JPS6214751B2 - - Google Patents
Info
- Publication number
- JPS6214751B2 JPS6214751B2 JP14694480A JP14694480A JPS6214751B2 JP S6214751 B2 JPS6214751 B2 JP S6214751B2 JP 14694480 A JP14694480 A JP 14694480A JP 14694480 A JP14694480 A JP 14694480A JP S6214751 B2 JPS6214751 B2 JP S6214751B2
- Authority
- JP
- Japan
- Prior art keywords
- heat exchanger
- refrigerant
- flat heat
- meandering
- exchanger tube
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
- 239000003507 refrigerant Substances 0.000 claims description 60
- 239000007788 liquid Substances 0.000 description 6
- 238000010586 diagram Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 238000005192 partition Methods 0.000 description 3
- 238000011144 upstream manufacturing Methods 0.000 description 3
- WYTGDNHDOZPMIW-RCBQFDQVSA-N alstonine Natural products C1=CC2=C3C=CC=CC3=NC2=C2N1C[C@H]1[C@H](C)OC=C(C(=O)OC)[C@H]1C2 WYTGDNHDOZPMIW-RCBQFDQVSA-N 0.000 description 2
- 238000001704 evaporation Methods 0.000 description 2
- 230000008020 evaporation Effects 0.000 description 2
- 230000005514 two-phase flow Effects 0.000 description 2
- 238000007664 blowing Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
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
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
- F28D1/0477—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
- F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
- F28F13/08—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by varying the cross-section of the flow channels
Description
【発明の詳細な説明】
本発明はカーエアコンに使用される熱交換器、
特にコルゲートフイン熱交換器に関するものであ
る。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a heat exchanger used in a car air conditioner,
In particular, it relates to corrugated fin heat exchangers.
従来のこの種熱交換器例えばカーエアコン蒸発
器は第１図に示すように、蛇行状に成形された偏
平伝熱（冷媒）管１の蛇行部に、その伝熱管１と
垂直方向に蛇行状のコルゲートフイン２を介在さ
せ、伝熱管１の両端にそれぞれ取付けられた冷媒
入口ヘツダ３および冷媒出口ヘツダ４に、冷媒入
口管５および冷媒出口管６をそれぞれ接続して構
成されている。７は空気流れを示す。 A conventional heat exchanger of this kind, for example, a car air conditioner evaporator, has a meandering shape in the meandering part of a flat heat transfer (refrigerant) tube 1 formed in a meandering shape in a direction perpendicular to the heat transfer tube 1, as shown in FIG. A refrigerant inlet pipe 5 and a refrigerant outlet pipe 6 are respectively connected to a refrigerant inlet header 3 and a refrigerant outlet header 4 attached to both ends of the heat transfer tube 1, respectively, with corrugated fins 2 interposed therebetween. 7 indicates air flow.
上記伝熱管１は第３図に示すように仕切板１ａ
により多数に区分されており、しかもその通路断
面積は第４図のＡに示すように入口から出口まで
同一に形成されている。このように形成された伝
熱管１内を冷媒が第２図に示すように流れてい
る。この冷媒が次第に蒸発してガス化すると、そ
の体積は増加し、ガス流速も増速するので、蒸発
器の出口付近における圧力損失は増大する。 The heat exchanger tube 1 has a partition plate 1a as shown in FIG.
The passage is divided into a large number of sections, and the cross-sectional area of the passage is the same from the inlet to the outlet, as shown at A in FIG. A refrigerant flows within the heat exchanger tube 1 formed in this manner as shown in FIG. As this refrigerant gradually evaporates and gasifies, its volume increases and the gas flow rate also increases, resulting in an increase in pressure loss near the outlet of the evaporator.
上記圧力損失を低減するためには、乾き度すな
わち気液二相流中のガスの重量流量割合により流
路断面積を第４図のＢに示すように入口Baから
出口Bbに至るにしたがつて大きくなるように変
化させ、ガス流速が余り大きくならないように考
慮する必要がある。凝縮器の場合には前記蒸発器
の場合と逆に入口より出口に至るにしたがつて小
さくなるように変化させねばならない。 In order to reduce the above pressure loss, the cross-sectional area of the flow path from the inlet Ba to the outlet Bb is changed as shown in B in Fig. 4 according to the dryness, that is, the weight flow rate ratio of the gas in the gas-liquid two-phase flow. It is necessary to take into consideration that the gas flow rate does not become too large. In the case of a condenser, the size must be changed from the inlet to the outlet, contrary to the case of the evaporator.
