JP3798108B2

JP3798108B2 - Heat exchanger

Info

Publication number: JP3798108B2
Application number: JP09193497A
Authority: JP
Inventors: 輝彦平; 宏範伊藤
Original assignee: 松下冷機株式会社
Priority date: 1997-04-10
Filing date: 1997-04-10
Publication date: 2006-07-19
Anticipated expiration: 2017-04-10
Also published as: JPH10288489A

Description

【０００１】
【発明の属する技術分野】
この発明は、空調・冷凍用に使用され、冷媒と空気などの流体間で熱の授受を行う熱交換器に関するものである。
【０００２】
【従来の技術】
従来の熱交換器としては特開平８−５４１９４号公報に示されているものがある。以下、図面を参照しながら上記従来の熱交換器を説明する。
【０００３】
図５は従来の熱交換器のフィンの平面図である。図５において１はフィン２に挿入されて密着された伝熱管で、内部を冷媒が流動する。
【０００４】
以上のように構成された熱交換器について、以下その動作を説明する。
伝熱管１の内部には冷媒が流動しており、熱交換器が凝縮器として用いられる際に伝熱管１ａ，１ｃ，１ｅより高温のガス冷媒が流入し、気流５と熱交換しながら、伝熱管１ｂ，１ｄ，１ｆより低温の液冷媒となって流出する。ここで冷媒の有する熱は伝熱管１、フィン２、伝熱管１へと順次伝えられる。そこで伝熱管１ａと１ｂ、伝熱管１ｃ，１ｄ、伝熱管１ｅ，１ｆとの列間にはフィン２に切断部３を設けて、冷媒出入り口伝熱管１間の熱伝導を防止している。これによって熱交換器から流出する冷媒を所定の温度まで低くするための伝熱管１の長さを短くできる。
【０００５】
【発明が解決しようとする課題】
しかしながら、上記従来の構成は切断部３の長さが短く、例えば、冷媒出口伝熱管１ｄは比較的高温の中間伝熱管１ｉから熱を奪って伝熱管１ｄ内を流動する冷媒の温度低下を妨げている。また、切断部３の長さを十分に長くした場合にはフィン２の大部分で列間を切断することとなり、フィン効率を低下させるために熱交換性能が低下する。
【０００６】
本発明は従来の課題を解決するもので、熱交換器から流出する冷媒を所定の温度まで低くするための伝熱管長さを著しく短くでき、かつ、フィン効率の低下を抑えて熱交換性能を大幅に向上できる熱交換器を提供することを目的とする。
【０００７】
【課題を解決するための手段】
この目的を達成するため本発明は、内部を冷媒が流動する連結された冷媒回路を構成する複数列で少なくとも１０段以上の複数段の伝熱管群と、前記伝熱管群が挿入され、その間を気流が流動する多数のフィンより成り、伝熱管の配管は気流に対して風下側の列に冷媒入り口伝熱管を設け、風上側の列に冷媒出口伝熱管を設けて構成され、前記冷媒入り口伝熱管と前記冷媒出口伝熱管との列間にある前記フィンの段方向にのみ、少なくとも高温のガス冷媒が流れる伝熱管と低温の過冷却液が流れる伝熱管との間の熱伝導を遮断するように複数段連続して切断される切断部を、複数段の切断されない部分を残して設けたのである。
【０００８】
これにより、冷媒を所定の温度まで低くするための伝熱管長さを著しく短くでき、かつ、フィン効率の低下を抑えて熱交換性能を向上できる。
【０００９】
また、本発明は、伝熱管の列ピッチＰｒと段ピッチＰｈとの比がＰｒ／Ｐｈ≦０．７に配列させたのである。
【００１０】
これにより、冷媒を所定の温度まで低くするための伝熱管長さを著しく短くでき、かつ、フィン効率の低下を抑えて、薄型の熱交換器で熱交換性能を大幅に向上できる。
【００１１】
また、本発明は、フィンに切り起こしが設けられ、切り起こしの占有面積Ａｓと全フィン面積Ａｆとの比がＡｓ／Ａｆ≦０．３としたのである。
【００１２】
これにより、冷媒を所定の温度まで低くするための伝熱管長さを著しく短くでき、かつ、フィン効率の低下を抑えて、低圧力損失で熱交換性能を大幅に向上できる。
【００１３】
また、本発明は、切断部の長さＬは冷媒出口伝熱管から冷媒の流れの反対方向に向けてＬ≧Ｐｈ×４としたのである。
【００１４】
これにより、冷媒を非常に低い所定の温度まで低くするための伝熱管長さを著しく短くでき、かつ、フィン効率の低下を抑えて熱交換性能を大幅に向上できる。
【００１５】
また、本発明の熱交換器は少なくとも１回以上折り曲げられ、下向き端部は列間に切断部を設けないとしたのである。
【００１６】
