EP0936432B1 - Heat exchanger for air conditioners - Google Patents

Heat exchanger for air conditioners Download PDF

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Publication number
EP0936432B1
EP0936432B1 EP97944133A EP97944133A EP0936432B1 EP 0936432 B1 EP0936432 B1 EP 0936432B1 EP 97944133 A EP97944133 A EP 97944133A EP 97944133 A EP97944133 A EP 97944133A EP 0936432 B1 EP0936432 B1 EP 0936432B1
Authority
EP
European Patent Office
Prior art keywords
heat transfer
upwind
downwind
transfer tubes
fin
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.)
Expired - Lifetime
Application number
EP97944133A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0936432A1 (en
EP0936432A4 (en
Inventor
Junichirou-Shiga-seisakusho of Daikin Ind. TANAKA
Yoshiaki-Shiga-seisakusho of Daikin Ind. FUKUMURA
Shoji-Shiga-seisakusho of Daikin Ind. Ltd NOBUI
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.)
Daikin Industries Ltd
Original Assignee
Daikin Industries 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 Daikin Industries Ltd filed Critical Daikin Industries Ltd
Publication of EP0936432A1 publication Critical patent/EP0936432A1/en
Publication of EP0936432A4 publication Critical patent/EP0936432A4/en
Application granted granted Critical
Publication of EP0936432B1 publication Critical patent/EP0936432B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated 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
    • F28D1/047—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
    • 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
    • F28F1/325—Fins with openings

