EP0624763A1 - Verflüssiger mit freiem Abfluss für eine Kälteanlage - Google Patents

Verflüssiger mit freiem Abfluss für eine Kälteanlage Download PDF

Info

Publication number
EP0624763A1
EP0624763A1 EP94303202A EP94303202A EP0624763A1 EP 0624763 A1 EP0624763 A1 EP 0624763A1 EP 94303202 A EP94303202 A EP 94303202A EP 94303202 A EP94303202 A EP 94303202A EP 0624763 A1 EP0624763 A1 EP 0624763A1
Authority
EP
European Patent Office
Prior art keywords
evaporator
refrigerant
refrigerator
phase separator
condenser
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.)
Withdrawn
Application number
EP94303202A
Other languages
English (en)
French (fr)
Inventor
James Day, (Nmn)
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.)
General Electric Co
Original Assignee
General Electric Co
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 General Electric Co filed Critical General Electric Co
Publication of EP0624763A1 publication Critical patent/EP0624763A1/de
Withdrawn legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • 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
    • 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
    • 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
    • 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

Definitions

  • the present invention generally relates to refrigeration systems, and more particularly relates to placement of a free-draining evaporator and a phase separator in a multievaporator refrigeration system to increase the efficiency thereof.
  • refrigerant In a typical refrigeration system, refrigerant circulates continuously through a closed circuit.
  • circuit refers to a physical apparatus whereas the term “cycle” as used herein refers to operation of a circuit, e.g., refrigeration cycles in a refrigeration circuit.
  • refrigerant refers to refrigerant in liquid, vapor and/or gas form or phase. Components of the closed circuit cause the refrigerant to undergo temperature/pressure changes. The temperature/pressure changes of the refrigerant result in energy transfer.
  • Typical components of a refrigeration system include, for example, compressors, condensers, evaporators, expansion valves, phase separators, control valves, and connecting piping all connected or coupled in a refrigerant flow relationship.
  • the terms "coupled” and “connected” are used herein interchangeably. When two components are coupled or connected, this means that the components are linked directly or indirectly in some manner in refrigerant flow relationship, even though another component or components may be positioned between the coupled or connected components. For example, even though other components, such as a phase separator or an expansion valve, are connected or coupled in the link between the compressor and evaporator, the compressor and evaporator are still coupled or connected.
  • a typical household refrigerator which includes a freezer compartment and a fresh food compartment, is one example of such an apparatus.
  • the freezer compartment is preferably maintained between -25° and -10°C, and the fresh food compartment is preferably maintained between +1° and +10°C.
  • This household refrigerator example is provided for illustrative purposes only. Many devices other than household refrigerators utilize refrigeration systems which include an evaporator operating at a temperature below a temperature at which the evaporator actually needs to operate.
  • a typical high efficiency multievaporator refrigeration system includes a first compressor coupled to a first evaporator operating at about -25°C (an actual range of about -35° to -20°C is typically used) for cooling the freezer of a typical household refrigerator and a second compressor coupled to a second evaporator operating at about +5°C for cooling the fresh food compartment of the typical household refrigerator.
  • a phase separator connected in a refrigerant flow relationship between the two evaporators separates the gaseous phase from the liquid phase of the refrigerant used in the refrigeration system and also stores an excess inventory of the liquid refrigerant.
  • the present invention is directed to an improvement in a refrigeration system having a compressor coupled to a condenser and a phase separator coupled to said evaporator and said condenser, whereby said evaporator comprises a conduit having an inlet connected to said condenser to receive refrigerant discharged from said condenser and an outlet connected to said phase separator, and whereby said phase separator is positioned below said conduit to gravitationally drain a substantial part of the liquid phase of said refrigerant from said outlet into said phase separator, said inlet being at a higher elevation than said outlet and said conduit being free from obstructions and portions which can inhibit gravitational drainage of said liquid phase