これにより、小さいスペースに大きな体積の熱交換器を収納でき、冷媒を所定の温度まで低くするための伝熱管長さを著しく短くでき、かつ、フィン効率の低下を抑えて、熱交換性能を大幅に向上できるとともに、この熱交換器を蒸発器として用いる際には、フィン表面への結露水が列間の切断部により阻害されず、なめらかに落下するために、低圧力損失にできる。
【００１７】
【発明の実施の形態】
本発明の請求項１に記載の発明は、
内部を冷媒が流動する連結された冷媒回路を構成する複数列で少なくとも１０段以上の複数段の伝熱管群と、前記伝熱管群が挿入され、その間を気流が流動する多数のフィンより成り、伝熱管の配管は気流に対して風下側の列に冷媒入り口伝熱管を設け、風上側の列に冷媒出口伝熱管を設けて構成され、前記冷媒入り口伝熱管と前記冷媒出口伝熱管との列間にある前記フィンの段方向にのみ、少なくとも高温のガス冷媒が流れる伝熱管と低温の過冷却液が流れる伝熱管との間の熱伝導を遮断するように複数段連続して切断される切断部を、複数段の切断されない部分を残して設けたものであり、冷媒入り口伝熱管と冷媒出口伝熱管を近接させて、その列間のみをフィンを熱的に遮断したことで、最小限の切断部長さで温度の著しく異なる伝熱管間の熱伝導を遮断でき、その他の切断されていない部分を多くとることで、フィン効率の低下を最小限に抑えることができるため、冷媒を所定の温度まで低くするための伝熱管長さを著しく短くでき、熱交換性能を向上できる。
【００１８】
請求項２に記載の発明は、請求項１に記載の発明に、さらに、伝熱管の列ピッチＰｒと段ピッチＰｈとの比がＰｒ／Ｐｈ≦０．７に配列されたものであり、伝熱管が高密度に配列された薄型の熱交換器において冷媒を所定の温度まで低くするための伝熱管長さを著しく短くでき、熱交換性能を向上できる。
【００１９】
請求項３に記載の発明は、請求項１に記載の発明に、さらに、フィンには切り起こしが設けられ、切り起こしの占有面積Ａｓと全フィン面積Ａｆとの比がＡｓ／Ａｆ≦０．３であるものであり、切り起こしが多い場合にはフィンの熱伝達率が向上するとともに、気流の圧力損失が増大する。従って、切り起こしの占有面積はある一定量以上に増やさないのが望ましい。また、切り起こしが多い場合には切り起こしのための切断部が多くなりフィン効率が低下する。従って温度差の異なる伝熱管間の熱伝導は切り起こしによって阻害され、列間に切断部を設けることによるフィン効率の低下率も少なくなる。従って、切り起こしの占有面積を前記の通り一定量以下とし、前記入り口伝熱管及び前記出口伝熱管の列間にのみに連続した切断部を設けることで、気流の圧力損失を小さく、熱交換性能も向上できる。
【００２０】
請求項４に記載の発明は、請求項１に記載の発明に、さらに、切断部の長さＬは冷媒出口伝熱管から冷媒の流れの反対方向に向けてＬ≧Ｐｈ×４としたものであり、凝縮器として用いる場合に冷媒が過冷却液となる領域を列間で切断することで、過冷却液全域への熱の流入を防止できるため、さらに熱交換性能を向上できる。
【００２１】
請求項５に記載の発明は、請求項１に記載の発明に、さらに、少なくとも１回以上折り曲げられ、下向き端部は列間に切断部を設けていないとしたものであり、熱交換器を蒸発器として用いた場合には、下向き端部において結露水の排出を列間の切断部で阻害することがないため、気流の圧力損失の増大を抑えて、凝縮器として用いる場合も、蒸発器として用いる場合も熱交換性能を向上できる。
【００２２】
【実施例】
以下、本発明による熱交換器の実施例について、図面を参照しながら説明する。
【００２３】
図１は、本発明の実施例によるフィンの平面図である。図２は、同実施例の熱交換器の斜視図である。図３は同実施例の冷媒回路図である。
【００２４】
図１，図２において、１１は伝熱管で、段ピッチＰｈと列ピッチＰｒによって２列１４段に配列され、図３に示す通り冷媒回路を構成している。１１ａ，１１ｂは冷媒入り口伝熱管で気流１５に対して後列側にある。１１ｃは冷媒出口伝熱管で気流１５に対して前列側にある。
【００２５】
１２は伝熱管１１が挿入密着されたフィンで、伝熱管１１ａ，１１ｂと１１ｃとの間に連続した切断部１３を長さＬ≒Ｐｈ×６で設けている。またフィン１２には切り起こし１４をフィン１２の面積Ａｆに対して切り起こし１４の占有面積ＡｓがＡｓ／Ａｆ＝０．１７で設けている。
【００２６】
１６は熱交換器で、主にはフィン１２と伝熱管１１で構成されており、略Λ状に折り曲げ、切り離している。
【００２７】
以上のように構成された熱交換器１６について、以下その動作を説明する。
まず、熱交換器１６が凝縮器として用いられる場合について説明する。
【００２８】
