JPS58217195A - Heat exchanger - Google Patents
Heat exchangerInfo
- Publication number
- JPS58217195A JPS58217195A JP57099604A JP9960482A JPS58217195A JP S58217195 A JPS58217195 A JP S58217195A JP 57099604 A JP57099604 A JP 57099604A JP 9960482 A JP9960482 A JP 9960482A JP S58217195 A JPS58217195 A JP S58217195A
- Authority
- JP
- Japan
- Prior art keywords
- heat exchanger
- air
- condensed water
- flat tube
- fin
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 239000003507 refrigerant Substances 0.000 claims abstract description 26
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 21
- 238000001704 evaporation Methods 0.000 abstract description 8
- 239000007788 liquid Substances 0.000 abstract description 6
- 230000000694 effects Effects 0.000 abstract description 5
- 238000000034 method Methods 0.000 abstract 1
- 210000002105 tongue Anatomy 0.000 description 7
- 230000008020 evaporation Effects 0.000 description 6
- 238000001816 cooling Methods 0.000 description 3
- 230000007423 decrease Effects 0.000 description 2
- 238000007791 dehumidification Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 241000269821 Scombridae Species 0.000 description 1
- 238000004378 air conditioning Methods 0.000 description 1
- 239000003795 chemical substances by application Substances 0.000 description 1
- 230000006866 deterioration Effects 0.000 description 1
- 238000007710 freezing Methods 0.000 description 1
- 230000008014 freezing Effects 0.000 description 1
- 235000020640 mackerel Nutrition 0.000 description 1
- 230000001737 promoting effect Effects 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F17/00—Removing ice or water from heat-exchange apparatus
- F28F17/005—Means for draining condensates from heat exchangers, e.g. from evaporators
-
- 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
- F28D1/0478—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 the conduits having a non-circular cross-section
-
- 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
- F28F1/126—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 consisting of zig-zag shaped fins
-
- 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
- F28F1/126—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 consisting of zig-zag shaped fins
- F28F1/128—Fins with openings, e.g. louvered fins
-
- 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
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
- F28D2021/0085—Evaporators
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Geometry (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
Description
【発明の詳細な説明】
本発明は、熱交換器に係わり、特にその構造に関し、熱
交換効率を向上させることを目的としたものである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a heat exchanger, and particularly to its structure, and is aimed at improving heat exchange efficiency.
一般に、自動車用空気調和機あるいは冷凍装置の熱交換
器に於て、空気側の伝熱面積の増大を計るために、空気
側のフィンとしてフルゲートフィンを用いた積層形勢交
換器が知られている。Generally, in heat exchangers for automobile air conditioners or refrigeration equipment, stacked exchangers are known that use full-gate fins as air-side fins in order to increase the heat transfer area on the air side. .
この種の代表的な例として第１図に示すものがあり、こ
のものは、偏平管（３）を蛇行状に折曲させ。A typical example of this type is shown in FIG. 1, in which a flat tube (3) is bent in a meandering shape.
一定間隔を有して複数本平行に並設され、この平行偏平
管（３１相互間にコルゲートフィン（４）を介在させた
ものであろうこり熱交換器は、偏平管（３）の多孔冷媒
通路（２）に冷媒が流れ、コルゲートフィン（４）群の
間を空気が流れ、空気と冷媒の熱交換は、フルゲートフ
ィン（４）を介して行なっている。また。A heat exchanger is a heat exchanger in which a plurality of parallel flat tubes (31) are arranged in parallel at regular intervals, and corrugated fins (4) are interposed between the flat tubes (3). Refrigerant flows through the passages (2), air flows between the corrugated fins (4), and heat exchange between the air and the refrigerant is performed via the full gate fins (4).
冷媒は入口側ヘッダー（６）より偏平管（３）の多孔冷
媒通路（２）を通り、出口側ヘッダ一部（８１に流れる
。The refrigerant flows from the inlet side header (6) through the porous refrigerant passage (2) of the flat tube (3) to a part of the outlet side header (81).
