JPH03137498A - Heat exchanger with liquid flowing means - Google Patents
Heat exchanger with liquid flowing meansInfo
- Publication number
- JPH03137498A JPH03137498A JP27493089A JP27493089A JPH03137498A JP H03137498 A JPH03137498 A JP H03137498A JP 27493089 A JP27493089 A JP 27493089A JP 27493089 A JP27493089 A JP 27493089A JP H03137498 A JPH03137498 A JP H03137498A
- Authority
- JP
- Japan
- Prior art keywords
- heat exchanger
- pipes
- fluid
- pipe
- 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.)
- Pending
Links
- 239000007788 liquid Substances 0.000 title abstract 3
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 38
- 239000012530 fluid Substances 0.000 claims abstract description 26
- 239000000463 material Substances 0.000 abstract description 16
- 238000009423 ventilation Methods 0.000 abstract description 10
- 229910052751 metal Inorganic materials 0.000 abstract description 7
- 239000002184 metal Substances 0.000 abstract description 7
- 229920005989 resin Polymers 0.000 abstract description 4
- 239000011347 resin Substances 0.000 abstract description 4
- 239000000919 ceramic Substances 0.000 abstract description 3
- 230000007423 decrease Effects 0.000 abstract description 2
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 6
- 229910052802 copper Inorganic materials 0.000 description 6
- 239000010949 copper Substances 0.000 description 6
- 238000005219 brazing Methods 0.000 description 5
- 239000000853 adhesive Substances 0.000 description 4
- 230000001070 adhesive effect Effects 0.000 description 4
- 230000000052 comparative effect Effects 0.000 description 4
- 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 3
- 238000000034 method Methods 0.000 description 3
- 239000003822 epoxy resin Substances 0.000 description 2
- 229920000647 polyepoxide Polymers 0.000 description 2
- 229910000679 solder Inorganic materials 0.000 description 2
- BQCADISMDOOEFD-UHFFFAOYSA-N Silver Chemical compound [Ag] BQCADISMDOOEFD-UHFFFAOYSA-N 0.000 description 1
- 239000000956 alloy Substances 0.000 description 1
- 229910045601 alloy Inorganic materials 0.000 description 1
- 229910052782 aluminium Inorganic materials 0.000 description 1
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 1
- 239000012298 atmosphere Substances 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 239000003795 chemical substances by application Substances 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000004744 fabric Substances 0.000 description 1
- 239000010408 film Substances 0.000 description 1
- 230000005660 hydrophilic surface Effects 0.000 description 1
- LQBJWKCYZGMFEV-UHFFFAOYSA-N lead tin Chemical compound [Sn].[Pb] LQBJWKCYZGMFEV-UHFFFAOYSA-N 0.000 description 1
- 238000005259 measurement Methods 0.000 description 1
- 239000004745 nonwoven fabric Substances 0.000 description 1
- 229910052709 silver Inorganic materials 0.000 description 1
- 239000004332 silver Substances 0.000 description 1
- 238000005476 soldering Methods 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- 239000002470 thermal conductor Substances 0.000 description 1
- 239000002759 woven fabric Substances 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
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は熱交換器に関する。より詳しくは熱交換効率の
よい熱交換器に関する。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a heat exchanger. More specifically, the present invention relates to a heat exchanger with high heat exchange efficiency.
〔従来の技術と発明が解決しようとする課題〕現在おも
に用いられている熱交換器の形状は管内流体と管外流体
との間の熱交換効率を高めるために管内流体用パイプの
外周にプレート上のフィンを取り付けたものであり、フ
ィン形状も使用目的や使用条件によりさまざまな種類の
ものが提案されており、より熱交換効率の高い熱交換器
が望まれている。こうした中で、最近ピンフィン型の熱
交換器が有望なものの一つと考えられている。[Prior art and problems to be solved by the invention] The shape of the heat exchanger mainly used at present has a plate on the outer periphery of the pipe for the fluid inside the pipe in order to increase the heat exchange efficiency between the fluid inside the pipe and the fluid outside the pipe. The above fins are attached, and various types of fin shapes have been proposed depending on the purpose and conditions of use, and a heat exchanger with higher heat exchange efficiency is desired. Under these circumstances, pin-fin type heat exchangers have recently been considered to be one of the most promising.