伝熱管１１ａ，１１ｂから流入した高温高圧ガス冷媒はフィン１２を介して気流１５に放熱しながら、ほぼ一定温度の気液二相冷媒、低温の過冷却液冷媒となって伝熱管１１ｃから流出する。このとき、冷媒は伝熱管１１ｄから伝熱管１１ｃの間で過冷却液となっている。
【００２９】
このとき、フィン１２には切り起こし１４を設けているために、フィン効率を著しく低下させることなく、かつ、気流１５の圧力損失を著しく増大させることなく、効率よく熱交換性能を向上させている。また、切断部１３によって、高温のガス冷媒が流れる伝熱管１１ａ，１１ｂと低温の過冷却液伝熱管１１ｄ〜１１ｃの間の熱伝導を遮断できるため、冷媒を所定の温度まで低くするための伝熱管１１の長さを著しく短くでき、熱交換性能を向上できる。その他の切断されていない部分を多くとることで、フィン効率の低下を最小限に抑えることができる。
【００３０】
また、段ピッチＰｈと列ピッチＰｒとの比がＰｒ／Ｐｈ＝０．６であるために薄型の熱交換器１６を構成できている。ここで、特開平２−１６６３９４号公報に示された、列間を切断した場合のフィン効率についての特性図を図４に示す。図に示す通り、Ｐｒ／Ｐｈ≦０．７以下の場合に列間を分断するとフィン効率が大きく低下する。従って本実施例では冷媒温度のほぼ同じ伝熱管１１間では列間を切断することなく、フィン効率の低下を防止しているために、この部分での熱交換性能の低下がない。
【００３１】
つぎに、熱交換器１６が蒸発器として用いられる場合について説明する。
気流１５が冷却されながらフィン１２の表面に付着した結露水は熱交換器１６の下方向に落下する。本実施例においては、フィン１２の両下端部近傍は列間に切断部１３を設けていないために、結露水の上方よりの落下を妨げることがなく、気流１５の圧力損失を最小限に抑えることができる。
【００３２】
【発明の効果】
以上説明したように請求項１に記載の発明は、内部を冷媒が流動する連結された冷媒回路を構成する複数列で少なくとも１０段以上の複数段の伝熱管群と、前記伝熱管群が挿入され、その間を気流が流動する多数のフィンより成り、伝熱管の配管は気流に対して風下側の列に冷媒入り口伝熱管を設け、風上側の列に冷媒出口伝熱管を設けて構成され、前記冷媒入り口伝熱管と前記冷媒出口伝熱管との列間にある前記フィンの段方向にのみ、少なくとも高温のガス冷媒が流れる伝熱管と低温の過冷却液が流れる伝熱管との間の熱伝導を遮断するように複数段連続して切断される切断部を、複数段の切断されない部分を残して設けたものであり、冷媒を所定の温度まで低くするための伝熱管長さを著しく短くでき、熱交換性能を向上できる。
【００３３】
請求項２に記載の発明は、請求項１に記載の発明に加えて、伝熱管の列ピッチＰｒと段ピッチＰｈとの比がＰｒ／Ｐｈ≦０．７に配列されたものであり、伝熱管が高密度に配列された薄型の熱交換器において熱交換性能を向上できる。
【００３４】
請求項３に記載の発明は、請求項１に記載の発明に加えて、フィンには切り起こしが設けられ、切り起こしの占有面積Ａｓと全フィン面積Ａｆとの比がＡｓ／Ａｆ≦０．３であるものであり、気流の圧力損失も小さく、熱交換性能も向上できる。
【００３５】
請求項４に記載の発明は、請求項１に記載の発明に加えて、切断部の長さＬは冷媒出口伝熱管から冷媒の流れの反対方向に向けてＬ≧Ｐｈ×４としたものであり、凝縮器として用いる場合に冷媒が過冷却液となる領域を列間で切断することで、さらに熱交換性能を向上できる。
【００３６】
請求項５に記載の発明は、請求項１に記載の発明に加えて、少なくとも１回以上折り曲げられ、下向き端部は列間に切断部を設けていないとしたものであり、熱交換器を蒸発器として用いた場合にも、気流の圧力損失の増大を抑えて、凝縮器として用いる場合も、蒸発器として用いる場合も熱交換性能を向上できる。
【図面の簡単な説明】
【図１】本発明による熱交換器の実施例のフィンの平面図
【図２】同実施例の熱交換器の斜視図
【図３】同実施例の熱交換器の冷媒回路図
【図４】同実施例の熱交換器の列間を切断した場合のフィン効率の特性図
【図５】従来の熱交換器のフィンの平面図
【符号の説明】
１１伝熱管
１１ａ，１１ｂ冷媒入り口伝熱管
１１ｃ冷媒出口伝熱管
１２フィン
１３切断部
１４切り起こし
１５気流
１６熱交換器[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a heat exchanger that is used for air conditioning and refrigeration and transfers heat between fluids such as refrigerant and air.
[0002]