この場合、熱交換器に要望されることは、熱交換効率を
更に向上させる事であり、コルゲートフィン〔４）Ｋル
ーバ（９）を形成したものが提案されている。第３図、
第４図はフィン形状の一例を示し。In this case, what is required of the heat exchanger is to further improve the heat exchange efficiency, and a heat exchanger having corrugated fins [4] and K louvers (9) has been proposed. Figure 3,
FIG. 4 shows an example of a fin shape.
コルゲートフィン（４）の表面を、空気流通方向Ｃに直
交方向に複数個の切込みを入れ、切込み細片を斜めにル
ーバ（９）状に起し、ルーバ（９）の前縁にて流通空気
の境界層を切断する効果により、伝熱特性を向上させて
いる。 −
上記の構造の熱交換器は、温熱交換を行なう空調用の冷
却器にも使用されているが、除湿を行なった場合、第５
図に示すように水平方向に平行なフィン群の間に、凝縮
水がブリッジを組んだり。A plurality of cuts are made in the surface of the corrugated fin (4) in a direction perpendicular to the air flow direction C, and the cut strips are raised diagonally in the shape of a louver (9), and the leading edge of the louver (9) is used to prevent the circulating air. The effect of cutting the boundary layer improves heat transfer properties. - The heat exchanger with the above structure is also used in air conditioning coolers that exchange heat, but when dehumidifying, the
As shown in the figure, condensed water forms a bridge between groups of horizontally parallel fins.
半円形状に滞留し、凝縮水のスムーズな流出が不可能で
ある。このため、流入空気の通路が妨げられ、流入空気
量の低下に伴ない熱交換特性が低下する。また、フィン
に付着する凝縮水により、フィン空気間の熱伝達特性が
低下し、熱交換特性が低下するという欠点があった。更
に、熱交換器内の冷媒の蒸発温度を低くして、熱交換特
性を増加させることは、凝縮水の凍結の問題があり、不
可能であった。The condensed water accumulates in a semicircular shape, making it impossible for the condensed water to flow out smoothly. For this reason, the passage of the inflowing air is obstructed, and the heat exchange characteristics deteriorate as the amount of inflowing air decreases. In addition, condensed water adhering to the fins deteriorates the heat transfer characteristics between the fins and the air, resulting in a deterioration of the heat exchange characteristics. Furthermore, it has been impossible to increase the heat exchange characteristics by lowering the evaporation temperature of the refrigerant in the heat exchanger due to the problem of freezing of condensed water.
本発明は、上述した欠点を解消したもので、熱交換器の
冷媒蒸発温度を空気入口側より出口側にて下げ、かつ、
凝縮水の水切り性能を改善して。The present invention eliminates the above-mentioned drawbacks, and lowers the refrigerant evaporation temperature of the heat exchanger at the outlet side than at the air inlet side, and
Improved draining performance of condensed water.
熱交換器の熱交換特性を向上させることを目的としたも
のである。The purpose is to improve the heat exchange characteristics of the heat exchanger.
以下９本発明の詳細を第６図乃至第７図に示す実施例に
より説明する。本発明の実施例は、内部処多孔の冷媒通
路（２）を形成した偏平管（３）で、かつ。The details of the present invention will be explained below with reference to the embodiments shown in FIGS. 6 and 7. An embodiment of the present invention is a flat tube (3) having a refrigerant passage (2) with internal treatment holes.
偏平管の偏平部外側の一部に両側表面とも冷媒方向に溝
（１２を設けた偏平管（３）を蛇行状に成形し、偏平管
（３）の直管部は一定間隔を有して、複数本平行に並設
され、この偏平管（３）の直管部相互間には。A flat tube (3) with grooves (12) in the direction of the refrigerant on both sides of the flat tube is formed in a serpentine shape on a part of the outside of the flat part of the flat tube, and the straight tube part of the flat tube (3) has a constant interval. , a plurality of tubes are arranged in parallel between the straight tube portions of the flat tube (3).
