JPH0674606A - Laminated heat exchanger - Google Patents
Laminated heat exchangerInfo
- Publication number
- JPH0674606A JPH0674606A JP4228227A JP22822792A JPH0674606A JP H0674606 A JPH0674606 A JP H0674606A JP 4228227 A JP4228227 A JP 4228227A JP 22822792 A JP22822792 A JP 22822792A JP H0674606 A JPH0674606 A JP H0674606A
- Authority
- JP
- Japan
- Prior art keywords
- flat tube
- shaped
- flow
- refrigerant
- heat exchanger
- 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.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/03—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 plate-like or laminated conduits
- F28D1/0308—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other
- F28D1/0325—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another
- F28D1/0333—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another the plates having integrated connecting members
- F28D1/0341—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another the plates having integrated connecting members with U-flow or serpentine-flow inside the conduits
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、空調機用の積層型熱交
換器に関する。FIELD OF THE INVENTION The present invention relates to a laminated heat exchanger for an air conditioner.
【０００２】[0002]
【従来の技術】図７，図８に基づいて従来の積層型熱交
換器を説明する。図７には従来の積層型熱交換器の側
面、図８には右側部の拡大断面を示してある。2. Description of the Related Art A conventional laminated heat exchanger will be described with reference to FIGS. FIG. 7 shows a side surface of the conventional laminated heat exchanger, and FIG. 8 shows an enlarged cross section of the right side portion.
【０００３】図７，図８において、１は偏平チューブで
あり偏平チューブ１はプレス成形された２枚のプレート
２が突合わされて形成されている。偏平チューブ１の一
端部（図中上端部）には出入口タンク部３が形成されて
いる。In FIGS. 7 and 8, 1 is a flat tube, and the flat tube 1 is formed by abutting two press-formed plates 2. An inlet / outlet tank portion 3 is formed at one end portion (upper end portion in the figure) of the flat tube 1.
【０００４】偏平チューブ１とコルゲートフィン４が交
互に積層され、出入口タンク部３が連結されて積層型熱
交換器（エバポレータ）５が構成されている。The flat tubes 1 and the corrugated fins 4 are alternately laminated, and the inlet / outlet tank portion 3 is connected to form a laminated heat exchanger (evaporator) 5.
【０００５】両端に位置する偏平チューブ１ａの外方側
はエンドプレート６となり、出入口タンク部３における
エンドプレート６には流通孔７が設けられている。一方
の流通孔７は流体としての冷媒の導入配管８に連結さ
れ、他方の流通孔７は冷媒の排出配管９に連結されてい
る。The outer sides of the flat tubes 1a located at both ends serve as end plates 6, and the end plates 6 in the inlet / outlet tank section 3 are provided with flow holes 7. One of the circulation holes 7 is connected to a refrigerant introduction pipe 8 as a fluid, and the other circulation hole 7 is connected to a refrigerant discharge pipe 9.
【０００６】導入配管８及び排出配管９はサイドプレー
ト１０で固定され、サイドプレート１０とエンドプレー
ト６の間にはコルゲートフィン４が設けられている。The introduction pipe 8 and the discharge pipe 9 are fixed by a side plate 10, and a corrugated fin 4 is provided between the side plate 10 and the end plate 6.
【０００７】出入口タンク部３は、偏平チューブ１の板
幅方向に入口部１１と出口部１２とに仕切られ、エバポ
レータ５を構成した際隣接する出入口タンク部３は入口
部１１同士及び出口部１２同士が連通孔１３によって連
通されている。The inlet / outlet tank portion 3 is partitioned into an inlet portion 11 and an outlet portion 12 in the plate width direction of the flat tube 1, and when the evaporator 5 is constructed, the adjacent inlet / outlet tank portions 3 are in the inlet portions 11 and the outlet portion 12. The communication holes 13 communicate with each other.
【０００８】図９，図１０に基づいて偏平チューブ１を
説明する。図９には偏平チューブ１を構成するプレート
２の正面、図１０には図９中のＸ−Ｘ線矢視を示してあ
る。The flat tube 1 will be described with reference to FIGS. 9 and 10. FIG. 9 shows the front surface of the plate 2 constituting the flat tube 1, and FIG. 10 shows a view taken along the line XX in FIG.
【０００９】プレート２の上端部には出入口タンク部３
を形成するための膨出部１４が設けられ、プレート２の
内空部は中央部の上下方向に延びる仕切壁１５によって
２つの室１６，１７に仕切られている。仕切壁１５は下
端部が欠如され、プレート２の下端は冷媒をＵターンさ
せるＵターン部１８となっている。２枚のプレート２を
突き合わせることで、仕切壁１５によって、出入口タン
ク部３が入口部１１と出口部１２とに仕切られると共
に、入口部１１に連続する室１６と出口部１２に連続す
る室１７とに仕切られる。更に、室１６と室１７とはＵ
ターン部１８で連通され、室１６，１７及びＵターン部
１８で流体通路が形成されている。An inlet / outlet tank section 3 is provided at the upper end of the plate 2.
A bulging portion 14 for forming a space is provided, and the inner space of the plate 2 is partitioned into two chambers 16 and 17 by a partition wall 15 that extends vertically in the central portion. The partition wall 15 lacks the lower end portion, and the lower end of the plate 2 is a U-turn portion 18 that makes a U-turn of the refrigerant. By abutting the two plates 2, the partition wall 15 partitions the inlet / outlet tank part 3 into an inlet part 11 and an outlet part 12, and a chamber continuous with the inlet part 11 and a chamber continuous with the outlet part 12. Divided into 17. Further, the chamber 16 and the chamber 17 are U
The turn portion 18 communicates with each other, and the chambers 16 and 17 and the U-turn portion 18 form a fluid passage.
