EP2447660A2 - Wärmetauscher und zugehöriges Mikrokanalrohr - Google Patents

Wärmetauscher und zugehöriges Mikrokanalrohr Download PDF

Info

Publication number
EP2447660A2
EP2447660A2 EP11187111A EP11187111A EP2447660A2 EP 2447660 A2 EP2447660 A2 EP 2447660A2 EP 11187111 A EP11187111 A EP 11187111A EP 11187111 A EP11187111 A EP 11187111A EP 2447660 A2 EP2447660 A2 EP 2447660A2
Authority
EP
European Patent Office
Prior art keywords
micro
heat exchanger
header
channel
exchanger according
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Withdrawn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
EP11187111A
Other languages
English (en)
French (fr)
Other versions
EP2447660A3 (de
Inventor
Young Min Kim
Hayase Gaku
Dong Hyun Kim
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
Publication of EP2447660A2 publication Critical patent/EP2447660A2/de
Publication of EP2447660A3 publication Critical patent/EP2447660A3/de
Withdrawn legal-status Critical Current

Links

Images

Classifications

    • 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
    • F28F1/24—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 transversely
    • F28F1/32—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 transversely the means having portions engaging further tubular elements
    • 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
    • F28D1/053—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 straight
    • F28D1/0535—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 straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/12—Fins with U-shaped slots for laterally inserting conduits