[Prior art]
A conventional heat exchanger is disclosed in Japanese Patent Laid-Open No. 8-54194. Hereinafter, the conventional heat exchanger will be described with reference to the drawings.
[0003]
FIG. 5 is a plan view of fins of a conventional heat exchanger. In FIG. 5, reference numeral 1 denotes a heat transfer tube inserted into and closely attached to the fin 2, in which the refrigerant flows.
[0004]
The operation of the heat exchanger configured as described above will be described below.
A refrigerant flows inside the heat transfer tube 1, and when the heat exchanger is used as a condenser, a gas refrigerant having a temperature higher than that of the heat transfer tubes 1 a, 1 c, 1 e flows in and exchanges heat with the air flow 5, It flows out as a liquid refrigerant having a temperature lower than that of the heat transfer tubes 1b, 1d, and 1f. Here, the heat of the refrigerant is sequentially transmitted to the heat transfer tubes 1, the fins 2, and the heat transfer tubes 1. Therefore, the cut portions 3 are provided in the fins 2 between the rows of the heat transfer tubes 1a and 1b, the heat transfer tubes 1c and 1d, and the heat transfer tubes 1e and 1f to prevent heat conduction between the refrigerant inlet / outlet heat transfer tubes 1. Thereby, the length of the heat transfer tube 1 for lowering the refrigerant flowing out from the heat exchanger to a predetermined temperature can be shortened.
[0005]
[Problems to be solved by the invention]
However, the length of the cutting part 3 is short in the above-described conventional configuration. For example, the refrigerant outlet heat transfer tube 1d takes heat away from the relatively high temperature intermediate heat transfer tube 1i and prevents the temperature drop of the refrigerant flowing in the heat transfer tube 1d. ing. Moreover, when the length of the cutting part 3 is made sufficiently long, the rows are cut at most of the fins 2, and the heat exchange performance is lowered in order to reduce the fin efficiency.