本発明の目的は、吹出し空気温度をほぼ一様に
して快適性を向上させることにある。 An object of the present invention is to improve comfort by making the temperature of the blown air substantially uniform.
第１番目の発明の特徴は、偏平伝熱管を空気流
れの方向に沿つて上流側と下流側に分割すると共
に、これらの分割偏平伝熱管の両端に中間ヘツダ
をそれぞれ取付けて上、下流の偏平伝熱管を連結
し、一方前記分割偏平伝熱管のうち一部の分割偏
平伝熱管の蛇行部中間に冷媒入口ヘツダを、残部
の分割偏平伝熱管の蛇行部中間に冷媒出口ヘツダ
をそれぞれ取付けたものであり、第２番目の発明
の特徴は、偏平伝熱管を空気流れの方向に沿つて
大、小の通路断面積を有するように分割し、この
分割された偏平伝熱管の両端に中間ヘツダをそれ
ぞれ取付けて上、下流の偏平伝熱管を連結し、一
方、その蛇行部中間の分割偏平伝熱管の一方に冷
媒入口ヘツダを、他方に冷媒出口ヘツダをそれぞ
れ取付けたものである。 The first feature of the invention is that the flat heat exchanger tube is divided into upstream and downstream sides along the direction of air flow, and intermediate headers are attached to both ends of these divided flat heat exchanger tubes to separate the upper and downstream flat heat exchanger tubes. Heat exchanger tubes are connected, and a refrigerant inlet header is installed in the middle of the meandering part of some of the divided flat heat exchanger tubes, and a refrigerant outlet header is installed in the middle of the meandering part of the remaining divided flat heat exchanger tubes. The second feature of the invention is that the flat heat exchanger tube is divided into sections having large and small passage cross-sectional areas along the direction of air flow, and intermediate headers are provided at both ends of the divided flat heat exchanger tube. The upper and downstream flat heat exchanger tubes are connected to each other, and a refrigerant inlet header is attached to one of the divided flat heat exchanger tubes in the middle of the meandering portion, and a refrigerant outlet header is attached to the other.
上記第１番目の発明の構成によれば、熱交換器
の中央から供給された冷媒が両端に向つて流れ、
両端の中間ヘツダに達した後中央に向つて流れ、
空気との交換能力が大きい冷媒入口側と、空気と
の交換能力が小さい冷媒出口側との両方を同じ空
気が通るので、交換能力の低い冷媒出口側を通る
空気は交換能力の高い冷媒入口側で交換能力が増
大され、その結果冷媒と空気との熱交換が全体的
にほぼ一様になり、これにより吹出し空気温度が
ほぼ一様となつて快適性が向上する。 According to the configuration of the first invention, the refrigerant supplied from the center of the heat exchanger flows toward both ends,
After reaching the intermediate headers at both ends, it flows toward the center,
The same air passes through both the refrigerant inlet side, which has a high exchange capacity with air, and the refrigerant outlet side, which has a low exchange capacity with air, so the air that passes through the refrigerant outlet side, which has a low exchange capacity, is transferred to the refrigerant inlet side, which has a high exchange capacity. The exchange capacity is increased, and as a result, the heat exchange between the refrigerant and the air becomes substantially uniform throughout, thereby making the outlet air temperature substantially uniform and improving comfort.
第２番目の発明は、第１番目の発明と同様の構
成を備えているから上記第１番目のものと同様の
作用効果を奏するとともに、冷媒の通路断面積が
大、小のものからなり、これらが連絡されている
から、この通路は、２段階に変化する通路断面積
となり、冷媒が液から蒸気に変化した場合の体積
膨脹、又はその逆の体積縮小に適合した冷媒通路
を構成することができる。その結果、冷媒側の圧
力損失が小さくなり、冷媒の循環量が増え、熱交
換能力が増大する。また冷媒側の圧力損失が小さ
くなると、偏平伝熱管内の冷媒の圧力が圧力損失
により高くなるのが押えられるので、冷媒の蒸発
圧力は低く維持され、蒸発温度も低くなるから、
その分冷却能力が増加する。 Since the second invention has the same configuration as the first invention, it exhibits the same effects as the first invention, and the refrigerant passage cross-sectional area is large and small. Because these are connected, this passage has a passage cross-sectional area that changes in two stages, and constitutes a refrigerant passage that is suitable for volume expansion when the refrigerant changes from liquid to vapor, or vice versa. I can do it. As a result, the pressure loss on the refrigerant side is reduced, the amount of refrigerant circulated is increased, and the heat exchange capacity is increased. In addition, when the pressure loss on the refrigerant side becomes smaller, the pressure of the refrigerant inside the flat heat transfer tube is prevented from increasing due to pressure loss, so the evaporation pressure of the refrigerant is maintained low, and the evaporation temperature is also lowered.