Definitions

  • Embodiments of the present disclosure relate to a heat exchanger of an air conditioner having a structure capable of achieving enhancements in drainage and heat transfer performance.
  • Heat exchangers which implement one part of the refrigeration cycle, are used in equipment such as air conditioners and refrigerators.
  • Heat exchangers include a plurality of fins arranged to be spaced apart from one another, and a plurality of refrigerant tubes, which is installed to come into contact with the plural fins, to guide refrigerant.
  • air flowing into the heat exchanger from the outside undergoes heat exchange while passing through the fins, so that cooling operation or heating operation is achieved.
  • Heat exchangers are classified into fin & tube type and parallel flow type heat exchangers in accordance with shapes of the fin and tube and coupling relations therebetween.
  • the fin & tube type heat exchanger has a structure in which press-worked fins are layered, and a plurality of circular tubes is then fitted between adjacent ones of the layered fins through a press-fit process.
  • the parallel flow type heat exchanger has a structure in which a fin having a corrugated shape is joined between flat elliptical tubes through a brazing process.
  • the parallel flow type heat exchanger is superior in terms of heat exchange efficiency, as compared to the fin & tube type heat exchanger.
  • drainage of condensed water from the parallel flow type heat exchanger may be troublesome.
  • FMC fin micro-channel heat exchanger
  • a heat exchanger includes a first header extending vertically and connected with an inflow tube and an outflow tube, a second header spaced apart from the first header by a desired distance and arranged parallel to the first header, and a plurality of flat micro-channel tubes arranged horizontally while being vertically spaced apart from one another by a desired clearance and arranged in a front row and a rear row between the first header and the second header, and micro-channels are formed in each of the micro-channel tubes.
  • the front row and rear row micro-channel tubes may be alternately arranged in a zigzag formation.
  • the front row and rear row micro-channel tubes may be arranged to be horizontally aligned with each other.
  • the micro-channel tubes may have a pitch Tp satisfying a range of about 7mm ⁇ Tp ⁇ 11mm.
  • a thickness Tt of each micro-channel tube may satisfy a range of about 2mm ⁇ Tt ⁇ 3.5mm.
  • a wall thickness Tow of each micro-channel tube may satisfy a range of about 0.1mm ⁇ Tow ⁇ 0.35mm.
  • a width Wc of each micro-channel may satisfy a range of about 0.5mm ⁇ Wc ⁇ 1.5mm.
  • the inflow tube may be connected to a lower side of the first header, whereas the outflow tube may be connected to an upper side of the first header.
  • the first and second headers may include respective front tanks and respective rear tanks.
  • a micro-channel tube assembly for a heat exchanger including a plurality of micro-channel tubes, wherein the micro-channel tubes are arranged horizontally while being vertically spaced apart from one another by a desired clearance and are arranged in a front row and a rear row between the first header and the second header extending vertically, and a thickness Tt of each micro-channel tube satisfies a range of about 2mm ⁇ Tt ⁇ 3.5mm.
  • a micro-channel tube assembly for a heat exchanger including a plurality of micro-channel tubes, wherein the micro-channel tubes are arranged horizontally while being vertically spaced apart from one another by a desired clearance and are arranged in a front row and a rear row between the first header and the second header extending vertically, and a wall thickness Tow of each micro-channel tube satisfies a range of about 0.1mm ⁇ Tow ⁇ 0.35mm.
  • a micro-channel tube assembly for a heat exchanger comprising a plurality of micro-channel tubes, wherein the micro-channel tubes are arranged horizontally while being vertically spaced apart from one another by a desired clearance and are arranged in a front row and a rear row between the first header and the second header extending vertically, and a width Wc of each micro-channel tube satisfies a range of about 0.5mm ⁇ Wc ⁇ 1.5mm.
  • the front row and rear row micro-channel tubes may be alternately arranged in a zigzag formation.
  • the front row and rear row micro-channel tubes may be arranged to be horizontally aligned with each other.
  • FIG. 1 is a perspective view illustrating an external appearance of a heat exchanger according to an exemplary embodiment of the present disclosure.
  • the heat exchanger 1 includes a first header 10, a second header 20, micro-channel tubes 30, and fins 40.
  • the first header 10 and the second header 20 extend vertically while being spaced apart from each other by a desired distance.
  • Tube coupling portions (not shown) are formed at facing walls of the first and second headers 10 and 20. Each tube coupling portion is formed by cutting the corresponding header wall to a size in accordance with a cross section of the corresponding micro-channel tube 30 to couple the micro-channel tube 30 to the tube coupling portion.
  • the first header 10 and the second header 20 include respective front tanks 11 and 21 and respective rear tanks 12 and 22.
  • the front tanks 11 and 21 and the rear tanks 12 and 22 are partitioned by partition walls, respectively.
  • Each of the front tanks 11 and 21 and the rear tanks 12 and 22 may be further vertically partitioned by baffles 13.
  • the micro-channel tubes 30 are installed between the first and second headers 10 and 20, to guide refrigerant by communicating the first header 10 with the second header 20.
  • Each of the micro-channel tubes 30 is a path through which refrigerant passes. Refrigerant is compressed or expanded while circulating in an air conditioner (not shown), so that cooling and heating may be achieved.
  • the micro-channel tubes 30, which are vertically spaced apart from one another by a desired clearance, are arranged in two rows, namely, a front row and a rear row. That is, the micro-channel tubes 30 include front row micro-channel tubes 31 and rear row micro-channel tubes 32.
  • the front row and rear row micro-channel tubes 31 and 32 are alternately arranged in a zigzag formation.
  • the front row and rear row micro-channel tubes 31 and 32 may be arranged to be horizontally aligned with each other, as shown in FIG. 4 .
  • an inflow tube 14 into which refrigerant flows and an outflow tube 15 from which heat-exchanged refrigerant while passing through the micro-channel tubes 30 is discharged are connected to the first header 10.
  • the inflow and outflow tubes 14 and 15 may be respectively connected to lower and upper sides of the first header 10, in order to prevent accumulation of refrigerant droplets caused by gravity, even if refrigerant flowing into the first header 10 has both a gas phase and a liquid phase.
