrigerant circuit, an entire cooling mode refrigerant circuit, a freezing mode refrigerant circuit, a flow path switching device, and an ejector.
  • the main refrigerant circuit may include a vapor liquid separator separating a refrigerant into a vapor refrigerant and a liquid refrigerant, a compressor compressing a refrigerant by introducing the vapor refrigerant, which is separated in the vapor liquid separator and a condenser condensing a refrigerant compressed by the compressor.
  • the entire cooling mode refrigerant circuit may be configured to pass through a first expansion device, a first evaporator, and a second evaporator.
  • the freezing mode refrigerant circuit may be configured to pass through the second expansion device and the second evaporator to bypass the first expansion device and the first evaporator.
  • the flow path switching device may be configured to switch a flow path to allow a liquid refrigerant introduced from the vapor liquid separator to flow through at least one of the entire cooling mode refrigerant circuit and the freezing mode refrigerant circuit.
  • the ejector may mix a refrigerant, which is discharged from the condenser in the main refrigerant circuit, and a refrigerant, which is discharged from the second evaporator in at least one of the entire cooling mode refrigerant circuit and the freezing mode refrigerant circuit, to introduce to the vapor liquid separator
  • the ejector may increase a pressure of a refrigerant discharged from the condenser and a refrigerant discharged from the second evaporator, and discharge to the vapor liquid separator.
  • a control method of a cooling apparatus provided with a first refrigerant circuit configured to allow a refrigerant discharged from a compressor to flow to a suction side of the compressor by passing through a condenser, an ejector, and a vapor liquid separator; a second refrigerant circuit configured to allow the refrigerant to be sucked into an inlet of the ejector to be circulated by passing through the ejector, the vapor liquid separator, a first expansion device, a first evaporator cooling a first cooling compartment, and a second evaporator cooling a second cooling compartment; a third refrigerant circuit configured to allow the refrigerant passing through the vapor liquid separator to be sucked into an inlet of the ejector by passing through a second expansion device and the second evaporator to bypass the first expansion device and the first evaporator, and a flow path switching device installed on a portion of a discharge side of the
  • the amount of a refrigerant flow in the entire cooling mode and the freezing mode may be adjusted by controlling the number of rotation of the compressor when an operation through the first refrigerant circuit and the second refrigerant circuit is referred to as an entire cooling mode, and an operation through the first refrigerant circuit and the third refrigerant circuit is referred to as a freezing mode.
  • the first evaporator may be defrosted by supplying the compressed refrigerant discharged from the compressor to the second refrigerant circuit since the third refrigerant circuit may be closed and the second refrigerant circuit may be opened by controlling the flow path switching device when driving the compressor is stopped.
  • FIG. 1 is a view of a cooling apparatus according to a first embodiment of the present disclosure
  • FIG. 2 is a view of a refrigerant flow in an ejector in the cooling apparatus according to a first embodiment of the present disclosure
  • FIG. 3 is a Mollier diagram of the cooling apparatus according to a first embodiment of the present disclosure
  • FIG. 4 is a view of operations of each component in each mode of the cooling apparatus according to a first embodiment of the present disclosure
  • FIG. 5 is a view of a control diagram of the cooling apparatus according to a first embodiment of the present disclosure
  • FIG. 6A is a view of a multi cycle type cooling apparatus
  • FIG. 6B is a table comparing the multi cycle type cooling apparatus with the cooling apparatus according to a first embodiment of the present disclosure
  • FIG. 7 is a view of a cooling apparatus according to a second embodiment of the present disclosure.
  • FIG. 8 is a Mollier diagram of the cooling apparatus according to a second embodiment of the present disclosure.
  • FIG. 9 is a view of a cooling apparatus according to a third embodiment of the present disclosure.
  • FIG. 10 is a Mollier diagram of the cooling apparatus according to a third embodiment of the present disclosure.
  • FIG. 11 is a schematic view of a refrigerator provided with a cooling apparatus according to a fourth embodiment of the present disclosure.
  • FIG. 12 is a view of the cooling apparatus according to a fourth embodiment of the present disclosure.
  • FIG. 1 is a view of a cooling apparatus according to a first embodiment of the present disclosure.
  • FIG. 2 is a view of the amount of refrigerant flow in an ejector in the cooling apparatus according to a first embodiment of the present disclosure.
  • a compressor 110 , a condenser 120 , a first evaporator 154 , a second evaporator 164 , and an ejector 130 may be connected by a refrigerant pipe so that a closed loop refrigerant circuit may be provided.
  • a cooling apparatus may include a first refrigerant circuit, a second refrigerant circuit, and a third refrigerant circuit.
  • a refrigerant discharged from the compressor 110 may flow a suction side of the compressor 110 by passing through the condenser 120 , the ejector 130 , and a vapor liquid separator 140 .
  • a refrigerant may flow the ejector 130 , the vapor liquid separator 140 , a first expansion device 152 , a first evaporator 154 , and a second evaporator 164 and be sucked into a suction unit 132 of the ejector 130 to be circulated.