ピンフィン型熱交換器の管内流体用パイプの構成はプレ
ートフィン型と同様で段状に平行且つ等間隔でパイプが
配置されている。しかしパイプは偏平パイプであり、こ
の偏平パイプの偏平面と隣合った偏平パイプの偏平面に
垂直にピンフィンが配列されている。ピンフィン熱交換
器はコンデンサ、ラジェータ等の用途ではプレートフィ
ン型に比べて熱交換効率が優れているために熱交換器の
コンパクト化が可能である。しかし、エバポレータ、水
冷式熱交換器等の用途ではピンフィンの表面温度が大気
の露点以下となるためにピンフィンの表面に凝縮による
水滴が発生し、この水滴が水平に配置された偏平パイプ
の偏平面上に溜ることにより、通風抵抗が増大するため
著しく熱交換効率が低下する。この現象は熱交換器の性
能向上とコンパクト化のためにフィンピッチを狭くした
ピンフィン型熱交換器において特に顕著に現れる。本発
明は、このような欠点を克服して、優れた熱交換効率の
熱交換器を提供することを目的とする。The configuration of the fluid pipes in the pin-fin type heat exchanger is similar to that of the plate-fin type heat exchanger, and the pipes are arranged parallel to each other in a stepped manner and at equal intervals. However, the pipe is a flat pipe, and the pin fins are arranged perpendicularly to the flat plane of the flat pipe adjacent to the flat pipe. Pin-fin heat exchangers have better heat exchange efficiency than plate-fin heat exchangers in applications such as condensers and radiators, so they can be made more compact. However, in applications such as evaporators and water-cooled heat exchangers, the surface temperature of the pin fins is below the dew point of the atmosphere, causing water droplets to condense on the surface of the pin fins. By accumulating on the top, ventilation resistance increases and heat exchange efficiency decreases significantly. This phenomenon is particularly noticeable in pin-fin type heat exchangers in which the fin pitch is narrowed in order to improve the performance and make the heat exchanger more compact. The present invention aims to overcome these drawbacks and provide a heat exchanger with excellent heat exchange efficiency.
本発明は管内流体用パイプ間にピンフィンが配置されて
いる熱交換器において、積層された管内流体用パイプの
空気流の下流側の側面にパイプ間を接続する流水手段を
設けることを特徴とする。The present invention is a heat exchanger in which pin fins are arranged between the pipes for fluid in the pipes, and is characterized in that a water flow means for connecting the pipes is provided on the downstream side of the air flow of the stacked pipes for fluid in the pipes. .
以下本発明の一例を示す添付図面を参照して本発明を記
述する。The invention will now be described with reference to the accompanying drawings, which illustrate an example of the invention.
第1図、第2図は本発明の熱交換器の実施例を示す。1
は等間隔をあけて設けられた複数の管内流体用パイプで
あり、この管内流体用パイプ1と隣接する管内流体用パ
イプ1の間には複数のピンフィン2が互いに所定の間隔
をあけて平行に配置され、それぞれ管内流体用パイプl
の偏平部に固着されている。1 and 2 show an embodiment of the heat exchanger of the present invention. 1
are a plurality of pipes for fluid in a pipe provided at equal intervals, and a plurality of pin fins 2 are arranged in parallel with each other at a predetermined distance between the pipes for fluid in a pipe 1 and the pipes for fluid in a pipe adjacent to each other. arranged, respectively, pipes for fluid in the pipes l
It is fixed to the flat part of.