The cooling capacity increases accordingly.
以下本発明の実施例を図面について説明する。 Embodiments of the present invention will be described below with reference to the drawings.
第５図において、８Ａ〜８Ｃは１本の蛇行状偏
平管８を空気流れ７の方向に沿つて任意数（図で
は３本）に等分割した蛇行状偏平伝熱管で、これ
らの偏平伝熱管８Ａ〜８Ｃは第６図に示すように
仕切板９により任意数（図では３個）に区分され
ている。１０は偏平伝熱管８Ａ〜８Ｃの蛇行部
に、これと垂直に介設された蛇行状フイン、１１
Ａ，１１Ｂは偏平伝熱管８Ａ〜８Ｃの両端に取付
けられた中間ヘツダ、１３，１４は偏平伝熱管８
Ａ〜８Ｃの蛇行部中間において偏平伝熱管８Ｃお
よび偏平伝熱管８Ｂ，８Ａにそれぞれ取付けられ
た冷媒入口ヘツダおよび出口ヘツダ、１５，１６
は冷媒入口ヘツダ１２および冷媒出口ヘツダ１３
にそれぞれ接続された冷媒入口管および冷媒出口
管である。 In Fig. 5, 8A to 8C are meandering flat heat exchanger tubes obtained by dividing one meandering flat tube 8 into an arbitrary number (three in the figure) of equal parts along the direction of the air flow 7, and these flat heat exchanger tubes. 8A to 8C are divided into an arbitrary number (three in the figure) by a partition plate 9, as shown in FIG. 10 is a serpentine fin installed perpendicularly to the serpentine portion of the flat heat exchanger tubes 8A to 8C, 11
A and 11B are intermediate headers attached to both ends of the flat heat exchanger tubes 8A to 8C, and 13 and 14 are the flat heat exchanger tubes 8.
Refrigerant inlet header and outlet header, 15, 16 attached to the flat heat exchanger tube 8C and the flat heat exchanger tubes 8B, 8A, respectively, in the middle of the meandering part of A to 8C.
are the refrigerant inlet header 12 and the refrigerant outlet header 13
a refrigerant inlet pipe and a refrigerant outlet pipe respectively connected to the refrigerant inlet pipe and the refrigerant outlet pipe.
次に上記のような構成からなる本実施例の作用
について説明する。 Next, the operation of this embodiment configured as described above will be explained.
冷媒入口管１５より供給される冷媒は液を多量
に含んだ気液二相流であり、この冷媒は冷媒入口
ヘツダ１３に流入して左右両方向に分配され、さ
らに偏平伝熱管８Ｃ内を流通しながら蒸発し、ガ
スが多量になつた頃に偏平伝熱管８Ｃの両端に設
けられた中間ヘツダ１１Ａ，１１Ｂに流入する。
この中間ヘツダ１１Ａ，１１Ｂに流入した冷媒は
さらに偏平伝熱管８Ａ，８Ｂ内を流通して中央部
に設けた冷媒出口ヘツダ１４に流入した後に、冷
媒出口管１６より流出する。その冷媒は冷媒出口
ヘツダ１４に至るまでに蒸発して完全にガス化さ
れている。 The refrigerant supplied from the refrigerant inlet pipe 15 is a gas-liquid two-phase flow containing a large amount of liquid, and this refrigerant flows into the refrigerant inlet header 13, is distributed in both left and right directions, and further flows through the flat heat exchanger tube 8C. When the amount of gas increases, it flows into intermediate headers 11A and 11B provided at both ends of the flat heat exchanger tube 8C.