  • a refrigerant passed through the vapor liquid separator 140 may flow a second expansion device 162 and the second evaporator 164 , and be sucked into the suction unit 132 to bypass the first expansion device 152 and the first evaporator 154 .
  • the first refrigerant circuit may be referred to as a main refrigerant circuit
  • the second refrigerant circuit may be referred to as an entire cooling mode circuit
  • the third refrigerant circuit may be referred to as a freezing mode refrigerant circuit.
  • the first evaporator 154 and the second evaporator 164 are not limited thereto, but according to one embodiment of the present disclosure, the first evaporator 154 may be used for a refrigerating compartment 150 of a refrigerator, and the second evaporator 164 may be used for a freezing compartment 160 of a refrigerator. That is, the first evaporator 154 may be referred to as a refrigerating compartment evaporator and the second evaporator 164 may be referred to as a freezing compartment evaporator.
  • a flow path switching device 170 may control a refrigerant flow between the second refrigerant circuit and the third refrigerant circuit. Particularly, the flow path switching device 170 may be installed in a discharge side of the vapor liquid separator 140 to switch a flow path so that a liquid refrigerant passed through the vapor liquid separator 140 may pass at least one of the second and the third refrigerant circuit.
  • the flow path switching device 170 may include a three way valve.
  • the flow path switching device 170 may include a first valve 171 opening/closing the second refrigerant circuit and a second valve 172 opening/closing the third refrigerant circuit.
  • a condenser fan motor 122 driving a condenser fan 121 , a first fan motor 158 driving a first fan 157 of the refrigerating compartment 150 , and a second fan motor 168 driving a second fan 167 of the freezing compartment 160 may be further provided.
  • a first defrost heater 156 and a second defrost heater 166 may be provided in the first evaporator 154 and the second evaporator 164 to remove frost on surface of the evaporators.
  • An operating refrigerant flowing in the cooling apparatus may include HCs isobutane (R600a) and propane (R290), HFCs R134a, and HFOs R1234yf.
  • Expansion devices 152 , 162 , 280 , and 390 may include a capillary, a capillary tube and an electronic expansion valve (EV).
  • EV electronic expansion valve
  • the ejector 130 may include a nozzle 131 , a suction unit 132 , a mixing unit 133 , and a diffuser 134 .
  • a refrigerant discharged from the condenser 120 may be referred to as a main refrigerant and refrigerant discharge from the second evaporator 164 may be referred to as a sub refrigerant.
  • the main refrigerant may flow to the mixing unit 133 through the nozzle 131 , and the sub refrigerant may be sucked into the suction unit 132 , mixed with the main refrigerant in the mixing unit 133 and then flow out from the ejector 130 through the diffuser 134 .
  • the main refrigerant may be isentropic expansion and an enthalpy difference between the front and the back of the nozzle 131 may cause a speed difference of the main refrigerant. Therefore, the main refrigerant may be ejected at high speed from an outlet of the nozzle 131 .
  • the main refrigerant discharged from the condenser 120 may be introduced to an inlet of the nozzle 131 of the ejector 130 .
  • a flow velocity of the main refrigerant may be increased and a pressure may be decreased after passing through the nozzle 131 in the ejector 130 .
  • the main refrigerant may flow in a low pressure and the sub refrigerant, which flows in a saturated gas state due to passing through the second evaporator 164 through the second refrigerant circuit or the third refrigerant circuit, may be sucked into the suction unit 132 of the ejector 130 due to a pressure difference with the main refrigerant having relative lower pressure than saturation pressure.
  • the main refrigerant passed through the nozzle 131 and the sub refrigerant suctioned through the suction unit 132 may be mixed in the mixing unit 133 of the ejector 130 .
  • a flow velocity of the mixed refrigerant may be reduced while passing through the diffuser 134 installed an outlet of the ejector 130 and having a fan shape, and a pressure of the mixed refrigerant may be increased and introduced to the vapor liquid separator 140 .
  • a vapor refrigerant may be introduced to the suction unit of the compressor 110 , and a liquid refrigerant may pass the expansion device 152 and 162 to be a proper temperature and pressure thereof, which is required by the evaporator 154 and 164 , and be introduced to the evaporator 154 and 164 .
  • a refrigerant in the outlet of the evaporator 154 and 164 may become a saturated gas state since a refrigerant is evaporated by absorbing heat from the ambient air while passing through the evaporator 154 and 164 .
  • the refrigerant in the saturated gas state may be sucked into the suction unit 132 of the ejector 130 , as mentioned above, and a refrigerant circulation may be maintained.
  • a pressure of a refrigerant sucked into the compressor 110 may be increased comparing with a cycle without the ejector 130 , thus the amount of work of the compressor 110 may be reduced when a refrigerant introduced to the compressor 110 is compressed to a condensation temperature.
  • a liquid refrigerant passed through the vapor liquid separator 140 may flow in the evaporator 154 and 164 provided on the second refrigerant circuit or the third refrigerant circuit so that a cooling capacity may be improved and Coefficient of Performance (COP) of an entire cycle may be increased.