Definitions

  • the present invention relates to a heat exchanger for use in an air conditioner or the like and more particularly, to a so-called crossed-fin-and-tube type heat exchanger in which heat transfer tubes penetrate a plurality of fins arranged side by side, in a crossed manner.
  • a heat pump type air conditioner In heating the inside of a room by means of a heat pump type air conditioner employing a refrigerant circuit, its indoor heat exchanger is made to function as a condenser and its outdoor heat exchanger is made to function as an evaporator.
  • a representative of the heat exchangers capable of functioning as a condenser is a crossed-fin-and-tube type heat exchanger, and its prior art example is shown in Fig. 10.
  • a plurality of fins 40 made of a metal, such as aluminum, having a good heat conduction are arranged in parallel with one another at predetermined intervals, and a plurality of hairpin type heat transfer tubes 11 are inserted in the fins with their end portions connected to one another by U-shaped communication tubes 12.
  • a plurality of heat transfer tubes 13 and a plurality of heat transfer tubes 14 are aligned, in a staggered form as a whole, at an upwind half 40a and a downwind half 40b, respectively, of each of the plurality of fins 40.
  • a refrigerant from a compressor flows through an inlet tube 9 and diverges in two vertical directions to flow into the downwind heat transfer tubes 14, at which the refrigerant exchanges heat with air A passing the fins 40. Thereafter the refrigerant flows into the upwind heat transfer tubes 13. The refrigerant that has flowed into the upwind heat transfer tubes 13 further exchanges heat with the air A passing the fins 40. Then, after converging from the two vertical directions, the refrigerant flows out through an outlet tube 8 and returns to the compressor by way of a pressure reducing device and an evaporator.
  • Fig. 11 is a diagram showing the temperature at several portions of the hairpin type heat transfer tubes 11 and the U-shaped communication tube 12 in the aforementioned prior art heat exchanger.
  • the connection structure of the hairpin type heat transfer tubes 11 and the U-shaped communication tube 12 is shown on the left-hand side of the figure, and their temperatures are shown in the graph on the right-hand side.
  • the temperature has the highest value of about 90 °C in the vicinity of the inlet tube 9. On the other hand, the temperature has the lowest value of about 30 °C in the vicinity of the outlet tube 8.
  • disorder occurs in the temperature change at portions B and C enclosed by dashed lines.
  • the heat transfer tubes (inlet vicinity heat transfer tubes) 14a located in the vicinity of the inlet tube 9 and having the highest temperature and the heat transfer tubes (outlet vicinity heat transfer tubes) 13a located in the vicinity of the outlet tube 8 and having the lowest temperature are arranged close to each other and they share the same fins 40. That is, in regard to the portion B, the inlet vicinity heat transfer tubes 14a are arranged close to and above and below the outlet vicinity heat transfer tube 13a located on the lower side.
  • the high-temperature heat of a superheated gas which flows through the inlet vicinity heat transfer tube 14a is transferred via the fin 40 and imparted to a supercooled liquid which flows through the outlet vicinity heat transfer tube 13a, so that a significant temperature rise occurs.
  • the outlet vicinity heat transfer tubes 13a is arranged close to and above and below the inlet vicinity heat transfer tube 14a on the upper side. Therefore, the low-temperature heat of the supercooled liquid which flows through the outlet vicinity heat transfer tube 13a is also imparted, transferred via the fin 40, to the superheated gas which flows through the inlet vicinity heat transfer tube 14a, so that a significant temperature fall occurs.
  • a plurality of slits 41 are provided between the upwind heat transfer tubes 13 and the downwind heat transfer tubes 14 so that the slits 41 thermally separate the upwind halves 40a from the downwind halves 40b of the fins 40 (e.g., refer to Japanese Patent Laid-Open Publication No. HEI 3-194370).
  • the bending rigidity of the fins 40 is degraded in a direction in which the fins 40 are arranged (i.e., in the direction in which the heat transfer tubes 13 and 14 are inserted) as shown in the figure.
  • the fins 40 are deformed during these works, and this causes problems that the heat exchanging ability, or performance, of the heat exchanger is reduced and that the ventilation resistance increases.
  • EP-A-0 401 752 discloses a heat exchanger of a cross fin and tube type.
  • a plurality of fins is arranged in parallel to each other and perpendicular to the heat transfer tubes.