【００１０】室１６，１７には多数のリブ１９が突設さ
れ、室１６，１７内が迷路状に細分化されている。Ｕタ
ーン部１８には案内リブ２０が突設され、冷媒は案内リ
ブ２０によって室１６から室１７への流れ（Ｕターン）
が案内される。A large number of ribs 19 project from the chambers 16 and 17, and the insides of the chambers 16 and 17 are subdivided into a labyrinth. A guide rib 20 is provided on the U-turn portion 18 so that the refrigerant flows from the chamber 16 to the chamber 17 by the guide rib 20 (U-turn).
Will be guided.
【００１１】図１１に基づいて上述したエバポレータ５
における冷媒の流れを説明する。図１１には冷媒の流れ
状況を示してある。The evaporator 5 described above with reference to FIG.
The flow of the refrigerant will be described. FIG. 11 shows the flow state of the refrigerant.
【００１２】エバポレータ５は３つの群２１，２２，２
３に大別され、導入配管８及び排出配管９が接続される
群２１，２３における入口部１１及び出口部１２の配置
が同一となり、群２２における入口部１１及び出口部１
２の配置が逆になっている。群２１と群２２の間及び群
２２と群２３の間で対向する出入口タンク部３は、群２
１の出口部１２と群２２の入口部１１が連通し、群２２
の出口部１２と群２３の入口部１１が連通している。そ
して、群２１の入口部１１はエンドプレート６の流通孔
７により導入配管８につながれ、群２３の出口部１２は
エンドプレート６の流通孔７により排出配管９につなが
れている。The evaporator 5 comprises three groups 21, 22, 2
The groups 21 and 23 to which the introduction pipe 8 and the discharge pipe 9 are connected have the same arrangement of the inlet portion 11 and the outlet portion 12, and the inlet portion 11 and the outlet portion 1 in the group 22 are the same.
The arrangement of 2 is reversed. The inlet / outlet tank portions 3 facing each other between the groups 21 and 22 and between the groups 22 and 23 are
The outlet 12 of 1 and the inlet 11 of the group 22 communicate with each other,
The outlet 12 of the group and the inlet 11 of the group 23 communicate with each other. The inlet portion 11 of the group 21 is connected to the introduction pipe 8 by the flow hole 7 of the end plate 6, and the outlet portion 12 of the group 23 is connected to the discharge pipe 9 by the flow hole 7 of the end plate 6.
【００１３】導入配管８からエバポレータ５に導入され
た冷媒３１は、群２１の入口部１１から室１６を通って
Ｕターン部１８に送られ、Ｕターン部１８でＵターンさ
れて室１７を通って出口部１２に送られる。群２１の出
口部１２に送られた冷媒３１は、群２２の入口部１１に
送られて群２１と同様な流れで群２３に送られ、群２３
の流体通路（室１６，１７，Ｕターン部１８）を通って
排出配管９から排出される。The refrigerant 31 introduced into the evaporator 5 from the introduction pipe 8 is sent from the inlet portion 11 of the group 21 through the chamber 16 to the U-turn portion 18, is U-turned in the U-turn portion 18 and passes through the chamber 17. Sent to the outlet section 12. The refrigerant 31 sent to the outlet 12 of the group 21 is sent to the inlet 11 of the group 22 and sent to the group 23 in the same flow as the group 21,
Is discharged from the discharge pipe 9 through the fluid passage (chambers 16, 17, U-turn portion 18).
【００１４】この間、コルゲートフィン４の間に空気３
２が送られ、冷媒３１の蒸発潜熱を利用して空気３２が
冷却される。During this time, air 3 is caught between the corrugated fins 4.
2 is sent and the air 32 is cooled using the latent heat of vaporization of the refrigerant 31.
【００１５】[0015]
【発明が解決しようとする課題】上述したエバポレータ
５では、偏平チューブ１のプレート２の内側の室１６，
１７に多数のリブ１９を設けて冷媒の伝熱面積を拡大さ
せているが、流路が迷路状になって冷媒がスムーズに流
れない虞があった。また、Ｕターン部１８では案内リブ
２０によって冷媒のＵターンが案内されているが、Ｕタ
ーン部１８では遠心力により気液二相の冷媒が分離し、
流れ方向に対して気体と液体を均等に分配できず、熱交
換効率が低下する虞があった。In the evaporator 5 described above, the chamber 16 inside the plate 2 of the flat tube 1,
Although a large number of ribs 19 are provided on 17 to increase the heat transfer area of the refrigerant, there is a risk that the flow path becomes a labyrinth and the refrigerant does not flow smoothly. Further, the U-turn of the refrigerant is guided by the guide rib 20 in the U-turn portion 18, but the U-turn portion 18 separates the gas-liquid two-phase refrigerant by centrifugal force,
The gas and the liquid cannot be evenly distributed in the flow direction, which may reduce the heat exchange efficiency.
