JPH0682031B2 - Air heat exchanger - Google Patents
Air heat exchangerInfo
- Publication number
- JPH0682031B2 JPH0682031B2 JP63288473A JP28847388A JPH0682031B2 JP H0682031 B2 JPH0682031 B2 JP H0682031B2 JP 63288473 A JP63288473 A JP 63288473A JP 28847388 A JP28847388 A JP 28847388A JP H0682031 B2 JPH0682031 B2 JP H0682031B2
- Authority
- JP
- Japan
- Prior art keywords
- air
- heat exchanger
- array
- tubes
- pipe
- 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 - Fee Related
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- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Description
【発明の詳細な説明】 （産業上の利用分野） 本発明は、安価であって製作も容易であり耐久性、保守
管理も容易であるとともに熱伝達率も良好な空気式熱交
換器に関する。Description: TECHNICAL FIELD The present invention relates to an air heat exchanger that is inexpensive, easy to manufacture, durable, easy to maintain and has a good heat transfer coefficient.
（従来の技術） 第７図は従来のフィンコイル型熱交換器の一例であっ
て、器体１内にフィン付管17が設けられており、器体１
の下方には空気取入口18、上方には空気流出口４、排気
ファン５が設けられ、またフィン付管17の上方に洗滌用
噴水管19、器体１の底部に排水管20を有している。(Prior Art) FIG. 7 shows an example of a conventional fin-coil heat exchanger, in which a finned pipe 17 is provided in the body 1.
Is provided with an air inlet 18 below, an air outlet 4 and an exhaust fan 5 above, a washing fountain pipe 19 above the finned pipe 17, and a drain pipe 20 at the bottom of the body 1. ing.
この従来例は冷凍又はヒートポンプサイクルに適用する
一例であって、サイクルをヒートポンプとして、すなわ
ちフィン付管17を蒸発器コイルとして作動させる場合、
圧縮機６から管系10を経て凝縮器７へ流入した冷媒は、
ここで液化して入口13から流入し出口14から流出する流
体に熱を放出する。液体冷媒は管系９を経て膨脹弁８で
減圧されてフィン付管17に入って蒸発し冷却作用を遂行
して再び圧縮機６に戻りサイクルを繰返す。This conventional example is an example applied to a refrigeration or heat pump cycle, and when the cycle is operated as a heat pump, that is, when the finned tube 17 is operated as an evaporator coil,
The refrigerant flowing from the compressor 6 through the pipe system 10 into the condenser 7 is
Here, heat is released to the fluid that is liquefied and flows in from the inlet 13 and flows out from the outlet 14. The liquid refrigerant is decompressed by the expansion valve 8 through the pipe system 9, enters the finned pipe 17, evaporates, performs a cooling action, and returns to the compressor 6 again to repeat the cycle.
一方排気ファン５により空気取入口18から流入した空気
はフィン付管17の配列管を流れて冷却され空気流出口４
から流出する。洗滌用噴水管19はフィン付管17の掃除及
び除霜のためのものである。On the other hand, the air flowing in from the air intake 18 by the exhaust fan 5 flows through the array pipe of the finned pipes 17 and is cooled, and the air outlet 4
Drained from. The cleaning fountain pipe 19 is for cleaning and defrosting the finned pipe 17.
このフィンコイル型の熱交換器は管の表面に多数のフィ
ンを植設したフィン付管を多数列、多段層に並べること
により空気との熱伝達率を良好にするように計っている
が、構造が複雑で製作も工数を要し保守管理も容易でな
いばかりでなく、熱伝達率も高くない欠点がある。なお
冷房目的の場合は、フィン付管17が空気式凝縮器になり
凝縮器７は冷水用蒸発器になるが配管系は省略する。This fin coil type heat exchanger is designed to improve the heat transfer coefficient with air by arranging a number of finned tubes with many fins planted on the surface of the tube in multiple rows and in multiple layers, Not only is the structure complicated, it requires man-hours for manufacturing, maintenance is not easy, and the heat transfer coefficient is not high. For cooling purposes, the finned pipe 17 serves as an air condenser and the condenser 7 serves as an evaporator for cold water, but the piping system is omitted.
