JPH11183076A - Heat exchanger - Google Patents
Heat exchangerInfo
- Publication number
- JPH11183076A JPH11183076A JP9358155A JP35815597A JPH11183076A JP H11183076 A JPH11183076 A JP H11183076A JP 9358155 A JP9358155 A JP 9358155A JP 35815597 A JP35815597 A JP 35815597A JP H11183076 A JPH11183076 A JP H11183076A
- Authority
- JP
- Japan
- Prior art keywords
- fin
- heat exchanger
- pipe
- fins
- air
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- 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
- F28F1/24—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 and extending transversely
- F28F1/32—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 and extending transversely the means having portions engaging further tubular elements
- F28F1/325—Fins with openings
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、熱交換器に関し、
特に冷房・暖房兼用の空気調和機に用いるに好適な熱交
換器に関する。The present invention relates to a heat exchanger,
Particularly, the present invention relates to a heat exchanger suitable for use in an air conditioner for both cooling and heating.
【０００２】[0002]
【従来の技術】図６は、空気調和器の室内ユニットの例
を示す断面図であって、該室内ユニット１は、吸込グリ
ル２、エアフィルタ３、ケーシング４、３個の熱交換器
５とドレンパン６ａと６ｃ、タンジェンシャルファン
７、ルーバ８及びフラップ９から構成されている。2. Description of the Related Art FIG. 6 is a sectional view showing an example of an indoor unit of an air conditioner. The indoor unit 1 includes a suction grill 2, an air filter 3, a casing 4, three heat exchangers 5, It comprises drain pans 6a and 6c, a tangential fan 7, a louver 8 and a flap 9.
【０００３】空気調和機が冷房運転された時、室内ユニ
ット１のタンジェンシャルファン７が回転し、室内の空
気は吸込グリル２、エアフィルタ３、熱交換器５を通っ
て冷やされ、ルーバ８、フラップ９で風向を決められ室
内に吹出される。室外ユニット（図示せず）の圧縮機で
圧縮され吐出された冷媒は、凝縮器で放熱し液化する。
この冷媒液は、室内ユニット１の熱交換器５に分配さ
れ、該熱交換器５に設けられたパイプ１１を通過しなが
ら吸熱し、パイプ１１の外側を流れる空気を冷却したあ
と再び室外ユニットの圧縮器に戻される。When the air conditioner is operated for cooling, the tangential fan 7 of the indoor unit 1 rotates, and the air in the room is cooled through the suction grill 2, the air filter 3 and the heat exchanger 5, and is cooled. The wind direction is determined by the flap 9 and the air is blown into the room. The refrigerant compressed and discharged by the compressor of the outdoor unit (not shown) radiates heat in the condenser and is liquefied.
This refrigerant liquid is distributed to the heat exchanger 5 of the indoor unit 1, absorbs heat while passing through the pipe 11 provided in the heat exchanger 5, cools the air flowing outside the pipe 11, and then returns to the outdoor unit. Returned to compressor.
【０００４】暖房運転時、室内ユニット１のタンジェン
シャルファン７が回転し、室内の空気は、吸込グリル
２、エアフィルタ３、熱交換器５を通って暖められて、
ルーバ８、フラップ９で風向を決められて室内に吹出さ
れる。室外ユニット（図示せず）の圧縮機から吐出され
た冷媒は、熱交換器５に分配され、該熱交換器５に設け
られたパイプ１１中で凝縮して空気を暖める。この冷媒
液は室外ユニットの室外熱交換器で蒸発し、屋外の空気
より吸熱したあと、ガス化して圧縮機に戻る。[0004] During the heating operation, the tangential fan 7 of the indoor unit 1 rotates, and the indoor air is heated through the suction grill 2, the air filter 3 and the heat exchanger 5,
The wind direction is determined by the louver 8 and the flap 9 and the air is blown into the room. The refrigerant discharged from the compressor of the outdoor unit (not shown) is distributed to the heat exchanger 5 and condenses in the pipe 11 provided in the heat exchanger 5 to warm the air. This refrigerant liquid evaporates in the outdoor heat exchanger of the outdoor unit, absorbs heat from outdoor air, gasifies and returns to the compressor.