  • COP Coefficient of Performance
  • FIG. 3 is a Mollier diagram of the cooling apparatus according to a first embodiment of the present disclosure.
  • the compressor 110 may suction a low temperature and low pressure refrigerant from the vapor liquid separator 140 and compress low temperature and low pressure refrigerant with superheated steam having high temperature and high pressure (7 ⁇ 1).
  • the superheated refrigerant with a high temperature and a high pressure by the compressor 100 may become a liquid refrigerant while passing through the condenser 120 to exchange heat with the ambient air (1 ⁇ 2).
  • the main refrigerant may be introduced to the nozzle 131 of the ejector 130 . While a pressure of the refrigerant introduced to the nozzle 131 is reduced, a state of the refrigerant may be changed, that is a second state, and thus the refrigerant in the outlet of the nozzle 131 may have a high speed and a low pressure (2 ⁇ 3).
  • a suction flow path part having a shape of a concentric circle disposed on the same cross section with the outlet of the nozzle 131 may have a low pressure.
  • a refrigerant passed through only the second evaporator 164 or both of the first evaporator 154 and the second evaporator 164 according to driving modes is referred to as a sub refrigerant
  • the sub refrigerant may be introduced through the suction unit 132 of the ejector 130 .
  • the pressure of the main refrigerant in the outlet of the nozzle 131 may be lower than that of the sub refrigerant passed through the evaporator 154 and 164 so that the sub refrigerant may be sucked through the suction unit 132 of the ejector 130 .
  • the main refrigerant passed through the nozzle and the sub refrigerant passed through the evaporator 154 and 164 may be mixed so that momentum may be transferred (3 ⁇ 4, 3′ ⁇ 4), and the mixed refrigerant may be introduced to the diffuser 134 through the mixing unit 133 (4 ⁇ 5).
  • a flow velocity of the refrigerant may be reduced and a pressure of the refrigerant may be increased. Accordingly, while the refrigerant having increased pressure, a vapor refrigerant among the refrigerant having increased pressure may be introduced to the compressor 110 (5 ⁇ 7), and work of compression of the compressor 110 may be reduced as much as increased pressure by the ejector 130 thereby saving electricity.
  • the refrigerant passed through the ejector 130 may be introduced to the vapor liquid separator 140 and may be separated into a vapor refrigerant and a liquid refrigerant.
  • the vapor refrigerant from the vapor liquid separator 140 may be introduced to the suction unit of the compressor 110 (5 ⁇ 7), and the liquid refrigerant may be introduced to the flow path switching device 170 (5 ⁇ 8).
  • the expansion device 152 and 162 may be provided to generate a certain temperature, which is required by the first evaporator 154 and the second evaporator 164 , and a the refrigerant may have a pressure drop while passing through the expansion device 152 and 162 .
  • the first valve 171 is opened, and the second valve 172 is closed.
  • the liquid refrigerant discharged from the vapor liquid separator 140 may have a pressure drop while passing through the first expansion device 152 (8 ⁇ 9).
  • the refrigerant having a pressure drop may be circulated along the second refrigerant circuit to pass through the first evaporator 154 and the second evaporator 165 (9 ⁇ 10 ⁇ 6).
  • the refrigerant passing through the second evaporator 164 may be sucked through the suction unit 132 of the ejector 130 and during suctioning a pressure of the refrigerant may be decreased by the main refrigerant introduced through the nozzle 131 (6 ⁇ 3′).
  • the first valve 171 may be closed, and the second valve 172 may be opened.
  • the liquid refrigerant discharged from the vapor liquid separator 140 may have a pressure drop while passing through the second expansion device 162 (8 ⁇ 11).
  • the refrigerant having decreased pressure may be circulated along the third refrigerant circuit to bypass the first evaporator 154 and to pass through the second evaporator 164 (11 ⁇ 6′).
  • the refrigerant passing through the second evaporator 164 may be sucked through the suction unit 132 of the ejector 130 and during suctioning a pressure of the refrigerant may be decreased by the main refrigerant introduced through the nozzle 131 (6′ ⁇ 3′).
  • the flow path switching device 170 may be provided to switch a refrigerant flow between the second refrigerant circuit and the third refrigerant circuit according to temperature.
  • Only the liquid refrigerant from the vapor liquid separator 140 may pass through the expansion device 152 and 162 to flow in the evaporator 154 and 164 so that a cooling capacity may be increased, thereby improving the efficiency of the entire cycle.
  • FIG. 4 is a view of operations of each component in each mode of the cooling apparatus according to a first embodiment of the present disclosure.
  • Pressure change of the refrigerant and changes in an evaporation temperature in the each evaporator according to the pressure change when the entire cooling mode and the freezing mode of a refrigerator according to an embodiment of the present disclosure are as follows.
  • a refrigerant discharged from the condenser 120 may be firstly evaporated in the first evaporator 162 after firstly decompressing in the first expansion device 152 .
  • the refrigerant firstly evaporated in the first evaporator 154 may be secondly evaporated in the second evaporator 164 .