コルゲートフィン（４）が折曲部（５）を偏平管（３）
にハンダ付されている。偏平管（３）の入口は、冷媒通
路（２）方向と直交して入口側ヘッダー（６）が設置さ
れており、入口側ヘッダー（６）には、冷媒入口バイブ
（７）が接続されている。また、偏平管（３）の出口部
には。The corrugated fin (4) connects the bent part (5) to the flat tube (3)
is soldered to. At the inlet of the flat tube (3), an inlet header (6) is installed perpendicular to the direction of the refrigerant passage (2), and a refrigerant inlet vibrator (7) is connected to the inlet header (6). There is. Also, at the outlet of the flat tube (3).
冷媒通路（２）方向と直交して、出口側ヘッダー（８）
が設置されている。入口側ヘッダー（６）は、断面積を
一部狭小せしめた絞り部αυが設けられ、偏平管（３）
の溝部＠の位置と合致している。コルゲートフィン（４
）には、空気直通方向と直交する方向に多数の切り込み
細片を切り起こして、ルーバ（９）を形成させている。Orthogonal to the direction of the refrigerant passage (2), the outlet side header (8)
is installed. The inlet header (6) is provided with a constricted part αυ whose cross-sectional area is partially narrowed, and the flat pipe (3)
It matches the position of the groove @. Corrugated fin (4
), a louver (9) is formed by cutting and raising a large number of strips in a direction perpendicular to the direct air flow direction.
更に、コルゲートフィン（４）のルーバ（９１群の間ニ
は、舌片（１３が偏平管（３）の溝部ＵＺへ向って凝縮
水を誘導する穴Ｉの空気流れ方向に対して前縁または後
縁のいずれか一方に下方に向って折曲形成され。Furthermore, the louvers (91 groups) of the corrugated fins (4) have tongues (13) that are located at the front edge or in the air flow direction of the holes I that guide condensed water toward the grooves UZ of the flat tube (3). A downward bend is formed on either side of the trailing edge.
かつ、上下方向に連続してつらなるよう形成されている
。また、舌片（１３の位置は、偏平管（３）の溝部Ｃｌ
７Ｊと入口側ヘッダー（６）の絞り部αηと同じ位置に
設けられ、かつ、空気流通方向との間にある所定の角度
θ （０〈θ≦９０°）をなしている。Moreover, it is formed so as to be continuous in the vertical direction. In addition, the position of the tongue piece (13) is the groove part Cl of the flat tube (3).
7J and the throttle part αη of the inlet header (6), and form a predetermined angle θ (0<θ≦90°) with the air flow direction.
次に上述した構成の熱交換器の作用について説明する。Next, the operation of the heat exchanger configured as described above will be explained.
まず、膨張弁や毛細管（いずれも図示せず）により減圧
された液冷媒は、冷媒入口バイブ（７）より入口側ヘッ
ダー（６）に導入される。入口側ヘッダー（６）には絞
り部（１１１が設置されているので、絞り部ｔ１１１よ
り後方へ流れる液冷媒は、絞り部Ｉの効果により、絞り
部Ｕの前方に流れる液冷媒より０、２ Ｓｏ、 ５ ｋ
ｇ／ａｒｔ程度減圧される。First, liquid refrigerant whose pressure has been reduced by an expansion valve and a capillary tube (none of which are shown) is introduced into the inlet side header (6) from the refrigerant inlet vibrator (7). Since the inlet side header (6) is provided with a constriction part (111), the liquid refrigerant flowing backward from the constriction part t111 is 0.2 times lower than the liquid refrigerant flowing in front of the constriction part U due to the effect of the constriction part I. So, 5k
The pressure is reduced by about g/art.