ここで管内流体用パイプ1及びピンフィン2に用いる線
状熱伝導体としては、銀、銅、アルミニウム等の純金属
あるいは合金または前金属にハンダメツキ、スズメツキ
等を施した金属等、熱伝導性のよい材料を用いることが
できるが、これらに限定されるものではない。Here, the linear thermal conductor used for the internal fluid pipe 1 and the pin fin 2 is a pure metal or alloy such as silver, copper, aluminum, or a metal with good thermal conductivity, such as a metal that has been soldered or tin-plated. Non-limiting materials can be used.
管内流体用パイプ1の構成としてはサーペンタイン型と
ヘッダ型及び各々を複合したものがある。The internal fluid pipe 1 may have a serpentine type, a header type, or a combination of each type.
サーペンタイン型は第1図に示すように、−本の直線状
の偏平パイプをS字状に屈曲させたものまたは直線状パ
イプと隣接する直線状パイプの両端を交互にU形状のベ
ンド3で接続した構造をいう。U型状ベンド3の断面形
状は特に限定しないが管内流体の圧力損失を小さくする
ためには円形のものを用いるとよい。As shown in Figure 1, the serpentine type is made by bending straight flat pipes into an S-shape, or connecting straight pipes and both ends of adjacent straight pipes alternately with U-shaped bends 3. It refers to the structure that Although the cross-sectional shape of the U-shaped bend 3 is not particularly limited, it is preferable to use a circular shape in order to reduce the pressure loss of the fluid within the pipe.
ヘッダ型は第2図に示すように、複数の直線状パイプの
両端を1対のマニホールド5に開口接続した構造を言う
。The header type refers to a structure in which both ends of a plurality of straight pipes are open-connected to a pair of manifolds 5, as shown in FIG.
管内流体用パイプ1とピンフィン2の接合はろう付によ
り行うが、このろう付に使うろう材はパイプ、ピンフィ
ンの材質により異なり、例えば銅を用いた場合、鉛−錫
を主成分とするはんだが好ましく、用いる材質により適
宜選定すればよく、あるいは熱伝導性のよい樹脂を用い
てもよい。The fluid pipe 1 and pin fin 2 are joined by brazing, but the brazing material used for this brazing differs depending on the material of the pipe and pin fin. For example, if copper is used, solder containing lead-tin as the main component may Preferably, the material may be appropriately selected depending on the material used, or a resin with good thermal conductivity may be used.
流水手段4としては金属、セラミック、樹脂等で温度に
よる形状変化をおこさないものが用いられるが、排水性
をよくするため表面に親水性を持つものまたは親水性を
付与したものが好ましい。The water flowing means 4 may be made of metal, ceramic, resin, or the like that does not change its shape due to temperature, but preferably has a hydrophilic surface or one whose surface has been imparted with hydrophilic properties in order to improve drainage.
さらに流水手段4にも熱交換をさせるため流水手段4と
してピンフィンと同様の材料を用いてもよい。Furthermore, in order to allow the water flow means 4 to exchange heat, the water flow means 4 may be made of the same material as the pin fin.
流水手段4としては棒状物、シート状物が用いられる。As the water flowing means 4, a rod-like object or a sheet-like object is used.
棒状物の断面形状は特に限定しないが通風抵抗を小さく
するためには円形のものを用いるとよい。シート状物は
織物、編物、不織布、フィルムに穴の開けたものが用い
られるが通風抵抗を小さくするためにシート状物の空隙
部の面積占有率が70%以上、好ましくは90%以上が
よい。The cross-sectional shape of the bar is not particularly limited, but it is preferable to use a circular bar in order to reduce ventilation resistance. The sheet-like material used is a woven fabric, knitted fabric, non-woven fabric, or film with holes, but in order to reduce ventilation resistance, the area occupation rate of the voids in the sheet-like material should be 70% or more, preferably 90% or more. .
