JPH0674608A - Laminated heat exchanger - Google Patents
Laminated heat exchangerInfo
- Publication number
- JPH0674608A JPH0674608A JP4228229A JP22822992A JPH0674608A JP H0674608 A JPH0674608 A JP H0674608A JP 4228229 A JP4228229 A JP 4228229A JP 22822992 A JP22822992 A JP 22822992A JP H0674608 A JPH0674608 A JP H0674608A
- Authority
- JP
- Japan
- Prior art keywords
- flat tube
- corrugated inner
- refrigerant
- plate
- flow
- 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６，図７に基づいて従来の積層型熱交
換器を説明する。図６には従来の積層型熱交換器の側
面、図７には図６中の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. 6 shows a side surface of a conventional laminated heat exchanger, and FIG. 7 shows an enlarged cross section of the right side portion in FIG.
【０００３】図６，図７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. 6 and 7, reference numeral 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 circulation hole 7 is connected to a refrigerant introduction pipe 8 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８，図９に基づいて偏平チューブ１を説
明する。図８には偏平チューブ１を構成するプレート２
の正面、図９には図８中のIX−IX線矢視を示してある。The flat tube 1 will be described with reference to FIGS. 8 and 9. FIG. 8 shows a plate 2 that constitutes the flat tube 1.
The front view of FIG. 8 and FIG. 9 are taken along line IX-IX 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１０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１０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. 10 shows the flow condition 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。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.
【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、該偏平チューブに入口タ
ンク部及び出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入口タ
ンク部と前記出口タンク部との間における前記流体通路
に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、該波形インナフィンの端縁部の高さを前記プレ
ートの流体通路形成部のプレス成形深さより小さくした
ことを特徴とする。The structure of the present invention for solving the above-mentioned problems is achieved by abutting two press-formed plates into a flat tube, and the flat tube is provided with an inlet tank section and an outlet tank section. A laminated type in which a fluid passage is formed in the flat tube for forming a fluid flowing from the inlet tank portion between the two plates to the outlet tank portion, and the flat tubes and corrugated fins are alternately laminated. In the heat exchanger, a corrugated inner fin that divides and forms a plurality of flow passages is formed in the fluid passage between the inlet tank portion and the outlet tank portion of the flat tube, and the edge portion of the corrugated inner fin is inserted. The height is smaller than the press-forming depth of the fluid passage forming portion of the plate.
【００１７】[0017]
【作用】偏平チューブは、波形インナフィンによって流
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。波形インナフィンの端縁部の
高さは、プレートの流体通路形成部のプレス成形深さよ
り小さいので、２枚のプレートを突き合わせる際に、接
合部に波形インナフィンの端縁部が挾まれたり、波形イ
ンナフィンがずれることがない。In the flat tube, a plurality of channels are formed by corrugated inner fins so that the flow of fluid becomes smooth and the channel area is increased. Since the height of the edge of the corrugated inner fin is smaller than the press forming depth of the fluid passage forming portion of the plate, when the two plates are abutted, the edge of the corrugated inner fin is caught in the joint, Inner fin does not shift.
【００１８】[0018]
【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には積層型熱
交換器の側面、図５には図４中のV-V 線矢視を示してあ
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, FIG. 4 shows a side surface of the laminated heat exchanger, and FIG. 5 shows a view taken along the line VV in FIG.
【００１９】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.
【００２０】図４に示すように、偏平チューブ４１とコ
ルゲートフィン６５が交互に積層され、出入口タンク部
４３が連結されて積層型熱交換器（エバポレータ）６６
が構成される。図中６７は流体としての冷媒の導入配
管、６８は冷媒の排出配管である。As shown in FIG. 4, the flat tubes 41 and the corrugated fins 65 are alternately laminated, and the inlet / outlet tank portion 43 is connected to the laminated heat exchanger (evaporator) 66.
Is configured. In the figure, 67 is a pipe for introducing a refrigerant as a fluid, and 68 is a pipe for discharging the refrigerant.