【０００５】上記構成の空気調和機の室内ユニット１に
あっては、大きさ即ち外形寸法を変えずに大能力を得た
いというコンパクト化の要求があり、このため、熱交換
器５の性能向上を計る必要がある。図７に、熱交換器５
の外形図を示した。熱交換器５のパイプ１１は、肉厚
０．３〜０．４ｍｍの薄い銅管で構成されている。そし
て、パイプ１１の外側に、０．１〜０．２ｍｍの厚さの
アルミ材料等から成形されたフィン１２が介装されてい
る。このため、フィン１２には、図８に示すように、パ
イプ１１を挿入するためのフィン孔１４が形成されてい
る。また、パイプ１１とフィン１２の間の熱抵抗（接触
抵抗）を減らすために、パイプ１１を拡管し、フィン１
２との隙間をなくしている。[0005] In the indoor unit 1 of the air conditioner having the above structure, there is a demand for downsizing in order to obtain a large capacity without changing the size, that is, the external dimensions. Therefore, the performance of the heat exchanger 5 is improved. Need to be measured. FIG. 7 shows the heat exchanger 5
Is shown. The pipe 11 of the heat exchanger 5 is formed of a thin copper tube having a thickness of 0.3 to 0.4 mm. A fin 12 formed of an aluminum material or the like having a thickness of 0.1 to 0.2 mm is interposed outside the pipe 11. For this reason, the fin 12 has a fin hole 14 for inserting the pipe 11 as shown in FIG. In order to reduce the thermal resistance (contact resistance) between the pipe 11 and the fin 12, the pipe 11 is expanded and the fin 1
The gap with 2 has been eliminated.
【０００６】[0006]
【発明が解決しようとする課題】パイプ１１の内部に冷
媒が流れ、フィン１２には風が強制的に流されるが、空
気側の熱伝達率は、冷媒の熱伝達よりはるかに小さい。
従って、フィン１２として、図８〜図１０に示すような
形状と寸法を持つ切りおこし１６ａを設けて表面積を大
きくし、その形状を曲面として空気の流れを乱流とさせ
熱伝達率の向上を計ったフィン１２ａが用いられてい
る。Although the refrigerant flows inside the pipe 11 and the wind is forced to flow through the fins 12, the heat transfer coefficient on the air side is much smaller than the heat transfer of the refrigerant.
Therefore, the fins 12 are provided with cutouts 16a having the shapes and dimensions as shown in FIGS. 8 to 10 to increase the surface area, and make the airflow turbulent by making the shape a curved surface to improve the heat transfer coefficient. The measured fins 12a are used.
【０００７】また、熱交換器５をさらにコンパクトにす
るため、フィンとフィンとの間隙（フィンピッチ）を、
図９に示す現状の１．４ｍｍから１．３ｍｍと小さくす
ると、フィンの表面積は増加するが、空気側の圧力損失
が大きくなり、期待したほどの効果がでないという問題
があった。In order to make the heat exchanger 5 more compact, the gap between the fins (fin pitch) is
When the diameter is reduced from 1.3 mm to 1.3 mm as shown in FIG. 9, the surface area of the fin increases, but the pressure loss on the air side increases, and there is a problem that the expected effect is not obtained.
【０００８】本発明は前記事情に鑑みてなされたもの
で、フィンの間隙を小さくしても空気側の圧力損失が小
さく、このためコンパクト化が可能で、しかも熱交換効
率に優れた熱交換器を提供することを目的とする。[0008] The present invention has been made in view of the above circumstances, and even if the gap between the fins is reduced, the pressure loss on the air side is small, so that the heat exchanger can be made compact and has excellent heat exchange efficiency. The purpose is to provide.
【０００９】[0009]
【課題を解決するための手段】本発明課題は、冷媒が流
れるパイプと、該パイプがフィン孔に挿通されて、前記
冷媒と前記パイプの外側を流れる空気との間の熱交換効
率を高めるフィンとを備えた熱交換器において、前記フ
ィンは、フィンピッチが１．１ｍｍ〜１．４ｍｍで、フ
ィンには切りおこしが設けられ、該切りおこしは、隣り
合うフィン孔とフィン孔との間に間隔をおいて２本設け
られ、且つ、該切りおこしの幅をａとしたとき、前記間
隔が（４．５〜７）ａとされていることを特徴とする熱
交換器とすることで解決されるし、また冷媒が流れるパ
イプと、該パイプがフィン孔に挿通されて、前記冷媒と
前記パイプの外側を流れる空気との間の熱交換効率を高
めるフィンとを備えた熱交換器において、フィンには切
りおこしが設けられ、該切りおこしは、隣り合うフィン
孔とフィン孔との間に間隔をおいて平行に設けられ、且
つ前記切りおこしの延長線と前記フィン孔の中心同士を
結ぶ直線とのなす角度が１０゜〜３０゜であることを特
徴とする熱交換器とすることで解決される。SUMMARY OF THE INVENTION An object of the present invention is to provide a fin for improving the heat exchange efficiency between the refrigerant and air flowing outside the pipe by inserting the pipe through a fin hole. Wherein the fins have a fin pitch of 1.1 mm to 1.4 mm, and the fins are provided with cuts and raised, and the cuts and raised are formed between adjacent fin holes. It is possible to solve the problem by providing a heat exchanger characterized in that two spaces are provided at an interval and the width of the cut and raised portion is a, and the interval is (4.5 to 7) a. In addition, in a heat exchanger including a pipe through which a refrigerant flows, and a fin in which the pipe is inserted into a fin hole to increase heat exchange efficiency between the refrigerant and air flowing outside the pipe. The fins are cut and raised The cut and raised portion is provided in parallel with an interval between adjacent fin holes and has an angle of 10 ° between an extension of the cut and raised portion and a straight line connecting the centers of the fin holes. The problem can be solved by using a heat exchanger characterized by being up to 30 °.