流水手段は接着剤、はんだ付け、ろう付、熱接着、超音
波接着により管内流体用パイプの空気流の下流側の側面
に第3菌(A)および第3図(B)に示すように固着さ
れる。接着剤、はんだ、ろう材も排水性をよくするため
表面に親水性を持つものまたは親水性を付与したものが
好ましい。The water flowing means is fixed to the downstream side of the air flow of the pipe for internal fluid by adhesive, soldering, brazing, thermal bonding, or ultrasonic bonding as shown in Figure 3 (A) and Figure 3 (B). be done. Adhesives, solders, and brazing materials preferably have hydrophilic properties or have been imparted with hydrophilic properties in order to improve drainage.
第3図(C)は空気流の下流側の最前列のピンフィンの
近傍から流水手段4に通ずる水滴誘導手段6を設けた構
造を示すもので、これにより凝縮水の排水性がさらに向
上する。FIG. 3(C) shows a structure in which a water drop guiding means 6 is provided which communicates with the water flowing means 4 from the vicinity of the pin fin in the front row on the downstream side of the air flow, thereby further improving the drainage performance of condensed water.
水滴誘導手段6としては金属、セラミック、樹脂等で温
度による形状変化をおこさないものが用いられるが、排
水性をよくするため表面に親水性を持つものまたは親水
性を付与したものが好ましい。さらに水滴誘導手段6に
も熱交換をさせるため水滴誘導手段6としてピンフィン
と同様の金属を用いてもよい。The water droplet guiding means 6 may be made of metal, ceramic, resin, or the like that does not change its shape due to temperature, but preferably has a surface that is hydrophilic or has been imparted with hydrophilicity in order to improve drainage. Further, the water droplet guiding means 6 may be made of the same metal as the pin fin in order to cause heat exchange to occur in the water droplet guiding means 6 as well.
また水滴誘導手段6としてピンフィン近傍から流水手段
に向けてパイプに刻みを入れてもよい。Further, as the water drop guiding means 6, a notch may be made in the pipe from the vicinity of the pin fin toward the water flowing means.
上記のようにして構成した流水手段及び水滴誘導手段を
設けたピンフィン型熱交換器は従来のピンフィン型熱交
換器より凝縮水の排水性が良好なため通風抵抗を低くす
ることができる。The pin-fin type heat exchanger provided with the water flowing means and the water droplet guiding means configured as described above has better drainage of condensed water than the conventional pin-fin type heat exchanger, so that the ventilation resistance can be lowered.
次に本発明による熱交換器の実施例を示し、併せて比較
例の熱交換器を用いた場合の熱交換性能を示す。Next, examples of the heat exchanger according to the present invention will be shown, and the heat exchange performance when using a heat exchanger of a comparative example will also be shown.
実施例1
下記に示した条件で第1図に示すピンフィン熱交換器を
作る。Example 1 A pin fin heat exchanger shown in FIG. 1 was made under the conditions shown below.
・熱交換器タイプ サーペンタイン型・ピンフィ
ンの条件
材 質 銅
断面形状 円形
線 径 200/1mφピン高さ
h=15m田
入ロビンピッチ Pfx= 1.0印奥行ピンピッ
チ Pfz = 0.5 mm・直線状管内流体用
パイプ、U型状ベンドの条件材 質
銅
断面形状 偏平
長 径 18.0mm短 径
5.、Om田平坦部の幅 12
.0mm
パイプの長さ 200.0mm
バイブの段数 15段
・管内流体の条件 冷水(5℃)・流体手段の条
件
材 質 銅
形 状 円形断面の棒
円 径 1mmφ本 数
40本
ピッチ 5mm
取付方法 熱交換器の下流側でビンと平行に
取付
接着方法 エポキシ樹脂系接着剤実施例2
実施例1の熱交換器に下記に示した条件の水滴誘導手段
を設けた構造を実施例2とした。・Heat exchanger type Serpentine type ・Pin fin conditions Material Copper Cross-sectional shape Circular wire Diameter 200/1mφ Pin height
h = 15m Tairi Robin pitch Pfx = 1.0 mark depth pin pitch Pfz = 0.5 mm / Straight pipe for fluid in pipe, conditions for U-shaped bend Materials
Copper cross-sectional shape Flat length Diameter 18.0mm Minor diameter
5. , Width of Om field flat part 12
.. 0mm Length of pipe 200.0mm Number of stages of vibrator 15 stages / Conditions of fluid in the pipe Cold water (5℃) / Conditions of fluid means Material Copper Shape Rod with circular cross section Diameter 1mmφ Number of pipes
40 pieces pitch 5mm Mounting method Mount parallel to the bottle on the downstream side of the heat exchanger Adhesion method Epoxy resin adhesive Example 2 A structure in which the heat exchanger of Example 1 is provided with a water droplet guiding means under the conditions shown below. This was referred to as Example 2.