また、第８図は、従来の流動層型熱交換器の一例の一部
の構造を示すものであって、メッシュ網23で支持された
ガラスビーズ等の流動粒子24中に裸直管25が設けられ、
裸直管25の下方にはスリット状の噴口27を有するスリッ
ト板26が設けられている。この装置では気流がメッシュ
網23を経てスリット板26の噴口27から裸直管25の下部に
向けて噴射され、流動粒子24を巻き込みながら裸直管25
の表面に固体接触をし、上下波浪運動と共に空気と接触
しながら熱交換が行われる。FIG. 8 shows a structure of a part of an example of a conventional fluidized bed heat exchanger, in which a bare straight pipe 25 is contained in a fluidized particle 24 such as glass beads supported by a mesh net 23. Is provided,
Below the bare straight pipe 25, a slit plate 26 having a slit-shaped nozzle 27 is provided. In this device, the airflow is jetted from the nozzle 27 of the slit plate 26 toward the lower part of the bare straight pipe 25 through the mesh net 23, and the bare straight pipe 25 is entrained while entraining the fluidized particles 24.
The solids are in contact with the surface of the, and the heat exchange is performed while contacting with the air as the wave moves up and down.
この装置は熱伝達率は非常に良くなるが、メッシュ網2
3、スリット状の噴口27、流動粒子24からなる流動層等
により風圧抵抗が大であって圧損が高いばかりでなく、
本装置を凝縮器や蒸発器として使用する場合には、コイ
ル面の霜除去の効果はあるものの戸外の気象条件に大き
く左右され、雨や雪に弱い欠点があり、また保守管理に
も出費がかさむ等の欠点を免れない。This device has a very good heat transfer coefficient,
3, not only the wind pressure resistance is large and the pressure loss is high due to the fluidized bed composed of the slit-shaped nozzle 27, the fluid particles 24, etc.
When this device is used as a condenser or evaporator, it has the effect of removing frost on the coil surface, but it is greatly affected by outdoor weather conditions, has the drawback of being weak in rain and snow, and is expensive to maintain. It suffers from drawbacks such as being bulky.
（発明が解決しようとする課題） 従来技術には前記のように種々の問題がある。本発明は
前記の欠点を解消する熱交換器を得ることを目的とする
ものである。(Problems to be Solved by the Invention) As described above, the related art has various problems. The present invention aims to obtain a heat exchanger that overcomes the above-mentioned drawbacks.
（課題を解決するための手段） 本発明の空気式熱交換器は前記の目的を達成するために 加熱又は冷却されるべき流体を流通させる複数の配列管
を設け、該配列管と適宜の間隔をおいて気流分配板を設
けるとともに、該分配板にスリット状に連続する噴口が
複数設けられていること、 該噴口の長手方向の中心線の各々が対応する前記配列管
の長手方向の中心線の各々とそれぞれ一致するように形
成され、前記各噴口からのジェット気流が前記各配列管
の対応するそれぞれの前記中心線に向けて噴射されるよ
うになっていること により構成されるものである。(Means for Solving the Problems) The air heat exchanger of the present invention is provided with a plurality of array pipes through which a fluid to be heated or cooled is circulated in order to achieve the above object, and the array pipes and an appropriate interval are provided. An airflow distribution plate is provided, and the distribution plate is provided with a plurality of continuous nozzles in the shape of slits. Each longitudinal centerline of the nozzles corresponds to the longitudinal centerline of the array pipe. Are formed so as to respectively coincide with each other, and the jet airflow from each of the nozzles is jetted toward the corresponding center line of each of the array pipes. .
（作用） 本発明の空気式熱交換器において各配列管の長手方向の
中心線に沿い設けられた気流分配板のスリット状に連続
する各噴口から気流が該配列管の前記中心線に向ってジ
ェット状に噴出して前記各配列管の周囲にコアンダ効果
に基く気流の流れが形成され、これにより気流と配列管
面ひいては管内の流体との熱伝達が良好に行われ、従来
のフィン付管に比べて４ないし５倍の断熱効率が得られ
るとともに保守管理も容易となる。(Operation) In the air heat exchanger of the present invention, the airflow is directed toward the center line of the array pipe from each of the slit-like continuous nozzles of the air flow distribution plate provided along the center line of the array pipe in the longitudinal direction. A jet-like jet is formed around each of the array pipes to form a flow of air flow based on the Coanda effect, which allows good heat transfer between the air flow and the array pipe surface, and thus the fluid in the pipes. The insulation efficiency is 4 to 5 times higher than that of, and maintenance management is easy.
（実施例） 本発明の空気式熱交換器の第１の実施例を第１図と第２
図により説明する。(Embodiment) FIG. 1 and FIG. 2 of the first embodiment of the air heat exchanger of the present invention.