【００１６】[0016]
【課題を解決するための手段】上記課題を解決するため
の本発明の構成は、プレス成形された２枚のプレートを
突合わせて偏平チューブとし、該偏平チューブの一端部
に出入口タンク部を形成すると共に、入口タンク部から
前記２枚のプレート間に流入した流体を前記偏平チュー
ブの他端部でＵターンさせて出口タンク部に導く流体通
路を該偏平チューブに形成し、該偏平チューブとコルゲ
ートフィンとを交互に積層してなる積層型熱交換器にお
いて、前記偏平チューブの前記出入口タンク部と前記他
端部の間における前記流体通路の直線部分に長さ方向に
沿う流路を複数分離して区画形成する波形インナフィン
を挿入し、流体をＵターンさせる前記流体通路のＵター
ン部にＵ字状流路を複数分離して区画形成したことを特
徴とする。The structure of the present invention for solving the above-mentioned problems is a flat tube formed by abutting two press-formed plates, and an inlet / outlet tank portion is formed at one end of the flat tube. In addition, the flat tube is formed with a fluid passage for making a U-turn at the other end of the flat tube to guide the fluid flowing between the two plates from the inlet tank section to the outlet tank section. In a laminated heat exchanger in which fins are alternately laminated, a plurality of flow passages along the length direction are separated in a straight line portion of the fluid passage between the inlet / outlet tank portion of the flat tube and the other end portion. A corrugated inner fin for partitioning is inserted, and a plurality of U-shaped flow paths are separated and partitioned at the U-turn portion of the fluid passage for making a U-turn of the fluid.
【００１７】またＵ字状流路は、２枚のプレートの突合
わせ面に複数のＵ字状ビードをプレス成形して形成され
ていることを特徴とする。Further, the U-shaped flow path is characterized in that a plurality of U-shaped beads are press-molded on the abutting surfaces of the two plates.
【００１８】またＵ字状流路は、Ｕ字状の流路を複数分
離して区画形成するＵ字状波形インナフィンをＵターン
部に挿入して形成されていることを特徴とする。Further, the U-shaped flow passage is characterized in that a U-shaped corrugated inner fin for separating and forming a plurality of U-shaped flow passages is formed in the U-turn portion.
【００１９】また流体通路は、波形インナフィンとＵ字
状波形インナフィンを一体に形成した一つのインナフィ
ンを偏平チューブに挿入して形成されていることを特徴
とする。Further, the fluid passage is characterized in that one inner fin in which the corrugated inner fin and the U-shaped corrugated inner fin are integrally formed is inserted into the flat tube.
【００２０】[0020]
【作用】偏平チューブは、波形インナフィンによって直
線部分の流路が複数分離して形成され、流体の流れがス
ムーズになり流路面積が増大される。また、Ｕターン部
にＵ字状流路を複数分離して区画形成したので、流体の
流れに澱みが生じることがなくなると共に、遠心力に伴
なう気液二相流冷媒の分離が区画された一つのＵ字状流
路内だけとなり、気液分配量の分布が小さくなる。In the flat tube, a plurality of linear flow paths are formed by corrugated inner fins so that the flow of fluid becomes smooth and the flow path area is increased. Further, since a plurality of U-shaped flow paths are separated and formed in the U-turn portion, stagnation does not occur in the fluid flow, and separation of the gas-liquid two-phase refrigerant due to centrifugal force is separated. Since there is only one U-shaped flow path, the distribution of gas-liquid distribution becomes small.
【００２１】また、Ｕターン部のＵ字状流路をＵ字状波
形インナフィンを挿入することにより区画形成したの
で、Ｕ字状流路を細かく区画することができ、流体通路
の全体で流体の流れをきめ細かく制御することができ
る。Further, since the U-shaped channel of the U-turn portion is partitioned and formed by inserting the U-shaped corrugated inner fins, the U-shaped channel can be finely partitioned, and the entire fluid passage is filled with fluid. The flow can be finely controlled.
【００２２】また、一つのインナフィンで直線部分とＵ
ターン部の流路を連続して区画形成したので、流体通路
における冷媒の流路を連続させて流体の流れを均一にす
ることができる。In addition, one inner fin and a straight line portion and U
Since the flow passage of the turn portion is continuously formed by partitioning, the flow passage of the refrigerant in the fluid passage can be made continuous to make the flow of the fluid uniform.
【００２３】[0023]
【実施例】図１には本発明の一実施例に係る積層型熱交
換器における偏平チューブの分解斜視、図２には偏平チ
ューブを構成するプレートの接合面を表わす正面、図３
には図２中の矢印III 部の詳細状態、図４には偏平チュ
ーブの横断面を示してある。FIG. 1 is an exploded perspective view of a flat tube in a laminated heat exchanger according to an embodiment of the present invention, FIG. 2 is a front view showing a joint surface of plates constituting the flat tube, and FIG.
2 shows a detailed state of an arrow III portion in FIG. 2, and FIG. 4 shows a cross section of the flat tube.
【００２４】偏平チューブ４１はプレス成形された２枚
のプレート４２が突合わされて形成されている。偏平チ
ューブ４１の一端部（図２中上端部）には出入口タンク
部４３が形成されている。The flat tube 41 is formed by abutting two press-formed plates 42. An inlet / outlet tank portion 43 is formed at one end portion (upper end portion in FIG. 2) of the flat tube 41.
【００２５】偏平チューブ４１と図７，図８で示したコ
ルゲートフィン４が交互に積層され、出入口タンク部４
３が連結されて積層型熱交換器（エバポレータ）が構成
される。The flat tubes 41 and the corrugated fins 4 shown in FIGS. 7 and 8 are alternately laminated to form the inlet / outlet tank section 4
3 are connected to form a laminated heat exchanger (evaporator).
【００２６】出入口タンク部４３は、偏平チューブ４１
の板幅方向に入口部４４と出口部４５とに仕切られ、エ
バポレータを構成した際、隣接する出入口タンク部４３
は入口部４４同士及び出口部４５同士が連通孔４６によ
って連通されている。The inlet / outlet tank portion 43 is a flat tube 41.
