EP1771690B1 - Kondensator für kühlvorrichtung - Google Patents

Kondensator für kühlvorrichtung Download PDF

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Publication number
EP1771690B1
EP1771690B1 EP04808235A EP04808235A EP1771690B1 EP 1771690 B1 EP1771690 B1 EP 1771690B1 EP 04808235 A EP04808235 A EP 04808235A EP 04808235 A EP04808235 A EP 04808235A EP 1771690 B1 EP1771690 B1 EP 1771690B1
Authority
EP
European Patent Office
Prior art keywords
condenser
refrigerant tube
tube parts
heat
refrigerant
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.)
Not-in-force
Application number
EP04808235A
Other languages
English (en)
French (fr)
Other versions
EP1771690A4 (de
EP1771690A1 (de
Inventor
Jang-seok 103-2504 Kumho Apt.200 LEE
Kyeong-yun 1615-4 Bongcheon-7-dong KIM
Sung A202 Halla Villa 147 JHEE
Nam-soo 9/1 402 Doongji Villa CHO
Kyong-bae Refrigerator Group PARK
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.)
LG Electronics Inc
Original Assignee
LG Electronics Inc
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
Priority claimed from KR1020040097603A external-priority patent/KR100490722B1/ko
Application filed by LG Electronics Inc filed Critical LG Electronics Inc
Publication of EP1771690A4 publication Critical patent/EP1771690A4/de
Publication of EP1771690A1 publication Critical patent/EP1771690A1/de
Application granted granted Critical
Publication of EP1771690B1 publication Critical patent/EP1771690B1/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0477—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
    • 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
    • F25B39/04—Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/122—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and being formed of wires
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/34—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending obliquely
    • F28F1/36—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending obliquely the means being helically wound fins or wire spirals
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D23/00—General constructional features
    • F25D23/003—General constructional features for cooling refrigerating machinery