It will be described with reference to the drawings.
１は空気式熱交換器の器体、２は加熱又は冷却されるべ
き流体を流通させる配列管としての裸管又はローフィン
管（以下、単に「裸管」と言う）、３は空気流入口、４
は空気流出口、５は排気ファン、9,10は冷凍機の管系、
６は圧縮機、７は凝縮器、８は膨脹弁、11は裸管２と適
宜の間隔をおいて設けられた気流分配板としてのスリッ
ト板、12はスリット状に連続する噴口である。各噴口12
の長手方向の中心線は対応する裸管２の長手方向の中心
線とそれぞれ一致する位置となるように形成されてい
る。Reference numeral 1 is a body of an air heat exchanger, 2 is a bare tube or a low fin tube (hereinafter, simply referred to as “bare tube”) as an array tube for circulating a fluid to be heated or cooled, 3 is an air inlet, Four
Is an air outlet, 5 is an exhaust fan, 9 and 10 are refrigerator pipe systems,
Reference numeral 6 is a compressor, 7 is a condenser, 8 is an expansion valve, 11 is a slit plate as an air flow distribution plate provided at an appropriate interval from the bare pipe 2, and 12 is a continuous nozzle in a slit shape. 12 nozzles
The center lines in the longitudinal direction of are formed at positions corresponding to the center lines of the corresponding bare tubes 2 in the longitudinal direction.
この実施例は空気式熱交換器を冷凍又はヒートポンプサ
イクルに適用する一例であって、サイクルをヒートポン
プとして、すなわち裸管２を蒸発器コイルとして作動さ
せる場合、圧縮機６から管系10を経て凝縮器７へ流入し
た冷媒は、ここで液化して入口13から流入し出口14から
流出する流体に熱を放出する。液体媒体は管系９を経て
膨脹弁８で減圧されて裸管２に入って蒸発し冷却作用を
遂行して再び圧縮機６に戻りサイクルを繰返す。This embodiment is an example in which the air heat exchanger is applied to a refrigeration or heat pump cycle, and when the cycle is operated as a heat pump, that is, when the bare tube 2 is operated as an evaporator coil, condensation is performed from the compressor 6 through the pipe system 10. The refrigerant that has flowed into the vessel 7 is liquefied here and releases heat to the fluid that flows in from the inlet 13 and flows out from the outlet 14. The liquid medium is decompressed by the expansion valve 8 through the pipe system 9, enters the bare pipe 2, evaporates, performs a cooling action, and returns to the compressor 6 again to repeat the cycle.
一方、排気ファン５により空気流入口３から流入した低
風圧の空気は裸管２の直下のスリット板11の多数の噴口
12からジェット気流として裸管２の下部に向けて噴射さ
れる。噴口12は第２図に示すように配列管である裸管２
の長手方向の中心線に沿った直下の位置に開孔されてい
るので、裸管２の全長に亘り、所謂コアンダ効果による
「空気の流れ」を裸管２の管周面に生じて裸管２を包絡
し、熱伝達率をきわめて良好にする。On the other hand, the air of low wind pressure that has flowed in from the air inlet 3 by the exhaust fan 5 has a large number of nozzles in the slit plate 11 directly below the bare pipe 2.
It is jetted from 12 as a jet stream toward the lower part of the bare tube 2. As shown in FIG. 2, the spout 12 is a bare pipe 2 which is an array pipe.
Since a hole is formed immediately below the center line in the longitudinal direction of the bare pipe 2, a "air flow" due to the so-called Coanda effect is generated on the circumferential surface of the bare pipe 2 over the entire length of the bare pipe 2. Envelopes 2 to make the heat transfer rate very good.
本実施例の熱伝達率Kkcal/m2.h.℃を従来のフィンコイ
ル型の熱交換器と％の比で比べると、フィンコイル型の
１に対して４〜５倍の高い熱伝達率が得られる。Comparing the heat transfer coefficient Kkcal / m 2 .h. ° C. of this embodiment with that of a conventional fin coil type heat exchanger in% ratio, the heat transfer coefficient is 4 to 5 times higher than 1 of the fin coil type. Is obtained.