【００１０】前記のように本発明の熱交換器は、フィン
ピッチが１．１ｍｍ〜１．４ｍｍとされているのでコン
パクト化が可能である。このようにコンパクト化して
も、隣り合うフィン孔とフィン孔との間に切りおこしが
間隔をおいて２本設けられ、且つ、これらの２本の切り
おこしは、切りおこしの幅をａとしたとき、前記間隔が
（４．５〜７）ａとなるように設けられているので、空
気側の圧力損失が大きくなり難く、また、フィンにより
空気が効果的に乱流とされるため熱交換効率に優れた熱
交換器である。As described above, the heat exchanger of the present invention has a fin pitch of 1.1 mm to 1.4 mm, so that the heat exchanger can be made compact. Even in such a compact size, two fins are provided between adjacent fin holes at an interval, and the width of the two fins is a. At this time, since the interval is set to be (4.5 to 7) a, the pressure loss on the air side is unlikely to increase, and the air is effectively turbulent by the fins, so that heat exchange is performed. It is a highly efficient heat exchanger.
【００１１】[0011]
【発明の実施の形態】本発明の熱交換器の第１実施形態
例は、図６に示す室内熱交換器５において、フィン１２
として、図１〜図３に示すフィン１２ｂを用いた熱交換
器である。なお、図１は、本発明の熱交換器に用いるフ
ィンの例を示す正面図であり、図２は図１に示すフィン
のＢ−Ｂ線断面図であり、図３は図１に示すフィンのＡ
矢視図である。本発明の熱交換器は、冷媒が流れるパイ
プ１１と、該パイプ１１がフィン孔１４に挿通されるこ
とで、パイプ１１の外側に接触して前記冷媒と前記パイ
プ１１の外側を流れる空気との間の熱交換効率を高める
フィン１２ｂとを備えた熱交換器であって、前記フィン
１２ｂは、フィンピッチｐが１．１ｍｍ〜１．４ｍｍ
で、フィン１２ｂには、図１に示すように、隣り合うフ
ィン孔１４の中心同士を結ぶ直線に平行に多数の切りお
こし１６ｂが設けられ、該切りおこし１６ｂは、隣り合
うフィン孔１４とフィン孔１４との間に間隔ｂをおいて
平行に２本ずつ並列して設けられ、且つ、切りおこし１
６ｂの幅をａ（ｍｍ）としたとき、前記間隔ｂ（ｍｍ）
が（４．５〜７）ａとされている熱交換器である。DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment of a heat exchanger according to the present invention is similar to the indoor heat exchanger 5 shown in FIG.
Is a heat exchanger using the fins 12b shown in FIGS. FIG. 1 is a front view showing an example of a fin used in the heat exchanger of the present invention, FIG. 2 is a sectional view taken along line BB of the fin shown in FIG. 1, and FIG. 3 is a fin shown in FIG. A
It is an arrow view. The heat exchanger of the present invention includes a pipe 11 through which a refrigerant flows, and a pipe 11 inserted into a fin hole 14, which contacts the outside of the pipe 11 to form a flow of the refrigerant and air flowing outside the pipe 11. And a fin 12b for improving the heat exchange efficiency between the fins 12b, wherein the fin 12b has a fin pitch p of 1.1 mm to 1.4 mm.
As shown in FIG. 1, the fin 12b is provided with a large number of cuts 16b in parallel with a straight line connecting the centers of the adjacent fin holes 14, and the cut 16b is formed between the fins 14 and the adjacent fin holes 14. The two holes are provided in parallel with each other with a space b between the holes 14 and cut and raised.
When the width of 6b is a (mm), the interval b (mm)
Is (4.5-7) a.
【００１２】フィンピッチｐが１．１ｍｍ未満である
と、空気抵抗が過大となり、風量、性能が低下し、また
騒音が大きくなる傾向にあり、１．４ｍｍを超えると、
熱交換効率が低下し易く、また熱交換器をコンパクトに
し難い。フィンピッチｐの望ましい範囲は、１．２５〜
１．３５ｍｍである。切りおこし１６ｂ同士の間隔ｂが
４．５ａ未満でれば、隣り合う２本の切りおこし１６ｂ
同士が接近し過ぎて、空気抵抗が大きく、フィンピッチ
を小さくするのに不適当であるとともに空気の流れを効
果的に乱流とし難い。また、切りおこし１６ｂ同士の間
隔ｂが７ａを超えて離れ過ぎると、空気の流れを効果的
に乱流とし難い。望ましくは、間隔ｂは（５〜６．５）
ａである。When the fin pitch p is less than 1.1 mm, the air resistance becomes excessive, the air volume and performance tend to decrease, and the noise tends to increase. When the fin pitch p exceeds 1.4 mm, the fin pitch p exceeds 1.4 mm.