【００２１】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 is a U-turn portion 50 that makes a U-turn of the refrigerant. By abutting the two plates 42,
The partition wall 47 allows the entrance / exit tank section 43 to move into the entrance section 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. 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.
【００２２】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５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 (straight line portions) of the fluid passage 51. As shown in FIG. 5, 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.
【００２３】室４８，４９には仕切壁４７に沿って平行
に延びプレート４２の外側が溝状となる突壁６７が成形
されている。２枚のプレート４２を突き合わせて接合し
た際、図５に示すように、波形インナフィン５２，５３
は中央部が突壁６７に挾まれた状態で装着される。A projection wall 67 is formed in each of the chambers 48 and 49 so as to extend in parallel with the partition wall 47 and the outside of the plate 42 has a groove shape. When the two plates 42 are butted and joined to each other, as shown in FIG.
Is mounted with the central portion sandwiched by the protruding wall 67.
【００２４】突壁６７によってプレート４２の外側に溝
を形成することにより、偏平チューブ４１の外側面に
は、仕切壁４７によって形成される溝と突壁６７によっ
て形成される溝とが存在することになり、凝縮水の流下
を促進させて露飛びを防止することができる。By forming the groove on the outer side of the plate 42 by the projecting wall 67, the groove formed by the partition wall 47 and the groove formed by the projecting wall 67 exist on the outer surface of the flat tube 41. Therefore, the flow of condensed water can be promoted to prevent dew splashing.
【００２５】図５に示すように、波形インナフィン５
２，５３の端縁部５２ｃ，５３ｃの高さＰはプレート４
２の室４８，４９形成部のプレス成形深さＱより小さく
なっている。これにより、波形インナフィン５２，５３
を室４８，４９に配して２枚のプレート４２を突き合わ
せて接合した際、波形インナフィン５２，５３の端縁部
５２ｃ，５３ｃがプレート４２の接合縁４２ａに挟まれ
ることがない。また、波形インナフィン５２，５３の端
縁部５２ｃ，５３ｃがプレート４２の接合縁４２ａに押
されて波形インナフィン５２，５３がずれることがな
い。As shown in FIG. 5, the corrugated inner fins 5
The height P of the edge portions 52c and 53c of the plates 2 and 53 is the plate 4
It is smaller than the press forming depth Q of the forming portion of the second chambers 48 and 49. Thereby, the corrugated inner fins 52, 53
When the two plates 42 are abutted against each other in the chambers 48, 49 and joined together, the end edge portions 52c, 53c of the corrugated inner fins 52, 53 are not sandwiched by the joining edges 42a of the plate 42. In addition, the edge portions 52c and 53c of the corrugated inner fins 52 and 53 are not pushed by the joint edge 42a of the plate 42, and the corrugated inner fins 52 and 53 are not displaced.
【００２６】従って、この波形インナフィン５２，５３
を用いることにより、２枚のプレート４２で形成される
室４８，４９内の所定位置に確実にしかも容易に波形イ
ンナフィン５２，５３を配設することができる。Therefore, the corrugated inner fins 52, 53
By using, the corrugated inner fins 52, 53 can be reliably and easily arranged at predetermined positions in the chambers 48, 49 formed by the two plates 42.
【００２７】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.
【００２８】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 flow passages 54 and 55 outside the flat tube 41 in the width direction 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.
【００２９】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.
【００３０】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 in the divided flow paths 54 and 55 and the U-shaped flow path 56, the refrigerant flows from the inner side to the inner side and the outer side to the outer side of the fluid passage 51, 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.
【００３１】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 becomes small, and the thermal efficiency is less likely to decrease due to the deviation, and the heat exchange amount does not become nonuniform due to stagnation in the refrigerant flow.
【００３２】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 protrusion 6 is formed on the joint edge 42a of the plate 42 and on 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.
【００３３】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 flow path 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.
【００３４】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 and the pitch of the U-shaped flow passage 56 are different, 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.
【００３５】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.