  • FIG. 2 is a view schematically illustrating a fin structure of the heat exchanger according to an exemplary embodiment of the present disclosure.
  • FIG. 3 is a sectional view taken along line I - I of FIG. 2 .
  • a fin body 43 in each fin 40 is formed to have a plate shape with a certain width and height.
  • the fin body 43 may be a rectangular thin plate.
  • Each fin 40 is installed to come into contact with the corresponding micro-channel tubes 30, and may be formed as widely as possible so that the section thereof to radiate or absorb heat becomes wider.
  • Heat of refrigerant flowing inside the micro-channel tubes 30 is transferred to air flowing around the fins 40 via the micro-channel tubes 30 and fins 40, thereby easily radiating heat to the outside.
  • front row slots 44 and rear row slots 45 are formed at each of the fins 40 so that the front row and rear row micro-channel tubes 31 and 32 are fitted into the front row slots 44 and the rear row slots 45, respectively.
  • collars 47 perpendicular to the fin body 43 are formed respectively at peripheral areas of the front row and rear row slots 44 and 45 to easily fit the front row and rear row micro-channel tubes 31 and 32 into the corresponding front row and rear row slots 44 and 45 respectively, thereby securing a desired joining force.
  • the fins 40 are arranged to be evenly spaced in parallel with a flow direction of air. Thus, air may execute heat exchange while naturally flowing along surfaces of the fins 40 without greatly undergoing resistance caused by the fins 40.
  • the front row and rear row slots 44 and 45 of each fin 40 are also arranged in a zigzag formation.
  • the front row and rear row slots 44 and 45 of each fin 40 are also arranged to be horizontally aligned with each other, of course.
  • front row and rear row louvers 41 and 42 or front row and rear row slits 46a and 46b are formed between the vertically adjacent slots 44 and between the vertically adjacent slots 45 respectively, to enhance heat transfer efficiency by increasing a contact area with air.
  • the louvers 41 and 42 and the slits 46a and 46b may also be formed together.
  • Each of the louvers 41 and slits 46a are formed between the vertically adjacent front row slots 44, and each of the louvers 42 and slits 46b are formed between the vertically adjacent rear row slots 45.
  • each fin 40 the front row louvers 41 and the rear row louvers 42 are symmetrically arranged in a width direction of the fin 40, and each of the front row louvers 41 and the rear row louvers 42 is formed so that a portion of the fin body 43 is slightly bent from a plane of the fin 40 in an upward or downward direction to be inclined at a desired angle. Accordingly, air flowing along the fins 40 is dispersed by the louvers 41 and 42, and growth of a boundary layer is restrained, so that heat exchange efficiency may be enhanced.
  • FIG. 5 is a view schematically illustrating a fin structure of the heat exchanger according to another exemplary embodiment of the present disclosure.
  • FIG. 6 is a sectional view taken along line II - II of FIG. 5 .
  • FIG. 7 is a view schematically illustrating a fin structure of the heat exchanger according to another exemplary embodiment of the present disclosure.
  • slits 46a may be formed between vertically adjacent slots 44 and, similarly, slits 46b may be formed between vertically adjacent slots 45. Air is changed into turbulent air while flowing into openings of the slits 46a and 46b, and the turbulent air circulates around the micro-channel tubes 30, and thus heat exchange efficiency may be improved.
  • front row slots 44 and rear row slots 45 of each fin 40 may be arranged in a zigzag formation or to be horizontally aligned with each other.
  • FIG. 8 is a view schematically illustrating a fin structure of the heat exchanger according to another exemplary embodiment of the present disclosure.
  • FIG. 9 is a sectional view taken along line III ⁇ III of FIG. 8 .
  • FIG. 10 is a view schematically illustrating a fin structure of the heat exchanger according to another exemplary embodiment of the present disclosure.
  • louvers 41 and 42 and slits 46a and 46b in each fin 40 may also be formed together, and front row slots 44 and rear row slots 45 in each fin 40 may be arranged in a zigzag formation or to be horizontally aligned with each other. Since the remaining components are the same as those according to another exemplary embodiment of the present disclosure, no description will be given.
  • each of the micro-channel tubes 30 has a flat shape, and a plurality of micro-channels 33 is formed in the micro-channel tube 30 to guide refrigerant in the micro-channel tube 30.
  • each of the micro-channel tubes 30 may have a circular shape in a cross section, the micro-channel tube 30 may have a flat shape to expand a heat transfer area.
  • FIGS. 12 to 15 are graphs illustrating variations in quantity of heat according to the thickness of each micro-channel tube, the pitch of the adjacent micro-channel tubes, the wall thickness of each micro-channel tube, and the width of each micro-channel, respectively.
  • performance of the heat exchanger may vary depending on the thickness Tt of each micro-channel tube 30, the pitch Tp of the adjacent micro-channel tubes 30, the wall thickness Tow of each micro-channel tube 30, and the width Wc of each micro-channel 33.
  • the thickness Tt of each micro-channel tube 30 may be determined in a range of 2mm ⁇ Tt ⁇ 3.5mm.
  • the pitch Tp of the adjacent micro-channel tubes 30 may be determined in a range of 7mm ⁇ Tp ⁇ 11 mm.
  • the quantity of heat Q may converge upon a maximum value if the pitch Tp of the adjacent micro-channel tubes 30 approaches approximately 7mm.
  • the quantity of heat Q increases as the wall thickness Tow of each micro-channel tube 30 decreases, the quantity of heat Q converges upon a maximum value if the wall thickness Tow of each micro-channel tube 30 approaches approximately 0.1mm.
  • the quantity of heat Q increases as the width Wc of each micro-channel 33 increases, the quantity of heat Q subsequently has a maximum value when the width Wc is in a range of approximately 0.5mm ⁇ Wc ⁇ 1.5mm, and then the quantity of heat Q reduces again.
  • the heat exchanger including the micro-channel tubes 30, which are horizontally arranged while being vertically spaced apart from one another by a desired clearance and are arranged in the front row and the rear row between the first header and the second header extending vertically, when the thickness Tt of each micro-channel tube 30, the pitch Tp of the adjacent micro-channel tubes 30, the wall thickness Tow of each micro-channel tube 30, and the width Wc of each micro-channel 33 satisfy the above-described ranges respectively, the heat exchanger may simultaneously realize optimal performance while securing drainage performance.
  • a fin micro-channel heat exchanger having a structure capable of achieving enhancements in drainage and heat transfer performance.