  • the heat transfer tubes of the upwind side and downwind side are arranged in a staggered form as a whole.
  • the upwind half is thermally separated from the downwind half by a plurality of cut lines which are arranged spaced from each other in a specified direction and at least one of which is extended in a direction intersecting the direction of arrangement of the cut lines.
  • the upwind transfer tubes and the downwind transfer tubes are arranged in a staggered form as a whole and each cut line is located between the mutually adjacent upwind heat transfer tube and the downwind transfer tube, and extended intersecting an imaginary line which connects the centres of the mutually adjacent upwind and downwind heat transfer tubes having an approximately identical diameter.
  • the upwind half and the downwind half of each fin are formed with raised positions having cut edges which protrude into an airflow pass and extend in a direction intersecting a direction of airflow.
  • the cut lines are arranged in a middle portion formed between the upwind raised portions and the downwind raised portions.
  • the present invention has been developed to solve the aforementioned problems, and its object is to provide a heat exchanger capable of securing a sufficient rigidity of the fins while preventing the possible occurrence of unnecessary heat conduction via the fins.
  • the present invention provides a heat exchanger of a crossed-fin-and-tube type according to one of claims 1, 2, 3 or 4.
  • a plurality of fins are placed side by side, a plurality of upwind heat transfer tubes penetrate an upwind half of each fin and are aligned in a specified direction in the upwind half, a plurality of downwind heat transfer tubes penetrate a downwind half of each fin and are aligned in the downwind half in a direction substantially identical to the direction in which the upwind heat transfer tubes are aligned, and the upwind half is thermally separated from the downwind half by a plurality of cut lines which are arranged, spaced from each other, in a specified direction, characterized in that at least one of the cut lines is extended in a direction intersecting the direction of arrangement of the cut lines.
  • an angle made between the direction in which the cut lines are arranged and the direction in which the at least one cut line extends is ⁇ , preferably, a relationship of 5° ⁇ ⁇ ⁇ 175° is satisfied.
  • the upwind heat transfer tubes and the downwind heat transfer tubes are arranged in a staggered form as a whole, and each cut line is located between mutually adjacent upwind heat transfer tube and downwind heat transfer tube, and extended intersecting an imaginary line which connects centers of the mutually adjacent upwind and downwind heat transfer tubes.
  • the upwind heat transfer tubes and the downwind heat transfer tubes are made to have an approximately identical diameter whose magnitude is represented by W1, each cut line is extended in a region centered on the imaginary line and having a width represented by W2, and an expression of 0.4 ⁇ W2/W1 ⁇ 1.3 holds.
  • the degradation in the rigidity of the fins is avoided under the normal working conditions while more surely preventing the unnecessary heat conduction via the fins.
  • the upwind half and downwind half of each fin are formed with raised portions having cut edges which protrude into an air flow path and extend in a direction intersecting a direction of air flow, and the cut lines are arranged in a middle portion formed between the upwind raised portions and the downwind raised portions.
  • the heat exchanging ability, or performance is enhanced by the raised portions. Furthermore, the degradation in the rigidity of the fins is reduced while preventing the possible occurrence of unnecessary heat conduction via the fins.
  • a higher-temperature refrigerant flows through the downwind heat transfer tubes and a lower-temperature refrigerant flows through the upwind heat transfer tubes, and the upwind half of each fin is formed with a fin connecting portion which is interposed between two upwind raised portions and which is located on an upwind side of the downwind heat transfer tubes.
  • an expression of 5° ⁇ ⁇ ⁇ 175° holds.
  • mutually adjacent cut lines are extended in such a manner that they intersect the direction of alignment of the upwind heat transfer tubes or the downwind heat transfer tubes in opposite directions. In this case, the unnecessary heat conduction via the fins is still more surely prevented and a sufficient rigidity of the fins is also secured.
  • Fig. 1 is a refrigerant circuit diagram of a heat pump air conditioner provided with a refrigerant circuit.
  • a reference numeral 1 denotes a compressor
  • a reference numeral 2 denotes a four-way selector valve
  • a reference numeral 3 denotes an indoor heat exchanger provided with an indoor fan 7