Is divided into an inlet portion 44 and an outlet portion 45 in the plate width direction, and when the evaporator is configured, the adjacent inlet / outlet tank portion 43
The inlet portions 44 are communicated with each other and the outlet portions 45 are communicated with each other through a communication hole 46.
【００２７】プレート４２の内空部は中央部の上下方向
に延びる仕切壁４７によって２つの室４８，４９に仕切
られている。仕切壁４７は下端部が欠如され、プレート
４２の下端は流体としての冷媒をＵターンさせるＵター
ン部５０となっている。２枚のプレート４２を突き合わ
せることで、仕切壁４７によって、出入口タンク部４３
が入口部４４と出口部４５とに仕切られると共に、入口
部４４に連続する室４８と出口部４５に連続する室４９
とに仕切られる。更に、室４８と室４９とはＵターン部
５０で連通され、室４８，４９及びＵターン部５０で流
体通路５１が形成されている。The inner space of the plate 42 is divided into two chambers 48, 49 by a partition wall 47 extending in the vertical direction at the center. The partition wall 47 lacks the lower end portion, and the lower end of the plate 42 serves as a U-turn portion 50 that makes a U-turn of the refrigerant as a fluid. By abutting the two plates 42, the partition wall 47 allows the entrance / exit tank part 43
Is partitioned into an inlet portion 44 and an outlet portion 45, and a chamber 48 continuous with the inlet portion 44 and a chamber 49 continuous with the outlet portion 45.
It is divided into and. Further, the chamber 48 and the chamber 49 are communicated with each other by the U-turn portion 50, and the fluid passage 51 is formed by the chambers 48, 49 and the U-turn portion 50.
【００２８】流体通路５１の室４８，４９の部分（直線
部分）には波形インナフィン５２，５３が挿入されてい
る。図４に示すように、波形インナフィン５２，５３に
は、室４８，４９の長さ方向（上下方向）に沿う流路５
４，５５が複数分離して区画形成されるように、長さ方
向に沿った波形５２ａ，５３ａが複数形成されている。Corrugated inner fins 52 and 53 are inserted in the chambers 48 and 49 of the fluid passage 51 (straight portions). As shown in FIG. 4, in the corrugated inner fins 52 and 53, the flow path 5 along the length direction (vertical direction) of the chambers 48 and 49 is provided.
A plurality of corrugations 52a and 53a are formed along the length direction so that a plurality of sections 4 and 55 are partitioned and formed.
【００２９】流体通路５１のＵターン部５０の部分に
は、冷媒のＵターンを案内するためのＵ字状流路５６が
複数分離して区画形成されている。Ｕ字状流路５６はプ
レート４２の突合わせ面にプレス成形された複数のＵ字
状ビード５７によって形成され、Ｕ字状流路５６はプレ
ート４２の形状に沿ったＵ字形となっている。In the U-turn portion 50 of the fluid passage 51, a plurality of U-shaped flow paths 56 for guiding the U-turn of the refrigerant are divided and formed. The U-shaped channel 56 is formed by a plurality of U-shaped beads 57 press-molded on the abutting surface of the plate 42, and the U-shaped channel 56 has a U-shape that follows the shape of the plate 42.
【００３０】室４８，４９間で冷媒が流れる場合、偏平
チューブ４１の幅方向外側の流路５４，５５を流れる冷
媒は、Ｕターン部５０の外側のＵ字状流路５６を流れ
る。また、偏平チューブ４１の幅方向内側の流路５４，
５５を流れる冷媒は、Ｕターン部５０の内側のＵ字状流
路５６を流れる。つまり、偏平チューブ４１内の冷媒
は、内側から内側、外側から外側を通って流体通路５１
を流れる。When the refrigerant flows between the chambers 48 and 49, the refrigerant flowing in the widthwise outer flow passages 54 and 55 of the flat tube 41 flows in the U-shaped flow passage 56 outside the U-turn portion 50. In addition, the flow path 54 on the inner side in the width direction of the flat tube 41,
The refrigerant flowing through 55 flows through the U-shaped flow path 56 inside the U-turn portion 50. That is, the refrigerant in the flat tube 41 passes through the fluid passage 51 from the inside to the inside and from the outside to the outside.
Flowing through.
【００３１】上述した偏平チューブ４１では、入口部４
４から流入した流体としての冷媒は、波形インナフィン
５２で区画された流路５４を通ってＵターン部５０に導
かれ、Ｕ字状ビード５７で区画されたＵ字状流路５６で
Ｕターンされ、波形インナフィン５３で区画された流路
５５を通って出口部４５まで流れる。この偏平チューブ
４１とコルゲートフィンとを交互に積層したエバポレー
タ全体における冷媒及び空気の流れの一例は、図１１で
示した状況と同一である。In the flat tube 41 described above, the inlet portion 4
Refrigerant as a fluid flowing in from No. 4 is guided to the U-turn portion 50 through the flow path 54 partitioned by the corrugated inner fin 52, and is U-turned by the U-shaped flow path 56 partitioned by the U-shaped bead 57. , Through the flow passage 55 defined by the corrugated inner fin 53 to the outlet portion 45. An example of the flow of the refrigerant and the air in the entire evaporator in which the flat tubes 41 and the corrugated fins are alternately laminated is the same as the situation shown in FIG. 11.