Landscapes

  • 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)
EP11187111.7A 2010-10-28 2011-10-28 Wärmetauscher und zugehöriges Mikrokanalrohr Withdrawn EP2447660A3 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
KR1020100106369A KR20120044848A (ko) 2010-10-28 2010-10-28 열교환기 및 그 마이크로채널튜브

Publications (2)

Publication Number Publication Date
EP2447660A2 true EP2447660A2 (de) 2012-05-02
EP2447660A3 EP2447660A3 (de) 2015-03-04

Family

ID=45001647

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11187111.7A Withdrawn EP2447660A3 (de) 2010-10-28 2011-10-28 Wärmetauscher und zugehöriges Mikrokanalrohr

Country Status (4)

Country Link
US (1) US20120103582A1 (de)
EP (1) EP2447660A3 (de)
KR (1) KR20120044848A (de)
CN (1) CN102563980A (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105241285A (zh) * 2015-10-31 2016-01-13 卢雁显 超导暖气片

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
USD749201S1 (en) * 2012-08-02 2016-02-09 Mitsubishi Electric Corporation Fin-plate for heat exchanger
USD775315S1 (en) * 2012-08-02 2016-12-27 Mitsubishi Electric Corporation Fin-plate for heat exchanger
JP6189263B2 (ja) * 2014-07-28 2017-08-30 井上ヒーター株式会社 熱交換器用フィンおよびこれを備えた熱交換器
JP6706839B2 (ja) * 2016-03-11 2020-06-10 パナソニックＩｐマネジメント株式会社 フィンチューブ熱交換器
DE102017211397A1 (de) * 2017-07-04 2019-01-10 Volkswagen Aktiengesellschaft Verfahren zum Betrieb einer Klimatisierungseinrichtung für ein Kraftfahrzeug
US11047631B2 (en) * 2019-02-20 2021-06-29 Caterpillar Inc. Bumper clip for tube type heat exchangers

