EP3073210A1 - Réfrigérateur avec une efficacité - Google Patents

Réfrigérateur avec une efficacité Download PDF

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Publication number
EP3073210A1
EP3073210A1 EP15161544.0A EP15161544A EP3073210A1 EP 3073210 A1 EP3073210 A1 EP 3073210A1 EP 15161544 A EP15161544 A EP 15161544A EP 3073210 A1 EP3073210 A1 EP 3073210A1
Authority
EP
European Patent Office
Prior art keywords
evaporator
refrigerator according
refrigerant
tube
refrigerator
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Withdrawn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
EP15161544.0A
Other languages
German (de)
English (en)
Inventor
Alberto Cernuschi
Enzo Mario Rivis
Paolo Sicher
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.)
Whirlpool Corp
Original Assignee
Whirlpool Corp
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 Whirlpool Corp filed Critical Whirlpool Corp
Priority to EP15161544.0A priority Critical patent/EP3073210A1/fr
Priority to US15/079,905 priority patent/US20160282031A1/en
Priority to BR102016006791A priority patent/BR102016006791A2/pt
Publication of EP3073210A1 publication Critical patent/EP3073210A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/37—Capillary tubes
    • 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
    • F25D11/00—Self-contained movable devices, e.g. domestic refrigerators
    • F25D11/02—Self-contained movable devices, e.g. domestic refrigerators with cooling compartments at different temperatures
    • F25D11/022—Self-contained movable devices, e.g. domestic refrigerators with cooling compartments at different temperatures with two or more 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D15/00—Devices not covered by group F25D11/00 or F25D13/00, e.g. non-self-contained movable devices
    • 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