水滴誘導手段
材 質 銅
形 状 円形断面の棒
円 径 1mmφピッチ
5mm
接着方法 エポキシ樹脂系接着剤比較例
第4図(A)〜第4図(D)に示す構造を有する熱交換
器を作る。この比較例の熱交換器は実施例1の熱交換器
から流水手段を除去したものであり、その他の条件は実
施例1と同一である。Water droplet guide material Material: Copper Shape: Rod with circular cross section Diameter: 1mmφ pitch
5mm Adhesion method Comparative example of epoxy resin adhesive A heat exchanger having the structure shown in FIGS. 4(A) to 4(D) is made. The heat exchanger of this comparative example was obtained by removing the water flow means from the heat exchanger of Example 1, and the other conditions were the same as those of Example 1.
前記実施例及び比較例の熱交換器について熱通過率及び
通風抵抗を測定した。The heat transfer rate and ventilation resistance of the heat exchangers of the Examples and Comparative Examples were measured.
測定に用いる装置は第5図に示す吸引型風洞装置であり
、測定する熱交換器101の流路断面は3001111
11X 3001+1111ある。矢印106の方向に
流れる空気の風量は熱線風速計104 (@日吉製11
YBRIDANεMOMETERDP70C)を用いて
風速を測定し、流路断面と風速値で求め、熱交換器の通
風抵抗は熱交換器の前後の静圧差をマノメータ105を
用いて圧力損失として測定した。熱交換器の管内流体用
バイブ内には、熱交換器人口102から冷水が流され、
熱交換器内で空気流と熱交換された冷水が熱交換器出口
103から排出され流量計を経て水温コントローラに戻
る。The device used for the measurement is a suction type wind tunnel device shown in FIG. 5, and the cross section of the flow path of the heat exchanger 101 to be measured is 3001111.
There are 11X 3001+1111. The volume of air flowing in the direction of arrow 106 is measured using hot wire anemometer 104 (@Hiyoshi 11
The wind speed was measured using a YBRIDAN εMOMETER DP70C) and determined from the flow path cross section and the wind speed value, and the ventilation resistance of the heat exchanger was measured by measuring the static pressure difference before and after the heat exchanger as a pressure loss using a manometer 105. Cold water is flowed from the heat exchanger population 102 into the pipe fluid vibe of the heat exchanger,
The cold water that has undergone heat exchange with the air flow in the heat exchanger is discharged from the heat exchanger outlet 103 and returns to the water temperature controller via the flow meter.
前記冷水流量と熱交換器入口の冷水温度、出口の冷水温
度から水側熱交換量Qwを求め熱通過率Kを下式で求め
た。The water side heat exchange amount Qw was determined from the cold water flow rate, the cold water temperature at the inlet of the heat exchanger, and the cold water temperature at the outlet, and the heat transfer rate K was determined using the following formula.