  • the present invention is also directed to a refrigerator comprising: compressor means; condenser means connected in a refrigerant flow relationship with said compressor means for condensing refrigerant discharged from said compressor means; a fresh food compartment; first evaporator means for refrigerating said fresh food compartment and having an inlet connected to said condenser means to receive refrigerant discharged from said condenser means and an outlet connected to phase separator means positioned below said first evaporator means to gravitationally drain a substantial part of the unevaporated liquid phase of said refrigerant from said outlet into said phase separator means, said first evaporator means comprising a conduit free from any portion which can inhibit said gravitational drainage of said liquid phase of the refrigerant; a freezer compartment; second evaporator means for refrigerating said freezer compartment and connected to receive at least part of the refrigerant discharged from said phase separator means; and a refrigerant flow switching valve for alternately conveying refrigerant from either said first or said second
  • said evaporator is one in a multi-evaporator system.
  • the fresh food compartment in use, is maintained at a temperature warmer than said freezer compartment.
  • FIGURE 1 illustrates a refrigeration system incorporating a free-draining evaporator of the present invention.
  • FIGURE 2 represents a free-draining evaporator of the preferred embodiment.
  • FIGURE 3 represents a block diagram of a household refrigerator incorporating a refrigeration system having a free-draining fresh food evaporator and a freezer evaporator.
  • the present invention is believed to have its greatest utility in refrigeration systems and particularly in household refrigerator freezers. However, it also has utility in other refrigeration applications such as control of multiple air conditioner units.
  • FIGURE 1 illustrates a refrigeration system 100 in accordance with the preferred form of the invention.
  • Refrigeration system 100 includes a compressor unit 102 coupled to a condenser 104, which condenses a substantial part of refrigerant used in refrigeration system 100.
  • a first expansion means such as capillary tube 106, is coupled to the outlet of condenser 104 and inlet 107 of first evaporator 108, also known as a high pressure evaporator.
  • Inlet 107 is positioned at a higher elevation than outlet 109 of first evaporator 108 and said first evaporator is preferably configured so as to slope downward at all points, as shown.
  • first evaporator 108 comprises a conduit free from obstructions and portions that can inhibit free flow of the refrigerant in the liquid phase passing therethrough.
  • Phase separator 110 includes a screen 112 disposed adjacent to the inlet of phase separator 110, a gas or vapor phase-containing portion 114 and a liquid phase-containing portion 116. Screen 112 prevents clogging of the conduits of the refrigeration system by trapping dirt or sediment passing therethrough. Although sometimes referred to herein as vapor-containing portion 114 or simply as vapor portion 114, it should be understood that this portion of phase separator 110 may have gas and/or vapor disposed therein.
  • Vapor portion 114 is coupled by conduit 120 to supply a high pressure refrigerant as a first input to refrigerant flow switching valve 118.
  • the intake of conduit 120 is so positioned in vapor portion 114 that liquid refrigerant passing through vapor portion 114 to liquid-containing portion 116 does not enter said intake.
  • the outlet of liquid-containing portion 116 is coupled to second expansion means 122, such as an expansion valve or a capillary tube.
  • Second expansion means 122 is sometimes referred to herein as a throttle.
  • Inlet 123 of second evaporator 124 also known as a low pressure evaporator, is coupled to the outlet of second expansion means 122, and outlet 125 of second evaporator 124 is coupled to provide a low pressure refrigerant as a second input to refrigerant flow switching valve 118.
  • Second expansion means 122 and second evaporator 124 produce a temperature drop in the refrigerant flowing therethrough.
  • the refrigeration effect is preferably captured by blowing air across second evaporator 124 into a freezer compartment (not shown) of refrigeration system 100 when used as a household refrigerator.
  • Second evaporator 124 preferably has the same physical structure as first evaporator 108.