The refrigerant flowing into the intermediate headers 11A, 11B further flows through the flat heat exchanger tubes 8A, 8B, flows into the refrigerant outlet header 14 provided in the center, and then flows out from the refrigerant outlet pipe 16. By the time the refrigerant reaches the refrigerant outlet header 14, it has been evaporated and completely gasified.
上記のように冷媒が入口（冷媒入口ヘツダ）１
３より出口（冷媒出口ヘツダ）１４に至るまでに
流通する通路断面積は第７図の実線に示すように
変化する。同図の破線は従来例の通路断面積を示
す。この図より明らかなように本実施例では乾き
度と共に通路断面積が増加しているので、ガス流
速の増大は抑制されるから圧力損失を低減させる
ことができる。前記出口１４におけるガス流速は
従来例のそれに比べると3/4倍となるので、圧力
損失が流速の２乗に比例すると仮定すれば、圧力
損失を約60％に低減することができる。 As shown above, the refrigerant is inlet (refrigerant inlet header) 1
The cross-sectional area of the passage from 3 to the outlet (refrigerant outlet header) 14 changes as shown by the solid line in FIG. The broken line in the figure indicates the cross-sectional area of the passage in the conventional example. As is clear from this figure, in this example, the cross-sectional area of the passage increases with the degree of dryness, so that the increase in gas flow rate is suppressed, and therefore the pressure loss can be reduced. Since the gas flow velocity at the outlet 14 is 3/4 times that of the conventional example, the pressure loss can be reduced to about 60%, assuming that the pressure loss is proportional to the square of the flow velocity.
第８図に示す従来例のように、冷媒入口ヘツダ
３を経て偏平伝熱管１を流通させた後に、冷媒出
口ヘツダ４を経て流出させるものでは、その出口
付近がスーパーヒート領域内にあるため、その吹
き出し空気の温度は温度分布線１５に示すように
著しく上昇する。 In the conventional example shown in FIG. 8, in which the flat heat exchanger tubes 1 are made to flow through the refrigerant inlet header 3 and then flowed out through the refrigerant outlet header 4, the vicinity of the exit is within the superheat region. The temperature of the blown air increases significantly as shown by temperature distribution line 15.
これに対し第９図に示す本実施例のように、冷
媒を冷媒入口ヘツダ１３を経て偏平伝熱管１８Ｃ
を流通させ、ついで中間ヘツダ１１Ａ，１１Ｂを
経て偏平伝熱管１８Ａ，１８Ｂを流通させた後
に、冷媒出口ヘツダ１４を経て流出させるもので
は、空気上流側の液冷媒が十分であり、かつスー
パーヒート領域も狭いため、吹き出し空気の温度
は温度分布線１６に示すようにほぼ一様である。 On the other hand, as in the present embodiment shown in FIG. 9, the refrigerant is passed through the refrigerant inlet header 13 and
In the case where the liquid refrigerant on the air upstream side is sufficient and the liquid refrigerant on the air upstream side is sufficient, and then the flat heat exchanger tubes 18A, 18B are allowed to flow through the intermediate headers 11A, 11B, and then flowed out through the refrigerant outlet header 14. Since the area is narrow, the temperature of the blown air is almost uniform as shown by the temperature distribution line 16.
本実施例では１本の偏平伝熱管８を３本の偏平
伝熱管８Ａ〜８Ｃに等分割した場合について説明
したが、これに代り第１０図に示すように１本の
偏平伝熱管１７を大、小の通路断面積を有する２
本の偏平伝熱管１７Ａ，１７Ｂに分割し、あるい
は第１１図に示すように偏平伝熱管１７を仕切板
１８により大、小断面積を有する２通路１７Ｃ，
１７Ｄに区分しても同様な効果をうることができ
る。 In this embodiment, the case where one flat heat exchanger tube 8 is equally divided into three flat heat exchanger tubes 8A to 8C has been explained, but instead of this, one flat heat exchanger tube 17 is divided into three flat heat exchanger tubes 8A to 8C. , with a passage cross-sectional area of small 2
Alternatively, as shown in FIG. 11, the flat heat exchanger tube 17 can be divided into two passages 17C having large and small cross-sectional areas with a partition plate 18.
A similar effect can be obtained even by dividing into 17D.