The heat exchange efficiency tends to decrease, and it is difficult to make the heat exchanger compact. The desirable range of the fin pitch p is 1.25 to
1.35 mm. If the interval b between the cuts and raises 16b is less than 4.5a, two adjacent cuts and raises 16b
Because they are too close to each other, the air resistance is high, which is inappropriate for reducing the fin pitch, and it is difficult to effectively make the air flow turbulent. If the interval b between the cuts 16b is too large, exceeding 7a, it is difficult to effectively make the air flow turbulent. Preferably, the interval b is (5-6.5)
a.
【００１３】本発明において、フィン１２ｂのフィンピ
ッチｐは、例えば１．３ｍｍ程度とされる。また、図１
に示すごとく、縦に一列に並んでいるフィン孔１４の隣
り合うフィン孔１４とフィン孔１４との間に、切りおこ
し１６ｂ、１６ｂを２本づつ所定間隔ｂをおいて平行に
設けることで、フィン１２ｂには、多数の切りおこし１
６ｂを設ける。切りおこし１６ｂの幅ａは、例えば１．
２ｍｍ程度とされ、２本の切りおこし１６ｂと１６ｂと
の間の間隔ｂを、例えば６．８ｍｍとしたものを、フィ
ン１２ｂとして用いることができる。フィン１２ｂの切
りおこし１６ｂの長さは、図３に示すように、上側の長
さは８ｍｍ程度、下側の長さは１１ｍｍ程度とする。ま
た、切りおこし１６ｂの高さは、例えば、図３に示すよ
うに０．６ｍｍ程度とする。In the present invention, the fin pitch p of the fins 12b is, for example, about 1.3 mm. FIG.
As shown in FIG. 3, by providing two cuts 16b, 16b in parallel between the fin holes 14 adjacent to the fin holes 14 which are vertically arranged in a line at a predetermined interval b, two by two, The fins 12b have a large number of
6b is provided. The width a of the cut and raised portion 16b is, for example, 1.
A fin 12b having a length of about 2 mm and an interval b between the two cut-and-raised portions 16b, for example, 6.8 mm can be used. As shown in FIG. 3, the length of the cut-and-raised portion 16b of the fin 12b is about 8 mm at the upper side and about 11 mm at the lower side. The height of the cut and raised portion 16b is, for example, about 0.6 mm as shown in FIG.
【００１４】前記フィン１２ｂは、０．１〜０．２ｍｍ
の厚さのアルミ材料等から成形される。この際、アルミ
材料等をほぼコの字状及びほぼ逆コの字状に部分的に切
り裂き、これらの切断されていない部分を底辺として折
り曲げることで切りおこし１６ｂを形成できる。切りお
こし１６ｂは、フィン１２ｂとフィン１２ｂとの間を流
れる空気の流れを乱流とし、パイプ１１を流れる冷媒と
空気との間の熱交換効率を高めるために形成される。フ
ィンに形成された孔であるフィン孔１４には冷媒が通る
パイプ１１が挿通される。The fin 12b is 0.1 to 0.2 mm
Molded from an aluminum material or the like having a thickness of At this time, the aluminum material or the like is partially cut in a substantially U-shape or a substantially inverted U-shape, and the uncut portion is bent as a base to form the cut 16b. The cut and raised portions 16b are formed in order to make the flow of air flowing between the fins 12b and the fins 12b turbulent and increase the heat exchange efficiency between the refrigerant flowing through the pipe 11 and the air. The pipe 11 through which the refrigerant passes is inserted into the fin hole 14 which is a hole formed in the fin.
【００１５】図６に示す室内ユニット１の熱交換器５と
して前記フィン１２ｂを有する熱交換器を用いた場合、
室内の空気は吸込グリル２、エアフィルタ３を通り、フ
ィン１２ｂを有する熱交換器５により熱交換され、ルー
バ８、フラップ９で風向を決められ室内に吹出される。
この熱交換器５は１．１ｍｍ〜１．４ｍｍのフィンピッ
チｐでフィン１２ｂを多数有し、しかも、隣り合うパイ
プ１１とパイプ１１の間毎に間隔ｂをおいて２本ずつ切
りこみ１６ｂを有し、且つ、前記間隔ｂが切りおこし１
６ｂの幅をａとしたとき、（４．５〜７）ａであるの
で、コンパクトにでき、しかも冷媒と空気との間の熱交
換効率に優れる。When a heat exchanger having the fins 12b is used as the heat exchanger 5 of the indoor unit 1 shown in FIG.