  • Thermostat 127 which is preferably user adjustable, receives current flow from an external power source designated by the legend "POWER IN" and is connected to compressor unit 102. When cooling is required, thermostat 127 provides an output signal which activates compressor unit 102 to cause a "refrigeration cycle on" condition. When the desired temperature in, for example, the freezer compartment is reached no more cooling is required and thermostat 127 provides an output signal which deactivates compressor unit 102 to a "refrigeration cycle off" condition. In a household refrigerator, for example, thermostat 127 is preferably located in the freezer compartment.
  • Capillary tube 106 is shown in thermal contact with conduit 120 which connects phase separator vapor portion 114 with refrigerant flow switching valve 118. Capillary tube 106 is also in thermal contact with conduit 130 which couples second evaporator 124 to refrigerant flow switching valve 118. Thermal contact is achieved, for example, by soldering the exterior of capillary tube 106 and a portion of the exterior of conduits 120 and 130 together side by side. Capillary tube 106 in FIGURE 1 is shown as being wrapped around conduits 120 and 130 in a schematic representation of a heat transfer relationship.
  • the heat transfer occurs in a counterflow arrangement, i.e., the refrigerant flowing in capillary tube 106 proceeds in a direction opposite to the flow of refrigerant in conduits 120 and 130.
  • a counterflow heat exchange arrangement increases the heat exchange efficiency in comparison to a heat exchange arrangement wherein the flows proceed in the same direction,.
  • first evaporator 108 contains refrigerant at a temperature of approximately -5°C.
  • Second evaporator 124 contains refrigerant at a temperature of approximately -25°C.
  • Second expansion means 122 is adjusted to provide barely superheated vapor flow at the outlet of second evaporator 124.
  • Preferably all the refrigerant exiting from outlet 125 of second evaporator 124 is in gaseous form.
  • Switching valve 118 controls the flow of refrigerant passing through respective evaporators 108 and 124 to compressor unit 102.
  • thermostat 127 activates compressor unit 102.
  • Vapor from second evaporator 124 enters compressor unit 102 when switching valve 118 is configured to allow conduits 130 and 132 to be in flow communication.
  • vapor from phase separator 110 enters compressor unit 102 when switching valve 118 is configured to allow conduits 120 and 132 to be in flow communication.
  • STATE 1 When switching valve 118 is configured to provide flow communication between conduits 120 and 132, or similarly disposed conduits, this condition is hereinafter referred to as STATE 2.
  • refrigerant at about 1.4 kg./cm.2 absolute is disposed in conduits 130 and 131, and refrigerant at about 2.8 kg./cm.2 absolute is disposed in conduits 120 and 121.
  • the inlet pressure to compressor unit 102 is about 1.4 kg./cm.2 when switching valve 118 is in STATE 1 and about 2.8 kg./cm.2 when switching valve 118 is in STATE 2.
  • Switching valve 118 operated by utilizing this pressure difference between STATE 1 and STATE 2, is more fully described in commonly assigned U.S. Patents 5,156,016 and 5,184,473, both of which are incorporated herein by reference.
  • Capillary tube 106 is preferably sized to obtain some subcooling of the liquid exiting condenser 104. Subcooling is defined as cooling of a given fluid below its saturation temperature. By subcooling a fluid, more heat can be removed by the refrigeration system. Capillary tube 106 is generally a fixed length, small bore tube. Due to the small tube diameter of capillary tube 106, a high pressure drop occurs across the capillary tube length thus reducing the pressure of the refrigerant to its saturation pressure.
  • Capillary tube 106 meters the flow of refrigerant and maintains a pressure difference between condenser 104 and first evaporator 108.
  • Conduit heating by means of capillary tube 106 warms conduits 120 and 130 sufficiently to avoid condensation and also cools the refrigerant in capillary tube 106 flowing to first evaporator 108. Even though the warming of refrigerant in conduits 120 and 130 adversely affects system efficiency, the beneficial effect provided by the cooling of refrigerant in capillary tube 106 far outweighs such a loss of efficiency.