Definitions

  • the present invention relates to a refrigerator with a refrigerant circuit comprising a compressor, a condenser, an expansion device, a first evaporator downstream the expansion device, a second evaporator downstream the first evaporator, a heat exchanger to cause heat exchange between refrigerant downstream the condenser and upstream said first evaporator, on one side, and refrigerant downstream the second evaporator and upstream the compressor, on the other side.
  • the refrigeration circuit of a refrigerator of the above type is shown in figure 1 .
  • GB 2143014 suggests using two evaporators in the refrigeration circuit and with heat exchangers between the compressor and one of the evaporators and between the two evaporators respectively.
  • This known solution is quite complex since it uses a diverter valve, two capillary tubes and a suction pipe from the compressor which has a fork, one arm leading to one evaporator and the other arm leading to the other evaporator.
  • the refrigeration circuit of a refrigerator presents an additional heat exchanger to cause heat exchange between refrigerant downstream the condenser and upstream the first evaporator, on a first side, and refrigerant downstream the first evaporator and upstream the second evaporator, on a second side, the expansion device being a single capillary tube that is configured to act as said first side of both heat exchangers.
  • a type of refrigerator similar to the one according to the present invention is known from “dual evaporator” or “sequential evaporator” type refrigerators, but these refrigerators use a non-azeotropic mixture of at least two different refrigerants, for instance propane (R-290) and n-butane (R-600), which has an appropriate gliding temperature difference (GTD) during evaporation and condensation phases.
  • GTD gliding temperature difference
  • With a refrigeration cycle using the above mixture known also as Lorenz-Meutzner cycle, it is possible to have identical or at least similar energy saving performances of a dual evaporator refrigeration circuit using a mono-component refrigerant and a by-pass two-circuit cycle, where a 3-way electrovalve is used.
  • a refrigerator of this type is disclosed by US 5 207 077 and EP 2 592 366 .
  • the expansion device is placed immediately upstream the first evaporator, i.e. the low-temperature evaporator.
  • the expansion device is identified in the drawing as an expansion valve, while in EP 2592366 the expansion device is a capillary tube arranged at the side of the first evaporator.
  • the presence of the valve does increase the overall cost of the appliance, and it may create problem of condensation on suction tube.
  • the optimum capillary tube length is of the order of 10 - 15 m if similar energy consumption performances of a bypass two-circuit cycle are to be obtained.
  • the expansion device is a capillary tube that is configured to act as said first side of both heat exchangers.
  • the capillary tube is used externally to the other tubes of the refrigerant circuit, and the refrigerant flow in the capillary tube is in counter flow with reference to the refrigerant flow in the tube of the refrigerant circuit.
  • the capillary tube may be used internally to the other tube.
  • the applicant has surprisingly discovered that the same circuit designed for a non-azeotropic mixture of refrigerants presents thermodynamic advantages even if used with a single refrigerant, i.e. a refrigerant whose composition is made mainly by a single chemical compound.
  • a single refrigerant i.e. a refrigerant whose composition is made mainly by a single chemical compound.
  • This result could not be expected and therefore the choice of using a circuit specifically designed for a non-azeotropic mixture of refrigerants for a single mono-compound refrigerant could not be predicted by a person skilled in the art.
  • the single capillary tube is parallel and in contact with the tube from the freezer evaporator, and has a length of at least 700 mm.
  • the capillary tube is wrapped around the tube from the freezer evaporator, and has a length of at least 1000 mm, with a contact length on such tube of at least 400 mm.
  • the second heat exchanger between the capillary tube and the suction tube upstream the compressor is dimensioned as in traditional refrigerators.
  • the refrigerant circuit comprises a compressor 10, a condenser 12, usually placed on back wall of the refrigerator, cooled by natural convection or with forced air, a drier 14 as normally used on a domestic refrigerator / freezer appliance.
  • the circuit Downstream the drier, the circuit comprises a single capillary tube 16 with an internal diameter comprised between 0.60 and 0.80mm.
  • the capillary tube 16 is schematically represented as a tube with a plurality of loops, only for distinguishing it from the suction tube (in the technical field of domestic refrigerators it is usual to represent a capillary in this way).
  • the circuit comprises a first heat exchanger 18 and a second heat exchanger 20.
  • the first heat exchanger 18 presents a first side made by a capillary tube portion 16a in contact with a portion 22 of the circuit tube between first or low temperature evaporator 17 (placed in the freezer compartment - not shown) and second or higher temperature evaporator 19 (placed in the fridge compartment - not shown).
  • a detail of such heat exchanger is shown in figure 3 , and applicant has determined through experimental tests that the length of this tube/tube heat exchanger (with two parallel straight tubes taped together by means of an adhesive aluminum tape - not shown in the drawings for sake of clarity) is preferably at least 0,7 m, more preferably more than 1 m.
  • the total length of the capillary tube is preferably higher than 3,5 m.
  • internal diameter of the suction tube 22 is preferably comprised between 5 and 8 mm.
  • the capillary tube 16a is wrapped around the tube 22 of the refrigerant circuit with use of an aluminum tape (not shown).
  • the length of the suction tube on which the capillary is spirally wound is preferably higher that 0,4 m, with a length of the wrapped capillary higher than 1 m.
  • the second heat exchanger 20 is similarly composed of a capillary tube portion 16b and a portion 24 of suction tube upstream the compressor 10.
  • the length of such double-pipe heat exchanger 20 is substantially similar to the one known from usual refrigerators, and therefore it will not be further described here.
  • the solution according to the invention can be applied to direct cooled evaporator products (static evaporators in freezer and fridge compartments) and hybrid products (no frost freezer and static fridge).
  • Energy consumption of same product without the additional heat exchanger according to the invention has an energy consumption of approximately 470 Wh/24h, therefore about 5% higher if compared to a refrigerator according to the invention.
  • Additional heat exchanger cools down more refrigerant in the capillary: that allows that refrigerant comes to evaporator with less vapor, increasing the evaporator efficiency.

Landscapes

  • 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)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP15161544.0A 2015-03-27 2015-03-27 Réfrigérateur avec une efficacité Withdrawn EP3073210A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP15161544.0A EP3073210A1 (fr) 2015-03-27 2015-03-27 Réfrigérateur avec une efficacité
US15/079,905 US20160282031A1 (en) 2015-03-27 2016-03-24 Refrigerator with enhanced efficiency
BR102016006791A BR102016006791A2 (pt) 2015-03-27 2016-03-28 refrigerador com eficiência aprimorada

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP15161544.0A EP3073210A1 (fr) 2015-03-27 2015-03-27 Réfrigérateur avec une efficacité

Publications (1)

Publication Number Publication Date
EP3073210A1 true EP3073210A1 (fr) 2016-09-28

Family

ID=52875498

Family Applications (1)

Application Number Title Priority Date Filing Date
EP15161544.0A Withdrawn EP3073210A1 (fr) 2015-03-27 2015-03-27 Réfrigérateur avec une efficacité

Country Status (3)