これらの液冷媒は、偏平管（３）内の多孔の冷媒通路（
２）を通り、蛇行しながら出口側ヘッダー（８１に導び
かれる。由に、絞り部（１１１の前後に於て、偏平管（
３）の温度は約５ ａｅｇ異なり、前方より後方の方が
当然温度が低い状態である。一方、熱交換器（１）に流
通する空気は、ルーバ（９）群を設けたフルゲートフィ
ン（４）により、除湿・冷却され、フィンに付着した凝
縮水は大側から舌片Ｑ３により、溝部１ｚへ案内され下
方へ排出される。また、風速により飛び去ろうとする凝
縮水の水滴は、舌片（１３により保持されて、後方へ流
れて行くのを防止されている。These liquid refrigerants pass through the porous refrigerant passages (
2) and is guided to the outlet side header (81) while meandering.
The temperature in 3) differs by about 5 aeg, and the temperature is naturally lower at the rear than at the front. On the other hand, the air flowing through the heat exchanger (1) is dehumidified and cooled by the full gate fin (4) provided with a group of louvers (9), and the condensed water adhering to the fin is removed from the large side by the tongue piece Q3 into the groove. It is guided to 1z and discharged downward. Further, water droplets of condensed water that tend to fly away due to wind speed are held by the tongue pieces (13) and are prevented from flowing backward.
大幅に除湿された空気は、舌片（１３以後に於て蒸発温
度の更に低い液冷媒と熱交換して、熱交換器より外へ流
通する。The significantly dehumidified air exchanges heat with the liquid refrigerant having a lower evaporation temperature at the tongue piece (after 13) and flows out of the heat exchanger.
次に本発明の実施例による特性を、第１２図に示し説明
すると、空気流通の上流側にて、特に除湿・冷却作用を
行ない、除湿された凝縮水は偏平管溝部より下方に排出
し、空気流通の下流側にて更に低い蒸発温度による熱交
換器で冷却作用を行なう。そして、熱交換器の空気入口
をＸ部とし。Next, the characteristics of the embodiment of the present invention are illustrated and explained in FIG. 12. Particularly, dehumidification and cooling are performed on the upstream side of the air circulation, and the dehumidified condensed water is discharged downward from the flat pipe groove. On the downstream side of the air flow, a heat exchanger with a lower evaporation temperature performs the cooling action. Then, the air inlet of the heat exchanger is designated as part X.
凝縮水排出用偏平管溝部をＹ部、空気出口部を２部とす
ると、Ｘ−Ｙ間には空気は除湿・冷却され。If the condensed water discharge flat pipe groove section is the Y section and the air outlet section is the 2 section, the air between X and Y is dehumidified and cooled.
凝縮水は排水される。更に、Ｙ−Ｚ部では、蒸発温度が
低下している。Condensed water is drained. Furthermore, in the Y-Z section, the evaporation temperature is lowered.
以上説明したように本発明によれば、従来に比べて空気
との温度差が大きくなり、冷却効果が増大する。また、
凝縮水もコルゲートフィン間に滞留しないため、空気抵
抗も少なくなり、熱交換量が増大する。さらに、入口空
気と出口空気の温度差は従来は△Ｔ１ であり９本発明
では△Ｔ２となる。即ち、従来の熱交換器では果し得な
かった除湿を伴なう用途に、蒸発温度を更に下げて使用
できるようになり、大幅な軽量化、小型化を可能にして
、コスト低減を計るとともに、大幅な熱交換効率の向上
を促進させるなど本発明による利益には多大なものがあ
る
なお１本発明の詳細な説明中、コルゲートフィン（４）
の穴α４に舌片α３を形成して偏平管（３）の溝σ２へ
凝縮水を啓導するように構成したが、第１０図および第
１１図に示すように偏平管（３）の溝部σ２に合致させ
て、コルゲートフィン（４）を冷媒通路方向で２分割し
て、すきま四を設けるように構成しても良く１本発明と
同様な効果を奏するものである。As explained above, according to the present invention, the temperature difference with air becomes larger than in the conventional case, and the cooling effect increases. Also,
Since condensed water does not accumulate between the corrugated fins, air resistance also decreases and the amount of heat exchange increases. Further, the temperature difference between the inlet air and the outlet air is conventionally ΔT1, but in the present invention it is ΔT2. In other words, it is now possible to lower the evaporation temperature for applications involving dehumidification, which could not be achieved with conventional heat exchangers, making it possible to significantly reduce weight and size, thereby reducing costs. There are many benefits of the present invention, such as promoting a significant improvement in heat exchange efficiency.In the detailed description of the present invention, corrugated fins (4)
The tongue piece α3 is formed in the hole α4 of the flat tube (3) to guide the condensed water to the groove σ2 of the flat tube (3). In accordance with σ2, the corrugated fins (4) may be divided into two in the refrigerant passage direction to provide four gaps, and the same effect as the present invention can be obtained.