  • first evaporator 108 The expansion of the liquid refrigerant in first evaporator 108 causes a part of the liquid refrigerant to evaporate. Refrigerant in the liquid and vapor phases exiting from first evaporator 108 then enters phase separator 110. The liquid refrigerant accumulates in liquid-containing portion 116 and vapor accumulates in vapor portion 114 of phase separator 110. By gravitational draining of the liquid refrigerant from first evaporator 108 into phase separator 110, the unevaporated liquid head in first evaporator 108 is significantly reduced. Such a liquid head is typically present in the evaporators of conventional refrigerator systems. Conduit 120 supplies vapor from vapor portion 114 to switching valve 118. The vapor from phase separator 110 is generally at about -5°C.
  • thermostat 127 activates compressor unit 102, and when valve 118 is in STATE 1, liquid from liquid-containing portion 116 of phase separator 110 evaporates as it flows through throttle 122 into second evaporator 124.
  • the temperature and pressure of refrigerant entering second evaporator 124 from throttle 122 significantly drop and any remaining liquid refrigerant evaporates in second evaporator 124, which further cools second evaporator 124 to about -25°C.
  • refrigerant flows, albeit slowly, through first evaporator 108 when valve 118 is in STATE 1.
  • a sufficient refrigerant charge is typically supplied to system 100 to maintain the liquid refrigerant in phase separator 110 at the desired level.
  • the pressure at the input of compressor unit 102 when valve 118 is in STATE 1 is determined by the pressure at which refrigerant exists in a two-phase equilibrium at -25°C.
  • the pressure at compressor unit 102 when valve 118 is in STATE 2 is determined by the saturation pressure of refrigerant at -5°C.
  • the temperature of condenser 104 has to be greater than ambient temperature for condenser 104 to function as a condenser.
  • the refrigerant within condenser 104 may be at +40°C.
  • the pressure of refrigerant in condenser 106 depends upon the refrigerant selected.
  • Compressor unit 102 may be any type of compressor or mechanism which provides a compressed refrigerant output.
  • compressor unit 102 may be a single stage compressor, a plurality of compressors, a compressor having a plurality of stages, or any combination of compressors.
  • Compressor unit 102 may be, for example, a rotary or reciprocating type compressor.
  • a compressor with a small volume inlet chamber is preferred since gases at two different pressures are alternately being compressed.
  • a rotary compressor with an inlet chamber volume of one cubic inch that gets compressed to 4.6 cm.2 per compressor revolution is satisfactory.
  • the refrigeration system 100 illustrated in FIGURE 1 requires less energy than a dual evaporator, single-compressor circuit with the same cooling capacity. Some efficiency advantages come about due to the fact that only about half the amount of refrigerant needs to be pumped through the system. Furthermore, once first evaporator 108 attains its equilibrium temperature, the liquid phase refrigerant continually drains into phase separator 110, thereby being made available to cool second evaporator 124 and during the "refrigeration cycle off" condition, all the excess liquid phase refrigerant drains into phase separator 110 and is then immediately made available to second evaporator 124 at the start of the next "refrigeration cycle on" condition without producing the delay inevitably present in a conventional dual evaporator refrigeration system.
  • FIGURES 2A and 2B illustrate, in more detail, a preferred embodiment of the invention utilized in the multievaporator refrigeration system described in FIGURE 1, with like elements having the same reference numerals.
  • evaporator/phase separator assembly 200 comprising evaporator 108 having inlet 107 and outlet 109 coupled to phase separator 110 positioned below evaporator 108.
  • Evaporator 108 is oriented as shown by "UP” and “DOWN” arrows in FIGURE 2, in such a way that outlet 109 is positioned at a lower elevation than inlet 107. A substantially vertical orientation is preferred.
  • Evaporator 108 has no obstruction or portion that would inhibit free drainage due to the force of gravity of substantially all of the liquid phase refrigerant flowing through said evaporator. It preferably comprises a conduit continually sloped from inlet 107 to outlet 109, as shown. Rung portion 212 of the conduit that forms evaporator 108 between inlet 107 and point 216 is shaped to position inlet 107 at a higher elevation than or the same elevation as point 216. Similarly, any point on curved portion 218 is at a higher elevation than any point on rung portion 219. This geometry results in a conduit free from obstructions and portions in which the liquid phase refrigerant may accumulate. Such a geometry is repeated throughout the rung portions of evaporator 108. Preferably, any downstream point on the conduit of evaporator 108 is below any upstream adjacent point.