【００３２】偏平チューブ４１内を流れる冷媒は、区画
された流路５４，５５及びＵ字状流路５６を流れるの
で、流体通路５１の内側から内側、外側から外側を冷媒
が流れ、Ｕターン部５０での遠心力に伴なう気液二相流
冷媒の分離がＵ字状流路５６内だけとなり、二相流冷媒
の気液それぞれの分配量の分布が小さくなる。また、Ｕ
ターン部５０のＵ字状流路５６はプレート４２の形状に
沿ったＵ字形となっているので、冷媒の流れに澱みが生
じることがなくなる。Since the refrigerant flowing in the flat tube 41 flows through the divided flow paths 54 and 55 and the U-shaped flow path 56, the refrigerant flows from the inside to the inside of the fluid passage 51 and from the outside to the outside, and the U-turn portion. The separation of the gas-liquid two-phase flow refrigerant due to the centrifugal force at 50 occurs only in the U-shaped flow path 56, and the distribution of the distribution amount of each gas-liquid of the two-phase flow refrigerant becomes small. Also, U
Since the U-shaped flow path 56 of the turn portion 50 has a U-shape conforming to the shape of the plate 42, stagnation does not occur in the refrigerant flow.
【００３３】このため、冷媒の気液分配量の分布が小さ
くなって偏りによる熱効率の低下が生じにくくなると共
に、冷媒の流れに澱みが生じて熱交換量が不均一になる
ことがなくなる。For this reason, the distribution of the gas-liquid distribution amount of the refrigerant is reduced, and the thermal efficiency is less likely to decrease due to the deviation, and the flow of the refrigerant is prevented from becoming stagnation and the heat exchange amount is not nonuniform.
【００３４】図３に示すように、プレート４２の接合縁
４２ａ及び仕切壁４７のＵターン部５０側には、突起６
１がプレス成形されている。突起６１により波形インナ
フィン５２，５３の室４８，４９内での位置決めが行な
われ、Ｕ字状流路５６（Ｕ字状ビード５７）の上端位置
に対する波形インナフィン５２，５３の下端縁５２ｂ，
５３ｂの位置が規制される。As shown in FIG. 3, the projection 6 is formed on the joint edge 42a of the plate 42 and the U-turn portion 50 side of the partition wall 47.
1 is press-molded. Positioning of the corrugated inner fins 52, 53 in the chambers 48, 49 is performed by the protrusion 61, and the lower end edges 52b of the corrugated inner fins 52, 53 with respect to the upper end position of the U-shaped flow path 56 (U-shaped bead 57),
The position of 53b is restricted.
【００３５】Ｕ字状流路５６の上端位置と波形インナフ
ィン５２，５３の下端縁５２ｂ，５３ｂとの隙間Ｓは
０．５mm乃至５mmに設定されている。The gap S between the upper end position of the U-shaped channel 56 and the lower end edges 52b and 53b of the corrugated inner fins 52 and 53 is set to 0.5 mm to 5 mm.
【００３６】この隙間Ｓが０．５mm未満の場合、波形イ
ンナフィン５２，５３で形成された流路５４，５５のピ
ッチとＵ字状流路５６のピッチが異なるため、Ｕ字状流
路５６を形成するＵ字状ビード５７と合致する流路５
４，５５を通る冷媒が流れにくくなってしまう。When the gap S is less than 0.5 mm, the pitch of the flow passages 54 and 55 formed by the corrugated inner fins 52 and 53 is different from the pitch of the U-shaped flow passage 56, so that the U-shaped flow passage 56 is formed. Flow path 5 that matches the U-shaped bead 57 to be formed
It becomes difficult for the refrigerant passing through 4, 55 to flow.
【００３７】また、隙間Ｓが５mmを越えると、プレート
４２をろう付けして接合した際に、末ろう付け部が大き
くなって耐圧強度が不足してしまう。If the gap S exceeds 5 mm, when the plate 42 is brazed and joined, the end brazing portion becomes large and the pressure resistance becomes insufficient.
【００３８】図５，図６に基づいて偏平チューブの他の
例を説明する。図５にはＵ字状波形インナフィンを用い
た偏平チューブの分解斜視、図６には一体のインナフィ
ンを用いた偏平チューブの分解斜視を示してある。Another example of the flat tube will be described with reference to FIGS. FIG. 5 shows an exploded perspective view of a flat tube using a U-shaped corrugated inner fin, and FIG. 6 shows an exploded perspective view of a flat tube using an integral inner fin.
【００３９】図５に示すように、Ｕターン部５０にはＵ
字状の連続する流路を複数分離して区画形成するために
連続するＵ字形の波形を有するＵ字状波形インナフィン
６２が挿入されている。Ｕ字状波形インナフィン６２が
挿入されることにより、Ｕ字状流路が形成される。Ｕ字
状波形インナフィン６２の波形のピッチと波形インナフ
ィン５２，５３の波形５２ａ，５３ａのピッチは合致し
ている。As shown in FIG. 5, the U-turn section 50 has a U
A U-shaped corrugated inner fin 62 having a continuous U-shaped corrugation is inserted to divide and form a plurality of continuous U-shaped flow paths. By inserting the U-shaped corrugated inner fin 62, a U-shaped flow path is formed. The pitch of the waveform of the U-shaped corrugated inner fin 62 and the pitch of the waveforms 52a and 53a of the corrugated inner fins 52 and 53 match.
【００４０】Ｕターン部５０のＵ字状流路をＵ字状波形
インナフィン６２で形成したことにより、Ｕターン部５
０を含めた流路面積を増大させることができると共に、
Ｕターン部５０のＵ字状流路を室４８，４９での流路５
４，５５と同様に細かく区画することができ、Ｕターン
部５０での二相流冷媒の気液それぞれの分配量の分布が
極めて小さくなる。これにより、流体通路５１での冷媒
の流れをきめ細かく制御することができ、熱伝達性能が
向上する。By forming the U-shaped flow path of the U-turn portion 50 with the U-shaped corrugated inner fins 62, the U-turn portion 5 is formed.