以上説明したように、第１番目の発明によれ
ば、空気の吹出し温度をほぼ一様にし、快適性を
向上させることができ、第２番目の発明によれ
ば、第１番目の発明の効果に加え、冷媒側の圧力
損失を小さくできるとともに空気と冷媒との熱交
換能力を向上させることができる。 As explained above, according to the first invention, the air blowing temperature can be made almost uniform and comfort can be improved, and according to the second invention, the effect of the first invention can be achieved. In addition, the pressure loss on the refrigerant side can be reduced and the heat exchange ability between air and refrigerant can be improved.
第１図および第２図は従来のコルゲートフイン
熱交換器の斜視図および冷媒の流れの説明図、第
３図は第１図の偏平伝熱管の断面図、第４図は従
来品と本発明品の通路断面積の変化を示す図、第
５図は本発明のコルゲートフイン熱交換器の斜視
図、第６図は同実施例の偏平伝熱管の断面図、第
７図は同実施例の通路断面積の変化を示す図、第
８図および第９図は従来品および本発明品の吹出
し空気温度分布を説明する図、第１０図および第
１１図は本発明に使用される偏平伝熱管の変形例
を示す断面図である。
８Ａ〜８Ｃ……偏平伝熱管、１０……フイン、
１１Ａ，１１Ｂ……中間ヘツダ、１３……冷媒入
口ヘツダ、１４……冷媒出口ヘツダ。
Figures 1 and 2 are a perspective view of a conventional corrugated fin heat exchanger and an explanatory diagram of the flow of refrigerant, Figure 3 is a sectional view of the flat heat exchanger tube of Figure 1, and Figure 4 is a conventional product and the present invention. 5 is a perspective view of a corrugated fin heat exchanger of the present invention, FIG. 6 is a sectional view of a flat heat exchanger tube of the same embodiment, and FIG. 7 is a cross-sectional view of a flat heat exchanger tube of the same embodiment. Figures 8 and 9 are diagrams showing the change in passage cross-sectional area, Figures 8 and 9 are diagrams explaining the temperature distribution of the blown air of the conventional product and the product of the present invention, and Figures 10 and 11 are the flat heat exchanger tubes used in the present invention. It is a sectional view showing a modification of . 8A to 8C... flat heat exchanger tube, 10... fin,
11A, 11B... intermediate header, 13... refrigerant inlet header, 14... refrigerant outlet header.
Claims (1)
垂直に蛇行状フインを介設してなるコルゲートフ
イン熱交換器において、前記偏平伝熱管を空気流
れの方向に沿つて上流側と下流側に分割すると共
に、これらの分割偏平伝熱管の両端に中間ヘツダ
をそれぞれ取付けて上、下流の偏平伝熱管を連結
し、一方前記分割偏平伝熱管のうち一部の分割偏
平伝熱管の蛇行部中間に冷媒入口ヘツダを、残部
の分割偏平伝熱管の蛇行部中間に冷媒出口ヘツダ
をそれぞれ取付けたことを特徴とするコルゲート
フイン熱交換器。 ２ 蛇行状偏平伝熱管の蛇行部に前記伝熱管と垂
直方向に蛇行状フインを介設してなるコルゲート
フイン熱交換器において、前記偏平伝熱管を空気
流れの方向に沿つて大、小の通路断面積を有する
ように分割し、この分割された偏平伝熱管の両端
に中間ヘツダをそれぞれ取付けて上、下流の偏平
伝熱管を連結し、一方、その蛇行部中間の分割偏
平伝熱管の一方に冷媒入口ヘツダを、他方に冷媒
出口ヘツダをそれぞれ取付けたことを特徴とする
コルゲートフイン熱交換器。[Scope of Claims] 1. In a corrugated fin heat exchanger in which meandering fins are interposed in the meandering portion of a meandering flat heat exchanger tube perpendicularly to the heat exchanger tube, the flat heat exchanger tube is arranged along the direction of air flow. At the same time, intermediate headers are attached to both ends of these divided flat heat exchanger tubes to connect the upper and downstream flat heat exchanger tubes. A corrugated fin heat exchanger characterized in that a refrigerant inlet header is attached to the middle of the meandering part of the heat exchanger tube, and a refrigerant outlet header is attached to the middle of the meandering part of the remaining divided flat heat exchanger tubes. 2. In a corrugated fin heat exchanger in which meandering fins are interposed in the meandering portion of a meandering flat heat exchanger tube in a direction perpendicular to the heat exchanger tube, the flat heat exchanger tube is provided with large and small passages along the direction of air flow. The upper and downstream flat heat exchanger tubes are connected by attaching intermediate headers to both ends of the divided flat heat exchanger tubes. A corrugated fin heat exchanger characterized in that a refrigerant inlet header is attached to the other side, and a refrigerant outlet header is attached to the other side.