  • FIGURE 3 is a block diagram illustration of a household refrigerator 300 including insulated wall 302 forming fresh food compartment 304, discussed earlier, and freezer compartment 306.
  • FIGURE 3 is provided for illustrative purposes only, particularly to show one apparatus which has substantially separate compartments which require refrigeration at different temperatures.
  • fresh food compartment 304 and freezer compartment 306 are typically maintained at about +1 to +10° and -25° to -10°C, respectively.
  • first evaporator 108 (high pressure evaporator) is shown located in fresh food compartment 304 and second evaporator 124 (low pressure evaporator) in freezer compartment 306.
  • Phase separator 110 is positioned below first evaporator 108.
  • the location of the evaporators shown in FIGURE 3 is only for illustrative purposes and to facilitate ease of understanding and the present invention is not limited to the physical location of the evaporators, provided first evaporator 108 is oriented to achieve free drainage of the liquid refrigerant therefrom into phase separator 110. It is contemplated that the evaporators 108 and 124 could be located anywhere in the refrigerator or even outside the refrigerator with the evaporator-cooled air from each evaporator directed to the appropriate compartment via conduits, barriers and the like.
  • First and second evaporators 108 and 124 are respectively driven by compressor unit 102 and condenser 104 shown located in compressor/condenser compartment 316.
  • Control knob 318 is located in fresh food compartment 304 and temperature sensor 320 is disposed in freezer compartment 306.
  • Control knob 318 controls the temperature in compartment 304 and it may be calibrated to read in gradations of temperature desired therein. The operational features of control knob 318 are described in the aforementioned commonly assigned U.S. Patents 5,156,016 and 5,184,473.
  • Temperature sensor 320 sends a signal to compressor 312 to run or stop according to its setting.
  • First evaporator 308 is typically operated at about -10° to 0°C and the second evaporator 310 at about -35° to about -20°C to maintain fresh food compartment 304 at about +1 to +10° and freezer compartment 306 at about -25° to -10°C.
  • control knob 318 of a typical household refrigerator of 0.54 m.3 capacity is set at +3°C in fresh food compartment 304, that setting corresponds to a refrigerant temperature of about -4°C and pressure of about 3.2 kg./cm.2 absolute in first evaporator 308.
  • compressor unit 102 evacuates first evaporator 108, part of the refrigerant present in evaporator 108 boils and thereby lowers the pressure and the temperature of the refrigerant present in first evaporator 108 to about 2.5 kg./cm.2 absolute and about -6°C, respectively.
  • the high pressure refrigerant from evaporator 108 is transported to compressor unit 102 by valve 118 for about 5 seconds and the low pressure refrigerant from evaporator 124 is transported to compressor unit 102 for about 16 seconds.
  • the allocation of conveying time between the high pressure and the low pressure refrigerant to compressor unit 102 is a function of the cooling capacity of first evaporator 108 and second evaporator 124.
  • the capacity ratio between first evaporator 108 and second evaporator 124 for the aforedescribed refrigerator is about 3:1. Capacity ratio is defined as a ratio of the heat removing capacity in kcal.
  • Control knob 318 and sensor 320 are preferably user adjustable so that the user selects a temperature, or temperature range, at which each evaporator is to be activated and inactivated. In this manner, operation of the system is adjusted by the user.
  • the illustrative refrigeration system includes two evaporators which are selected to operate at desired refrigeration temperatures.
  • the invention can also employ more than two evaporators. Reduced energy use is provided by utilizing a plurality of evaporators. It is contemplated that in some refrigeration systems, all of the energy efficiencies and reduced costs provided by the present invention may not be strictly necessary. Thus, the invention may be modified to vary efficiency and costs relative to the described embodiments. For example, the number of rung portions of evaporator means used in the present invention, such as 212 or 219 shown in FIGURE 2, may be increased or decreased in accordance with the requirements of the refrigeration system. Furthermore, single or multiple rows of rung portions are contemplated.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
EP94303202A 1993-05-10 1994-05-03 Verflüssiger mit freiem Abfluss für eine Kälteanlage Withdrawn EP0624763A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US58847 1979-07-19
US5884793A 1993-05-10 1993-05-10