The air in the room passes through the suction grill 2 and the air filter 3 and is heat-exchanged by the heat exchanger 5 having the fins 12b. The air direction is determined by the louvers 8 and the flaps 9, and the air is blown into the room.
This heat exchanger 5 has a large number of fins 12b at a fin pitch p of 1.1 mm to 1.4 mm, and has two cuts 16b at intervals b between adjacent pipes 11. And the distance b is 1
When the width of 6b is a, it is (4.5-7) a, so that it can be made compact and has excellent heat exchange efficiency between refrigerant and air.
【００１６】前記の第１実施形態例の熱交換器５を、１
列分のみ図４に断面図で示した。この熱交換器５を蒸発
器として使用したとき、パイプ１１の中の冷媒によって
空気が冷却され、パイプ１１の下に水滴１８がたれ下が
り、フィン１２ｂとフィン１２ｂとの間にはさまれて容
易に流下せずに、伝熱面積を減少させる傾向がある。The heat exchanger 5 of the first embodiment is
FIG. 4 is a sectional view of only the rows. When this heat exchanger 5 is used as an evaporator, the air is cooled by the refrigerant in the pipe 11 and the water droplet 18 drips below the pipe 11 and is easily trapped between the fins 12b. The heat transfer area tends to be reduced without flowing down the heat transfer area.
【００１７】この点を改良したのが、図５に示すフィン
１２ｃを有する熱交換器である。この第２実施形態例の
熱交換器は、図５に示すように、フィンの切りおこし１
６ｂを垂直、即ち、パイプ１１が挿通されるフィン孔１
４の中心同士を結ぶ直線に対して、切りおこし１６ｂの
底辺を平行とするのではなくて、切りおこし１６ｂの底
辺の延長線と、隣り合うフィン孔１４の中心同士を結ぶ
直線とがなす角度（鋭角側の角度）θを１０゜〜３０゜
としたものである。この点を省いては、図４に示す熱交
換器と構成が同じである。The heat exchanger having the fins 12c shown in FIG. 5 improves this point. As shown in FIG. 5, the heat exchanger of the second embodiment has a fin
6b is vertical, that is, the fin hole 1 through which the pipe 11 is inserted.
The angle formed by the extension of the bottom of the cut and raised portion 16b and the straight line connecting the centers of the adjacent fin holes 14 instead of making the base of the cut and raised portion 16b parallel to the straight line connecting the centers of the four fin holes 14 (Angle on the acute angle side) θ is set to 10 ° to 30 °. Except for this point, the configuration is the same as that of the heat exchanger shown in FIG.
【００１８】この第２実施形態例の熱交換器の場合、パ
イプ１１の中を流れる冷媒によりパイプ１１とフィン１
２ｃが冷却されて、空気中の水分が凝縮して特にパイプ
１１の下に水滴がたれ下がるが、フィン１２ｃの切りお
こし１６ｂに水滴がひっかかり、該切りおこし１６ｂに
沿って流下する。そのため、水滴は大きくならずに流下
するため、フィンの伝熱面積を減少させることはない。
従って、第２実施形態例の熱交換器は、コンパクトで、
しかも水滴によってはフィンの伝熱面積が減少し難い熱
交換器である。なお、角度θが１０゜未満であれば、フ
ィンとフィンとの間にはさまれて容易に流下しないし、
３０゜を越えると切りおこしの傾斜が小さいので水滴が
切りおこしに沿って流下し難くなるとともに、パイプ間
に配置するために切りおこしの長さが短くなってしま
う。In the case of the heat exchanger of the second embodiment, the refrigerant flowing through the pipe 11
2c is cooled, water in the air is condensed, and water drops are dropped particularly below the pipe 11, but the water drops are caught on the cuts 16b of the fins 12c and flow down along the cuts 16b. Therefore, the water droplets flow down without being large, and the heat transfer area of the fins is not reduced.
Therefore, the heat exchanger of the second embodiment is compact,
Moreover, the heat exchanger is such that the heat transfer area of the fins is hardly reduced depending on the water droplets. If the angle θ is less than 10 °, the fin is sandwiched between the fins and does not easily flow down.
When the angle exceeds 30 °, the inclination of the cut and raised portion is small, so that it is difficult for water droplets to flow down along the cut and raised portion, and the length of the cut and shortened portion is reduced due to the arrangement between pipes.