また本実施例を流動層型の熱交換器と対比すると、全面
風速2m/secとして、フィンコイル型の熱伝達率の値は33
kcal/m2.h.℃であり、本実施例の130kcal/m2.h.℃に対
し、流動層型は160kcal/m2.h.℃と高いが、後者は流動
層と網があるため構造が複雑で空気抵抗が大であり、外
気天候に影響されることが大きく、管理も必要となる欠
点がある。これに対し本実施例は構造がきわめて単純で
前記のような欠点がない。Further, when the present example is compared with a fluidized bed type heat exchanger, the fin coil type heat transfer coefficient value is 33 when the overall wind speed is 2 m / sec.
a kcal / m 2 .h. ℃, relative 130kcal / m 2 .h. ℃ of this embodiment, the fluidized bed type 160kcal / m 2 .h. ℃ and high, the latter is fluidized layer and the network Therefore, the structure is complicated, the air resistance is large, it is greatly affected by the weather of the outside air, and there is a drawback that management is required. On the other hand, the present embodiment has a very simple structure and does not have the above-mentioned drawbacks.
第３図は本発明の空気式熱交換器の第２の実施例であ
る。第１の実施例は配列管としての裸管２群が一つの群
であったが、第３図においては３群にすなわち３段の層
に構成されている。そして各群の下部にはスリット状に
連続する噴口を有するスリット板11がそれぞれ設けられ
ており、空気流入口３から流入した空気は３段の層に分
流し、それぞれの層の配列管においてそれぞれ第１の実
施例と全く同様なコアンダ効果を発揮して良好な熱伝達
率が達成される。FIG. 3 shows a second embodiment of the air heat exchanger of the present invention. In the first embodiment, two groups of bare tubes as an array tube are one group, but in FIG. 3, they are composed of three groups, that is, three layers. Slit plates 11 each having a slit-shaped continuous nozzle are provided at the bottom of each group, and the air that has flowed in from the air inlet 3 is divided into three layers and arranged in each of the array tubes in each layer. The Coanda effect that is exactly the same as that of the first embodiment is exhibited, and a good heat transfer coefficient is achieved.
第４図は本発明の第３の実施例である。第１の実施例
（第１図）と空気の流れる方向が逆となっており、空気
は空気流入口4aから給気ファン5aによって供給され、器
体１内を下方へ流れて、空気流出口18から流出する。20
は排水管である。第１の実施例と空気の流れる方向は逆
であるが、その作用は同一である。FIG. 4 shows a third embodiment of the present invention. The flow direction of the air is opposite to that of the first embodiment (FIG. 1), and the air is supplied from the air inlet 4a by the air supply fan 5a and flows downward in the body 1 to the air outlet. Spill from 18. 20
Is a drainage pipe. The air flow direction is opposite to that of the first embodiment, but the operation is the same.
第５図は本発明の第４の実施例である。第２の実施例
（第３図）と空気の流れる方向が逆となっており、空気
は空気流入口4aから給気ファン5aによって供給され、器
体１内を下方へ流れ空気流出口18から流出する。第２の
実施例と空気の流れる方向は逆であるが、その作用は同
一である。FIG. 5 shows a fourth embodiment of the present invention. The flow direction of the air is opposite to that of the second embodiment (FIG. 3), and the air is supplied from the air inlet 4a by the air supply fan 5a and flows downward in the body 1 from the air outlet 18. leak. The air flow direction is opposite to that of the second embodiment, but the operation is the same.
第６図は本発明の第５の実施例である。本実施例では空
気式熱交換器１の器体が立方体に形成され、その４つの
側面及び底面に配列管としてのの裸管２が側面に沿って
垂直方向及び底面に沿って水平方向にそれぞれ設置され
るとともに、これらの裸管２の各内側にスリット板が適
宜の間隔をおいてそれぞれ設置され、かつこれらのスリ
ット板にはそれぞれ対面している各裸管２の中心線に沿
ってスリット状に連続する噴口12が形成されている。こ
の実施例によれば、器体内の空間の利用が有効に行われ
るので小さな寸法の器体によって熱交換量の大きなもの
が容易に得られる。FIG. 6 shows a fifth embodiment of the present invention. In this embodiment, the body of the air heat exchanger 1 is formed into a cube, and the bare tubes 2 as array tubes are provided on the four side surfaces and the bottom surface thereof along the side surfaces in the vertical direction and along the bottom surface in the horizontal direction, respectively. In addition to being installed, slit plates are installed inside each of the bare tubes 2 at appropriate intervals, and slits are provided along these slit plates along the center lines of the bare tubes 2 facing each other. The jet nozzle 12 is formed continuously. According to this embodiment, since the space in the body is effectively used, a body with a small size can easily obtain a large amount of heat exchange.
