JP5617220B2 - Heat exchanger and cooling system and refrigerator using the same - Google Patents

Heat exchanger and cooling system and refrigerator using the same Download PDF

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JP5617220B2
JP5617220B2 JP2009256736A JP2009256736A JP5617220B2 JP 5617220 B2 JP5617220 B2 JP 5617220B2 JP 2009256736 A JP2009256736 A JP 2009256736A JP 2009256736 A JP2009256736 A JP 2009256736A JP 5617220 B2 JP5617220 B2 JP 5617220B2
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collar
rectangular
long hole
heat exchanger
plate
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JP2011102656A (en
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砂田　正樹
正樹 砂田
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Panasonic Corp
Panasonic Holdings Corp
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Panasonic Corp
Matsushita Electric Industrial Co Ltd
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Priority to CN201410597384.XA priority patent/CN104501471B/en
Priority to CN201080045525.7A priority patent/CN102575911B/en
Priority to PCT/JP2010/006273 priority patent/WO2011058705A1/en
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    • 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
    • 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

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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)

Description

本発明は、家庭用あるいは業務用冷蔵庫、さらにはショーケース等において、冷却器（蒸発器）として用いられる所謂ドッグボーン型フィンアンドチューブ式熱交換器およびそれを用いた冷却システムおよび冷蔵庫に関するものである。   The present invention relates to a so-called dogbone type fin-and-tube heat exchanger used as a cooler (evaporator) in a household or commercial refrigerator, a showcase or the like, a cooling system using the same, and a refrigerator. is there.

近年、例えば家庭用冷蔵庫においては本体の外寸を固定し、庫内容量を大きくする傾向にあり、これに起因して冷却システム関連部品は、年々コンパクト化が要求されている。また、業務用冷蔵庫においては、省エネルギーモデルの発売が本格化し、これに起因して冷却システム関連部品のさらなる高効率化が要求されている。   In recent years, for example, home refrigerators tend to fix the outer dimensions of the main body and increase the internal capacity, and as a result, cooling system-related parts are required to be more compact year by year. In commercial refrigerators, the launch of energy-saving models has begun in earnest, and as a result, higher efficiency of cooling system-related parts is required.

そのような中で、熱交換器もコンパクト化や高効率化の要求が高まっている。   Under such circumstances, there is an increasing demand for compactness and high efficiency of heat exchangers.

一方で、原材料高騰により部品材料の合理化の要求も高まり、熱交換器性能を高めることと併せて、材料の薄肉合理化が求められている。   On the other hand, the demand for rationalization of component materials has increased due to soaring raw materials, and in addition to improving the performance of heat exchangers, there has been a demand for rationalization of thin materials.

その一例として、プレートフィンに加工された、所謂ドッグボーン型の長孔に、サーペンタイン状の冷媒チューブを挿入してなり、且つ、経済的なアルミニウムパイプを用いることが可能で、高効率化要素を備えた、ドックボーン型熱交換器が知られている（例えば、特許文献１及び、特許文献２参照）。   For example, a serpentine refrigerant tube is inserted into a so-called dogbone-shaped long hole processed into a plate fin, and an economical aluminum pipe can be used. There are known dockbone type heat exchangers (see, for example, Patent Document 1 and Patent Document 2).

図１０乃至図１２は、上記特許文献１に記載された従来の熱交換器を示すものである。   10 to 12 show a conventional heat exchanger described in Patent Document 1 described above.

図１３は、上記特許文献２に記載された従来の熱交換器を示すものである。   FIG. 13 shows a conventional heat exchanger described in Patent Document 2.

上記従来の熱交換器１０１の構成は、直管部及び曲管部が連続して所定のピッチで蛇行状に曲げ加工された冷媒チューブ１０２と、長孔１０４を板面に複数設けたプレートフィン１０３を具備し、前記プレートフィン１０３を複数相互に間隔を有して配置し、前記長孔１０４に前記冷媒チューブ１０２を貫通させたもので、前記プレートフィン１０３において、前記長孔１０４の矩形部長手方向の両側に、切り起こし可能なカラー成形部１０４ｂを設けたものである。   The conventional heat exchanger 101 has a configuration in which a straight tube portion and a bent tube portion are continuously bent in a meandering manner at a predetermined pitch and a plate fin provided with a plurality of long holes 104 on a plate surface. 103, a plurality of the plate fins 103 are arranged at intervals, and the refrigerant tube 102 is passed through the long hole 104. In the plate fin 103, the length of the rectangular portion of the long hole 104 is The color molding portions 104b that can be cut and raised are provided on both sides in the hand direction.

以上のように構成された熱交換器１０１について、以下その動作を説明する。   The operation of the heat exchanger 101 configured as described above will be described below.

まず、図１２のプレートフィン１０３を用いた熱交換器１０１については、図１２のプレートフィン１０３の長孔１０４に冷媒チューブ１０２を挿入させると、冷媒チューブ１０２の曲げＲ部が通過するときにカラー成形部１０４ｂは弾性変形し、前記Ｒ部が通過後、弾性で元のフラット状態あるいは、その中間状態に戻る。よって、長孔１０４の矩形部の面積を極力小さくすることができるので、伝熱面積が増大し熱交換器の性能が向上するというものである。   First, regarding the heat exchanger 101 using the plate fin 103 of FIG. 12, when the refrigerant tube 102 is inserted into the long hole 104 of the plate fin 103 of FIG. The molded part 104b is elastically deformed, and after passing through the R part, it is elastic and returns to the original flat state or its intermediate state. Therefore, since the area of the rectangular part of the long hole 104 can be made as small as possible, the heat transfer area is increased and the performance of the heat exchanger is improved.

次に、図１３のプレートフィン１０３を用いた熱交換器１０１については、長孔１０４に矩形部両端カラー１０４ｂと円弧部カラー１０４ａをバーリング加工で一体成形したものである。この場合も長孔１０４の矩形部の面積を極力小さくすることができるので、伝熱面積が増大し熱交換器の性能が向上するというものである。   Next, the heat exchanger 101 using the plate fins 103 of FIG. 13 is obtained by integrally forming a rectangular end collar 104b and an arcuate collar 104a in a long hole 104 by burring. Also in this case, since the area of the rectangular portion of the long hole 104 can be reduced as much as possible, the heat transfer area is increased and the performance of the heat exchanger is improved.