Country Link
US (1) US20160282031A1 (fr)
EP (1) EP3073210A1 (fr)
BR (1) BR102016006791A2 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10712073B2 (en) * 2017-03-01 2020-07-14 Haier Us Appliance Solutions, Inc. Ternary natural refrigerant mixture that improves the energy efficiency of a refrigeration system
CN109869973B (zh) * 2017-12-05 2022-03-29 松下电器产业株式会社 冷冻冷藏库

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2753693A (en) * 1955-05-23 1956-07-10 Jr Elmer W Zearfoss Refrigerating apparatus
GB2143014A (en) 1983-05-16 1985-01-30 Hotpoint Ltd Refrigerator/freezer units
US4918942A (en) * 1989-10-11 1990-04-24 General Electric Company Refrigeration system with dual evaporators and suction line heating
US5092138A (en) * 1990-07-10 1992-03-03 The University Of Maryland Refrigeration system
US5157943A (en) * 1990-11-09 1992-10-27 General Electric Company Refrigeration system including capillary tube/suction line heat transfer
US5207077A (en) 1992-03-06 1993-05-04 The University Of Maryland Refrigeration system
DE102009001677A1 (de) * 2009-03-19 2010-09-23 BSH Bosch und Siemens Hausgeräte GmbH Kältegerät, Drosselrohr für ein Kältegerät und Verfahren zu dessen Herstellung
EP2592366A2 (fr) 2011-11-08 2013-05-15 Samsung Electronics Co., Ltd Cycle de frigorigène mixte non azéotrope et réfrigérateur ainsi équipé
EP2857778A1 (fr) * 2013-10-03 2015-04-08 Whirlpool Corporation Réfrigérateur avec mélange non azéotropique de réfrigérants d'hydrocarbures

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6370908B1 (en) * 1996-11-05 2002-04-16 Tes Technology, Inc. Dual evaporator refrigeration unit and thermal energy storage unit therefore
EP1782000A4 (fr) * 2004-07-09 2007-10-10 Junjie Gu Systeme de refrigeration
JP5023721B2 (ja) * 2006-01-31 2012-09-12 ダイキン工業株式会社 食い込み式管接続構造
JP5128424B2 (ja) * 2008-09-10 2013-01-23 パナソニックヘルスケア株式会社 冷凍装置

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2753693A (en) * 1955-05-23 1956-07-10 Jr Elmer W Zearfoss Refrigerating apparatus
GB2143014A (en) 1983-05-16 1985-01-30 Hotpoint Ltd Refrigerator/freezer units
US4918942A (en) * 1989-10-11 1990-04-24 General Electric Company Refrigeration system with dual evaporators and suction line heating
US5092138A (en) * 1990-07-10 1992-03-03 The University Of Maryland Refrigeration system
US5157943A (en) * 1990-11-09 1992-10-27 General Electric Company Refrigeration system including capillary tube/suction line heat transfer
US5207077A (en) 1992-03-06 1993-05-04 The University Of Maryland Refrigeration system
DE102009001677A1 (de) * 2009-03-19 2010-09-23 BSH Bosch und Siemens Hausgeräte GmbH Kältegerät, Drosselrohr für ein Kältegerät und Verfahren zu dessen Herstellung
EP2592366A2 (fr) 2011-11-08 2013-05-15 Samsung Electronics Co., Ltd Cycle de frigorigène mixte non azéotrope et réfrigérateur ainsi équipé
EP2857778A1 (fr) * 2013-10-03 2015-04-08 Whirlpool Corporation Réfrigérateur avec mélange non azéotropique de réfrigérants d'hydrocarbures

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
"Performance optimization of a Lorenz-Meutzner cycle charged with hydrocarbon mixtures for a domestic refrigerator-freezer", IJR, vol. 1, no. 35, January 2012 (2012-01-01), pages 36 - 46
WON JAE YOON ET AL: "Performance optimization of a LorenzMeutzner cycle charged with hydrocarbon mixtures for a domestic refrigerator-freezer", INTERNATIONAL JOURNAL OF REFRIGERATION, ELSEVIER, PARIS, FR, vol. 35, no. 1, 28 September 2011 (2011-09-28), pages 36 - 46, XP028336834, ISSN: 0140-7007, [retrieved on 20111006], DOI: 10.1016/J.IJREFRIG.2011.09.014 *

Also Published As

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US20160282031A1 (en) 2016-09-29
BR102016006791A2 (pt) 2016-10-25

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