【００１９】[0019]
【実施例】フィンピッチｐが１．３ｍｍで、切りおこし
１６ｂの幅ａを１．２ｍｍとし、２本の切りおこし１６
ｂ同士の間隔ｂを６．８ｍｍとし、図１〜３に示す形状
と寸法を備えた、フィン１２ｂを準備した。そして、フ
ィン１２ｂを備えた本発明の熱交換器を用いて、空気調
和器の室内ユニットを作製した。一方、図８〜図１０で
示される形状と寸法を有する従来例のフィン１２ａを準
備した。該フィン１２ａは、図９に示すようにフィンピ
ッチが１．４ｍｍで、フィンの切りおこし１６ａは片面
側で数えて６ヶ所で、その幅は図８に示すように１．２
ｍｍであった。そして、フィン１２ａを備えた従来の熱
交換器を用いて空気調和器の室内ユニットを作製した。
更に、平板状フィンを備えた熱交換器を用いて室内ユニ
ットを作製した。これらの室内ユニットの性能の解析結
果を表１に示す。但し、フィン表面温度（Ｔw）は４０
゜Ｃ、流入空気温度（Ｔi）は２０゜Ｃとした。EXAMPLE The fin pitch p was 1.3 mm, the width a of the cut and raised 16b was 1.2 mm, and two cut and raised portions 16b were used.
Fins 12b were prepared having an interval b between 6.8 mm and having the shapes and dimensions shown in FIGS. And the indoor unit of the air conditioner was produced using the heat exchanger of this invention provided with the fin 12b. On the other hand, a conventional fin 12a having the shapes and dimensions shown in FIGS. 8 to 10 was prepared. The fins 12a have a fin pitch of 1.4 mm as shown in FIG. 9, and the fins 16a are six places counted on one side, and have a width of 1.2 as shown in FIG.
mm. And the indoor unit of the air conditioner was produced using the conventional heat exchanger provided with the fin 12a.
Further, an indoor unit was manufactured using a heat exchanger provided with flat fins. Table 1 shows the analysis results of the performance of these indoor units. However, the fin surface temperature (Tw) is 40
゜ C, the inflow air temperature (Ti) was set to 20 ° C.
【００２０】[0020]
【表１】 [Table 1]
【００２１】表１は凝縮器としての性能と空気の圧力損
失を示している。空気の熱交換器出口と入口の温度差Δ
Ｔは、風速１ｍ／ｓの場合を示している。従来のフィン
１２ａを用いた場合は１９．２１ｋに対し、フィン１２
ｂを用いた本発明は、フィン孔１４とフィン孔１４との
間に２本の切りおこし１６ｂを形成する等の簡素化され
た形状であるにもかかわらず１８．７６ｋで、平板状フ
ィン（プレートフィン）の１５．８５に対しては効率が
よかった。温度効率εで示すと、プレートフィン０．７
９に対し、従来のフィン１２ａを用いた場合が０．９６
で最も効率がよく、フィン１２ｂを用いた本発明は０．
９４で少し悪かった。これに対し風速１ｍ／ｓのときの
１列当たりの空気の圧力損失（列当圧損）ΔＰａはプレ
ートフィン２．８２Ｐａで最も少なく、従来のフィン１
２ａを用いた場合は７．８６Ｐａで最も大きく、フィン
１２ｂを用いた本発明の場合は５．１５Ｐａで、従来の
フィン１２ａを用いた場合よりも少なかった。Table 1 shows the performance as a condenser and the pressure loss of air. Temperature difference Δ between outlet and inlet of air heat exchanger
T indicates a case where the wind speed is 1 m / s. When the conventional fin 12a is used, the fin 12
The present invention using the b-type fins (18.76 k) has a simplified shape such as forming two cut-and-raised portions 16 b between the fin holes 14. The efficiency was good for 15.85 of the plate fin). In terms of temperature efficiency ε, plate fin 0.7
9 compared with 0.96 when the conventional fin 12a was used.
The present invention using the fins 12b is the most efficient.
94 was a bit bad. On the other hand, when the wind speed is 1 m / s, the pressure loss ΔPa of the air per row (row equivalent pressure loss) ΔPa is the smallest at 2.82 Pa of the plate fin,
The maximum was 7.86 Pa when 2a was used, and 5.15 Pa in the case of the present invention using the fin 12b, which was smaller than that when the conventional fin 12a was used.
【００２２】この従来のフィン１２ａと本発明に用いる
フィン１２ｂを同一のファンを使って送風し、ファンの
動力を同一にしたとき、その能力はフィン１２ｂを用い
た本発明の方が風量をだすことができ、熱交換器単体の
凝縮器としての能力（単体能力比）は従来のフィン１２
ａを用いた場合に比較して１８％増となった。また、ユ
ニットの暖房能力（ユニット能力比）としては３％の能
力増を計ることができた。When the conventional fin 12a and the fin 12b used in the present invention are blown using the same fan and the power of the fan is made the same, the capacity of the present invention using the fin 12b is larger than that of the fan. The capacity of the heat exchanger alone as a condenser (unit capacity ratio) is the same as that of the conventional fin 12.
a was increased by 18% as compared with the case where a was used. The heating capacity of the unit (unit capacity ratio) could be increased by 3%.