特許第２８１１６０１号公報Japanese Patent No. 2811601 特開２００２−２４３３８２号公報JP 2002-243382 A

しかしながら、従来の特許文献１の構成では、プレートフィン１０３の長孔１０４に冷媒チューブ１０２を挿入させると、冷媒チューブ１０２の曲げＲ部が通過するときにカラー成形部１０４ｂは弾性変形し、前記Ｒ部が通過後、弾性で元のフラット状態あるいは、その中間状態に戻るためには、プレートフィン１０３にある程度の強度が必要となり、一般的には板厚を大きくする必要がある。つまり、従来の特許文献１では、長孔１０４の円弧部にカラー成形部が存在していないのは、プレートフィン１０３の板厚が大きいと考えられ、カラー成形部をあえて付ける必要がないからだと思われる。したがって、プレートフィン１０３の板厚を薄くすることができないので材料コストが増大するという課題を有していた。   However, in the conventional configuration of Patent Document 1, when the refrigerant tube 102 is inserted into the long hole 104 of the plate fin 103, the collar molding portion 104b is elastically deformed when the bent R portion of the refrigerant tube 102 passes, and the R In order to return to the original flat state or the intermediate state with elasticity after the passage, the plate fin 103 needs to have a certain degree of strength, and generally needs to have a large plate thickness. That is, in the conventional patent document 1, the reason why the color molding part does not exist in the arc part of the long hole 104 is that the plate fin 103 is considered to have a large thickness, and it is not necessary to dare to attach the color molding part. Seem. Therefore, since the plate thickness of the plate fin 103 cannot be reduced, there is a problem that the material cost increases.

また、従来の特許文献２の構成では、長孔１０４に矩形部両端カラー１０４ｂと円弧部カラー１０４ａをバーリング加工で一体成形したので、一見、円弧部と矩形部の加工を同時に１回で済ませることができるので金型が安価になるように思えるが、円弧部先端は材料が伸びる加工で、矩形部先端は材料が伸びない加工であり、それらの継ぎ目部分の形状を安定させるには、材料特性及び金型に工夫が必要であり、加工性的には難しくなる。さらに、熱交換器１０１を蒸発器として用いた場合は、円弧部カラー１０４ａと矩形部カラー１０４ｂの継ぎ目部分に水滴が溜まり易くなり、除霜後のウエットスタート時の冷却性能が低下するのはもちろん、着霜目詰まりによる不冷の要因にも成り得るという課題を有していた。   Moreover, in the structure of the conventional patent document 2, since the rectangular portion end collar 104b and the arc portion collar 104a are integrally formed in the elongated hole 104 by burring processing, at first glance, the arc portion and the rectangular portion can be processed once at a time. Although it seems that the mold is cheaper, the tip of the arc part is a process in which the material is stretched, and the tip of the rectangular part is a process in which the material is not stretched. In addition, it is necessary to devise the mold, and it becomes difficult in terms of workability. Furthermore, when the heat exchanger 101 is used as an evaporator, water droplets are likely to accumulate at the joint between the arcuate collar 104a and the rectangular collar 104b, and of course the cooling performance at the time of wet start after defrosting is lowered. In addition, there was a problem that it could be a cause of uncooling due to frost clogging.

本発明は上記従来の課題を解決するもので、ドッグボーン型熱交換器におけるプレートフィンの長孔部の伝熱面積を有効活用する上で、着霜・除霜の信頼性を考慮した高効率且つ経済的な熱交換器とそれを用いた冷却システムを提供することを目的とするものである。   The present invention solves the above-mentioned conventional problems, and in order to effectively utilize the heat transfer area of the long holes of the plate fins in the dog bone type heat exchanger, it is highly efficient considering the reliability of frosting and defrosting. It is another object of the present invention to provide an economical heat exchanger and a cooling system using the heat exchanger.

上記従来の課題を解決するために、本発明の熱交換器は、直管部及び曲管部が連続して所定のピッチで蛇行状に曲げ加工された断面形状が略円形状の冷媒チューブと、矩形部と、前記矩形部の両側短辺に連続して形成された円弧部と、を有し、前記矩形部の幅より前記円弧部の幅が大きく形成された長孔を板面に複数設けたプレートフィンを具備し、
前記プレートフィンを複数相互に間隔を有して配置し、前記長孔に前記冷媒チューブを貫通させた熱交換器であって、
前記プレートフィンにおいて、前記長孔の前記矩形部の長手方向の両側及び前記長孔の前記円弧部に、前記プレートフィン面に対して切り起こしたカラーを設け、前記カラーのうち、前記矩形部に成形した矩形部カラーと、前記直管部と密着固定するための縁を立てて前記長孔の円弧部に成形された円弧部カラーとは、分断されており、前記プレートフィンに形成された前記長孔を前記冷媒チューブの前記曲管部が貫通することにより、前記直管部が前記プレートフィンと密着した構成となるものである。 In order to solve the above-described conventional problems, a heat exchanger according to the present invention includes a refrigerant tube having a substantially circular cross section in which a straight pipe portion and a curved pipe portion are continuously bent in a meandering manner at a predetermined pitch. A rectangular portion and an arc portion formed continuously on the short sides on both sides of the rectangular portion, and a plurality of long holes formed in the plate surface having a larger width of the arc portion than the width of the rectangular portion. With plate fins provided,
A plurality of the plate fins are arranged with a space between each other, and the refrigerant tube is passed through the long hole,
Wherein the plate fins, said arcuate portions in the longitudinal direction of both sides and the long hole of the rectangular portion of the slot, the-collar cut and raised relative to the plate fin surface is provided, of the-collar, the rectangular The rectangular collar formed on the part and the arc part collar formed on the arc part of the elongated hole with an edge for tightly fixing to the straight pipe part are divided and formed on the plate fin. In addition, the straight pipe part is in close contact with the plate fin by the curved pipe part of the refrigerant tube passing through the long hole.

これにより、冷媒チューブを挿入するときに、冷媒チューブのＲ部が長孔を通過する際に、長孔矩形部のカラー成形部と接触することが無くなり、プレートフィンの強度を上げるために板厚を大きくする必要がなくなる。また、長孔の矩形部カラーと円弧部カラーを一体化成形するには、プレートフィンの伸縮性が必要になり、薄肉品では加工が困難となる。よって、カラー成形の加工性も容易になる。さらに、円弧部カラーと矩形部カラーの継ぎ目部分に水滴が溜まり難くなるので、プレートフィンの長孔部の伝熱面積を有効活用できるのはもちろん、着霜目詰まりの回避、除霜後の冷却性能の維持も可能となり、高い信頼性を実現し、高効率且つ経済的な熱交換器およびそれを用いた冷却システムおよび冷蔵庫を提供することができる。   Thus, when the refrigerant tube is inserted, when the R portion of the refrigerant tube passes through the long hole, it does not come into contact with the collar forming portion of the long hole rectangular portion, and the plate thickness is increased in order to increase the strength of the plate fin. There is no need to increase In addition, in order to integrally form the rectangular hole collar and arcuate collar of the long hole, the elasticity of the plate fins is required, and it is difficult to process with a thin product. Therefore, the processability of color molding becomes easy. In addition, water droplets are less likely to accumulate at the joint between the arc and rectangular collars, so the heat transfer area of the long holes of the plate fins can be used effectively, as well as avoiding clogging of frost and cooling after defrosting. Performance can be maintained, and high reliability can be realized, and a highly efficient and economical heat exchanger, a cooling system using the heat exchanger, and a refrigerator can be provided.