Publications (1)

Publication Number Publication Date
EP0624763A1 true EP0624763A1 (de) 1994-11-17

Family

ID=22019268

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94303202A Withdrawn EP0624763A1 (de) 1993-05-10 1994-05-03 Verflüssiger mit freiem Abfluss für eine Kälteanlage

Country Status (2)

Country Link
EP (1) EP0624763A1 (de)
JP (1) JPH0755273A (de)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1998039605A1 (en) * 1997-03-04 1998-09-11 Frigoscandia Equipment Ab A refrigeration system and a separator therefor
WO2003023297A1 (de) * 2001-09-13 2003-03-20 BSH Bosch und Siemens Hausgeräte GmbH Kältegerät mit zwei verdampfern
FR2864212A1 (fr) * 2003-12-19 2005-06-24 Armines Ass Pour La Rech Et Le Systeme thermodynamique a evaporation etagee et a sous refroidissement renforce adapte a des melanges a grand glissement de temperature
EP1593918A3 (de) * 2004-05-06 2008-12-03 Air Liquide Deutschland GmbH Indirekte Kühlung bei Kühlfahrzeugen
WO2014048485A1 (en) * 2012-09-28 2014-04-03 Electrolux Home Products Corporation N. V. Refrigerator
CN103994596A (zh) * 2014-05-28 2014-08-20 合肥美的电冰箱有限公司 制冷设备和制冷系统
EP2772706A3 (de) * 2013-02-28 2015-04-01 Whirlpool Corporation Kühlsystem mit Verdichter mit doppeltem Einlassventil
US9441866B2 (en) 2013-09-04 2016-09-13 Whirlpool Corporation Variable expansion device with thermal choking for a refrigeration system
EP3619481A4 (de) * 2017-05-02 2021-01-27 Rolls-Royce North American Technologies, Inc. Verfahren und vorrichtung für isothermische kühlung

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH11108483A (ja) * 1997-10-03 1999-04-23 Hitachi Ltd 空気調和機

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US602371A (en) * 1898-04-12 Hydraulic lubricator
US1853724A (en) * 1928-07-24 1932-04-12 Chicago Pneumatic Tool Co Evaporating process and apparatus
FR971034A (de) * 1951-01-11
EP0485147A1 (de) * 1990-11-09 1992-05-13 General Electric Company Kühlsystem

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US602371A (en) * 1898-04-12 Hydraulic lubricator
FR971034A (de) * 1951-01-11
US1853724A (en) * 1928-07-24 1932-04-12 Chicago Pneumatic Tool Co Evaporating process and apparatus
EP0485147A1 (de) * 1990-11-09 1992-05-13 General Electric Company Kühlsystem