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP14694480A JPS5773392A (en) | 1980-10-22 | 1980-10-22 | Corrugated fin type heat exchanger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP14694480A JPS5773392A (en) | 1980-10-22 | 1980-10-22 | Corrugated fin type heat exchanger |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5773392A JPS5773392A (en) | 1982-05-08 |
| JPS6214751B2 true JPS6214751B2 (en) | 1987-04-03 |
Family
ID=15419097
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP14694480A Granted JPS5773392A (en) | 1980-10-22 | 1980-10-22 | Corrugated fin type heat exchanger |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5773392A (en) |
Families Citing this family (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6076786U (en) * | 1983-10-27 | 1985-05-29 | 昭和アルミニウム株式会社 | Heat exchanger |
| JPS61135173U (en) * | 1985-02-13 | 1986-08-22 | ||
| US4995453A (en) * | 1989-07-05 | 1991-02-26 | Signet Systems, Inc. | Multiple tube diameter heat exchanger circuit |
| US5368097A (en) * | 1992-10-27 | 1994-11-29 | Sanden Corporation | Heat exchanger |
| US6185957B1 (en) * | 1999-09-07 | 2001-02-13 | Modine Manufacturing Company | Combined evaporator/accumulator/suctionline heat exchanger |
| JP3766016B2 (en) | 2001-02-07 | 2006-04-12 | カルソニックカンセイ株式会社 | Fuel cell heat exchanger |
| DE10248665A1 (en) * | 2002-10-18 | 2004-04-29 | Modine Manufacturing Co., Racine | Heat exchanger in serpentine design |
| BR0303172A (en) * | 2003-07-21 | 2005-04-05 | Multibras Eletrodomesticos Sa | Evaporator for refrigerator |
| JP2018048769A (en) * | 2016-09-21 | 2018-03-29 | 豊田通商株式会社 | Heat exchanger |
| CN106524594A (en) * | 2016-10-13 | 2017-03-22 | 杭州三花家电热管理系统有限公司 | Coil pipe type heat exchanger |
-
1980
- 1980-10-22 JP JP14694480A patent/JPS5773392A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5773392A (en) | 1982-05-08 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US20060054312A1 (en) | Evaporator using micro-channel tubes | |
| JPH0587752B2 (en) | ||
| US6431264B2 (en) | Heat exchanger with fluid-phase change | |
| KR100497847B1 (en) | Evaporator | |
| JPS6214751B2 (en) | ||
| AU2017444848B2 (en) | Heat exchanger and refrigeration cycle device | |
| JP2001221535A (en) | Refrigerant evaporator | |
| JPH04268128A (en) | Heat exchanger | |
| JP3367235B2 (en) | Refrigeration cycle of vehicle air conditioner | |
| JP3158509B2 (en) | Refrigerant condenser | |
| JPH02106697A (en) | Lamination type heat exchanger | |
| JPS62131195A (en) | Heat exchanger | |
| JPH0642885Y2 (en) | Refrigerator Evaporator | |
| JPH10170098A (en) | Laminated evaporator | |
| JPH01310297A (en) | Plate fin for heat exchanger and fin tube type heat exchanger | |
| JP2677420B2 (en) | Heat exchanger for refrigerant condenser | |
| JPS61191889A (en) | Heat exchanger | |
| JP2003222436A (en) | Heat exchanger for heat pump type air conditioner | |
| JP2001133076A (en) | Heat exchanger | |
| JPH085198A (en) | Air conditioning heat exchanger | |
| JPH04254170A (en) | Multiunit type refrigerant evaporator | |
| JPH07103609A (en) | Heat exchanger for freezing cycle | |
| JPH04263793A (en) | Heat exchanger | |
| JP2001141382A (en) | Air heat exchanger | |
| JPH02143094A (en) | Heat exchanger equipped with heat transfer tube |