第９図に本発明の熱交換器と従来の流動層型及びフィン
コイル型の熱交換器の実施の一例について熱伝達率Ｋを
比較して示している。排気ファンによって熱交換器に流
入した空気の流速（前面風速）が0.1〜5.0m/secである
場合、従来技術と本発明の実施例では図のようなＫ値の
変化を示す。これによれば、流動層の粒子のメッシュが
297〜420μｍの流動層型の熱交換器のＫ値が最も高く、
粒子のメッシュが710〜1000μｍ及び1410〜2000μｍの
流動層型の熱交換器と本発明の空気式熱交換器のＫ値が
これに次ぎ、フィンコイル型の熱交換器のＫ値が最も低
いことが分る。FIG. 9 shows a comparison of the heat transfer coefficient K of an example of implementation of the heat exchanger of the present invention and the conventional fluidized bed type and fin coil type heat exchangers. When the flow velocity (front wind velocity) of the air that has flowed into the heat exchanger by the exhaust fan is 0.1 to 5.0 m / sec, the prior art and the embodiment of the present invention show a change in the K value as shown in the figure. According to this, the particle mesh of the fluidized bed
The K value of the fluidized bed type heat exchanger of 297 to 420 μm is the highest,
The K value of the fluidized-bed heat exchanger having a particle mesh of 710 to 1000 μm and 1410 to 2000 μm and the air heat exchanger of the present invention is the second highest, and that of the fin coil heat exchanger is the lowest. I understand.
なお本発明の実施例では噴口から噴射するジェット気流
の流速は30m/secとなる（熱交換器の全横断面積に対し
噴口の横断面積の総和が約８％として）。In the embodiment of the present invention, the flow velocity of the jet air stream jetted from the jet port is 30 m / sec (assuming that the total cross-sectional area of the jet port is about 8% of the total cross-sectional area of the heat exchanger).
（発明の効果） 本発明は加熱又は冷却されるべき流体を流通させる配列
管の長手方向の中心線に沿いスリット状に連続する噴口
の長手方向の中心線を位置させるように設けた気流分配
板を単に配置させるという構造であるので、従来技術に
比べ構造が単純であり、工作も簡単であるにも拘らず、
熱伝達率は良好である。フィンコイル型は内部の掃除に
道具がうまく入らずメンテナンスが困難であるが、本発
明では、汚れや埃りの洗滌も容易である。(Effects of the Invention) The present invention provides an airflow distribution plate provided so as to position the longitudinal center line of the nozzles continuous in a slit shape along the longitudinal center line of the array pipe through which the fluid to be heated or cooled flows. Since the structure is simply arranged, the structure is simple compared to the conventional technology and the work is easy,
The heat transfer coefficient is good. The fin-coil type is difficult to maintain because tools cannot be put in for cleaning the inside, but in the present invention, it is easy to clean dirt and dust.
更に冬期に外気熱源蒸発器に使用した場合、管の水滴を
本発明のジェット気流で吹き飛ばすことによって管下面
に付着する水滴の氷結することが防止できる。Further, when used in an outside air heat source evaporator in winter, it is possible to prevent freezing of water droplets attached to the lower surface of the tube by blowing away the water droplets of the tube with the jet stream of the present invention.
一方、流動層型のように圧損が大とならず、また流動層
型のものに比べて流動粒子材料や不蝕性メッシュ網など
が不要となる。また、流動層型の熱交換器は、流動粒子
を用いるので昼間や天候の良いときの作動には問題がな
いが、夜間とか悪天候等の気象条件の悪いときには流動
粒子の濡れに基く流動状態の不良化がおこるおそれがあ
り所謂、全天候型の熱交換器とは言い難いが、本発明の
空気式熱交換器は前記のような欠点がない。On the other hand, the pressure loss is not so large as in the fluidized bed type, and the fluidized particle material and the non-corrosive mesh net are not required as compared with the fluidized bed type. Further, since the fluidized bed type heat exchanger uses fluidized particles, there is no problem in operation during the daytime or when the weather is good, but when the weather conditions such as nighttime and bad weather are bad, the fluidized state based on the wetting of the fluidized particles Although it is hard to say that it is a so-called all-weather heat exchanger because it may be defective, the air heat exchanger of the present invention does not have the above-mentioned drawbacks.