【００２３】[0023]
【発明の効果】以上説明したように、本発明によれば、
コンパクトで熱交換効率に優れた熱交換器が得られ、ま
た、凝縮した水滴によりフィンの伝熱面積が減少し難
い、熱交換効率に優れた熱交換器が得られる。As described above, according to the present invention,
A compact heat exchanger having excellent heat exchange efficiency can be obtained, and a heat exchanger having excellent heat exchange efficiency, in which the heat transfer area of the fin is hardly reduced due to condensed water droplets.
【図１】 本発明の熱交換器に用いるフィンの例を示す
正面図である。FIG. 1 is a front view showing an example of a fin used for a heat exchanger of the present invention.
【図２】 図１に示すフィンのＢ−Ｂ線断面図である。FIG. 2 is a sectional view taken along line BB of the fin shown in FIG.
【図３】 図１に示すフィンのＡ矢視図である。FIG. 3 is a view of the fin shown in FIG.
【図４】 本発明の熱交換器の例を示す要部断面図であ
る。FIG. 4 is a sectional view of a main part showing an example of the heat exchanger of the present invention.
【図５】 本発明の熱交換器の他の例を示す要部断面図
である。FIG. 5 is a sectional view of a main part showing another example of the heat exchanger of the present invention.
【図６】 空気調和器の室内ユニットの例を示す断面図
である。FIG. 6 is a cross-sectional view illustrating an example of an indoor unit of the air conditioner.
【図７】 室内ユニットに用いる熱交換器の例を示す断
面図である。FIG. 7 is a cross-sectional view illustrating an example of a heat exchanger used for an indoor unit.
【図８】 熱交換器に用いる従来例のフィンを示す正面
図である。FIG. 8 is a front view showing a conventional fin used for a heat exchanger.
【図９】 図８に示すフィンのＢ−Ｂ線断面図である。FIG. 9 is a sectional view of the fin shown in FIG. 8 taken along line BB.
【図１０】 図８に示すフィンのＡ矢視図である。FIG. 10 is a view of the fin shown in FIG.
１・・室内ユニット、２・・吸込グリル、３・・エアフ
ィルタ、４・・ケーシング、５・・熱交換器、６ａ、６
ｃ・・ドレインパン、７・・タンジェンシャルファン、
８・・ルーバ、９・・フラップ、１１・・パイプ（銅
管）、１２、１２ａ、１２ｂ、１２ｃ・・フィン、１４
・・フィン孔、１６、１６ａ、１６ｂ・・切りおこし、
１８・・水滴1. Indoor unit, 2. Suction grill, 3. Air filter, 4. Casing, 5. Heat exchanger, 6a, 6
c · · drain pan, 7 · tangential fan,
8. Louver, 9 flap, 11 pipe (copper tube), 12, 12a, 12b, 12c fin, 14
..Fin holes, 16, 16a, 16b
18. Water drops
Claims (3)
ン孔に挿通されて、前記冷媒と前記パイプの外側を流れ
る空気との間の熱交換効率を高めるフィンとを備えた熱
交換器において、前記フィンは、フィンピッチが１．１
ｍｍ〜１．４ｍｍで、フィンには切りおこしが設けら
れ、該切りおこしは隣り合うフィン孔とフィン孔との間
に間隔をおいて２本設けられ、且つ、該切りおこしの幅
をａとしたとき、前記間隔が（４．５〜７）ａとされて
いることを特徴とする熱交換器。1. A heat exchanger comprising: a pipe through which a refrigerant flows; and a fin that is inserted into a fin hole to increase a heat exchange efficiency between the refrigerant and air flowing outside the pipe. The fin has a fin pitch of 1.1.
mm to 1.4 mm, the fin is provided with a cut and raised, two such cuts are provided at an interval between adjacent fin holes, and the width of the cut and raised is a Wherein the interval is (4.5 to 7) a.
士を結ぶ直線とのなす角度が１０゜〜３０゜であること
を特徴とする請求項１記載の熱交換器。2. The heat exchanger according to claim 1, wherein an angle between an extension of the cutting and raising and a straight line connecting the centers of the fin holes is 10 ° to 30 °.