The flow passage area including 0 can be increased, and
The U-shaped flow path of the U-turn part 50 is the flow path 5 in the chambers 48 and 49
As in the case of Nos. 4 and 55, it can be finely divided, and the distribution of the distribution amounts of the gas and liquid of the two-phase flow refrigerant in the U-turn section 50 becomes extremely small. Thereby, the flow of the refrigerant in the fluid passage 51 can be finely controlled, and the heat transfer performance is improved.
【００４１】Ｕ字状波形インナフィン６２では、Ｕ字形
の波形によって連続するＵ字状の流路を区画形成した
が、直線状の波形を複数組合わせてＵ字状の流路を区画
形成するようにしても良い。In the U-shaped corrugated inner fin 62, a continuous U-shaped flow path is defined by a U-shaped waveform, but a plurality of linear waveforms may be combined to form a U-shaped flow path. You can
【００４２】図６に示すように、プレート４２の室４
８，４９及びＵターン部５０には、波形インナフィン５
２，５３とＵ字状波形インナフィン６２を一体に形成し
た一つのインナフィン６３が挿入されている。インナフ
ィン６３が挿入されることにより、流路５４，５５及び
Ｕ字状流路が連続して区画形成される。As shown in FIG. 6, the chamber 4 of the plate 42
The corrugated inner fins 5 are provided on the 8, 49 and U-turn portions 50.
One inner fin 63 in which the Nos. 2, 53 and the U-shaped corrugated inner fin 62 are integrally formed is inserted. By inserting the inner fin 63, the flow paths 54 and 55 and the U-shaped flow path are continuously defined.
【００４３】一つのインナフィン６３で流路５４，５５
及びＵ字状流路を連続して区画することにより、偏平チ
ューブ内での冷媒の流路が連続した状態になり、冷媒の
流れが均一になって熱交換量を均一に保つことができ
る。また、部品点数も少なくなり、コスト低減が図れ
る。The flow paths 54 and 55 are formed by one inner fin 63.
By continuously partitioning the U-shaped flow path, the flow path of the refrigerant in the flat tube becomes continuous, and the flow of the refrigerant becomes uniform, so that the heat exchange amount can be kept uniform. Also, the number of parts is reduced, and the cost can be reduced.
【００４４】インナフィン６３には、波形インナフィン
５２，５３間に仕切壁４７を挿入させる溝部が形成され
ているが、波形インナフィン５２，５３を連続させて仕
切壁４７同士の接合部に挟み込むようにすることで、全
体を一体にした略矩形状の一つのインナフィンとするこ
とができ、成形が容易となる。The inner fin 63 is formed with a groove for inserting the partition wall 47 between the corrugated inner fins 52 and 53, but the corrugated inner fins 52 and 53 are continuously arranged so as to be sandwiched between the joints between the partition walls 47. As a result, the inner fin can be integrally formed into a single substantially rectangular shape, which facilitates molding.
【００４５】上述した偏平チューブでは、波形インナフ
ィン５２，５３によって室４８，４９の長さ方向の流路
５４，５５を分離して形成しているので、冷媒の流れを
スムーズにさせて流路面積を増大させることができる。
また、Ｕターン部５０にＵ字状流路を複数分離して区画
形成したので、冷媒の流れに澱みが生じることがなくな
ると共に、Ｕターン部５０での遠心力に伴なう気液二相
流冷媒の分離が区画されたＵ字状流路内だけとなり、気
液分配量の分布が小さくなる。In the flat tube described above, the flow passages 54 and 55 in the lengthwise direction of the chambers 48 and 49 are formed separately by the corrugated inner fins 52 and 53, so that the flow of the refrigerant is made smooth and the flow passage area is increased. Can be increased.
In addition, since a plurality of U-shaped flow paths are separated and formed in the U-turn portion 50, stagnation does not occur in the flow of the refrigerant, and gas-liquid two-phase due to centrifugal force in the U-turn portion 50 is generated. The separation of the flow refrigerant is only in the partitioned U-shaped flow path, and the distribution of the gas-liquid distribution amount becomes small.
【００４６】また、Ｕ字状波形インナフィン６２を挿入
することによりＵターン部５０のＵ字状流路を区画形成
したので、Ｕ字状流路を細かく区画することができ、流
体通路５１の全体で冷媒の流れをきめ細かく制御するこ
とができる。Further, since the U-shaped channel of the U-turn portion 50 is defined by inserting the U-shaped corrugated inner fin 62, the U-shaped channel can be finely partitioned, and the entire fluid passage 51 is formed. The flow of the refrigerant can be finely controlled by.
【００４７】また、一つのインナフィン６３で室４８，
４９及びＵターン部５０の流体通路５１を連続して区画
形成したので、冷媒の流路が連続し流れを均一にするこ
とができる。In addition, one inner fin 63 is used for the chamber 48,
Since 49 and the fluid passage 51 of the U-turn part 50 are continuously defined and formed, the flow path of the refrigerant is continuous and the flow can be made uniform.