  • a freezing compartment 150 fan and a refrigerating compartment 150 fan may be driven at the same time.
  • a proper temperature of a general freezing compartment may be approximately ⁇ 18° C., and a proper temperature of a general refrigerating compartment may be approximately 3° C.
  • a difference between the proper temperature for the refrigerating compartment and the proper temperature for the freezing compartment may be large. Therefore, when increasing the evaporation temperature of the each evaporator to prevent the refrigerating compartment from being excessively cooling, the freezing compartment 160 may be not sufficiently cooled.
  • the freezing compartment 160 except the refrigerating compartment 150 may be cooled according to a low evaporation temperature so that a temperature in the freezing compartment 160 may quickly reach a target temperature.
  • the entire cooling mode is switched to the freezing mode.
  • the second valve 172 of the flow path switching device 170 is opened, that is the first valve 171 is closed, so that the refrigerant discharged from the condenser 120 may flow to the second evaporator 164 through the second expansion device 162 .
  • the refrigerant may be evaporated in the second evaporator 164 . Due to the decompression of the refrigerant by the second expansion 162 , the evaporation temperature of the second evaporator 164 may be lower than that of the first evaporator 154 . At this time, only the freezing compartment 160 fan may be driven.
  • the compressor 110 may include an inverter compressor 110 and, the amount of refrigerant flow flowing in the refrigerant circuit may be reduced by controlling the number of rotation of the compressor.
  • the compressor 110 and the second fan 167 may be stopped.
  • the first fan 157 may be operated during a certain time t 1 , the first valve 171 may be opened, the second valve 172 may be closed, and 3° C. air inside the refrigerating compartment 150 may be circulated so that frost on the first evaporator 154 may be defrosted.
  • Moisture generated during the defrosting may secure a high level of about 75% humidity inside the refrigerating compartment 150 to significantly contribute to keeping vegetables fresh.
  • FIG. 5 is a view of a control diagram of the cooling apparatus according to a first embodiment of the present disclosure.
  • a refrigerator may provide various cooling modes by controlling a control unit 60 , such as MICOM (Microcomputer).
  • FIG. 5 is a control diagram by the control unit 60 provided on the refrigerator according to one embodiment of the present disclosure.
  • a key input unit 52 a refrigerating compartment temperature detecting unit 54 , a freezing compartment temperature detecting unit 56 , and a first evaporator temperature detecting unit 58 may be connected to an input port of the control unit 60 .
  • various function keys may be provided and the various function keys may be related to setting driving conditions of the refrigerator, such as setting refrigerating modes and setting target temperatures.
  • the refrigerating compartment temperature detecting unit 54 and the freezing compartment temperature detecting unit 56 may detect temperatures inside the refrigerating compartment 150 and the freezing compartment 160 , respectively to provide the temperatures to the control unit 60 .
  • the first evaporator temperature detecting unit 58 may detect an evaporation temperature of the refrigerant in the first evaporator 154 to provide to the control unit 60 .
  • a compressor driving unit 62 , a first fan driving unit 64 , a second fan driving unit 66 , a flow path switching device driving unit 68 , a display unit 70 , and a defrost heater driving unit 72 may be connected to an output port of the control unit 60 .
  • the driving units except for the display unit 70 may drive the compressor 110 , the refrigerating compartment fan motor 158 , the freezing compartment fan motor 168 , the first valve 171 and the second valve 172 of the flow path switching device 170 , and the defrost heater 156 and 166 , respectively.
  • the display unit 70 may display an operation state of the cooling apparatus, various setting values, temperatures, etc.
  • the control unit 60 may control the flow path switching device 170 to allow a refrigerant to be circulated on at least one of the second refrigerant circuit and the third refrigerant circuit, as illustrated in FIG. 5 , so that various cooling modes may be realized.
  • a representative cooling mode in the refrigerator according to one embodiment of the present disclosure may be a first cooling mode, that is an entire cooling mode, and a second cooling mode, that is a freezing mode.
  • the entire cooling mode may be defined as an operation mode cooling both the refrigerating compartment 150 and the freezing compartment 160 .
  • the control unit 60 may open the first valve 171 of the flow path switching device 170 to realize the entire cooling mode. In the entire cooling mode, a refrigerant discharge from the condenser 120 may be circulated through the first expansion device 152 , the first evaporator 154 and the second evaporator 164 .
  • the freezing mode may be defined as an operation mode cooling only the freezing compartment 160 .
  • the control unit 60 may open the second valve 172 of the flow path switching device 170 to realize the freezing mode.
  • a refrigerant discharge from the condenser 120 may be circulated through the second expansion device 162 , and the second evaporator 164 .
  • the refrigerator when cooling the refrigerating compartment 150 and the freezing compartment 160 through the first evaporator 154 and the second evaporator 164 , respectively, the refrigerator may be initially operated in a simultaneous cooling mode, and when reaching a predetermined temperature, the simultaneous cooling mode may be switched to a cooling mode cooling only the freezing compartment 160 , thereby maximizing cooling capacity.