本発明の熱交換器およびそれを用いた冷却システムおよび冷蔵庫は、ドッグボーン型熱交換器におけるプレートフィンの長孔部の伝熱面積を有効活用できるのはもちろん、着霜・除霜の信頼性を考慮した高効率且つ経済的な熱交換器およびそれを用いた冷却システムおよび冷蔵庫を提供することができる。   The heat exchanger of the present invention and the cooling system and refrigerator using the heat exchanger can effectively utilize the heat transfer area of the long holes of the plate fins in the dog bone type heat exchanger, as well as the reliability of frosting and defrosting. It is possible to provide a highly efficient and economical heat exchanger in consideration of the above, a cooling system and a refrigerator using the heat exchanger.

本発明の実施の形態１における熱交換器の側面図Side view of heat exchanger in Embodiment 1 of the present invention 同実施の形態１における熱交換器の正面図Front view of heat exchanger in embodiment 1 同実施の形態１におけるプレートフィンの斜視図The perspective view of the plate fin in Embodiment 1 同実施の形態１におけるプレートフィンの断面図Sectional drawing of the plate fin in Embodiment 1 本発明の実施の形態２におけるプレートフィンの斜視図The perspective view of the plate fin in Embodiment 2 of this invention 同実施の形態２におけるプレートフィンの断面図Sectional drawing of the plate fin in Embodiment 2 本発明の実施の形態３における熱交換器のプレートフィン部分拡大斜視図Plate fin part expansion perspective view of the heat exchanger in Embodiment 3 of this invention 同実施の形態３における熱交換器のプレートフィン部分拡大斜視図Plate fin part expansion perspective view of the heat exchanger in Embodiment 3 本発明の実施の形態４における冷却システムの模式図The schematic diagram of the cooling system in Embodiment 4 of this invention 従来の熱交換器の側面図Side view of conventional heat exchanger 同熱交換器の正面図Front view of the heat exchanger 従来のプレートフィンの斜視図A perspective view of a conventional plate fin 従来のプレートフィンの斜視図A perspective view of a conventional plate fin

請求項１に記載の発明は、直管部及び曲管部が連続して所定のピッチで蛇行状に曲げ加工された断面形状が略円形状の冷媒チューブと、矩形部と、前記矩形部の両側短辺に連続して形成された円弧部と、を有し、前記矩形部の幅より前記円弧部の幅が大きく形成された長孔を板面に複数設けたプレートフィンを具備し、
前記プレートフィンを複数相互に間隔を有して配置し、前記長孔に前記冷媒チューブを貫通させた熱交換器であって、
前記プレートフィンにおいて、前記長孔の前記矩形部の長手方向の両側及び前記長孔の前記円弧部に、前記プレートフィン面に対して切り起こしたカラーを設け、前記カラーのうち、前記矩形部に成形した矩形部カラーと、前記直管部と密着固定するための縁を立てて前記長孔の円弧部に成形された円弧部カラーとは、分断されており、前記プレートフィンに形成された前記長孔を前記冷媒チューブの前記曲管部が貫通することにより、前記直管部が前記プレートフィンと密着した構成となるものである。 The invention according to claim 1 is a refrigerant tube having a substantially circular cross-sectional shape in which a straight pipe portion and a curved pipe portion are continuously bent in a meandering manner at a predetermined pitch, a rectangular portion, and the rectangular portion. An arc portion formed continuously on both short sides, and a plate fin provided with a plurality of long holes formed on the plate surface in which the width of the arc portion is larger than the width of the rectangular portion,
A plurality of the plate fins are arranged with a space between each other, and the refrigerant tube is passed through the long hole,
Wherein the plate fins, said arcuate portions in the longitudinal direction of both sides and the long hole of the rectangular portion of the slot, the-collar cut and raised relative to the plate fin surface is provided, of the-collar, the rectangular The rectangular collar formed on the part and the arc part collar formed on the arc part of the elongated hole with an edge for tightly fixing to the straight pipe part are divided and formed on the plate fin. In addition, the straight pipe part is in close contact with the plate fin by the curved pipe part of the refrigerant tube passing through the long hole.

かかる構成とすることにより、冷媒チューブを挿入するときに、冷媒チューブのＲ部が長孔を通過する際に、長孔矩形部のカラー成形部と接触することが無くなり、プレートフィンの強度を上げるために板厚を大きくする必要がなくなる。また、長孔の矩形部カラーと円弧部カラーを一体化成形するには、プレートフィンの伸縮性が必要になり、薄肉品では加工が困難となる。よって、カラー成形の加工性も容易になる。さらに、円弧部カラーと矩形部カラーの継ぎ目部分に水滴が溜まり難くなるので、プレートフィンの長孔部の伝熱面積を有効活用できるのはもちろん、着霜目詰まりの回避、除霜後の冷却性能の維持も可能となり、高い信頼性を実現し、高効率且つ経済的な熱交換器を提供することができる。   With this configuration, when the refrigerant tube is inserted, when the R portion of the refrigerant tube passes through the long hole, it does not come into contact with the color molding portion of the long hole rectangular portion, and the strength of the plate fin is increased. Therefore, it is not necessary to increase the plate thickness. In addition, in order to integrally form the rectangular hole collar and arcuate collar of the long hole, the elasticity of the plate fins is required, and it is difficult to process with a thin product. Therefore, the processability of color molding becomes easy. In addition, water droplets are less likely to accumulate at the joint between the arc and rectangular collars, so the heat transfer area of the long holes of the plate fins can be used effectively, as well as avoiding clogging of frost and cooling after defrosting. Performance can be maintained, and high reliability can be realized, and a highly efficient and economical heat exchanger can be provided.

請求項２に記載の発明は、請求項１に記載の熱交換器において、長孔の矩形部に成形したカラーの高さと、長孔の円弧部に成形したカラーの高さを、同等の高さにするものである。   According to a second aspect of the present invention, in the heat exchanger according to the first aspect, the height of the collar formed in the rectangular portion of the long hole is equal to the height of the collar formed in the arc portion of the long hole. It is what you want.

かかる構成とすることにより、円弧部と矩形部を同時にバーリング加工することが可能なので、バーリング型のパンチ・ダイとプレートフィン素材との摩擦抵抗を、円弧部と矩形部で同等の高さにできる。よって、金型の加工バランスがよくなり、金型寿命が延びる。したがって、安価な熱交換器を提供することができる。   By adopting such a configuration, the arc portion and the rectangular portion can be subjected to burring at the same time, so that the frictional resistance between the burring punch and die and the plate fin material can be made equal in the arc portion and the rectangular portion. . Therefore, the processing balance of the mold is improved, and the mold life is extended. Therefore, an inexpensive heat exchanger can be provided.