  • reference numeral 4 denotes a pressure reducing device, such as a capillary tube
  • a reference numeral 5 denotes an outdoor heat exchanger provided with an outdoor fan 6.
  • a reference numeral 8 denotes an accumulator.
  • a refrigerant flows from the compressor 1 through the indoor heat exchanger 3, pressure reducing device 4 and outdoor heat exchanger 5 and is thereafter fed back to the compressor 1.
  • the indoor heat exchanger 3 functions as a condenser and the outdoor heat exchanger 5 functions as an evaporator.
  • Fig. 2 schematically shows the construction of the above indoor heat exchanger 3 which functions as a condenser in the heating operation, wherein components similar to those of the prior art heat exchanger shown in Fig. 10 are denoted by the same reference characters.
  • the structure of this indoor heat exchanger 3 is similar to that of the prior art shown in Fig. 10 except for the configuration of the fins 10.
  • a number of fins 10 made of a metal, such as aluminum, having a good heat conduction are arranged side by side in parallel with each other at specified intervals, and a plurality of hairpin type heat transfer tubes 11 are inserted in the fins 10 with their end portions connected to one another by U-shaped communication tubes 12.
  • a plurality of heat transfer tubes 13 and a plurality of heat transfer tubes 14 are arranged in a vertical direction, in a staggered form as a whole, at an upwind half 10a and a downwind half 10b, respectively, of the fins 10.
  • the refrigerant from the compressor 1 flows through an inlet tube 9 and diverges in two vertical directions to flow into the downwind heat transfer tubes 14, at which the refrigerant exchanges heat with air A passing the fins 10. Thereafter the refrigerant flows into the upwind heat transfer tubes 13. The refrigerant that has flowed into the upwind heat transfer tubes 13 further exchanges heat with the air A passing the fins 10. Then, after converging from the two vertical directions, the refrigerant flows out through an outlet tube 8 and returns to the compressor 1 by way of the pressure reducing device 4 and the evaporator 5.
  • reference numeral 13 denotes the upwind heat transfer tube and reference numeral 14 denotes the downwind heat transfer tube.
  • the figure shows the cross-sections of the heat transfer tubes. These heat transfer tubes 13 and 14 have an identical diameter, the magnitude of which is represented by W1 in the figure.
  • a reference numeral 15 denotes a cut line. The cut lines 15 each extend intersecting an imaginary line 20 which connects the centers of the mutually adjacent upwind heat transfer tube 13 and downwind heat transfer tube 14.
  • the intersection point is located in a position satisfying the following relationship: 0.2 ⁇ L2/L1 ⁇ 0.8
  • the cut line 15 is provided in a region centered on the imaginary line 20 and having a width W2 which satisfies the following relationship: 0.4 ⁇ W2/W1 ⁇ 1.3
  • the cut line 15 is provided within a range of 5° ⁇ ⁇ ⁇ 175° so that the adjacent cut lines 15 intersect the direction in which the downwind heat transfer tubes are arranged, in the mutually reverse directions, as shown in Fig.
  • the plurality of cut lines 15 are extended at the fins 10.
  • the cut lines 15 are arranged along the vertical direction in which the downwind heat transfer tubes 14 and/or the upwind heat transfer tubes 13 are aligned, and the directions in which the cut lines extend make specified angles of 5° to 175° relative to the direction in which the downwind and/or upwind heat transfer tubes are arranged.
  • the directions in which the cut lines 15 extend do not coincide with the direction X in which the cut lines are arranged. This avoids the degradation in the rigidity of the fins which will cause the bending of the fins with the direction X of arrangement of the cut lines serving as a center of the bending. Consequently, it is possible to enhance the workability in handling the fins 10 and also to prevent the reduction of the heat exchanging ability and the increase of the ventilation resistance which are caused by the deformation of the fins 10.
  • Fig. 4 shows another embodiment of the heat exchanger of the present invention.
  • components similar to those of the embodiment shown in Fig. 3 are denoted by the same reference characters.
  • upwind raised portions 16 and 17 are formed at an upwind half 100a of each fin 100
  • downwind raised portions 18 are formed at a downwind half 100b of the fin 100.
  • These raised portions 16, 17 and 18 are of the so-called slit type, formed by raising a part of the surface of each fin 100 (see Fig. 5B).
  • Their cut edges 16a, 17a and 18a protrude in the air flow path of the air A so as to intersect the air flow direction A.