Definitions

  • the present invention relates to a condenser for a refrigerator, and more particularly, to a condenser for a refrigerator for minimizing the difference of air flow rate between a front side and a rear side thereof when heat exchange with ambient air in the condenser is performed by blowing operation of a cooling fan installed to a side of the condenser.
  • a refrigerator is an apparatus for freezing and refrigerating food in a freezing compartment and a refrigerating compartment by changing phase of refrigerant according to a refrigerant cycle of compression, condensation, expansion, and evaporation, and its structure is depicted in Fig. 1 .
  • Fig. 1 is a vertical elevation view schematically illustrating the structure of a general refrigerator.
  • the refrigerator includes a main body 1 divided into a freezer compartment 3 and a refrigerator compartment 4 by a partition 2 disposed between the freezer compartment 3 and the refrigerator compartment 4, a freezer compartment door 3a and a refrigerator door 4a respectively hinged to the front sides of the freezer compartment 3 and the refrigerator compartment 4, a heat exchanging chamber 5 including an evaporator 6 and a blower fan 7 and disposed at the rear side of the freezer compartment 3.
  • the partition 2 is formed with a freezer return duct 21 and a refrigerator return duct 22, for respectively returning chilled air in the freezer compartment 3 and the refrigerator compartment 4 to the heat exchanging chamber 5.
  • a chilled air duct 8 is formed at the rear side of the refrigerator compartment 4 to communicate with the freezer compartment 3 and has a plurality of chilled air discharge ports 8a.
  • a machine room M is formed at the rear lower side of the main body 1 to accommodate a compressor 9 and a condenser (not shown).
  • Air in the freezer compartment 3 and the refrigerator compartment 4 is sucked into the heat exchanging chamber 5 by the blower fan 7 of the heat exchanging chamber 5 through the freezer return duct 21 and the refrigerator return duct 22 formed in the partition 2 to undergo heat-exchange in the evaporator 6, and is discharged into the freezer compartment 3 and the refrigerator compartment 4 through the chilled air discharge ports 8a of the chilled air duct 8, and this cycle is repeated.
  • frost is attacked to the surfaces of the evaporator 6 due to the temperature difference between ambient air and the air circulating in the freezer compartment 3 and the refrigerator compartment 4 re-introduced into the evaporator via the freezer compartment return duct 21 and the refrigerator return duct 22.
  • the evaporator 6 includes a defrost heater 10 at the lower side thereof, and defrosting water generated when the frost is defrosted is collected in a defrosting water vessel (not shown) provided at the lower side of the main body 1 via a defrosting water discharge pipe 11.
  • the machine room M is provided with the compressor 9 for changing a low-temperature-and-low-pressure gaseous refrigerant into a high-temperature-and-high-pressure gaseous refrigerant, a condenser 12 for condensing the high-temperature-and-high-pressure gaseous refrigerant into a room-temperature-and-high-pressure liquid refrigerant by performing heat-exchange between the high-temperature-and-high-pressure gaseous refrigerant generated by the compressor 9 and ambient air, and a cooling fan 13 for blowing the introduced ambient air in the machine room M to the condenser 12.
  • the compressor 9 for changing a low-temperature-and-low-pressure gaseous refrigerant into a high-temperature-and-high-pressure gaseous refrigerant
  • a condenser 12 for condensing the high-temperature-and-high-pressure gaseous refrigerant into a room-temperature-and-high-pressure liquid refriger
  • the condenser 12 as shown in Fig. 3 , has a wire-on-tube structure such that straight tube parts are parallel to each other, "U"-shaped tube parts are connected to the straight tube parts in zigzag fashion to form a serpentine shaped refrigerant tube 121 and to have multiple layers, and wire radiator fins 122 with a small circular cross-section are placed on the serpentine shaped refrigerant tube 121 and welded thereto by spot-welding.
  • the refrigerant tube 121 has a staggered arrangement formed from the front side facing the cooling fan 13 to the rear side thereof.
  • the straight tube parts and the "U"-shaped tube parts of the refrigerant tube 121 are misaligned with the same in other layers.
  • KR 2001 0073641 describes a condenser according to the preamble of claim 1.
  • a condenser including: an inline arrangement in which a refrigerant tube is arranged such that refrigerant tube parts are arranged in lines in the forward and backward direction; and a staggered arrangement in which the refrigerant tube parts are arranged at the rear side of the inline arrangement in the forward and backward direction to misaligned with to each other; and wherein the ratio of the inline arrangement with respect to the staggered arrangement ranges from 50% to 60%, a distance (S1) between the refrigerant tube parts in a row direction ranges from 10 mm to 15 mm, and a distance (S2) between the refrigerant tube parts ranges from 5 mm to 10 mm.
  • the ratio of the inline arrangement to the staggered arrangement is 50%, the distance (S1) between the refrigerant tube parts in the row direction is 11 mm, and the distance (S2) between the refrigerant tube parts is 6 mm.
  • the refrigerant tube has radiator fins and is bent in the zigzag fashion to have multiple layers.
  • the radiator fins have a screw shape and are integrally formed with the outer circumference of the refrigerant tube.
  • the refrigerant tube is constructed such that extruded refrigerant tube parts are straightened by plastic deformation using rollers, the radiator fins are formed on the outer circumference of the refrigerant tube by cutting the outer circumference of the refrigerant tube, and the refrigerant tube formed with the radiator fins is bent in the serpentine shape in multiple layers.
  • the radiator fins are symmetrically formed on the outer circumference of the refrigerant tube and have a plurality of louvers penetrating the radiator fins in the vertical direction.
  • the louvers have a rectangular shape.
  • the radiator fins are made of aluminum plates having penetrating holes formed at a central portion thereof and are fixed around the outer circumference of the refrigerant tube at regular intervals.
  • Fig. 4 is a rear side view illustrating the structure of a machine room of a refrigerator employing a condenser according to a preferred embodiment of the present invention.
  • the machine room of a refrigerator is provided with a compressor 9 for changing a low-temperature-and-low-pressure gaseous refrigerant into a high-temperature-and-high-pressure gaseous refrigerant, a condenser 12 for condensing the high-temperature-and-high-pressure gaseous refrigerant into a room-temperature-and-high-pressure liquid refrigerant by performing heat-exchange between the high-temperature-and-high-pressure gaseous refrigerant generated by the compressor 9 with ambient air, and a cooling fan 13 for blowing the introduced ambient air in the machine room M to the condenser 12.
  • a compressor 9 for changing a low-temperature-and-low-pressure gaseous refrigerant into a high-temperature-and-high-pressure gaseous refrigerant