請求項３に記載の発明は、請求項１に記載の熱交換器において、長孔の矩形部に成形し
たカラーの高さを、長孔の円弧部に成形したカラーの高さより高くしたものである。 According to a third aspect of the present invention, in the heat exchanger according to the first aspect, the height of the collar formed on the rectangular portion of the long hole is higher than the height of the collar formed on the arc portion of the long hole. is there.

かかる構成とすることにより、長孔矩形部のフィン素材をより有効に活用でき、伝熱面積が増えるので、性能が向上する。また、矩形部のカラー高さを高くすることで、境界層前縁効果と乱流促進効果で、性能が向上する。よって高性能な熱交換器を提供することができる。   By adopting such a configuration, the fin material of the long hole rectangular portion can be used more effectively, and the heat transfer area is increased, so that the performance is improved. Further, by increasing the color height of the rectangular portion, the performance is improved by the boundary layer leading edge effect and the turbulent flow promoting effect. Therefore, a high-performance heat exchanger can be provided.

請求項４に記載の発明は、直管部及び曲管部が連続して所定のピッチで蛇行状に曲げ加工された断面形状が略円形状の冷媒チューブと、矩形部と、前記矩形部の両側短辺に連続して形成された円弧部と、を有し、前記矩形部の幅より前記円弧部の幅が大きく形成された長孔を板面に複数設けたプレートフィンを具備し、
前記プレートフィンを複数相互に間隔を有して配置し、前記長孔に前記冷媒チューブを貫通させた熱交換器であって、
前記長孔の前記矩形部の長手方向及び前記長孔の前記円弧部に切り起こし成形されたカラーを設け、前記カラーのうち、前記矩形部に成形した矩形部カラーと、前記直管部と密着固定するための縁を立てて前記長孔の円弧部に成形された円弧部カラーとは、分断されており、前記プレートフィンに形成された前記長孔を前記冷媒チューブの前記曲管部が貫通することにより、前記直管部が前記プレートフィンと密着した構成となるとともに、前記矩形部カラーを前記冷媒チューブ貫通後に、強制的に曲げ戻して前記プレートフィン面と同等の水平面にしたものである。 The invention according to claim 4 is a refrigerant tube having a substantially circular cross-sectional shape in which a straight pipe portion and a curved pipe portion are continuously bent in a meandering manner at a predetermined pitch, a rectangular portion, and the rectangular portion. An arc portion formed continuously on both short sides, and a plate fin provided with a plurality of long holes formed on the plate surface in which the width of the arc portion is larger than the width of the rectangular portion,
A plurality of the plate fins are arranged with a space between each other, and the refrigerant tube is passed through the long hole,
The longitudinal and molded-collar cut and raised in the arcuate portion of the slot of the rectangular portion of the slot provided, the out of-collar, and a rectangular collar molded on the rectangular portion, the straight tube portion The arc portion collar formed in the arc portion of the long hole with an edge for tightly fixing to the arc is divided, and the long hole formed in the plate fin is divided into the bent tube portion of the refrigerant tube. The straight pipe part is in close contact with the plate fin by penetrating the rectangular pipe, and the rectangular part collar is forcibly bent back after penetrating the refrigerant tube to make it a horizontal plane equivalent to the plate fin surface. It is.

かかる構成とすることにより、蒸発器として使用する場合に除霜時の水滴が明らかに溜まらない構造となり、熱交換器の設置方向を注意する必要が無くなり、除霜水の落下方向、風向に左右されない設計が可能となる。   With this configuration, when used as an evaporator, water drops during defrosting are not clearly collected, so there is no need to pay attention to the installation direction of the heat exchanger, and the defrosting water drop direction and wind direction are affected. Design that is not performed becomes possible.

請求項５に記載の発明は、請求項１から請求項４のいずれか一項に記載の熱交換器において、熱交換器の設置上下方向に対して、長孔長手方向の矩形部カラーの角度は、４５度以下でとしたものである。   According to a fifth aspect of the present invention, in the heat exchanger according to any one of the first to fourth aspects, an angle of the rectangular portion collar in the longitudinal direction of the long hole with respect to the installation vertical direction of the heat exchanger. Is 45 degrees or less.

かかる構成とすることにより、蒸発器として使用する場合に除霜時の水滴が、流れ落ちやすくなるので、水滴がより溜まり難くなり、着霜時に風路閉塞し難くなり、冷却能力の低下が遅くなる。また、着霜目詰まりの回避、除霜後の冷却性能の維持も可能となり、高い信頼性を実現し、高効率且つ経済的な熱交換器を提供することができる。   With this configuration, when used as an evaporator, water drops at the time of defrosting are likely to flow down, making it difficult for water drops to accumulate, making it difficult to block the air path during frost formation, and slowing down the cooling capacity. . In addition, it is possible to avoid clogging of frost and maintain the cooling performance after defrosting, realizing high reliability, and providing a highly efficient and economical heat exchanger.

請求項６に記載の発明は、圧縮機と、凝縮器と、減圧装置と、蒸発器と、前記蒸発器に強制通風させる送風機とを備えている冷却システムにおいて、請求項１から請求項５のいずれか一項に記載した熱交換器を蒸発器として用いた冷却システムである。   The invention according to claim 6 is a cooling system comprising a compressor, a condenser, a decompression device, an evaporator, and a blower for forcibly ventilating the evaporator. It is a cooling system using the heat exchanger as described in any one as an evaporator.

請求項７に記載の発明は、請求項６の冷却システムにより庫内を冷却し除霜手段を備えて蒸発器の除霜を行う冷蔵庫である。   Invention of Claim 7 is a refrigerator which cools the inside of a store | warehouse | chamber by the cooling system of Claim 6, and is equipped with a defrost means and defrosts an evaporator.

かかる構成とすることにより、冷却システムおよび冷蔵庫として、省エネ特性に優れたものとなり、高効率且つ経済的な冷却システムおよび冷蔵庫を提供することができる。   With this configuration, the cooling system and the refrigerator have excellent energy saving characteristics, and a highly efficient and economical cooling system and refrigerator can be provided.

以下、本発明の実施の形態について図面を参照しながら説明する。なお、この実施の形態によって本発明が限定されるものではない。   Hereinafter, embodiments of the present invention will be described with reference to the drawings. Note that the present invention is not limited to the embodiments.