  • a fin connecting portion 19 interposed between two upwind raised portions 16 and 17 located at the most downwind side is formed on the upwind side (the left-hand side in Fig. 4) of the downwind heat transfer tubes 14.
  • a plurality of cut lines 15 which each intersect an imaginary line 20 connecting the centers of the mutually adjacent upwind heat transfer tube 13 and downwind heat transfer tube 14.
  • the cut lines 15 are provided in a central part of the middle portion and within a lateral width W4 which satisfies the following expression: 0.4 ⁇ W4/W3 ⁇ 0.9
  • the direction X of arrangement of the cut lines 15 is approximately parallel to the direction of alignment of the downwind heat transfer tubes 14 and hence approximately parallel to the direction of alignment of the upwind heat transfer tubes 13 as well.
  • the cut line 15 is provided in a position for which the following expression holds: 0.3 ⁇ L4/L3 ⁇ 0.7 Further, the cut lines 15 are provided so that an angle ⁇ made between the direction X in which the cut lines are arranged and the direction in which the cut line extends is within a range of 5° ⁇ ⁇ ⁇ 175° and that the mutually adjacent cut lines 15 are extended in the mutually reverse directions.
  • the raised portions 16, 17 and 18 are provided on the surfaces of the fins 100 and their edges 16a, 17a and 18a are made to protrude in the air flow path of the air A. Therefore, the fins 100 have a high heat dissipation efficiency, and hence an improved heat exchanging ability. Then, by providing the heat exchanger having the thus improved heat exchanging ability with the cut lines 15, the unnecessary heat conduction via the fins 100 is prevented. Furthermore, similarly to the embodiment described with reference to Fig. 3, the cut lines 15 are arranged along the direction in which the downwind heat transfer tubes 14 or the upwind heat transfer tubes 13 are arranged, and the direction of extension of the cut line makes the specified angle of 5° to 175° relative to the direction of arrangement of the cut lines.
  • the directions of extension of the cut lines 15 do not coincide with the direction X of arrangement thereof, which enables the avoidance of the reduction in the rigidity of the fins 100 which may cause the fins to be bent along the direction X of arrangement of the cut lines. Consequently, the workability in handling the fins 100 is improved.
  • the cut lines 15 are provided between the upwind heat transfer tubes 13 and the downwind heat transfer tubes 14 at the fins 100, thereby preventing the unnecessary heat conduction from the downwind half 100b to the upwind half 100a of each fin 100. Further, a relationship of 0.4 ⁇ W4/W3 is made to hold, where W3 is the width of the middle portion formed between the upwind raised portions 16 and 17 and the downwind raised portions 18 and W3 is the width of the zone in which the cut lines 15 are provided. With this arrangement, the unnecessary heat conduction is infallibly suppressed, and as shown in the graph of Fig. 8, a good performance, or heat exchanging ability, is displayed as in the case of the aforementioned embodiment shown in Fig. 3.
  • the fins 100 provided with the raised portions 16, 17 and 18 have a good ability to exchange heat with the passing air A, the temperature tends to drop particularly in those portions that are located between the upwind heat transfer tubes 13 at the upwind half 100a, and this sometimes leads to an insufficient display of the heat exchanging ability.
  • the fin connecting portions 19 are provided on the upwind side of the downwind heat transfer tubes 14 in the present embodiment,part of the high-temperature heat of the downwind heat transfer tubes 14 through which the higher-temperature refrigerant flows is transferred to the upwind half 100a by way of the fin connecting portions 19. Therefore, an abnormal temperature reduction at the aforementioned portions of the upwind half is prevented, which allows the heat exchanging ability to be improved.
  • the present invention is not limited to the aforementioned embodiments.
  • the cut line 15 instead of providing the cut line by the elongated hole as shown in Fig. 5A, it is acceptable to form the cut line 15 of a slit type as shown in Fig. 5B in which a part of the fin is raised, or a louver type as shown in Fig. 5C in which a side portion is sunk (or raised), or a burring type as shown in Fig. 5D in which a flange is provided around the elongated hole.
  • the cut lines 15 are provided at the fins 10 and 100, and the cut lines 15 prevent the unnecessary heat conduction from the downwind halves 10b and 100b to the upwind halves 10a and 100a of the fins 10 and 100.
  • the cut lines 15 may be provided in the outdoor heat exchanger 5 which functions as a condenser in the cooling operation.
  • the heat exchanger of the present invention is used for a heat pump type air conditioner or the like provided with a refrigerant circuit.