ン孔に挿通されて、前記冷媒と前記パイプの外側を流れ
る空気との間の熱交換効率を高めるフィンとを備えた熱
交換器において、フィンには切りおこしが設けられ、該
切りおこしは隣り合うフィン孔とフィン孔との間に間隔
をおいて平行に設けられ、且つ、前記切りおこしの延長
線と前記フィン孔の中心同士を結ぶ直線とのなす角度が
１０゜〜３０゜であることを特徴とする熱交換器。3. A heat exchanger comprising: a pipe through which a refrigerant flows; and a fin through which the pipe is inserted through a fin hole to increase a heat exchange efficiency between the refrigerant and air flowing outside the pipe. The fin is provided with a cut and raised portion, the cut and raised portion is provided in parallel with an interval between adjacent fin holes, and connects an extension line of the cut and raised portion and the centers of the fin holes. An angle between the straight line and the straight line is 10 ° to 30 °.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP35815597A JP3790350B2 (en) | 1997-12-25 | 1997-12-25 | Heat exchanger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP35815597A JP3790350B2 (en) | 1997-12-25 | 1997-12-25 | Heat exchanger |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH11183076A true JPH11183076A (en) | 1999-07-06 |
| JP3790350B2 JP3790350B2 (en) | 2006-06-28 |
Family
ID=18457833
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP35815597A Expired - Lifetime JP3790350B2 (en) | 1997-12-25 | 1997-12-25 | Heat exchanger |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3790350B2 (en) |
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2001053755A1 (en) * | 2000-01-20 | 2001-07-26 | Vent-Rite Valve Corporation | Modular climate control unit |
| JP2002318088A (en) * | 2001-04-20 | 2002-10-31 | Hitachi Ltd | Heat exchanger and air conditioner |
| JP2003035497A (en) * | 2001-07-24 | 2003-02-07 | Mitsubishi Electric Corp | Heat exchanger |
| JP2006308238A (en) * | 2005-04-28 | 2006-11-09 | Kobe Steel Ltd | Heat exchanger |
| JP2008202907A (en) * | 2007-02-22 | 2008-09-04 | Mitsubishi Heavy Ind Ltd | Heat exchanger |
| JP2009127882A (en) * | 2007-11-20 | 2009-06-11 | Mitsubishi Electric Corp | Heat exchanger, indoor unit, and air conditioner |
| JP2010008034A (en) * | 2008-05-26 | 2010-01-14 | Panasonic Corp | Fin tube type heat exchanger |
| JP2011169585A (en) * | 2011-04-28 | 2011-09-01 | Mitsubishi Electric Corp | Heat exchanger |
| JP2011185590A (en) * | 2010-02-09 | 2011-09-22 | Sumitomo Light Metal Ind Ltd | Aluminum fin for heat exchanger and heat exchanger |
| JP2013068372A (en) * | 2011-09-22 | 2013-04-18 | Kakio Seimitsu:Kk | Fin member with auxiliary fin |
| CN105091340A (en) * | 2014-05-09 | 2015-11-25 | 樱花卫厨（中国）股份有限公司 | Efficient heat absorption piece for heat exchanger of gas water heater |
-
1997
- 1997-12-25 JP JP35815597A patent/JP3790350B2/en not_active Expired - Lifetime
Cited By (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2001053755A1 (en) * | 2000-01-20 | 2001-07-26 | Vent-Rite Valve Corporation | Modular climate control unit |
| US6725915B2 (en) | 2000-01-20 | 2004-04-27 | Vent-Rite Valve Corp. | Method of adjusting room air temperature |
| US6742582B1 (en) | 2000-01-20 | 2004-06-01 | Vent-Rite Valve Corp. | Modular climate control unit |
| JP2002318088A (en) * | 2001-04-20 | 2002-10-31 | Hitachi Ltd | Heat exchanger and air conditioner |
| JP2003035497A (en) * | 2001-07-24 | 2003-02-07 | Mitsubishi Electric Corp | Heat exchanger |
| JP4536583B2 (en) * | 2005-04-28 | 2010-09-01 | 株式会社神戸製鋼所 | Heat exchanger |
| JP2006308238A (en) * | 2005-04-28 | 2006-11-09 | Kobe Steel Ltd | Heat exchanger |
| JP2008202907A (en) * | 2007-02-22 | 2008-09-04 | Mitsubishi Heavy Ind Ltd | Heat exchanger |
| JP2009127882A (en) * | 2007-11-20 | 2009-06-11 | Mitsubishi Electric Corp | Heat exchanger, indoor unit, and air conditioner |
| JP2010008034A (en) * | 2008-05-26 | 2010-01-14 | Panasonic Corp | Fin tube type heat exchanger |
| JP2011185590A (en) * | 2010-02-09 | 2011-09-22 | Sumitomo Light Metal Ind Ltd | Aluminum fin for heat exchanger and heat exchanger |
| JP2011169585A (en) * | 2011-04-28 | 2011-09-01 | Mitsubishi Electric Corp | Heat exchanger |
| JP2013068372A (en) * | 2011-09-22 | 2013-04-18 | Kakio Seimitsu:Kk | Fin member with auxiliary fin |
| CN105091340A (en) * | 2014-05-09 | 2015-11-25 | 樱花卫厨（中国）股份有限公司 | Efficient heat absorption piece for heat exchanger of gas water heater |
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