  • a condenser 12 for condensing the high-temperature-and-high-pressure gaseous refrigerant into a room-temperature-and-high-
  • the condenser 12 is structured such that difference between flow rates at the front side of the condenser 12 facing the cooling fan 13 and the rear side of the condenser 12 is minimized.
  • the condenser 12 includes an inline arrangement 123 provided at the front side of the condenser 12 and a staggered arrangement 124 provided at the rear side of the condenser 12.
  • the inline arrangement 123 is structured such that straight tube parts of a refrigerant tube 121 are parallel to each other, "U"-shaped tube parts of the refrigerant pipe 121 are connected to the straight tube parts in zigzag fashion to have multiple layers, and the straight tube parts and the "U"-shaped tube parts are aligned with other tube parts in vertical and horizontal directions.
  • the stagger arrangement 124 is structured such that, like the conventional condenser, the straight tube parts and the "U"-shaped tube parts of the refrigerant pipe 121 are misaligned with the same in other layers in the horizontal direction.
  • the staggered arrangement of the conventional condenser 12 serves to increase contact area between ambient air blown by the cooling fan 13 and the refrigerant tube 121.
  • the inline arrangement 123 is provided at the front side of the condenser 121 as in the present invention, flow rate of ambient air may be increased due to decrease of the air pneumatic resistance.
  • the increase of the contact area between the refrigerant pipe 121 and ambient air may not be expected.
  • the condenser 12 is characterized in that difference between air flow rates at the front side and the rear side of the condenser 12 is minimized and the heat-transferring area of the condenser is increased.
  • the refrigerant tube 121 of the present invention is structured in the form of a refrigerant tube 125 of a screw-type heat exchanger.
  • the screw-type heat exchanger as shown in Fig. 6 , includes screw-shaped radiator fins 125a formed in the outer circumference of the refrigerant tube 121, and the refrigerant tube 125 formed with the radiator fins 125 is bent in the serpentine shape in multiple layers.
  • Reference numeral 120 is assigned to supports for supporting sides of the refrigerant tube 125.
  • the condenser 12 of a refrigerator includes the front side of the condenser 12 having the inline arrangement 123, the rear side thereof having the staggered arrangement 124 such that the difference between air flow rates at the front side and the rear side of the condenser 12 is minimized due to the decrease of the air pneumatic resistance.
  • the refrigerant tube 125 including the inline arrangement 123 and the staggered arrangement 124 is manufactured as a refrigerant tube in which the screw-shaped radiator fins 125a are formed on the outer circumference of the refrigerant tube 125 such that the heat-transferring area of the condenser 12 is increased and cooling performance of the condenser 12 is also increased.
  • the condenser 12 according to the preferred embodiment of the present invention when the condenser 12 according to the preferred embodiment of the present invention is compared with the conventional wire-on-tube condenser in terms of surface area, the condenser 12 according to the preferred embodiment of the present invention exhibits cooling performance equal to or greater than the cooling performance of the conventional condenser even when the condenser 12 has a surface area corresponding to 70 % of the surface area of the conventional condenser.
  • a heat exchanger used in the condenser must be designed taking sufficient consideration of heat-transferring performance and distance between tube parts, while the heat-transferring performance and performance of the condenser depends on the distance between the tube parts.
  • the applicant of the present invention has performed heat-transferring experiments according to variations of the distance between tube parts as follows, and as a result, has determined the optimal conditions.
  • heat exchangers as samples to be measured have 10 rows, 8 layers, the distances S1 of 8, 11, 14, and 16 mm, and the distance S2 of 6, 9, and 12 mm, respectively. The measurements were performed 12 times.
  • the heat exchanger is not restricted to 10 rows and 8 layers and may the number of layers and rows may be modified freely.
  • the tube parts of the condenser are arranged in the staggered arrangement.
  • sample No. 4 has S1, that is, the distance between tube parts, greater than that of sample No. 1, sample No. 4 exhibits better heat-transferring performance than the heat-transferring performance of the sample No. 1.
  • the heat-transferring performance is increased as the quantity of heat is increased, in particularly, sample Nos. 4, 5, 7, 8 exhibit the highest heat-transferring performance (See Fig. 10 ).
  • the heat exchanger having 50% inline arrangement of tube parts exhibited the highest heat-transferring performance
  • the heat exchanger having 70% inline arrangement of tube parts exhibited a secondary higher heat-transferring performance
  • the heat exchanger having 30% inline arrangement of tube parts exhibited a thirdly higher heat-transferring performance.
  • the heat exchanger provided with 50% to 60% inline arrangement of tube parts at the front side of the condenser exhibits optimal heat-transferring performance (See Fig. 12 ).
  • the structure of the radiator fins of the condenser according to the preferred embodiment of the present invention has the screw-shape and can be changed into the structure shown in Figs. 13 and 14 .
  • the radiator fins 125b are integrally formed with the outer circumference of the refrigerant tube 125 to be symmetrically arranged to each other and have a plurality of louvers penetrating the radiator fins 125b in the vertical direction.
  • the radiator fins 125d are made of aluminum plates to be fixed on the outer circumference of the refrigerant tube 125 at regular intervals, like the general fin-pipe type heat exchanger.
  • the radiator fins 125b are applied to the heat exchanger of the condenser by considering the heat-transferring efficiency, the intervals and arrangements of the tube parts, and more particularly, the radiator fins 125b satisfy the conditions such that the ratio of the inline arrangement of the tube parts to the staggered arrangement of the tube parts is set to 50% to 60%, S1 (the distance of the tube parts in the row direction) is set to 10 mm to 15 mm, and S2 (the distance of the tube parts in the vertical direction) is set to 5 mm to 10 mm.
  • the condenser for a refrigerator in accordance with the present invention, since the difference between air flow rates at the front side and the rear side of the condenser is minimized when the heat exchange of the condenser with ambient air is performed by the blowing operation of the cooling fan installed to a side of the condenser, condensing efficiency of the condenser is improved and power consumption thereof is reduced so that reliability and economic utility of the condenser are enhanced.
  • radiator fins such as screw-shaped radiator fins such that heat-transferring area is increased to guarantee sufficient heat-transferring area, so that heat-transferring efficiency and refrigerating performance of the condenser are enhanced due to sufficient heat-transferring area.