  • the refrigerant having increased pressure by the ejector 130 may be sucked into the compressor 110 so that work of compression may be reduced.
  • the entire cooling mode may allow a refrigerant passed through the first evaporator 154 to pass through the second evaporator 164 , so that a liquid refrigerant, which is not evaporated in the first evaporator 154 , may be evaporated in the second evaporator 164 , and thus a refrigerant sufficiently evaporated may be sucked into the suction unit 132 of the ejector 130 . Therefore, the suction operation of the ejector 130 may be smooth, and thereby a stable operation may be obtained. Further, the amount of refrigerant flow using in the entire cooling mode may be less than the amount of refrigerant flow using in the freezing mode, and a difference may be controlled by the number of a rotation of the inverter compressor 110 so that efficient operation may be obtained.
  • FIG. 6A is a view of a multi cycle type cooling apparatus
  • FIG. 6B is a table comparing the multi cycle type cooling apparatus with the cooling apparatus according to a first embodiment of the present disclosure.
  • FIG. 6A is a view illustrating a multi cycle type cooling apparatus (A) not having the ejector 130 and the vapor liquid separator 140
  • FIG. 6B is a table of comparing coefficient of performance of the multi cycle type cooling apparatus (A) with the cooling apparatus (B) according to one embodiment of the present disclosure.
  • the multi cycle type cooling apparatus (A) may include a first refrigerant circuit and a second refrigerant circuit and a flow path switching device 170 a .
  • a refrigerant discharged from a compressor 110 a may flow to a suction side of the compressor 110 a through a condenser 120 a , a first expansion device 152 a , a first evaporator 154 a and a second evaporator 164 a .
  • a refrigerant passed through the condenser 120 a may flow to a suction side of the compressor 110 a through a second expansion device 162 a and a second evaporator 164 a , and then bypass the first evaporator 154 a and the first expansion device 152 a .
  • the flow path switching device 170 a may switch a flow path so that the refrigerant may flow through at least one of the first refrigerant circuit and the second refrigerant circuit.
  • QR represents a freezing capacity in the refrigerating compartment 150
  • QF represents a freezing capacity in the freezing compartment 160
  • m represents a flow
  • Q 1 represents a freezing capacity in the entire cooling mode
  • W 1 represents the amount of work of the compressor 110 in the entire cooling mode
  • Q 2 represents freezing capacity in the freezing mode
  • W 2 represents the amount of work of the compressor 110 in the entire cooling mode.
  • Coefficient of Performance may be a value obtained by dividing a total freezing capacity (Qt) of the combined Q 1 and Q 2 with the total amount of work (Wt) of the compressor of the combined W 1 and W 2 .
  • Qt total freezing capacity
  • Wt total amount of work
  • each cooling capacity in the entire cooling mode and the freezing mode may set to be the same value to compare the performance of the cycle.
  • the cooling apparatus (B) may have a larger the amount of refrigerant flow since a vapor refrigerant and a liquid refrigerant may be independently circulated using by the vapor liquid separator 140 .
  • the first evaporator 154 may be bypassed so that the amount of refrigerant flow may be less.
  • COP of the cooling apparatus (B) may be improved by 1.2 times. That is, the vapor liquid separator 140 may allow the liquid refrigerant to sufficiently flow in the evaporator so that a cooling capacity may be improved and in comparison with the multi cycle type cooling apparatus (A) being not provided with the ejector 130 , the cooling apparatus may provided with the ejector 130 to increase pressure of suctioned refrigerant to the compressor 110 so that the amount of work of compression of the compressor 110 may be reduced.
  • FIG. 7 is a view of a cooling apparatus according to a second embodiment of the present disclosure
  • FIG. 8 is a Mollier diagram of the cooling apparatus according to a second embodiment of the present disclosure.
  • the diffuser 134 shown in the first embodiment is shown as the diffuser 234 in the second embodiment.
  • a cooling apparatus may include a first refrigerant circuit, a second refrigerant circuit, and a third refrigerant circuit.
  • a refrigerant discharged from a compressor 210 may flow to a suction side of the compressor 210 through a condenser 220 , an ejector 230 , and a vapor liquid separator 240 .
  • a refrigerant may be sucked into an inlet of the ejector 230 to be circulated by passing through the ejector 230 , the vapor liquid separator 240 , a first expansion device 252 , a first evaporator 254 and a second evaporator 264 .
  • the refrigerant passing through the vapor liquid separator 240 may be sucked into an inlet of the ejector 230 by passing through a second expansion device 262 and the second evaporator 264 to bypass the first expansion device 252 and the first evaporator 254 .
  • the first evaporator 254 and the second evaporator 264 are not limited thereto, but according to one embodiment of the present disclosure, the first evaporator 254 may be used in a refrigerating compartment 250 of a refrigerator, and the second evaporator 264 may be used in a freezing compartment 260 of a refrigerator. That is, the first evaporator 254 may be referred to as a refrigerating compartment evaporator and the second evaporator 264 may be referred to as a freezing compartment evaporator.