第１図は従来の熱交換器の斜視図、第２図は第１図の■
−…断面図、第３図は従来の熱交換器の要部斜視図、第
４図は従来のコルゲートフィンの斜視図、第５図は従来
のコルゲートフィン間の水滴付着状態を示す図、第６図
は本発明の実施例による熱交換器の斜視図、第７図は第
６図の■−■断面図、第８図は本発明の実施例による要
部平面図、第９図は本発明の実施例による要部斜視図。
第１０図は本発明の他の実施例を示す斜視図、第１１図
は第１０図の要部を示す拡大斜視図、第１２図は本発明
の実施例による熱交換特性図である。
なお９図中同一符号は同−又は相当部分を示し。
（１）は熱交換器、（２）は冷媒通路、（３）は偏平管
、（４）はコルゲートフィン、（６）は入口側ヘッダー
、（７）は冷媒通路、（８）は出口側ヘッダー、（９）
はルーバ、（１１は水滴、 （１１１は絞り部、鰺は溝
部、住３は舌片、 （ｔ４は穴。
（１５はすきまである。
代理人 葛野信−
Ｕ面のａ・古（内容に昨ｆなし）
第１図
第５図
第６図
第９図
第１０図
・ｆｆ１１１図
第１２図
Ｘ部 ７部 Ｚｌ
特許庁長官殿
■、事件の表示 特願昭 ５７−９９６０４号２
、発明の名称
熱交換器
３、補正をする者
事件との関係 特許出願人
住 所 東京都千代田区丸の内二丁目２番３号
名 称（６０１） 三菱電機株式会社代表者片山仁
八部
４、代理人
住 所 東京都千代田区丸の内二丁目２番３号
６、補正の対象
（１）明細書の全文
（２） 図面
Ｌ 補正の内容
（１）明細書の浄書（内容に変更なし）（２）図面の浄
書（内容に変更なし）Figure 1 is a perspective view of a conventional heat exchanger, and Figure 2 is the same as in Figure 1.
-...Cross-sectional view, Figure 3 is a perspective view of the main parts of a conventional heat exchanger, Figure 4 is a perspective view of a conventional corrugated fin, Figure 5 is a diagram showing the state of water droplet adhesion between conventional corrugated fins, 6 is a perspective view of a heat exchanger according to an embodiment of the present invention, FIG. 7 is a cross-sectional view taken along the line ■-■ of FIG. 6, FIG. 8 is a plan view of main parts according to an embodiment of the present invention, and FIG. FIG. 2 is a perspective view of essential parts according to an embodiment of the invention. FIG. 10 is a perspective view showing another embodiment of the present invention, FIG. 11 is an enlarged perspective view showing the main part of FIG. 10, and FIG. 12 is a heat exchange characteristic diagram according to the embodiment of the present invention. Note that the same reference numerals in Figure 9 indicate the same or equivalent parts. (1) is a heat exchanger, (2) is a refrigerant passage, (3) is a flat tube, (4) is a corrugated fin, (6) is an inlet side header, (7) is a refrigerant passage, (8) is an outlet side Header, (9)
is a louver, (11 is a water droplet, (111 is a squeeze part, a mackerel is a groove part, 3 is a tongue piece, (t4 is a hole. (15 is a gap. Figure 1 Figure 5 Figure 6 Figure 9 Figure 10, ff111 Figure 12 Part
, Name of the invention Heat exchanger 3, Relationship with the case of the person making the amendment Patent applicant address 2-2-3 Marunouchi, Chiyoda-ku, Tokyo Name (601) Mitsubishi Electric Corporation Representative Hitachi Katayama 4; Agent address: 2-2-3-6 Marunouchi, Chiyoda-ku, Tokyo Subject of amendment (1) Full text of the specification (2) Drawing L Contents of amendment (1) Engraving of the specification (no change in content) (2 ) Engraving of the drawing (no changes to the content)
Claims (1)
に形成し、冷媒通路と直角に設置された入口側ヘッダー
を上記入口部に接合し、かつ、上記出口部にも出口側ヘ
ッダーを接合し上記偏平管相互間にコルゲートフィンを
介在させた熱交換器であって、上記入口側ヘッダーの断
面積を一部分減少せしめる絞り部を上記入口側ヘッダー
の所定個所に設けるとともに、上記偏平管の偏平部表面
の上記絞り部に対応した位置に溝を設けたことを特徴と
する熱交換器。 （２） コルゲートフイ／は、そのフィンに一対の穴