【００３６】図２に示すように、プレート４２の接合縁
４２ａの４箇所にはかしめ止め部６８が設けられてい
る。２枚のプレート４２で形成される室４８，４９内に
波形インナフィン５２，５３を配し、プレート４２を突
き合わせてかしめ止め部６８により２枚のプレート４２
をかしめることで、波形インナフィン５２，５３が挿入
された偏平チューブ４１が組立品として構成される。As shown in FIG. 2, caulking preventing portions 68 are provided at four positions on the joint edge 42a of the plate 42. The corrugated inner fins 52, 53 are arranged in the chambers 48, 49 formed by the two plates 42, and the plates 42 are butted against each other and the caulking stop portion 68 is used to form the two plates 42.
By caulking, the flat tube 41 with the corrugated inner fins 52, 53 inserted therein is constructed as an assembly.
【００３７】上記構成の偏平チューブ４１を用いたエバ
ポレータ６６の製造方法を説明する。A method of manufacturing the evaporator 66 using the flat tube 41 having the above structure will be described.
【００３８】２枚のプレート４２で形成される室４８，
４９内に波形インナフィン５２，５３を挿入し、プレー
ト４２を突き合わせてかしめ止め部６８により２枚のプ
レート４２を一体にして組立品としての偏平チューブ４
１とする。A chamber 48 formed by two plates 42,
The corrugated inner fins 52 and 53 are inserted into the plate 49, the plates 42 are butted, and the two plates 42 are integrated by the caulking stop portion 68 to form a flat tube 4 as an assembly.
Set to 1.
【００３９】組立品の偏平チューブ４１とコルゲートフ
ィン６５とを交互に多数積層状態に組立て、これを炉中
でろう付け接合してエバポレータ６６を製造する。The flat tubes 41 and corrugated fins 65 of the assembly are alternately assembled in a laminated state, and these are brazed and joined in a furnace to manufacture an evaporator 66.
【００４０】上述した方法で製造したエバポレータ６６
は、予め偏平チューブ４１を組立品として作成している
ので、偏平チューブ４１を高い信頼性で作成することが
でき、冷媒漏れが生じることがない。Evaporator 66 manufactured by the method described above
Since the flat tube 41 is prepared in advance as an assembly, the flat tube 41 can be manufactured with high reliability and no refrigerant leakage occurs.
【００４１】上記構成のエバポレータ６６では、偏平チ
ューブ４１の室４８，４９の長さ方向の流路５４，５５
を波形インナフィン５２，５３によって分離形成してい
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、波形インナフィン５２，５
３の端縁部５２ｃ，５３ｃの高さＰをプレート４２の室
４８，４９形成分部のプレス成形深さＱより小さくした
ので、端縁部５２ｃ，５３ｃがプレート４２の接合縁４
２ａに乗り上げてプレート４２を接合した際に接合縁４
２ａに端縁部５２ｃ，５３ｃが挟まれることがない。ま
た、プレート４２の接合時に端縁部５２ｃ，５３ｃが接
合縁４２ａに押されて波形インナフィン５２，５３がず
れることがない。In the evaporator 66 having the above structure, the flow paths 54 and 55 in the lengthwise direction of the chambers 48 and 49 of the flat tube 41 are provided.
Are formed separately by the corrugated inner fins 52 and 53, the flow of the refrigerant can be made smooth and the flow passage area can be increased. Also, the corrugated inner fins 52, 5
Since the height P of the edge portions 52c and 53c of 3 is smaller than the press forming depth Q of the chamber 48 and 49 forming portion of the plate 42, the edge portions 52c and 53c are joined to the joint edge 4 of the plate 42.
When the plate 42 is joined by riding on 2a, the joining edge 4
The edge portions 52c and 53c are not sandwiched by 2a. In addition, the corrugated inner fins 52, 53 are not displaced by the edge portions 52c, 53c being pushed by the joint edge 42a when the plates 42 are joined.