  • a flow path switching device 270 may control the amount of refrigerant flow between the second refrigerant circuit and the third refrigerant circuit. Particularly, the flow path switching device 270 may be installed in a discharge side of the vapor liquid separator 240 to switch a flow path so that a liquid refrigerant passed through the vapor liquid separator 240 may pass at least one of the second and the third refrigerant circuit.
  • the flow path switching device 270 may include a three way valve.
  • the flow path switching device 270 may include a first valve 271 opening/closing the second refrigerant circuit and a second valve 272 opening/closing the third refrigerant circuit.
  • a condenser fan motor 222 driving a condenser fan 221 , a first fan motor 258 driving a first fan 257 of the refrigerating compartment 250 , and a second fan motor 268 driving a second fan 267 of the freezing compartment 260 may be further provided.
  • a first defrost heater 256 and a second defrost heater 266 may be provided in the first evaporator 254 and the second evaporator 264 to remove frost on surface of the evaporators.
  • the first refrigerant circuit may include heat exchangers 270 and 272 .
  • the heat exchanger 270 and 272 may be provided to exchange heat between a discharge unit of the condenser 220 and an inlet of the compressor 210 . It is desirable that a liquid refrigerant may be introduced to the compressor 210 , but a vapor refrigerant may be introduced. Thus, for the prevention of damage or the performance degradation of the compressor 210 , the heat exchangers 270 and 272 may be provided to exchange heat between an outlet of the condenser 220 and the inlet of the compressor 210 .
  • the heat exchangers 270 and 272 may include a first heat exchanger 270 provided on the discharge unit of the condenser 220 and a second heat exchanger 272 provided on the inlet of the compressor 210 .
  • a liquid refrigerant may be overheated to be a vapor refrigerant.
  • the first refrigerant circuit may include a third expansion device 280 .
  • the third expansion device 280 may be installed between the condenser 220 and the ejector 230 .
  • a refrigerant introduced to a nozzle 231 of the ejector 230 is in a two phase state, an efficiency of the ejector 230 may be improved. Therefore, the third expansion device 280 may be provided so that a humidity of a refrigerant discharged from the condenser 220 may be increased.
  • the third expansion device 280 the heat exchangers 270 and 272 may be provided at the same time.
  • the heat exchangers 270 and 272 may include a Suction Line heat exchanger (SLHX) provided between the third expansion device 280 and the suction unit of the compressor 210 .
  • Superheat of a refrigerant introduced to the compressor 210 may be obtained by the Suction Line heat exchanger (SLHX) so that a damage to the compressor 210 caused by introducing a liquid refrigerant may be prevented and an efficiency of the ejector may be improved by the third expansion device 230 .
  • SSHX Suction Line heat exchanger
  • the amount of pressure drop by the third expansion device 280 is within 30% of the amount of pressure drop by the nozzle 231 of the ejector 230 .
  • FIG. 9 is a view of a cooling apparatus according to a third embodiment of the present disclosure
  • FIG. 10 is a Mollier diagram of the cooling apparatus according to a third embodiment of the present disclosure.
  • the diffuser 134 shown in the first embodiment is shown as the diffuser 334 in the third embodiment.
  • a cooling apparatus may include a first refrigerant circuit, a second refrigerant circuit, and a third refrigerant circuit.
  • a refrigerant discharged from a compressor 310 may flow to a suction side of the compressor 310 through a condenser 320 , an ejector 330 , and a vapor liquid separator 340 .
  • a refrigerant may be sucked into an inlet of the ejector 330 to be circulated by passing through the ejector 330 , the vapor liquid separator 340 , a first expansion device 352 , a first evaporator 354 and a second evaporator 364 .
  • the refrigerant passing through the vapor liquid separator 340 may be sucked into an inlet of the ejector 330 by passing through a second expansion device 362 and the second evaporator 364 to bypass the first expansion device 352 and the first evaporator 354 .
  • the first evaporator 354 and the second evaporator 364 are not limited thereto, but according to one embodiment of the present disclosure, the first evaporator 354 may be used in a refrigerating compartment 350 of a refrigerator, and the second evaporator 364 may be used in a freezing compartment 360 of a refrigerator. That is, the first evaporator 354 may be referred to as a refrigerating compartment evaporator and the second evaporator 364 may be referred to as a freezing compartment evaporator.
  • a flow path switching device 370 may control the amount of refrigerant flow between the second refrigerant circuit and the third refrigerant circuit. Particularly, the flow path switching device 370 may be installed in a discharge side of the vapor liquid separator 340 to switch a flow path so that liquid refrigerant passed through the vapor liquid separator 340 may pass at least one of the second and the third refrigerant circuit.
  • the flow path switching device 370 may include a three way valve.
  • the flow path switching device 370 may include a first valve 371 opening/closing the second refrigerant circuit and a second valve 372 opening/closing the third refrigerant circuit.
  • a condenser fan motor 322 driving a condenser fan 321 , a first fan motor 358 driving a first fan 357 of the refrigerating compartment 350 , and a second fan motor 368 driving a second fan 367 of the freezing compartment 360 may be further provided.