が穿設され、偏平管の溝に向って凝縮水を誘導させる舌
片が上記穴の空気流れ方向に対して前線または後縁のい
ずれか一方に設けられたもので構成したことを特徴とす
る特許請求の範囲第１項記載の熱交換器。 （３） コルゲートフィンは、そのフィンの一部に形
成された穴に下方へ折曲された舌片を有し、かつこの舌
片を上下方向に連続的に形成したものであることを特徴
とする特許請求の範囲第１項、または第２項記載の熱交
換器 （４） コルゲートフィンは、そのフィンを冷媒通路
方向と直角方向で２分割したフィンの間にすきまを有し
、かつ、このすきまを溝の位置と合致した位置としたこ
とを特徴とする特許請求の範囲第１項記載の熱交換器。[Claims] (13) A flat tube with a porous refrigerant passage formed therein is formed in a meandering shape, an inlet side header installed perpendicular to the refrigerant passage is joined to the inlet part, and the outlet part A heat exchanger in which an outlet header is joined to the flat tubes and corrugated fins are interposed between the flat tubes, and a constriction part for partially reducing the cross-sectional area of the inlet header is provided at a predetermined location of the inlet header. and a heat exchanger characterized in that a groove is provided on the surface of the flat part of the flat tube at a position corresponding to the constricted part. (2) A corrugated fin has a pair of holes bored in the fin, Claim 1, characterized in that a tongue piece for guiding condensed water toward the groove of the flat tube is provided on either the front or rear edge of the hole with respect to the air flow direction. The heat exchanger according to item 1. (3) The corrugated fin has a tongue piece bent downward in a hole formed in a part of the fin, and the tongue piece is formed continuously in the vertical direction. A heat exchanger (4) according to claim 1 or 2, characterized in that the corrugated fin is divided into two parts in a direction perpendicular to the refrigerant passage direction. 2. The heat exchanger according to claim 1, wherein the heat exchanger has a gap, and the gap is located at a position that coincides with the position of the groove.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP57099604A JPS58217195A (en) | 1982-06-10 | 1982-06-10 | Heat exchanger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP57099604A JPS58217195A (en) | 1982-06-10 | 1982-06-10 | Heat exchanger |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS58217195A true JPS58217195A (en) | 1983-12-17 |
Family
ID=14251690
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP57099604A Pending JPS58217195A (en) | 1982-06-10 | 1982-06-10 | Heat exchanger |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS58217195A (en) |
Cited By (21)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4621685A (en) * | 1983-09-12 | 1986-11-11 | Diesel Kiki Co., Ltd. | Heat exchanger comprising condensed moisture drainage means |
| EP0962736A3 (en) * | 1998-06-01 | 2000-08-16 | Delphi Technologies, Inc. | Corrugated fin for evaporator with improved condensate removal |
| US6308527B1 (en) * | 1998-12-10 | 2001-10-30 | Denso Corporation | Refrigerant evaporator with condensed water drain structure |