K=Qw/(A・ΔQ)
ここでQwは水側熱交換量、Aは熱交換器全伝熱面積、
ΔQは空気側と冷水側の平均の温度差である。なお空気
流(25℃、60%RH)の風速は1 (m/5ec
)で測定した。K=Qw/(A・ΔQ) Here, Qw is the water side heat exchange amount, A is the total heat transfer area of the heat exchanger,
ΔQ is the average temperature difference between the air side and the cold water side. The wind speed of the air flow (25℃, 60%RH) is 1 (m/5ec
) was measured.
得られた結果を第1表に示す。The results obtained are shown in Table 1.
第1表より、本発明による熱交換器を用いることにより
、通風抵抗を抑えると共に伝熱性能が向上されることが
証明された。Table 1 proves that by using the heat exchanger according to the present invention, ventilation resistance can be suppressed and heat transfer performance can be improved.
第1表
〔発明の効果〕
本発明による熱交換器では、従来の熱交換器において凝
縮水滴によって生じていた通風抵抗が大幅に低減し、非
常に高い熱交換効率が得られ、その結果熱交換器のコン
パクト化が可能となる。Table 1 [Effects of the Invention] In the heat exchanger according to the present invention, the ventilation resistance caused by condensed water droplets in conventional heat exchangers is significantly reduced, and extremely high heat exchange efficiency is obtained, resulting in heat exchange The device can be made more compact.
第1図は本発明の熱交換器の一実施例の斜視図であり、
第2図は本発明の熱交換器の他の実施例の斜視図であり
、第3図(A)は第1図の熱交換器の正面図であり、第
3図(B)は第3図(A>の熱交換器の線A−A’によ
る断面図であり、第3図(C)は第3図(A)の熱交換
器に水滴誘導手段を設けた構造の線A−A’による断面
図であり、第4図(A)は従来のピンフィン熱交換器の
一実施例の斜視図であり、第4図(B)は第4図(A)
の熱交換器の正面図であり、第4図(C)は第4図(B
)の熱交換器の線A−A’による断面図であり、第4図
(D)は第4図(B)の熱交換器の線B−B’による断
面図であり、第5図は熱交換器の熱通過率を測定する装
置を示す正面図である。
1・・・管内流体用パイプ、
3・・・U形状ベンド、
5・・・マニホールド、
2・・・ピンフィン、
4・・・流水手段、
6・・・水滴誘導手段。
特許比願人
旭化成工業株式会社
特許出願代理人FIG. 1 is a perspective view of an embodiment of the heat exchanger of the present invention,
2 is a perspective view of another embodiment of the heat exchanger of the present invention, FIG. 3(A) is a front view of the heat exchanger of FIG. 1, and FIG. 3(B) is a perspective view of the heat exchanger of the present invention. FIG. 3(C) is a cross-sectional view taken along line AA' of the heat exchanger in FIG. Fig. 4(A) is a perspective view of an embodiment of a conventional pin fin heat exchanger, and Fig. 4(B) is a sectional view of Fig. 4(A).
Fig. 4(C) is a front view of the heat exchanger of Fig. 4(B).