  • a first defrost heater 356 and a second defrost heater 366 may be provided in the first evaporator 354 and the second evaporator 364 to remove frost on surface of the evaporators.
  • each evaporation temperature of the first evaporator 354 and the second evaporator 364 may be the same.
  • a surface of the first evaporator 354 may be frosted up, and when increasing the evaporation temperature of the second evaporator 364 to prevent frost, sufficient cooling of the freezing compartment 360 may not be obtained.
  • the first expansion device 352 may decrease a pressure of a refrigerant passing through the condenser 320 so that a refrigerant may be evaporated at an evaporation temperature required by the first evaporator 354 .
  • the intermediate expansion device 390 may decrease a pressure of the refrigerant passing through the first evaporator 354 once again so that the refrigerant may be evaporated at an evaporation temperature required by the second evaporator 364 . ( 12 in FIG. 10 ) That is because the evaporation temperature required by the second evaporator 364 may be lower than the evaporation temperature required by the first evaporator 354 .
  • the second expansion device 362 may decompress the refrigerant passing through the condenser 320 so that the refrigerant may be evaporated at an evaporation temperature required by the second evaporator 364 . That is the second expansion device 362 may directly decompress the refrigerant passing through the condenser 320 until the refrigerant may be evaporated at the evaporation temperature required by the second evaporator 364 , whereas the intermediate expansion device 390 may decrease a pressure of the refrigerant, which is firstly decompressed by the first expansion device 352 , once again.
  • a resistance of the second expansion device 362 may be larger than that of the intermediate expansion device 390 and accordingly a level of the decompression in the second expansion device 362 and the intermediate expansion device 390 may allow the evaporation temperature required by the second evaporator 364 to be realized.
  • an internal diameter of the intermediate expansion device 390 may be smaller than that of the refrigerant pipe disposed on the suction side of the compressor 310 , e.g. approximately 2 ⁇ 4 mm, so that the refrigerant may be compressed while passing through the intermediate expansion device 390 .
  • an evaporation temperature difference between two evaporators may be not significant, and when the internal diameter of the intermediate expansion device 390 is extremely small, an excessively large resistance may be generated in a refrigerant flow in which a liquid refrigerant and a vapor refrigerant are mixed in the first evaporator 354 and thereby a cooling speed of the refrigerating compartment 350 may be slow.
  • FIG. 11 is a schematic view of a refrigerator provided with a cooling apparatus according to a fourth embodiment of the present disclosure
  • FIG. 12 is a view of the cooling apparatus according to a fourth embodiment of the present disclosure.
  • the diffuser 134 shown in the first embodiment is shown as the diffuser 434 in the fourth embodiment.
  • a refrigerator may include a refrigerating compartment 401 , a freezing compartment 402 , and a converting compartment 403 . Those sections may be configured to have three independent temperature zones.
  • the refrigerator may be driven by a dual loop cycle.
  • the dual loop cycle may include a first cooling apparatus 404 and a second cooling apparatus 400 .
  • the first cooling apparatus 404 and the second cooling apparatus 400 may be independently operated without interfering with each other.
  • the first cooling apparatus 404 may be provided to lower a temperature inside the refrigerating compartment 401 to a target temperature.
  • the first cooling apparatus 404 may include a compressor 405 , a condenser 406 , an expansion device 407 , and an evaporator 408 .
  • a refrigerant compressed by the compressor 405 may be discharged in a liquid state having a high temperature and a high pressure while passing through the condenser 406 , and may be discharged in a vapor state having a low temperature and a low pressure while passing through the expansion device 407 and the evaporator 408 , and then be introduced once again to the compressor 405 .
  • the second cooling apparatus 400 may be provided to lower temperatures inside the freezing compartment 402 and the converting compartment 403 to a target temperature.
  • the second cooling apparatus 400 may include a first refrigerant circuit, a second refrigerant circuit, and a third refrigerant circuit.
  • a refrigerant discharged from a compressor 410 may flow to a suction side of the compressor 410 through a condenser 420 , an ejector 430 , and a vapor liquid separator 440 .
  • a refrigerant may be sucked into an inlet of the ejector 430 to be circulated by passing through the ejector 430 , the vapor liquid separator 440 , a first expansion device 452 , a first evaporator 454 and a second evaporator 464 .
  • the refrigerant passing through the vapor liquid separator 440 may be sucked into an inlet of the ejector 430 by passing through a second expansion device 462 and the second evaporator 464 to bypass the first expansion device 452 and the first evaporator 454 .
  • the first evaporator 454 and the second evaporator 464 are not limited thereto, but according to one embodiment of the present disclosure, the first evaporator 454 may be used in the converting compartment 403 of the refrigerator, and the second evaporator 464 may be used in the freezing compartment 460 of the refrigerator. That is, the first evaporator 454 may be referred to as the converting compartment evaporator and the second evaporator 464 may be referred to as a freezing compartment evaporator.