【００４２】[0042]
【発明の効果】本発明の積層型熱交換器は、偏平チュー
ブ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る。また、波形インナフィンの端
縁部の高さを、偏平チューブを構成するプレートの流体
通路形成部のプレス成形深さより小さくしたので、２枚
のプレートを突き合わせる際に、接合部に波形インナフ
ィンの端縁部が挾まれたり、波形インナフィンがずれる
ことがなく、波形インナフィンを用いた偏平チューブの
組立てが確実に行なえる。In the laminated heat exchanger of the present invention, since the flow passages of the flat tubes are divided and formed by corrugated inner fins, the flow of fluid can be made smooth and the flow passage area can be increased. . Further, since the height of the end edge portion of the corrugated inner fin is set to be smaller than the press forming depth of the fluid passage forming portion of the plate forming the flat tube, when the two plates are butted, the end portion of the corrugated inner fin is joined to the joint portion. The flat tube using the corrugated inner fins can be reliably assembled without the edges being pinched or the corrugated inner fins being displaced.
【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】積層型熱交換器の側面図。FIG. 4 is a side view of the laminated heat exchanger.
【図５】図４中のV-V 線矢視図。5 is a view taken along the line V-V in FIG.
【図６】従来の積層型熱交換器の側面図。FIG. 6 is a side view of a conventional laminated heat exchanger.
【図７】図６中の右側部の拡大断面図。FIG. 7 is an enlarged cross-sectional view of the right side portion in FIG.
【図８】偏平チューブを構成するプレートの正面図。FIG. 8 is a front view of a plate forming a flat tube.
【図９】図８中のIX−IX線矢視図。9 is a view taken along the line IX-IX in FIG.
【図１０】冷媒の流れ状況説明図。FIG. 10 is an explanatory view of the flow state of the refrigerant.
４１ 偏平チューブ ４２ プレート ４２ａ 接合縁 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 ５２ｃ，５３ｃ 端縁部 ５４ 流路 ５６ Ｕ字状流路 ５７ Ｕ字状ビード ６５ コルゲートフィン ６６ エバポレータ ６８ かしめ止め部 41 flat tube 42 plate 42a joining edge 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 fins 52c, 53c end edge portion 54 flow path 56 U-shaped flow path 57 U-shaped bead 65 Corrugated fin 66 Evaporator 68 Caulking stop
───────────────────────────────────────────────────── フロントページの続き (72)発明者 酒井 茂男 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 Shigeo Sakai 1 Takamichi, Iwazuka-cho, Nakamura-ku, Nagoya-shi, Aichi Mitsubishi Heavy Industries, Ltd. Nagoya Research Institute
Claims (1)
わせて偏平チューブとし、該偏平チューブに入口タンク
部及び出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入口タンク
部と前記出口タンク部との間における前記流体通路に流
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、該波形インナフィンの端縁部の高さを前記プレート
の流体通路形成部のプレス成形深さより小さくしたこと
を特徴とする積層型熱交換器。1. A flat tube formed by abutting two press-formed plates together to form an inlet tank section and an outlet tank section, and flowing between the two plates from the inlet tank section. A laminated heat exchanger in which a fluid passage for guiding a fluid to an outlet tank portion is formed in the flat tube, and the flat tubes and corrugated fins are alternately laminated, wherein the inlet tank portion and the outlet tank of the flat tube are A corrugated inner fin that divides and forms a plurality of flow passages into the fluid passage between the above-mentioned section and the partition is formed, and the height of the end edge portion of the corrugated inner fin is made smaller than the press forming depth of the fluid passage forming portion of the plate. A laminated heat exchanger characterized by the above.