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1998039605A1 (en) * 1997-03-04 1998-09-11 Frigoscandia Equipment Ab A refrigeration system and a separator therefor
AU722536B2 (en) * 1997-03-04 2000-08-03 John Bean Technologies Ab A refrigeration system and a separator therefor
WO2003023297A1 (de) * 2001-09-13 2003-03-20 BSH Bosch und Siemens Hausgeräte GmbH Kältegerät mit zwei verdampfern
FR2864212A1 (fr) * 2003-12-19 2005-06-24 Armines Ass Pour La Rech Et Le Systeme thermodynamique a evaporation etagee et a sous refroidissement renforce adapte a des melanges a grand glissement de temperature
WO2005059450A1 (fr) * 2003-12-19 2005-06-30 Armines Systeme thermodynamique a evaporation etagee et a sous refroidissement renforce adapte a des melanges a gran glissement de temperature
EP1593918A3 (de) * 2004-05-06 2008-12-03 Air Liquide Deutschland GmbH Indirekte Kühlung bei Kühlfahrzeugen
WO2014048485A1 (en) * 2012-09-28 2014-04-03 Electrolux Home Products Corporation N. V. Refrigerator
CN104685305A (zh) * 2012-09-28 2015-06-03 伊莱克斯家用产品公司 制冷器
EP2772706A3 (de) * 2013-02-28 2015-04-01 Whirlpool Corporation Kühlsystem mit Verdichter mit doppeltem Einlassventil
US9228762B2 (en) 2013-02-28 2016-01-05 Whirlpool Corporation Refrigeration system having dual suction port compressor
US9746208B2 (en) 2013-02-28 2017-08-29 Whirlpool Corporation Cooling system having dual suction port compressor
US9441866B2 (en) 2013-09-04 2016-09-13 Whirlpool Corporation Variable expansion device with thermal choking for a refrigeration system
US10215460B2 (en) 2013-09-04 2019-02-26 Whirlpool Corporation Variable expansion device with thermal choking for a refrigeration system
CN103994596A (zh) * 2014-05-28 2014-08-20 合肥美的电冰箱有限公司 制冷设备和制冷系统
EP3619481A4 (de) * 2017-05-02 2021-01-27 Rolls-Royce North American Technologies, Inc. Verfahren und vorrichtung für isothermische kühlung
US11215383B2 (en) 2017-05-02 2022-01-04 Rolls-Royce North American Technologies Inc. Method and apparatus for isothermal cooling
US11892208B2 (en) 2017-05-02 2024-02-06 Rolls-Royce North American Technologies Inc. Method and apparatus for isothermal cooling

Also Published As

Publication number Publication date
JPH0755273A (ja) 1995-03-03

Similar Documents

Publication Publication Date Title
US6351950B1 (en) Refrigeration system with variable sub-cooling
US4918942A (en) Refrigeration system with dual evaporators and suction line heating
US4910972A (en) Refrigerator system with dual evaporators for household refrigerators
EP0485146B1 (de) Kühlanlage mit Kältemittelströmungssteuerung
US5134859A (en) Excess refrigerant accumulator for multievaporator vapor compression refrigeration cycles
JP3343142B2 (ja) 冷蔵庫
US5079929A (en) Multi-stage refrigeration apparatus and method
US5428966A (en) Refrigeration system utilizing an expansion device in the evaporator
US5157943A (en) Refrigeration system including capillary tube/suction line heat transfer
EP0624763A1 (de) Verflüssiger mit freiem Abfluss für eine Kälteanlage
US5184473A (en) Pressure controlled switching valve for refrigeration system
US5157931A (en) Refrigeration method and apparatus utilizing an expansion engine
US6314747B1 (en) Vapor compression system and method
US5156016A (en) Pressure controlled switching valve for refrigeration system
EP0485147B1 (de) Kühlsystem
WO2004016996A1 (en) Evaporator for a refrigeration system
KR200274119Y1 (ko) 히트 펌프 시스템
EP0541328A1 (de) Kälteanlagen
EP0374688B1 (de) Doppelverdampferkühlvorrichtung für Haushaltskühlschränke
AU663873B2 (en) Refrigeration system
KR100522405B1 (ko) 냉동시스템에서 드라이어와 리시버탱크의 일체형 구조
KR200308189Y1 (ko) 냉장고
NZ248568A (en) Closed loop refrigeration system having controlled flow of refrigerant through evaporator containing an expansion engine which drives the compressor

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR GB IT

17P Request for examination filed

Effective date: 19950517

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION HAS BEEN WITHDRAWN

18W Application withdrawn

Withdrawal date: 19960711