| US6401809B1 (en) | 1999-12-10 | 2002-06-11 | Visteon Global Technologies, Inc. | Continuous combination fin for a heat exchanger |
| WO2003048670A1 (en) * | 2001-11-30 | 2003-06-12 | Modine Manufacturing Company | Heat exchanger for providing supercritical cooling of a working fluid in a transcritical cooling cycle |
| WO2003050468A1 (en) * | 2001-12-12 | 2003-06-19 | Modine Manufacturing Company | Split fin for a heat exchanger |
| KR20040017920A (en) * | 2002-08-22 | 2004-03-02 | 엘지전자 주식회사 | Condensate drainage of heat exchanger |
| JP2007505282A (en) * | 2003-09-11 | 2007-03-08 | ベール ゲーエムベーハー ウント コー カーゲー | Heat exchanger |
| WO2008091738A1 (en) * | 2007-01-23 | 2008-07-31 | Modine Manufacturing Company | Heat exchanger and method |
| US7448439B2 (en) * | 2002-07-09 | 2008-11-11 | Fujitsu Limited | Heat exchanger |
| JP2013036625A (en) * | 2011-08-03 | 2013-02-21 | Univ Of Tokyo | Corrugated fin type heat exchanger |
| CN103438745A (en) * | 2013-09-17 | 2013-12-11 | 杭州三花研究院有限公司 | Heat exchanger and fin thereof |
| EP2233874A4 (en) * | 2007-11-02 | 2013-12-18 | Sharp Kk | Heat exchanger |
| EP2196758A4 (en) * | 2007-10-04 | 2014-01-15 | Sharp Kk | Heat exchanger |
| WO2016013100A1 (en) * | 2014-07-25 | 2016-01-28 | 三菱電機株式会社 | Heat exchanger and air-conditioning and refrigerating apparatus with heat exchanger |
| WO2017215960A1 (en) * | 2016-06-16 | 2017-12-21 | BSH Hausgeräte GmbH | Refrigeration device having a refrigerant condenser with a lamella arrangement |
| CN107843031A (en) * | 2016-09-19 | 2018-03-27 | 杭州三花家电热管理系统有限公司 | Micro-channel heat exchanger |
| CN107923712A (en) * | 2015-08-14 | 2018-04-17 | 开利公司 | Micro-channel heat exchanger |
| US20190360755A1 (en) * | 2015-12-16 | 2019-11-28 | Sanhua (Hangzhou) Micro Channel Heat Exchanger Co., Ltd. | Heat exchanger coil and heat exchanger having the same |
| WO2022219919A1 (en) * | 2021-04-13 | 2022-10-20 | 三菱電機株式会社 | Heat exchanger and refrigeration cycle device |
| JP7305085B1 (en) * | 2022-04-12 | 2023-07-07 | 三菱電機株式会社 | Heat exchanger and refrigeration cycle equipment |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5523166U (en) * | 1978-08-02 | 1980-02-14 |
-
1982
- 1982-06-10 JP JP57099604A patent/JPS58217195A/en active Pending
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5523166U (en) * | 1978-08-02 | 1980-02-14 |
Cited By (29)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4621685A (en) * | 1983-09-12 | 1986-11-11 | Diesel Kiki Co., Ltd. | Heat exchanger comprising condensed moisture drainage means |
| EP0962736A3 (en) * | 1998-06-01 | 2000-08-16 | Delphi Technologies, Inc. | Corrugated fin for evaporator with improved condensate removal |
| US6308527B1 (en) * | 1998-12-10 | 2001-10-30 | Denso Corporation | Refrigerant evaporator with condensed water drain structure |
| EP1106951A3 (en) * | 1999-12-10 | 2003-09-03 | Visteon Global Technologies, Inc. | Continuous combination fin for a heat exchanger |