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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)
  • Other Air-Conditioning Systems (AREA)
  • Air Filters, Heat-Exchange Apparatuses, And Housings Of Air-Conditioning Units (AREA)
EP97944133A 1996-10-31 1997-10-16 Heat exchanger for air conditioners Expired - Lifetime EP0936432B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP30734296 1996-10-31
JP8307342A JPH10132480A (ja) 1996-10-31 1996-10-31 空気調和機用熱交換器
PCT/JP1997/003729 WO1998019126A1 (fr) 1996-10-31 1997-10-16 Echangeur de chaleur pour conditionneurs d'air

Publications (3)

Publication Number Publication Date
EP0936432A1 EP0936432A1 (en) 1999-08-18
EP0936432A4 EP0936432A4 (en) 2000-01-19
EP0936432B1 true EP0936432B1 (en) 2003-01-08

Family

ID=17967970

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97944133A Expired - Lifetime EP0936432B1 (en) 1996-10-31 1997-10-16 Heat exchanger for air conditioners

Country Status (12)

Country Link
EP (1) EP0936432B1 (xx)
JP (1) JPH10132480A (xx)
KR (1) KR20000034784A (xx)
CN (1) CN1159564C (xx)
AU (1) AU710016B2 (xx)
DE (1) DE69718343T2 (xx)
ES (1) ES2190544T3 (xx)
HK (1) HK1019354A1 (xx)
MY (1) MY118256A (xx)
PT (1) PT936432E (xx)
TW (1) TW415582U (xx)
WO (1) WO1998019126A1 (xx)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100347894B1 (ko) * 2000-07-06 2002-08-09 엘지전자주식회사 세경관형 열교환기
KR20040004967A (ko) * 2002-07-08 2004-01-16 한라공조주식회사 열교환기용 핀
JP4495090B2 (ja) * 2006-02-03 2010-06-30 ダイキン工業株式会社 空気調和装置
KR20090022840A (ko) * 2007-08-31 2009-03-04 엘지전자 주식회사 냉동장치의 열교환기
DE102008024562B4 (de) * 2008-05-21 2021-06-10 Stiebel Eltron Gmbh & Co. Kg Wärmepumpenvorrichtung mit einem Lamellenrohrwärmeübertrager als Verdampfer
CN102918348B (zh) 2010-05-31 2015-03-25 三电有限公司 热交换器以及使用该热交换器的热泵装置
CN103537529B (zh) * 2012-07-12 2015-08-26 珠海格力电器股份有限公司 一种风冷换热器的冲孔方法和一种风冷换热器
KR20140116625A (ko) * 2013-03-25 2014-10-06 엘지전자 주식회사 열교환기

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5553663A (en) * 1994-07-21 1996-09-10 Samsung Electronics Co., Ltd. Heat exchange for air conditioner

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58108394A (ja) * 1981-12-21 1983-06-28 Hitachi Ltd 熱交換器
JPS58138994A (ja) * 1982-02-15 1983-08-18 Fuji Heavy Ind Ltd 熱交換器
JPH02254269A (ja) * 1989-03-27 1990-10-15 Hitachi Ltd フインチューブ式熱交換器
DE3938842A1 (de) * 1989-06-06 1991-05-29 Thermal Waerme Kaelte Klima Verfluessiger fuer ein kaeltemittel einer fahrzeugklimaanlage
JP2753354B2 (ja) 1989-12-22 1998-05-20 株式会社日立製作所 空気調和機用熱交換器
DE4220823C2 (de) * 1992-06-25 1996-08-29 Thermal Waerme Kaelte Klima Heizungswärmetauscher für Personenkraftwagen mit mindestens zwei Teilwärmetauschern
JP3256634B2 (ja) * 1994-08-10 2002-02-12 三菱電機株式会社 熱交換器

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5553663A (en) * 1994-07-21 1996-09-10 Samsung Electronics Co., Ltd. Heat exchange for air conditioner

Also Published As

Publication number Publication date
EP0936432A1 (en) 1999-08-18
CN1159564C (zh) 2004-07-28
AU710016B2 (en) 1999-09-09
CN1228833A (zh) 1999-09-15
TW415582U (en) 2000-12-11
DE69718343T2 (de) 2003-09-18
HK1019354A1 (en) 2000-02-03
DE69718343D1 (de) 2003-02-13
AU4573197A (en) 1998-05-22
WO1998019126A1 (fr) 1998-05-07
JPH10132480A (ja) 1998-05-22
MY118256A (en) 2004-09-30
ES2190544T3 (es) 2003-08-01
PT936432E (pt) 2003-03-31
EP0936432A4 (en) 2000-01-19
KR20000034784A (ko) 2000-06-26

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