  • a flow path switching device 470 may control the amount of refrigerant flow between the second refrigerant circuit and the third refrigerant circuit. Particularly, the flow path switching device 470 may be installed in a discharge side of the vapor liquid separator 440 to switch a flow path so that a liquid refrigerant passed through the vapor liquid separator 440 may pass at least one of the second and the third refrigerant circuit.
  • the flow path switching device 470 may include a three way valve.
  • the flow path switching device 470 may include a first valve 471 opening/closing the second refrigerant circuit and a second valve 472 opening/closing the third refrigerant circuit.
  • a condenser fan motor 422 driving a condenser fan 421 , a first fan motor 458 driving a first fan 457 of the converting compartment 403 , and a second fan motor 468 driving a second fan 467 of the freezing compartment 460 may be further provided.
  • a first defrost heater 456 and a second defrost heater 466 may be provided in the first evaporator 454 and the second evaporator 464 to remove frost on surface of the evaporators
  • a cooling capacity may be improved, and the amount of work of compression may be reduced by increasing a pressure of a suction refrigerant of the compressor.
  • COefficient of Performance may be improved.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
US14/567,001 2013-12-12 2014-12-11 Cooling apparatus Abandoned US20150168024A1 (en)

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CN105972773A (zh) * 2016-05-31 2016-09-28 广东美的制冷设备有限公司 空调系统及其除霜控制方法
CN106016809A (zh) * 2016-05-31 2016-10-12 广东美的制冷设备有限公司 空调系统及其除霜控制方法
CN106918169A (zh) * 2017-04-13 2017-07-04 广东美的智美科技有限公司 流体处理装置和制冷系统
US20190032982A1 (en) * 2016-02-04 2019-01-31 Franke Technology And Trademark Ltd Refrigeration apparatus with a valve
US20210080164A1 (en) * 2018-05-28 2021-03-18 Canon Semiconductor Equipment Inc. Cooling apparatus, exposure apparatus including cooling apparatus, and industrial apparatus including cooling apparatus
US11073317B2 (en) * 2015-07-28 2021-07-27 Lg Electronics Inc. Refrigerator
US11473830B2 (en) 2018-03-09 2022-10-18 Electrolux Do Brasil S.A. Adaptive defrost activation method
CN115371278A (zh) * 2021-05-17 2022-11-22 青岛海尔电冰箱有限公司 一种喷射制冷系统及制冷设备
US11573035B2 (en) 2015-10-16 2023-02-07 Samsung Electronics Co., Ltd. Air conditioning device, ejector used therein, and method for controlling air conditioning device
US11692742B1 (en) * 2020-07-02 2023-07-04 Booz Allen Hamilton Inc. Thermal management systems

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KR102496363B1 (ko) * 2017-04-17 2023-02-06 삼성전자주식회사 냉장고
KR101996558B1 (ko) * 2018-06-20 2019-07-04 티이컴퍼니 유한회사 액화가스 냉열 이용을 위한 융복합 냉각 시스템
KR102046129B1 (ko) * 2018-06-20 2019-11-18 티이컴퍼니 유한회사 효율적인 제상 운전이 가능한 복합식 냉각 시스템
EP3699515B1 (de) * 2019-02-20 2023-01-11 Weiss Technik GmbH Temperierkammer und verfahren

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Cited By (12)

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Publication number Priority date Publication date Assignee Title
US11073317B2 (en) * 2015-07-28 2021-07-27 Lg Electronics Inc. Refrigerator
US11573035B2 (en) 2015-10-16 2023-02-07 Samsung Electronics Co., Ltd. Air conditioning device, ejector used therein, and method for controlling air conditioning device
US20190032982A1 (en) * 2016-02-04 2019-01-31 Franke Technology And Trademark Ltd Refrigeration apparatus with a valve
US10808977B2 (en) * 2016-02-04 2020-10-20 Franke Technology And Trademark Ltd Refrigeration apparatus with a valve
CN105972773A (zh) * 2016-05-31 2016-09-28 广东美的制冷设备有限公司 空调系统及其除霜控制方法
CN106016809A (zh) * 2016-05-31 2016-10-12 广东美的制冷设备有限公司 空调系统及其除霜控制方法
CN106918169A (zh) * 2017-04-13 2017-07-04 广东美的智美科技有限公司 流体处理装置和制冷系统
US11473830B2 (en) 2018-03-09 2022-10-18 Electrolux Do Brasil S.A. Adaptive defrost activation method
US20210080164A1 (en) * 2018-05-28 2021-03-18 Canon Semiconductor Equipment Inc. Cooling apparatus, exposure apparatus including cooling apparatus, and industrial apparatus including cooling apparatus
US11598565B2 (en) * 2018-05-28 2023-03-07 Canon Semiconductor Equipment Inc. Cooling apparatus having multiple evaporators for cooling objects having different amounts of heat generation, exposure apparatus including cooling apparatus, and industrial apparatus including cooling apparatus
US11692742B1 (en) * 2020-07-02 2023-07-04 Booz Allen Hamilton Inc. Thermal management systems
CN115371278A (zh) * 2021-05-17 2022-11-22 青岛海尔电冰箱有限公司 一种喷射制冷系统及制冷设备

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