4(D) is a sectional view taken along line BB' of the heat exchanger in FIG. 4(B), and FIG. 5 is a sectional view taken along line BB' of the heat exchanger in FIG. FIG. 2 is a front view showing a device for measuring the heat transfer rate of a heat exchanger. DESCRIPTION OF SYMBOLS 1... Pipe for internal fluid, 3... U-shaped bend, 5... Manifold, 2... Pin fin, 4... Water flow means, 6... Water drop guiding means. Patent applicant Asahi Kasei Industries Co., Ltd. Patent application agent
Claims (1)
換器において、積層された管内流体用パイプの空気流の
下流側の側面にパイプ間を接続する流水手段を設けるこ
とを特徴とする流水手段付き熱交換器。A heat exchanger in which pin fins are arranged between the pipes for fluid in the pipes, characterized in that a water flow means for connecting the pipes is provided on the downstream side of the air flow of the stacked pipes for fluid in the pipes. Heat exchanger.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP27493089A JPH03137498A (en) | 1989-10-24 | 1989-10-24 | Heat exchanger with liquid flowing means |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP27493089A JPH03137498A (en) | 1989-10-24 | 1989-10-24 | Heat exchanger with liquid flowing means |
Publications (1)
Publication Number | Publication Date |
---|---|
JPH03137498A true JPH03137498A (en) | 1991-06-12 |
Family
ID=17548525
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP27493089A Pending JPH03137498A (en) | 1989-10-24 | 1989-10-24 | Heat exchanger with liquid flowing means |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPH03137498A (en) |
Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH05172483A (en) * | 1991-12-20 | 1993-07-09 | Toshiba Corp | Heat exchanger |
JP2007285673A (en) * | 2006-04-20 | 2007-11-01 | Yanmar Co Ltd | Drain structure for corrugated type heat exchanger |
JP2008039322A (en) * | 2006-08-08 | 2008-02-21 | Univ Of Tokyo | Heat exchanger and heat exchange apparatus having the same |
JP2010255916A (en) * | 2009-04-24 | 2010-11-11 | Sharp Corp | Heat exchanger and air conditioner mounted with the same |
JP2015190750A (en) * | 2014-03-31 | 2015-11-02 | 株式会社日立製作所 | Heat exchanger and heat transfer pipe of heat exchanger |
WO2017017814A1 (en) * | 2015-07-29 | 2017-02-02 | 三菱電機株式会社 | Heat exchanger and refrigeration cycle apparatus |
WO2019058471A1 (en) * | 2017-09-21 | 2019-03-28 | 三菱電機株式会社 | Heat exchanger, air conditioner outdoor unit, and air conditioner |
CN116379807A (en) * | 2023-06-02 | 2023-07-04 | 广东美的暖通设备有限公司 | Heat exchange assembly, micro-channel heat exchanger and air conditioner |
-
1989
- 1989-10-24 JP JP27493089A patent/JPH03137498A/en active Pending
Cited By (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH05172483A (en) * | 1991-12-20 | 1993-07-09 | Toshiba Corp | Heat exchanger |
JP2007285673A (en) * | 2006-04-20 | 2007-11-01 | Yanmar Co Ltd | Drain structure for corrugated type heat exchanger |
JP2008039322A (en) * | 2006-08-08 | 2008-02-21 | Univ Of Tokyo | Heat exchanger and heat exchange apparatus having the same |
JP2010255916A (en) * | 2009-04-24 | 2010-11-11 | Sharp Corp | Heat exchanger and air conditioner mounted with the same |
JP2015190750A (en) * | 2014-03-31 | 2015-11-02 | 株式会社日立製作所 | Heat exchanger and heat transfer pipe of heat exchanger |
US10126075B2 (en) | 2014-03-31 | 2018-11-13 | Hitachi, Ltd. | Heat exchanger and heat transfer tube of the heat exchanger |
WO2017017814A1 (en) * | 2015-07-29 | 2017-02-02 | 三菱電機株式会社 | Heat exchanger and refrigeration cycle apparatus |
JPWO2017017814A1 (en) * | 2015-07-29 | 2018-02-01 | 三菱電機株式会社 | Heat exchanger and refrigeration cycle apparatus |
WO2019058471A1 (en) * | 2017-09-21 | 2019-03-28 | 三菱電機株式会社 | Heat exchanger, air conditioner outdoor unit, and air conditioner |
JPWO2019058471A1 (en) * | 2017-09-21 | 2020-04-02 | 三菱電機株式会社 | Heat exchangers, outdoor units of air conditioners and air conditioners |
CN116379807A (en) * | 2023-06-02 | 2023-07-04 | 广东美的暖通设备有限公司 | Heat exchange assembly, micro-channel heat exchanger and air conditioner |
CN116379807B (en) * | 2023-06-02 | 2024-01-02 | 广东美的暖通设备有限公司 | Heat exchange assembly, micro-channel heat exchanger and air conditioner |
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