（実施の形態１）
図１は、本発明の実施の形態１における熱交換器の側面図、図２は、同熱交換器の正面図、図３は、プレートフィンの斜視図、図４は、図３のＡ−Ａ線による同プレートフィンの側面からの断面図である。 (Embodiment 1)
1 is a side view of a heat exchanger according to Embodiment 1 of the present invention, FIG. 2 is a front view of the heat exchanger, FIG. 3 is a perspective view of a plate fin, and FIG. It is sectional drawing from the side surface of the same plate fin by A line.

図１、図２、図３及び図４において、熱交換器１は、内部を冷媒が流動する冷媒チューブ２と、所定間隔毎に配置された複数のプレートフィン３を具備している。   1, 2, 3, and 4, the heat exchanger 1 includes a refrigerant tube 2 in which a refrigerant flows and a plurality of plate fins 3 arranged at predetermined intervals.

冷媒チューブ２は、アルミ製あるいはアルミ合金製の一本の管体を、直管部と曲管部が連続し、列（左右）方向Ｘおよび段（上下）方向Ｙにおいて複数となるよう蛇行状に曲げ
加工されたサーペンタインチューブであり、曲管部を形成する接続管を用いることなく一本の冷媒流路を形成している。 The refrigerant tube 2 has a meandering shape in which a single pipe body made of aluminum or an aluminum alloy has a straight pipe portion and a curved pipe portion that are continuous in a row (left and right) direction X and a step (up and down) direction Y. The serpentine tube is bent into a single, and one refrigerant flow path is formed without using a connecting pipe that forms a curved pipe portion.

そして、プレートフィン３に形成された長孔４を冷媒チューブ２の曲管部が貫通することにより、冷媒チューブ２の直管部がプレートフィン３と密着した構成となっている。   And the straight pipe part of the refrigerant | coolant tube 2 becomes the structure which contact | adhered to the plate fin 3 because the curved pipe part of the refrigerant | coolant tube 2 penetrates the long hole 4 formed in the plate fin 3. FIG.

長孔４は、矩形部と円弧部を有し、該矩形部の両側短辺に前記円弧部がそれぞれ連続して形成された長穴状に形成されている。また、円弧部には、冷媒チューブ２の直管部と密着固定するための縁立成形された円弧部カラー４ａが設けられており、矩形部長手方向の両端にも、略垂直に縁立成形された矩形部カラー４ｂが設けられている。   The long hole 4 has a rectangular part and a circular arc part, and is formed in a long hole shape in which the circular arc part is continuously formed on both short sides of the rectangular part. Further, the arc portion is provided with an edge-shaped arc portion collar 4a for tightly fixing to the straight pipe portion of the refrigerant tube 2, and the edge portion is formed substantially vertically at both ends in the longitudinal direction of the rectangular portion. The rectangular portion collar 4b is provided.

以上のように構成された熱交換器１について、以下その動作、作用を説明する。   About the heat exchanger 1 comprised as mentioned above, the operation | movement and an effect | action are demonstrated below.

まず、冷媒チューブ２と複数のプレートフィン３を組立てる際に、冷媒チューブ２の曲管部がプレートフィン３の長孔４に挿入され通過していく。長孔４の矩形部カラー４ｂが略垂直に縁立成形されていることで、冷媒チューブ２の曲管部が、矩形部カラー４ｂと接触することなく通過できる。矩形部カラー４ｂが縁立されていないと、冷媒チューブ２の曲管部が通過するときに矩形部カラー４ｂを押し広げながら通過することになり、プレートフィン３の板厚を大きくするなどして強度を上げておかないと挿入することができない。よって、プレートフィン３の板厚を薄肉化する等の材料合理化が可能となる。   First, when the refrigerant tube 2 and the plurality of plate fins 3 are assembled, the bent tube portion of the refrigerant tube 2 is inserted into the long hole 4 of the plate fin 3 and passes therethrough. Since the rectangular portion collar 4b of the long hole 4 is edged and formed substantially perpendicularly, the bent tube portion of the refrigerant tube 2 can pass through without contacting the rectangular portion collar 4b. If the rectangular portion collar 4b is not erected, it passes through the rectangular portion collar 4b when the bent tube portion of the refrigerant tube 2 passes, and the plate fin 3 is increased in thickness. It cannot be inserted unless the strength is increased. Therefore, material rationalization such as reducing the plate thickness of the plate fin 3 becomes possible.

なお、一般的に、冷媒チューブ２の曲管部は偏平加工され、長孔４の矩形部の巾に挿入できるサイズになっており、冷媒チューブ２と複数のプレートフィン３が組立てられた後、冷媒チューブ２を液圧拡管等により拡径し、複数のプレートフィン２と密着固定される際に、元の直径程度に偏平が戻される。   In general, the bent tube portion of the refrigerant tube 2 is flattened and sized to be inserted into the width of the rectangular portion of the long hole 4. After the refrigerant tube 2 and the plurality of plate fins 3 are assembled, When the diameter of the refrigerant tube 2 is expanded by a hydraulic expansion pipe or the like and is fixed in close contact with the plurality of plate fins 2, the flatness is restored to the original diameter.

さらに、長孔４の矩形部カラー４ｂと円弧部カラー４ａを一体化成形するには、プレートフィンの伸縮性が必要になり、薄肉品では加工が困難なので、矩形部カラー４ｂと円弧部カラー４ａが分断していることで、加工が容易となり、よって同様に、プレートフィン３の板厚を薄肉化する等の材料合理化が可能となる。   Further, in order to integrally mold the rectangular portion collar 4b and the arc portion collar 4a of the long hole 4, it is necessary to have elasticity of the plate fins, and it is difficult to process with a thin product, so the rectangular portion collar 4b and the arc portion collar 4a. Since it is divided, processing becomes easy, and similarly, material rationalization such as reducing the plate thickness of the plate fin 3 becomes possible.

また、矩形部カラー４ｂと円弧部カラー４ａが分断していることで、円弧部カラー４ａと矩形部カラー４ｂの継ぎ目部分に水滴が溜まり難くなる。水滴が溜まると、冷却運転時、水滴を核として霜が成長・肥大化し、隣のプレートフィン３まで到達し、風路を閉塞させる時間が早まることになる。すると冷却能力が低下し冷えなくなる。さらに除霜しても霜が解けきらない可能性もあり、これを繰り返して霜が氷に変化し、熱交換器全体が氷の塊になって完全に冷えない現象も発生する。よって、プレートフィン３の長孔４により消失している伝熱面積を有効活用できるのはもちろん、着霜目詰まりの回避、除霜後の冷却性能の維持も可能となり、高い信頼性を実現し、高効率且つ経済的な熱交換器を提供することができる。   In addition, since the rectangular portion collar 4b and the arc portion collar 4a are divided, it is difficult for water droplets to accumulate at the joint portion between the arc portion collar 4a and the rectangular portion collar 4b. When water droplets accumulate, during cooling operation, frost grows and enlarges with the water droplets as the core, reaches the adjacent plate fin 3 and accelerates the time for closing the air passage. As a result, the cooling capacity is lowered and it cannot be cooled. Furthermore, even if the defrosting is performed, the frost may not be thawed. By repeating this, the frost changes to ice, and the entire heat exchanger becomes a lump of ice and does not completely cool. Therefore, not only can the heat transfer area lost due to the long holes 4 of the plate fins 3 be used effectively, it is possible to avoid clogging of frost and maintain the cooling performance after defrosting, realizing high reliability. A highly efficient and economical heat exchanger can be provided.