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2965357A (en) * 1956-01-24 1960-12-20 Modine Mfg Co Heat exchange structure
JPS56155391A (en) * 1980-04-30 1981-12-01 Nippon Denso Co Ltd Corrugated fin type heat exchanger
JPH0275892A (ja) * 1988-09-09 1990-03-15 Showa Alum Corp 熱交換器
KR0165067B1 (ko) * 1996-04-09 1999-01-15 구자홍 2열 플랫튜브형 열교환기
JPH1089870A (ja) * 1996-09-18 1998-04-10 Nippon Light Metal Co Ltd 熱交換器の製造方法及び熱交換器
DE10054158A1 (de) * 2000-11-02 2002-05-08 Behr Gmbh Mehrkammerrohr mit kreisförmigen Strömungskanälen
US6964296B2 (en) * 2001-02-07 2005-11-15 Modine Manufacturing Company Heat exchanger
US6745827B2 (en) * 2001-09-29 2004-06-08 Halla Climate Control Corporation Heat exchanger
US7000415B2 (en) * 2004-04-29 2006-02-21 Carrier Commercial Refrigeration, Inc. Foul-resistant condenser using microchannel tubing
TW200712401A (en) * 2005-09-30 2007-04-01 Seasonair M Sdn Bhd Heat exchangers
US10415894B2 (en) * 2006-01-26 2019-09-17 Ingersoll-Rand Company Fin and tube heat exchanger
WO2009002307A1 (en) * 2007-06-26 2008-12-31 Carrier Corporation Aluminum heat exchanger with pit resistant braze joints
CN101187513A (zh) * 2007-11-26 2008-05-28 苏州昆拓冷机有限公司 换热装置
CA2727671A1 (en) * 2008-06-13 2009-12-17 Goodman Global, Inc. Method for manufacturing tube and fin heat exchanger with reduced tube diameter and optimized fin produced thereby
JP5279514B2 (ja) * 2009-01-05 2013-09-04 三菱電機株式会社 熱交換器、その製造方法及びこの熱交換器を備えた空気調和機
CN101614492A (zh) * 2009-06-15 2009-12-30 浙江康盛股份有限公司 微通道冷凝器
CN101846420A (zh) * 2010-07-08 2010-09-29 合肥美的荣事达电冰箱有限公司 制冷设备

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105241285A (zh) * 2015-10-31 2016-01-13 卢雁显 超导暖气片
CN105241285B (zh) * 2015-10-31 2017-08-25 青岛恒泰散热器有限公司 超导暖气片

Also Published As

Publication number Publication date
KR20120044848A (ko) 2012-05-08
US20120103582A1 (en) 2012-05-03
CN102563980A (zh) 2012-07-11
EP2447660A3 (de) 2015-03-04

Similar Documents

Publication Publication Date Title
US20120103583A1 (en) Heat exchanger and fin for the same
EP2447660A2 (de) Wärmetauscher und zugehöriges Mikrokanalrohr
EP2369285B1 (de) Wärmetauscher
EP2840341B1 (de) Wärmetauscher
US20090173480A1 (en) Louvered air center with vortex generating extensions for compact heat exchanger
EP3875878B1 (de) Wärmetauscher und kühlzyklusvorrichtung
EP2699867B1 (de) Wärmetauscher
JP6120978B2 (ja) 熱交換器及びそれを用いた空気調和機
US20090242182A1 (en) Heat Exchanger Plate
KR20070102173A (ko) 열교환기
EP3644002B1 (de) Wärmetauscher, kühlzyklusvorrichtung und klimaanlage
US11346584B2 (en) Refrigerant evaporator and method for manufacturing same
CN107843031B (zh) 微通道换热器
CN110094901B (zh) 一种微通道换热器
JP2004263881A (ja) 伝熱フィン、熱交換器、カーエアコン用エバポレータ及びコンデンサ
WO2022206765A1 (zh) 换热器和空调系统
EP2224198A1 (de) Rippenrohrwärmetauscher
CN110595112A (zh) 换热器和具有其的空调器
KR101062650B1 (ko) 열교환기
CN110945300B (zh) 制冷剂分配器、热交换器及制冷循环装置
JP7006376B2 (ja) 熱交換器
WO2018008134A1 (ja) 熱交換器
CN217058489U (zh) 热交换器
KR100819011B1 (ko) 열교환기
CN110945299A (zh) 热交换器及制冷循环装置

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: A2

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: SAMSUNG ELECTRONICS CO., LTD.

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

RIC1 Information provided on ipc code assigned before grant

Ipc: F28D 1/053 20060101ALI20150127BHEP

Ipc: F28F 1/32 20060101AFI20150127BHEP

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

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20150905