Priority Applications (8)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP22822992A JP3281648B2 (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 |
| DE69315281T DE69315281T2 (en) | 1992-08-27 | 1993-08-25 | Plate heat exchanger and process for its manufacture |
| EP93113576A EP0584806B1 (en) | 1992-08-27 | 1993-08-25 | Stacked heat exchanger and method of manufacturing the same |
| 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 |
|---|---|---|---|
| JP22822992A JP3281648B2 (en) | 1992-08-27 | 1992-08-27 | Stacked heat exchanger |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0674608A true JPH0674608A (en) | 1994-03-18 |
| JP3281648B2 JP3281648B2 (en) | 2002-05-13 |
Family
ID=16873196
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP22822992A Expired - Fee Related JP3281648B2 (en) | 1992-08-27 | 1992-08-27 | Stacked heat exchanger |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3281648B2 (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2000105093A (en) * | 1998-09-29 | 2000-04-11 | Denso Corp | Heat exchanger |
| US6138354A (en) * | 1997-01-08 | 2000-10-31 | Denso Corporation | Method of manufacturing a corrugated plate by rolling for use as an inner fin of a heat exchanger |
| KR101405218B1 (en) * | 2012-12-17 | 2014-06-10 | 기아자동차 주식회사 | Egr cooler for vehicle |
| JP2016211809A (en) * | 2015-05-12 | 2016-12-15 | 株式会社デンソー | Cold storage heat exchanger |
| JP2017159856A (en) * | 2016-03-11 | 2017-09-14 | カルソニックカンセイ株式会社 | Evaporator with cold storage function |
| US10906380B2 (en) | 2016-03-11 | 2021-02-02 | Marelli Cabin Comfort Japan Corporation | Evaporator with cold storage function |
-
1992
- 1992-08-27 JP JP22822992A patent/JP3281648B2/en not_active Expired - Fee Related
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6138354A (en) * | 1997-01-08 | 2000-10-31 | Denso Corporation | Method of manufacturing a corrugated plate by rolling for use as an inner fin of a heat exchanger |
| JP2000105093A (en) * | 1998-09-29 | 2000-04-11 | Denso Corp | Heat exchanger |
| KR101405218B1 (en) * | 2012-12-17 | 2014-06-10 | 기아자동차 주식회사 | Egr cooler for vehicle |
| JP2016211809A (en) * | 2015-05-12 | 2016-12-15 | 株式会社デンソー | Cold storage heat exchanger |
| JP2017159856A (en) * | 2016-03-11 | 2017-09-14 | カルソニックカンセイ株式会社 | Evaporator with cold storage function |
| US10906380B2 (en) | 2016-03-11 | 2021-02-02 | Marelli Cabin Comfort Japan Corporation | Evaporator with cold storage function |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3281648B2 (en) | 2002-05-13 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JPH0674677A (en) | Manufacture of lamination type heat exchanger | |
| US5443116A (en) | Stacked heat exchanger | |
| JP5002797B2 (en) | Heat exchanger | |
| EP0661508B1 (en) | Layered heat exchangers | |
| AU670302B2 (en) | Stacked heat exchanger and method of manufacturing the same | |
| EP0590306B1 (en) | Stacked heat exchanger | |
| JP3281648B2 (en) | Stacked heat exchanger | |
| JP2984480B2 (en) | Stacked heat exchanger | |
| JPH0933187A (en) | Laminated heat exchanger | |
| JP2984481B2 (en) | Stacked heat exchanger | |
| JPH06123582A (en) | Stacked type heat exchanger | |
| JP2930486B2 (en) | Stacked heat exchanger | |
| JP3327584B2 (en) | Stacked heat exchanger | |
| JP4613083B2 (en) | Heat exchanger | |
| US5529119A (en) | Stacked heat exchanger | |
| JP3095540B2 (en) | Stacked heat exchanger | |
| JPH0674679A (en) | Lamination type heat exchanger | |
| JPH0674602A (en) | Laminated heat exchanger | |
| JP3073331B2 (en) | Stacked heat exchanger | |
| JPH0674686A (en) | Lamination type heat exchanger | |
| JPH06123590A (en) | Tacked type heat exchanger | |
| JPH06123589A (en) | Stacked type heat exchanger | |
| JPH06123522A (en) | Laminated heat exchanger | |
| JP2008281270A (en) | Heat exchanger | |
| JP3316492B2 (en) | Stacked heat exchanger |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| A02 | Decision of refusal |
Free format text: JAPANESE INTERMEDIATE CODE: A02 Effective date: 20000926 |
|
| LAPS | Cancellation because of no payment of annual fees |