また、図３で示す通り、長孔４の矩形部カラー４ｂの高さＨｂと、長孔４の円弧部カラー４ａの高さＨａを、同等の高さにすることで、円弧部カラー４ａと矩形部カラー４ｂを同時にバーリング加工することが容易になる。カラー高さが同じ場合、バーリング型のパンチ・ダイとプレートフィン素材との摩擦抵抗を、円弧部と矩形部で同等の高さにできる。よって、金型の加工バランスがよくなり、金型寿命が延びる。したがって、安価な熱交換器を提供することができる。   Further, as shown in FIG. 3, the height Hb of the rectangular portion collar 4b of the elongated hole 4 and the height Ha of the arc portion collar 4a of the elongated hole 4 are made equal to each other, It becomes easy to burring the rectangular collar 4b at the same time. When the collar height is the same, the frictional resistance between the burring type punch die and the plate fin material can be made equal in the arc portion and the rectangular portion. Therefore, the processing balance of the mold is improved, and the mold life is extended. Therefore, an inexpensive heat exchanger can be provided.

また、図１、図３で示すように、熱交換器１の設置上下方向に対して、長孔４の長手方向の矩形部カラー４ｂの角度θを、４５度以下にすることで、蒸発器として使用する場合
に除霜時の水滴が、流れ落ちやすくなるので、水滴がより溜まり難くなり、着霜時に風路閉塞し難くなり、冷却能力の低下を抑制することができる。また、着霜目詰まりの回避、除霜後の冷却性能の維持も可能となり、高い信頼性を実現し、高効率且つ経済的な熱交換器を提供することができる。 Moreover, as shown in FIGS. 1 and 3, by setting the angle θ of the rectangular portion collar 4 b in the longitudinal direction of the long hole 4 to 45 degrees or less with respect to the installation vertical direction of the heat exchanger 1, the evaporator When used as a water droplet, the water droplets at the time of defrosting are likely to flow down, so that the water droplets are less likely to accumulate, the air passage is not easily blocked at the time of frost formation, and a reduction in cooling capacity can be suppressed. In addition, it is possible to avoid clogging of frost and maintain the cooling performance after defrosting, realizing high reliability, and providing a highly efficient and economical heat exchanger.

（実施の形態２）
図５は、実施の形態２におけるプレートフィンの斜視図、図６は、図５のＢ−Ｂ線による同プレートフィンの側面からの断面図である。なお、先の実施の形態１と同様の構成要件については、同一の符号を付して説明する。 (Embodiment 2)
FIG. 5 is a perspective view of the plate fin in the second embodiment, and FIG. 6 is a cross-sectional view from the side of the plate fin taken along line BB in FIG. The same constituent elements as those in the first embodiment will be described with the same reference numerals.

図５、図６に示すプレートフィン３は、長孔４の矩形部カラー４ｂの高さＨｂを、長孔４の円弧部カラー４ａの高さＨａより高くしたものである。   In the plate fin 3 shown in FIGS. 5 and 6, the height Hb of the rectangular portion collar 4 b of the elongated hole 4 is made higher than the height Ha of the arc portion collar 4 a of the elongated hole 4.

以上のように構成されたプレートフィン３を使った熱交換器１の動作、作用を、以下に説明する。   The operation and action of the heat exchanger 1 using the plate fins 3 configured as described above will be described below.

まず、長孔４の矩形部カラー４ｂの高さＨｂを、長孔４の円弧部カラー４ａの高さＨａより高くしたことで、長孔４を成形する際にプレス切断される矩形部のフィン素材を極限まで有効に活用することができる。よって、伝熱面積が増えるので、性能が向上する。また、材料スクラップの量も削減でき資源を有効に使うことができる。
また、矩形部カラー４ｂの高さＨｂを高くすることで、熱交換器１を通過する空気が矩形部カラー４ｂを通過する際に、境界層前縁効果と乱流促進効果が発生し、性能が向上する。よって高性能な熱交換器を提供することができる。 First, the height Hb of the rectangular portion collar 4b of the long hole 4 is set higher than the height Ha of the arc portion collar 4a of the long hole 4, so that the fin of the rectangular portion that is press-cut when the long hole 4 is formed. The material can be used effectively to the limit. Therefore, since the heat transfer area increases, the performance is improved. In addition, the amount of material scrap can be reduced and resources can be used effectively.
Further, by increasing the height Hb of the rectangular portion collar 4b, when the air passing through the heat exchanger 1 passes through the rectangular portion collar 4b, a boundary layer leading edge effect and a turbulent flow promoting effect are generated. Will improve. Therefore, a high-performance heat exchanger can be provided.

（実施の形態３）
図７、図８は、実施の形態３における熱交換器のプレートフィン部分拡大斜視図である。つまり、直管部及び曲管部が連続して所定のピッチで蛇行状に曲げ加工された冷媒チューブ２と、長孔４を板面に複数設けたプレートフィン３を具備し、プレートフィン３を複数相互に間隔を有して配置し、長孔４に冷媒チューブ２を貫通させた熱交換器１からプレートフィン３の部分を抜き取り拡大し斜視図で示したものである。 (Embodiment 3)
7 and 8 are enlarged perspective views of a plate fin portion of the heat exchanger according to the third embodiment. That is, the straight tube portion and the bent tube portion are continuously provided with a refrigerant tube 2 bent in a meandering manner at a predetermined pitch, and a plate fin 3 having a plurality of long holes 4 provided on the plate surface. A plurality of plate fins 3 are extracted from the heat exchanger 1 that is arranged with a space between each other and the refrigerant tubes 2 are passed through the long holes 4, and is shown in an enlarged perspective view.

なお、先の実施の形態１と同様の構成要件については、同一の符号を付して説明する。   The same constituent elements as those in the first embodiment will be described with the same reference numerals.