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

Claims (9)

  1. Kondensator, der aufweist:
    eine Reihenanordnung (123), wobei eine Kühlmittelröhre (125) so angeordnet ist, daß Kühlmittelröhrenteile in die Vorwärts- und Rückwärtsrichtung in Reihen angeordnet sind;
    und
    eine versetzte Anordnung (124), wobei die Kühlmittelröhrenteile auf der Rückseite der Reihenanordnung (123) in die Vorwärts- und Rückwärtsrichtung so angeordnet sind, daß sie zueinander versetzt sind; dadurch gekennzeichnet, daß
    das Verhältnis der Reihenanordnung (123) bezüglich der versetzten Anordnung (124) von 50% bis 60% reicht, ein Abstand (S1) zwischen den Kühlmittelröhrenteilen in eine Reihenrichtung von 10 mm bis 15 mm reicht und ein Abstand (S2) zwischen den Kühlmittelröhrenteilen von 5 mm bis 10 mm reicht.
  2. Kondensator nach Anspruch 1, wobei das Verhältnis der Reihenanordnung (123) zur versetzten Anordnung (124) 50% beträgt, der Abstand (S1) zwischen den Kühlmittelröhrenteilen in die Reihenrichtung 11 mm beträgt, und der Abstand (S2) zwischen den Kühlmittelröhrenteilen 6 mm beträgt.
  3. Kondensator nach Anspruch 1 oder 2, wobei die Kühlmittelröhre (125) Kühlrippen (125a, 125b, 125d) aufweist und so in der Zickzackweise gebogen ist, daß sie mehrere Schichten aufweist.
  4. Kondensator nach Anspruch 3, wobei die Kühlrippen (125a) eine Schraubenform aufweisen und integral mit dem Außenumfang der Kühlmittelröhre (125) ausgebildet sind.
  5. Kondensator nach Anspruch 4, wobei die Kühlmittelröhre (125) so aufgebaut ist, daß extrudierte Kühlmittelröhrenteile unter Verwendung von Walzen durch plastische Verformung geradegerichtet sind, die Kühlrippen (125a) am Außenumfang der Kühlmittelröhre durch Schneiden des Außenumfangs der Kühlmittelröhre gebildet sind, und die mit den Kühlrippen ausgebildeten Kühlmittelröhre in mehreren Schichten in die Schlangenform gebogen sind.
  6. Kondensator nach Anspruch 3, wobei die Kühlrippen (125b) symmetrisch am Außenumfang der Kühlmittelröhre ausgebildet sind und mehrere Kühlschlitze (125c) aufweisen, die die Kühlrippen (125b) in die vertikale Richtung durchdringen.
  7. Kondensator nach Anspruch 6, wobei die Kühlschlitze (125c) eine rechteckige Form aufweisen.
  8. Kondensator nach Anspruch 3, wobei die Kühlrippen (125d) aus Aluminiumplatten bestehen, in deren Mittelabschnitt die Durchdringungslöcher ausgebildet sind, und in regelmäßigen Intervallen um den Außenumfang der Kühlmittelröhre (125) befestigt sind.
  9. Kühlvorrichtung, die einen Kondensator (12) nach einem der Ansprüche 1 bis 8 aufweist.
EP04808235A 2004-07-23 2004-11-26 Kondensator für kühlvorrichtung Not-in-force EP1771690B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
KR20040057771 2004-07-23
KR1020040097603A KR100490722B1 (ko) 2004-07-23 2004-11-25 냉장고의 응축기
PCT/KR2004/003091 WO2006009339A1 (en) 2004-07-23 2004-11-26 Condenser of refrigerator