| US6401809B1 (en) | 1999-12-10 | 2002-06-11 | Visteon Global Technologies, Inc. | Continuous combination fin for a heat exchanger |
| WO2003048670A1 (en) * | 2001-11-30 | 2003-06-12 | Modine Manufacturing Company | Heat exchanger for providing supercritical cooling of a working fluid in a transcritical cooling cycle |
| CN100380081C (en) * | 2001-11-30 | 2008-04-09 | 穆丹制造公司 | Heat exchanger for providing supercritical cooling of a working fluid in a transcritical cooling cycle |
| WO2003050468A1 (en) * | 2001-12-12 | 2003-06-19 | Modine Manufacturing Company | Split fin for a heat exchanger |
| US7448439B2 (en) * | 2002-07-09 | 2008-11-11 | Fujitsu Limited | Heat exchanger |
| KR20040017920A (en) * | 2002-08-22 | 2004-03-02 | 엘지전자 주식회사 | Condensate drainage of heat exchanger |
| JP2007505282A (en) * | 2003-09-11 | 2007-03-08 | ベール ゲーエムベーハー ウント コー カーゲー | Heat exchanger |
| WO2008091738A1 (en) * | 2007-01-23 | 2008-07-31 | Modine Manufacturing Company | Heat exchanger and method |
| EP2196758A4 (en) * | 2007-10-04 | 2014-01-15 | Sharp Kk | Heat exchanger |
| EP2233874A4 (en) * | 2007-11-02 | 2013-12-18 | Sharp Kk | Heat exchanger |
| JP2013036625A (en) * | 2011-08-03 | 2013-02-21 | Univ Of Tokyo | Corrugated fin type heat exchanger |
| CN103438745B (en) * | 2013-09-17 | 2016-04-13 | 杭州三花微通道换热器有限公司 | A kind of heat exchanger and fin thereof |
| CN103438745A (en) * | 2013-09-17 | 2013-12-11 | 杭州三花研究院有限公司 | Heat exchanger and fin thereof |
| WO2016013100A1 (en) * | 2014-07-25 | 2016-01-28 | 三菱電機株式会社 | Heat exchanger and air-conditioning and refrigerating apparatus with heat exchanger |
| JPWO2016013100A1 (en) * | 2014-07-25 | 2017-04-27 | 三菱電機株式会社 | HEAT EXCHANGER AND AIR CONDITIONING REFRIGERATOR HAVING THE HEAT EXCHANGER |
| CN107923712A (en) * | 2015-08-14 | 2018-04-17 | 开利公司 | Micro-channel heat exchanger |
| US10739076B2 (en) * | 2015-12-16 | 2020-08-11 | Sanhua (Hangzhou) Micro Channel Heat Exchanger Co., Ltd. | Heat exchanger coil and heat exchanger having the same |
| US20190360755A1 (en) * | 2015-12-16 | 2019-11-28 | Sanhua (Hangzhou) Micro Channel Heat Exchanger Co., Ltd. | Heat exchanger coil and heat exchanger having the same |
| WO2017215960A1 (en) * | 2016-06-16 | 2017-12-21 | BSH Hausgeräte GmbH | Refrigeration device having a refrigerant condenser with a lamella arrangement |
| CN107843031A (en) * | 2016-09-19 | 2018-03-27 | 杭州三花家电热管理系统有限公司 | Micro-channel heat exchanger |
| CN107843031B (en) * | 2016-09-19 | 2020-06-16 | 杭州三花微通道换热器有限公司 | Micro-channel heat exchanger |
| WO2022219919A1 (en) * | 2021-04-13 | 2022-10-20 | 三菱電機株式会社 | Heat exchanger and refrigeration cycle device |
| JPWO2022219919A1 (en) * | 2021-04-13 | 2022-10-20 | ||
| JPWO2022219719A1 (en) * | 2021-04-13 | 2022-10-20 | ||
| JP7305085B1 (en) * | 2022-04-12 | 2023-07-07 | 三菱電機株式会社 | Heat exchanger and refrigeration cycle equipment |
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