図７に示す通り、長孔４の矩形部長手方向両端に切り起こし成形されたカラー４ｂを、冷媒チューブ２貫通後に、強制的に曲げ戻してプレートフィン３の平面と同等の水平面にしたものである。これにより、熱交換器の設置上下方向と矩形部カラー４ｂは略平行すなわちおよそ平行に近い状態までとなり、蒸発器として使用する場合に除霜時の水滴が明らかに溜まらない構造となる。これにより、熱交換器の設置上下方向がフィンの平面に対し平行であれば、斜めに設置しても横に設置しても除霜水が溜まる構図にはならないので、熱交換器の設置方向に注意を払う設計をする必要が無くなり、除霜水の落下方向、風向に左右されない設計が可能となる。   As shown in FIG. 7, the collar 4 b that is cut and raised at both ends in the longitudinal direction of the rectangular portion of the long hole 4 is forcibly bent back after passing through the refrigerant tube 2 to be a horizontal plane equivalent to the plane of the plate fin 3. is there. Thereby, the installation vertical direction of the heat exchanger and the rectangular collar 4b are substantially parallel, that is, approximately parallel to each other, and when used as an evaporator, water drops during defrosting are clearly not accumulated. As a result, if the heat exchanger installation vertical direction is parallel to the plane of the fins, the installation of the defrosting water will not result in the composition of the defrost water being installed obliquely or sideways. Therefore, a design that is not influenced by the defrosting water falling direction and the wind direction is possible.

なお、図８に示す通り、長孔４の矩形部長手方向片端に切り起こし成形されたカラー４ｂを、冷媒チューブ２貫通後に、強制的に曲げ戻してプレートフィン３の平面と同等の水平面にしてもよい。矩形部の両端よりも片端にカラーを成形したほうが、容易に曲げ戻しが可能である。   As shown in FIG. 8, the collar 4 b that is cut and raised at one end in the longitudinal direction of the rectangular portion of the long hole 4 is forcibly bent back after passing through the refrigerant tube 2 to be a horizontal plane equivalent to the plane of the plate fin 3. Also good. It is easier to bend back when the collar is molded at one end than at both ends of the rectangular portion.

（実施の形態４）
図９は、実施の形態４における冷却システムの模式図である。本冷却システムは、圧縮機５と、凝縮器６と、減圧装置７と、蒸発器８と、蒸発器８に強制通風させる送風機９と
を備えている。なお、請求項１から請求項５のいずれか一項に記載した熱交換器を蒸発器８として用いた冷却システムである。 (Embodiment 4)
FIG. 9 is a schematic diagram of a cooling system according to the fourth embodiment. The present cooling system includes a compressor 5, a condenser 6, a decompression device 7, an evaporator 8, and a blower 9 that forcibly ventilates the evaporator 8. A cooling system using the heat exchanger according to any one of claims 1 to 5 as the evaporator 8.

また、前記冷却システムにより庫内を冷却し除霜手段（除霜ヒーター）を備えて蒸発器の除霜を行い前記蒸発器として構成されているため除霜時の水滴が明らかに溜まらない構造となり除霜の効率性と熱交換性を向上できる冷蔵庫である。   In addition, the interior of the refrigerator is cooled by the cooling system and is equipped with a defrosting means (defrosting heater) to defrost the evaporator and is configured as the evaporator so that water droplets at the time of defrosting are not clearly collected. It is a refrigerator that can improve the efficiency and heat exchange of defrosting.

前述の熱交換器はドッグボーン型熱交換器におけるプレートフィンの長孔部の伝熱面積を有効活用できるのはもちろん、着霜・除霜の信頼性を考慮した高効率且つ経済的な効果を有するを持つものであり、本冷却システムおよびこれを用いた冷蔵庫に搭載することにより、省エネ特性に優れたものとなり、高効率且つ経済的な冷却システムおよびこれを用いた冷蔵庫を提供することができる。   The heat exchanger described above can effectively utilize the heat transfer area of the long holes of the plate fins in the dog bone type heat exchanger, and also has a high efficiency and economical effect considering the reliability of frosting and defrosting. By having this cooling system and a refrigerator using the cooling system, the energy-saving characteristics are improved, and a highly efficient and economical cooling system and a refrigerator using the cooling system can be provided. .

本発明にかかる熱交換器とそれを用いた冷却システムは、着霜・除霜の信頼性を考慮したコストパフォーマンスの高いものなので、冷蔵庫、自販機等のように家庭用から産業用に亘る冷凍機器の冷却器、あるいは放熱器として幅広く利用することができるものである。   Since the heat exchanger according to the present invention and the cooling system using the heat exchanger have high cost performance in consideration of the reliability of frosting and defrosting, refrigeration equipment for household use to industrial use such as refrigerators and vending machines. It can be widely used as a cooler or heat radiator.

１ 熱交換器
２ 冷媒チューブ
３ プレートフィン
４ 長孔
４ａ 円弧部カラー
４ｂ 矩形部カラー
５ 圧縮機
６ 凝縮器
７ 減圧装置
８ 蒸発器
９ 送風機
１０ 除霜手段 DESCRIPTION OF SYMBOLS 1 Heat exchanger 2 Refrigerant tube 3 Plate fin 4 Long hole 4a Arc part color | collar 4b Rectangular part color | collar 5 Compressor 6 Condenser 7 Depressurizer 8 Evaporator 9 Blower 10 Defrost means

Claims (7)