第１図は本発明の空気式熱交換器の一実施例につきその
作動の全体を説明するフローシートダヤグラム、第２図
は第１図の実施例の要部の斜視図、第３図ないし第６図
はそれぞれ異なる実施例の要部の概略図、第７図は従来
技術であるフィンコイル型の熱交換器の作動の全体を説
明するフローシートダイヤグラム、第８図は従来技術の
流動層型の熱交換器の要部の説明図、第９図は本発明の
空気式熱交換器と従来技術の熱伝達率Ｋとの比較実験の
グラフである。 １……空気式熱交換器の器体、２……配列管としての裸
管又はローフィン管、11……気流分配板としてのスリッ
ト板、12……スリット状に連続する噴口。FIG. 1 is a flow sheet diagram for explaining the entire operation of an embodiment of the air heat exchanger of the present invention, and FIG. 2 is a perspective view of the essential parts of the embodiment of FIG. 1, FIGS. FIG. 6 is a schematic view of the essential parts of different embodiments, FIG. 7 is a flow sheet diagram for explaining the overall operation of a conventional fin coil type heat exchanger, and FIG. 8 is a conventional fluidized bed. FIG. 9 is an explanatory view of a main part of a heat exchanger of a mold, and FIG. 9 is a graph of a comparative experiment between the air heat exchanger of the present invention and the heat transfer coefficient K of the prior art. 1 ... Air heat exchanger body, 2 ... Bare tube or low fin tube as array tube, 11 ... Slit plate as airflow distribution plate, 12 ... Slit-like continuous nozzles.
Claims (4)
複数の配列管を設け、該配列管と適宜の間隔をおいて気
流分配板を設けるとともに、該分配板にスリット状に連
続する噴口が複数設けられており、該噴口の長手方向の
中心線の各々が対応する前記配列管の長手方向の中心線
の各々とそれぞれ一致するように形成され、前記各噴口
からのジェット気流が前記各配列管の対応するそれぞれ
の前記中心線に向けて噴射されるようにしたことを特徴
とする空気式熱交換器。1. A plurality of array pipes for circulating a fluid to be heated or cooled are provided, an air flow distribution plate is provided at an appropriate interval from the array pipes, and the distribution plate is provided with continuous nozzles in a slit shape. A plurality of nozzles are provided so that each of the longitudinal centerlines of the nozzles is aligned with each of the corresponding longitudinal centerlines of the array tubes, and the jet airflow from each nozzle is arranged in each of the arrays. An air heat exchanger, characterized in that the air is injected toward the respective corresponding center lines of the tubes.
成されている請求項１記載の空気式熱交換器。2. The air type heat exchanger according to claim 1, wherein the arrayed tubes are bare tubes or low fin tubes.
なる多数層の各群毎にスリット状に連続する噴口を有す
る気流分配板を有する請求項１又は２記載の空気式熱交
換器。3. The air-type heat generator according to claim 1 or 2, further comprising an airflow distribution plate having a plurality of groups of the arrayed pipes, and a plurality of multi-layered groups each having a slit-shaped continuous nozzle. Exchanger.
ないし３記載の空気式熱交換器。4. An array tube group is incorporated in a cube.
The air heat exchanger according to any one of claims 1 to 3.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP63288473A JPH0682031B2 (en) | 1988-11-15 | 1988-11-15 | Air heat exchanger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP63288473A JPH0682031B2 (en) | 1988-11-15 | 1988-11-15 | Air heat exchanger |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH02133793A JPH02133793A (en) | 1990-05-22 |
| JPH0682031B2 true JPH0682031B2 (en) | 1994-10-19 |
Family
ID=17730662
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP63288473A Expired - Fee Related JPH0682031B2 (en) | 1988-11-15 | 1988-11-15 | Air heat exchanger |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0682031B2 (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0441965U (en) * | 1990-07-25 | 1992-04-09 | ||
| JP5304826B2 (en) * | 2011-03-30 | 2013-10-02 | 新日鐵住金株式会社 | Carbon dioxide liquefaction device and carbon dioxide storage system |
| JP6218439B2 (en) * | 2013-06-04 | 2017-10-25 | 株式会社前川製作所 | Heat exchanger, belt conveyor cooling mechanism and cooling machine using the same |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5572789A (en) * | 1978-11-27 | 1980-05-31 | Kawasaki Heavy Ind Ltd | Method and apparatus for heat recovery |
-
1988
- 1988-11-15 JP JP63288473A patent/JPH0682031B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH02133793A (en) | 1990-05-22 |
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