【００４８】[0048]
【発明の効果】本発明の積層型熱交換器は、偏平チュー
ブの直線部分の流路を波形インナフィンにより複数分離
して区画形成すると共に、Ｕターン部にＵ字状流路を複
数分離して区画形成したので、流体の流れをスムーズに
させて流路面積を増大させることができ、Ｕターン部で
の流体の流れに澱みが生じない。また、Ｕターン部での
遠心力に伴なう気液二相流冷媒の分離が区画されたＵ字
状流路内だけとなり、気液分配量の分布が小さくなる。
この結果、流体の澱みによる熱交換量の不均一がなくな
ると共に流体の偏りによる熱効率低下が生じにくくな
る。In the laminated heat exchanger of the present invention, the flow path of the straight portion of the flat tube is divided into a plurality of sections by the corrugated inner fins to form a partition, and the U-turn section is divided into a plurality of U-shaped flow paths. Since the partition is formed, the fluid flow can be made smooth and the flow passage area can be increased, and no stagnation occurs in the fluid flow at the U-turn portion. Further, the separation of the gas-liquid two-phase flow refrigerant due to the centrifugal force in the U-turn section is limited to the U-shaped flow path, and the distribution of the gas-liquid distribution amount becomes small.
As a result, the nonuniformity of the heat exchange amount due to the stagnation of the fluid is eliminated, and the thermal efficiency is less likely to decrease due to the uneven distribution of the fluid.
【００４９】また、Ｕ字状波形インナフィンを挿入する
ことにより偏平チューブのＵターン部のＵ字状流路を区
画形成したので、Ｕ字状流路を細かく区画することがで
き、流体通路の全体で流体の流れを細かく制御すること
ができる。この結果、熱伝達性能を向上させることがで
きる。Further, since the U-shaped flow passage of the U-turn portion of the flat tube is defined by inserting the U-shaped corrugated inner fin, the U-shaped flow passage can be finely divided and the entire fluid passage can be formed. Can finely control the flow of fluid. As a result, the heat transfer performance can be improved.
【００５０】また、一つのインナフィンで偏平チューブ
の直線部及びＵターン部の流体通路を連続して区画形成
したので、流体の流路が連続し流れが均一になる。この
結果、熱交換量を均一に保つことができる。Further, since the fluid passages of the straight portion and the U-turn portion of the flat tube are continuously defined by one inner fin, the fluid passages are continuous and the flow becomes uniform. As a result, the amount of heat exchange can be kept uniform.
【００５１】従って、本発明の積層型熱交換器では、熱
交換効率向上を図ることができる。Therefore, in the laminated heat exchanger of the present invention, the heat exchange efficiency can be improved.
【図１】本発明の一実施例に係る積層型熱交換器におけ
る偏平チューブの分解斜視図。FIG. 1 is an exploded perspective view of a flat tube in a laminated heat exchanger according to an embodiment of the present invention.
【図２】偏平チューブを構成するプレートの接合面を表
わす正面図。FIG. 2 is a front view showing a joint surface of plates constituting the flat tube.
【図３】図２中の矢印III 部の詳細図。FIG. 3 is a detailed view of an arrow III portion in FIG.
【図４】偏平チューブの横断面図。FIG. 4 is a cross-sectional view of the flat tube.
【図５】Ｕ字状波形インナフィンを用いた偏平チューブ
の分解斜視図。FIG. 5 is an exploded perspective view of a flat tube using a U-shaped corrugated inner fin.
【図６】一体のインナフィンを用いた偏平チューブの分
解斜視図。FIG. 6 is an exploded perspective view of a flat tube using integral inner fins.
【図７】従来の積層型熱交換器の側面図。FIG. 7 is a side view of a conventional laminated heat exchanger.
【図８】図７中の右側部の拡大断面図。8 is an enlarged cross-sectional view of the right side portion in FIG.
【図９】偏平チューブを構成するプレートの正面図。FIG. 9 is a front view of a plate forming a flat tube.
【図１０】図９中のＸ−Ｘ線矢視図。FIG. 10 is a view on arrow XX in FIG. 9.
【図１１】積層型熱交換器の冷媒の流れ状況説明図。FIG. 11 is an explanatory diagram of a refrigerant flow state of the laminated heat exchanger.
４１ 偏平チューブ ４２ プレート ４３ 出入口タンク部 ４４ 入口部 ４５ 出口部 ４６ 連通孔 ４７ 仕切壁 ４８，４９ 室 ５０ Ｕターン部 ５１ 流体通路 ５２，５３ 波形インナフィン ５４，５５ 流路 ５６ Ｕ字状流路 ５７ Ｕ字状ビード ６１ 突起 ６２ Ｕ字状波形インナフィン ６３ インナフィン 41 flat tube 42 plate 43 inlet / outlet tank part 44 inlet part 45 outlet part 46 communication hole 47 partition wall 48, 49 chamber 50 U turn part 51 fluid passage 52, 53 corrugated inner fin 54, 55 flow passage 56 U-shaped flow passage 57 U U-shaped bead 61 Protrusion 62 U-shaped corrugated inner fin 63 Inner fin
───────────────────────────────────────────────────── フロントページの続き (72)発明者 五百川 博 愛知県西春日井郡西枇杷島町字旭町３丁目 １番地 三菱重工業株式会社エアコン製作 所内 (72)発明者 川合 秀直 愛知県名古屋市中村区岩塚町字高道１番地 三菱重工業株式会社名古屋研究所内 (72)発明者 松田 憲兒 愛知県名古屋市中村区岩塚町字高道１番地 三菱重工業株式会社名古屋研究所内 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Hiroshi Imokawa 3-chome, Asahi-cho, Nishibiwajima-cho, Nishi-Kasugai-gun, Aichi Prefecture Mitsubishi Heavy Industries, Ltd. Air-conditioner factory (72) Hidenao Kawai Iwatsuka-cho, Nakamura-ku, Nagoya-shi, Aichi No. 1 Highway in Nagoya Research Institute of Mitsubishi Heavy Industries, Ltd. (72) Inventor Kenji Matsuda Iwatsukacho, Nakamura-ku, Aichi Prefecture Nagoya No. 1 Highway Inside Nagoya Research Institute of Mitsubishi Heavy Industries, Ltd.