直管部及び曲管部が連続して所定のピッチで蛇行状に曲げ加工された断面形状が略円形状の冷媒チューブと、矩形部と、前記矩形部の両側短辺に連続して形成された円弧部と、を有し、前記矩形部の幅より前記円弧部の幅が大きく形成された長孔を板面に複数設けたプレートフィンを具備し、
前記プレートフィンを複数相互に間隔を有して配置し、前記長孔に前記冷媒チューブを貫通させた熱交換器であって、
前記プレートフィンにおいて、前記長孔の前記矩形部の長手方向の両側及び前記長孔の前記円弧部に、前記プレートフィン面に対して切り起こしたカラーを設け、前記カラーのうち、前記矩形部に成形した矩形部カラーと、前記直管部と密着固定するための縁を立てて前記長孔の円弧部に成形された円弧部カラーとは、分断されており、前記プレートフィンに形成された前記長孔を前記冷媒チューブの前記曲管部が貫通することにより、前記直管部が前記プレートフィンと密着した構成となることを特徴とする熱交換器。 The straight pipe part and the curved pipe part are continuously formed in a meandering manner in a meandering manner at a predetermined pitch, and a substantially circular refrigerant tube, a rectangular part, and short sides on both sides of the rectangular part are formed continuously. And a plate fin provided with a plurality of long holes formed on the plate surface, the width of the arc portion being larger than the width of the rectangular portion,
A plurality of the plate fins are arranged with a space between each other, and the refrigerant tube is passed through the long hole,
Wherein the plate fins, said arcuate portions in the longitudinal direction of both sides and the long hole of the rectangular portion of the slot, the-collar cut and raised relative to the plate fin surface is provided, of the-collar, the rectangular The rectangular collar formed on the part and the arc part collar formed on the arc part of the elongated hole with an edge for tightly fixing to the straight pipe part are divided and formed on the plate fin. Further, the straight pipe portion is in close contact with the plate fin by passing through the elongated hole through the curved pipe portion of the refrigerant tube. 長孔の矩形部に成形したカラーの高さと、長孔の円弧部に成形したカラーの高さが、同等の高さであることを特徴とする請求項１に記載の熱交換器。 2. The heat exchanger according to claim 1, wherein the height of the collar formed on the rectangular portion of the long hole is the same as the height of the collar formed on the arc portion of the long hole. 長孔の矩形部に成形したカラーの高さが、長孔の円弧部に成形したカラーの高さより高いことを特徴とする請求項１に記載の熱交換器。 The heat exchanger according to claim 1, wherein the height of the collar formed in the rectangular portion of the long hole is higher than the height of the collar formed in the arc portion of the long hole. 直管部及び曲管部が連続して所定のピッチで蛇行状に曲げ加工された断面形状が略円形状の冷媒チューブと、矩形部と、前記矩形部の両側短辺に連続して形成された円弧部と、を有し、前記矩形部の幅より前記円弧部の幅が大きく形成された長孔を板面に複数設けたプレートフィンを具備し、
前記プレートフィンを複数相互に間隔を有して配置し、前記長孔に前記冷媒チューブを貫通させた熱交換器であって、
前記長孔の前記矩形部の長手方向及び前記長孔の前記円弧部に切り起こし成形されたカラーを設け、前記カラーのうち、前記矩形部に成形した矩形部カラーと、前記直管部と密着固定するための縁を立てて前記長孔の円弧部に成形された円弧部カラーとは、分断されており、前記プレートフィンに形成された前記長孔を前記冷媒チューブの前記曲管部が貫通
することにより、前記直管部が前記プレートフィンと密着した構成となるとともに、前記矩形部カラーを前記冷媒チューブ貫通後に、強制的に曲げ戻して前記プレートフィン面と同等の水平面にしたことを特徴とする熱交換器。 The straight pipe part and the curved pipe part are continuously formed in a meandering manner in a meandering manner at a predetermined pitch, and a substantially circular refrigerant tube, a rectangular part, and short sides on both sides of the rectangular part are formed continuously. And a plate fin provided with a plurality of long holes formed on the plate surface, the width of the arc portion being larger than the width of the rectangular portion,
A plurality of the plate fins are arranged with a space between each other, and the refrigerant tube is passed through the long hole,
The longitudinal and molded-collar cut and raised in the arcuate portion of the slot of the rectangular portion of the slot provided, the out of-collar, and a rectangular collar molded on the rectangular portion, the straight tube portion The arc portion collar formed in the arc portion of the long hole with an edge for tightly fixing to the arc is divided, and the long hole formed in the plate fin is divided into the bent tube portion of the refrigerant tube. The straight pipe portion is in close contact with the plate fin by penetrating the plate portion, and the rectangular collar is forcibly bent back after penetrating the refrigerant tube to be a horizontal plane equivalent to the plate fin surface. A heat exchanger characterized by 熱交換器の設置上下方向に対して、長孔長手方向の矩形部カラーの角度は、４５度以下であることを特徴とする請求項１から請求項４のいずれか一項に記載の熱交換器。 The heat exchange according to any one of claims 1 to 4, wherein the angle of the rectangular collar in the longitudinal direction of the long hole is 45 degrees or less with respect to the installation vertical direction of the heat exchanger. vessel. 圧縮機と、凝縮器と、減圧装置と、蒸発器と、前記蒸発器に強制通風させる送風機とを備えている冷却システムにおいて、請求項１から請求項５のいずれか一項に記載した熱交換器を蒸発器として用いたことを特徴とする冷却システム。 The heat exchange according to any one of claims 1 to 5, wherein the cooling system includes a compressor, a condenser, a pressure reducing device, an evaporator, and a blower for forcibly ventilating the evaporator. A cooling system characterized by using an evaporator as an evaporator. 請求項６の冷却システムにより庫内を冷却し除霜手段を備えて蒸発器の除霜を行う冷蔵庫。 The refrigerator which cools the inside of a store | warehouse | chamber by the cooling system of Claim 6, and is equipped with a defrost means and defrosts an evaporator.
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Publication number Priority date Publication date Assignee Title
DE102011076172A1 (en) * 2011-05-20 2012-11-22 J. Eberspächer GmbH & Co. KG Finned heat exchangers
WO2013088462A1 (en) * 2011-12-12 2013-06-20 三菱電機株式会社 Refrigerator
JP2013224759A (en) * 2012-04-20 2013-10-31 Panasonic Corp Refrigerator
JP2014228235A (en) * 2013-05-24 2014-12-08 ホシザキ電機株式会社 Heat exchanger and refrigerator using heat exchanger for condenser or evaporator
CN105928410A (en) * 2016-06-16 2016-09-07 常州爱迪尔制冷科技有限公司 Fin with turning wing and heat exchanger
CN107869920B (en) * 2016-09-23 2024-06-14 青岛海尔智能技术研发有限公司 Fin type heat exchanger and heat pump system
CN106968774A (en) * 2017-03-24 2017-07-21 南宁八菱科技股份有限公司 A kind of endurance heat exchanger main sheet turnup structure
CN107289807A (en) * 2017-07-06 2017-10-24 贺迈新能源科技（上海）有限公司 Change the device and fin poling heat exchanger of fin poling heat exchanger fin spacing

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE544785A (en) * 1955-02-09
GB1017246A (en) * 1963-09-04 1966-01-19 Ford Motor Co Improvements in or relating to heat exchangers
JPS5136780Y2 (en) * 1971-11-15 1976-09-09
JPH0486491A (en) * 1990-07-30 1992-03-19 Showa Alum Corp Heat exchanger
JP3273894B2 (en) * 1996-09-20 2002-04-15 昭和電工株式会社 Heat exchanger
JPH11333539A (en) * 1998-05-27 1999-12-07 Matsushita Refrig Co Ltd Manufacture of heat exchanger
JP2002243382A (en) * 2001-02-21 2002-08-28 Matsushita Refrig Co Ltd Heat exchanger
JP2002257482A (en) * 2001-03-01 2002-09-11 Harman Kikaku:Kk Heat exchanger
JP3930408B2 (en) * 2002-09-25 2007-06-13 松下冷機株式会社 Manufacturing method of heat exchanger
JP2005121288A (en) * 2003-10-16 2005-05-12 Matsushita Electric Ind Co Ltd Heat exchanger
US7004241B2 (en) * 2003-10-30 2006-02-28 Brazeway, Inc. Flexible tube arrangement-heat exchanger design

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