Publications (3)

Publication Number Publication Date
EP1771690A4 EP1771690A4 (de) 2007-04-11
EP1771690A1 EP1771690A1 (de) 2007-04-11
EP1771690B1 true EP1771690B1 (de) 2010-06-16

Family

ID=35785422

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04808235A Not-in-force EP1771690B1 (de) 2004-07-23 2004-11-26 Kondensator für kühlvorrichtung

Country Status (3)

Country Link
EP (1) EP1771690B1 (de)
MX (1) MXPA06002415A (de)
WO (1) WO2006009339A1 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3129202A1 (fr) * 2021-11-12 2023-05-19 Cryofridge Europe Groupe cryogenique de refrigeration et procede de refrigeration associe

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2269956B8 (de) 2008-04-23 2020-01-01 Headway Technology Group (Qingdao) Co., Ltd. Mikrostromelektrolyse-sterilisationsalgizidvorrichtung und verfahren
IT1397613B1 (it) 2009-07-16 2013-01-18 Termal Srl Dispositivo di riscaldamento ad irraggiamento
KR20210070841A (ko) * 2019-12-05 2021-06-15 코웨이 주식회사 정수기용 응축기, 정수기용 응축기의 제조 방법 및 응축기를 구비하는 정수기

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1909005A (en) * 1930-06-16 1933-05-16 Wolverine Tube Company Method of making corrugated wall tubing
JPS5446065U (de) * 1977-09-07 1979-03-30
US6659170B1 (en) * 1996-06-17 2003-12-09 Hemant D. Kale Energy-efficient, finned-coil heat exchanger
JP3720177B2 (ja) * 1997-10-15 2005-11-24 三洋電機株式会社 熱交換器
KR100244206B1 (ko) * 1997-08-26 2000-03-02 구자홍 냉장고용 응축기
KR20000008536U (ko) * 1998-10-22 2000-05-15 이구택 열전달핀을 구비한 열교환기
KR100599035B1 (ko) * 2000-01-19 2006-07-12 삼성전자주식회사 냉동사이클용 핀형 열교환기
WO2003073023A1 (en) * 2002-02-28 2003-09-04 Lg Electronics Inc. Heat exchanger for refrigerator

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3129202A1 (fr) * 2021-11-12 2023-05-19 Cryofridge Europe Groupe cryogenique de refrigeration et procede de refrigeration associe
WO2023084162A1 (fr) * 2021-11-12 2023-05-19 Cryofridge Europe Groupe cryogénique de réfrigération et procédé de réfrigération associé

Also Published As

Publication number Publication date
EP1771690A4 (de) 2007-04-11
MXPA06002415A (es) 2007-01-19
WO2006009339A1 (en) 2006-01-26
EP1771690A1 (de) 2007-04-11

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