Claims (4)
わせて偏平チューブとし、該偏平チューブの一端部に出
入口タンク部を形成すると共に、入口タンク部から前記
２枚のプレート間に流入した流体を前記偏平チューブの
他端部でＵターンさせて出口タンク部に導く流体通路を
該偏平チューブに形成し、該偏平チューブとコルゲート
フィンとを交互に積層してなる積層型熱交換器におい
て、前記偏平チューブの前記出入口タンク部と前記他端
部の間における前記流体通路の直線部分に長さ方向に沿
う流路を複数分離して区画形成する波形インナフィンを
挿入し、流体をＵターンさせる前記流体通路のＵターン
部にＵ字状流路を複数分離して区画形成したことを特徴
とする積層型熱交換器。1. A flat tube produced by abutting two press-formed plates together to form an inlet / outlet tank section at one end of the flat tube, and a fluid flowing between the two plates from the inlet tank section. In the laminated heat exchanger, wherein a fluid passage for making a U-turn at the other end of the flat tube and leading to the outlet tank is formed in the flat tube, and the flat tubes and corrugated fins are alternately laminated. A fluid for U-turning the fluid by inserting a corrugated inner fin that divides and forms a plurality of flow passages along the length direction into a straight portion of the fluid passage between the inlet / outlet tank portion of the flat tube and the other end portion. A laminated heat exchanger characterized in that a plurality of U-shaped passages are separated and formed in a U-turn portion of a passage.
のＵ字状ビードをプレス成形して前記偏平チューブの前
記Ｕ字状流路を形成したことを特徴とする請求項１に記
載の積層型熱交換器。2. The U-shaped flow path of the flat tube is formed by press-molding a plurality of U-shaped beads on the abutting surfaces of the two plates. Stacked heat exchanger.
るＵ字状波形インナフィンを前記Ｕターン部に挿入して
前記偏平チューブの前記Ｕ字状流路を形成したことを特
徴とする請求項１に記載の積層型熱交換器。3. A U-shaped corrugated inner fin for partitioning and forming a plurality of U-shaped flow channels is formed in the U-turn portion to form the U-shaped flow channel of the flat tube. The laminated heat exchanger according to claim 1.
インナフィンを一体に形成した一つのインナフィンを前
記偏平チューブに挿入して前記流体通路を形成したこと
を特徴とする請求項３に記載の積層型熱交換器。4. The laminated type according to claim 3, wherein one inner fin integrally formed with the corrugated inner fin and the U-shaped corrugated inner fin is inserted into the flat tube to form the fluid passage. Heat exchanger.
Priority Applications (8)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP22822792A JP3327584B2 (en) | 1992-08-27 | 1992-08-27 | Stacked heat exchanger |
| TW082106689A TW234737B (en) | 1992-08-27 | 1993-08-19 | |
| KR1019930016272A KR0143540B1 (en) | 1992-08-27 | 1993-08-21 | Stacked heat exchanger and method of manufacturing the same |
| AU44815/93A AU670302B2 (en) | 1992-08-27 | 1993-08-24 | Stacked heat exchanger and method of manufacturing the same |
| US08/112,424 US5417280A (en) | 1992-08-27 | 1993-08-25 | Stacked heat exchanger and method of manufacturing the same |
| EP93113576A EP0584806B1 (en) | 1992-08-27 | 1993-08-25 | Stacked heat exchanger and method of manufacturing the same |
| DE69315281T DE69315281T2 (en) | 1992-08-27 | 1993-08-25 | Plate heat exchanger and process for its manufacture |
| CN93116791A CN1072352C (en) | 1992-08-27 | 1993-08-26 | Layered heat exchanger and manufacture of same |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP22822792A JP3327584B2 (en) | 1992-08-27 | 1992-08-27 | Stacked heat exchanger |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0674606A true JPH0674606A (en) | 1994-03-18 |
| JP3327584B2 JP3327584B2 (en) | 2002-09-24 |
Family
ID=16873166
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP22822792A Expired - Fee Related JP3327584B2 (en) | 1992-08-27 | 1992-08-27 | Stacked heat exchanger |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3327584B2 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009103360A (en) * | 2007-10-23 | 2009-05-14 | Tokyo Roki Co Ltd | Plate laminated heat exchanger |
| JP2011220643A (en) * | 2010-04-13 | 2011-11-04 | Tokyo Roki Co Ltd | Oil cooler |
| JP2014088995A (en) * | 2012-10-30 | 2014-05-15 | Calsonic Kansei Corp | Tube for heat exchanger |
-
1992
- 1992-08-27 JP JP22822792A patent/JP3327584B2/en not_active Expired - Fee Related
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009103360A (en) * | 2007-10-23 | 2009-05-14 | Tokyo Roki Co Ltd | Plate laminated heat exchanger |
| JP2011220643A (en) * | 2010-04-13 | 2011-11-04 | Tokyo Roki Co Ltd | Oil cooler |
| JP2014088995A (en) * | 2012-10-30 | 2014-05-15 | Calsonic Kansei Corp | Tube for heat exchanger |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3327584B2 (en) | 2002-09-24 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| A02 | Decision of refusal |
Free format text: JAPANESE INTERMEDIATE CODE: A02 Effective date: 20000718 |
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| LAPS | Cancellation because of no payment of annual fees |