[0006]
The present invention solves the conventional problem, and can significantly shorten the length of the heat transfer tube for lowering the refrigerant flowing out of the heat exchanger to a predetermined temperature, and suppresses the decrease in fin efficiency, thereby improving the heat exchange performance. It aims at providing the heat exchanger which can be improved significantly.
[0007]
[Means for Solving the Problems]
In order to achieve this object, the present invention includes a plurality of rows of heat transfer tube groups of at least 10 stages in a plurality of rows constituting a connected refrigerant circuit in which a refrigerant flows, and the heat transfer tube groups inserted between them. consists of a number of fins airflow flows, the pipe of the heat transfer tube is a refrigerant inlet heat transfer tubes arranged in columns on the leeward side of the air flow, the refrigerant outlet heat transfer tubes is formed by providing a column of the windward side, the refrigerant inlet Den Only in the step direction of the fin between the rows of the heat tubes and the refrigerant outlet heat transfer tubes, at least heat conduction between the heat transfer tubes through which the high-temperature gas refrigerant flows and the heat transfer tubes through which the low-temperature supercooling liquid flows is cut off. In other words, a plurality of cut portions that are continuously cut are provided, leaving a plurality of steps that are not cut .
[0008]
Thereby, the length of the heat transfer tube for lowering the refrigerant to a predetermined temperature can be remarkably shortened, and the heat exchange performance can be improved by suppressing the decrease in fin efficiency.
[0009]
In the present invention, the ratio between the row pitch Pr and the step pitch Ph of the heat transfer tubes is arranged so that Pr / Ph ≦ 0.7.
[0010]
Thereby, the length of the heat transfer tube for lowering the refrigerant to a predetermined temperature can be remarkably shortened, and the reduction in fin efficiency can be suppressed, and the heat exchange performance can be greatly improved with a thin heat exchanger.
[0011]
In the present invention, the fin is provided with a cut-and-raised portion, and the ratio of the cut-raised area As to the total fin area Af is As / Af ≦ 0.3.
[0012]
Thereby, the length of the heat transfer tube for lowering the refrigerant to a predetermined temperature can be remarkably shortened, and the decrease in fin efficiency can be suppressed, and the heat exchange performance can be greatly improved with low pressure loss.
[0013]
Further, according to the present invention, the length L of the cut portion is L ≧ Ph × 4 from the refrigerant outlet heat transfer tube in the direction opposite to the refrigerant flow.
[0014]
As a result, the length of the heat transfer tube for lowering the refrigerant to a very low predetermined temperature can be remarkably shortened, and the heat exchange performance can be greatly improved by suppressing the decrease in fin efficiency.
[0015]
Further, the heat exchanger of the present invention is bent at least once, and the downward end portion is not provided with a cutting portion between the rows.
[0016]
As a result, a large volume heat exchanger can be stored in a small space, the heat transfer tube length for reducing the refrigerant to a predetermined temperature can be remarkably shortened, and the decrease in fin efficiency can be suppressed, greatly increasing the heat exchange performance. In addition, when this heat exchanger is used as an evaporator, the condensed water on the fin surface is not hindered by the cut portions between the rows and falls smoothly, so that a low pressure loss can be achieved.
[0017]
DETAILED DESCRIPTION OF THE INVENTION
The invention described in claim 1 of the present invention
It is composed of a plurality of rows of heat transfer tube groups of at least 10 stages in a plurality of rows constituting a connected refrigerant circuit in which the refrigerant flows inside, and a plurality of fins into which the heat transfer tube groups are inserted, and airflow flows between them. The pipe of the heat transfer tube is configured by providing a refrigerant inlet heat transfer tube in a row on the leeward side with respect to the air flow, and providing a refrigerant outlet heat transfer tube in the row on the windward side, and a row of the refrigerant inlet heat transfer tube and the refrigerant outlet heat transfer tube Cutting that is continuously cut in a plurality of stages so as to cut off heat conduction between at least the heat transfer tube through which the high-temperature gas refrigerant flows and the heat transfer tube through which the low-temperature supercooled liquid flows, only in the step direction of the fins between them The part is provided by leaving a plurality of uncut portions , and the refrigerant inlet heat transfer tube and the refrigerant outlet heat transfer tube are brought close to each other, and the fins are thermally blocked only between the rows, thereby minimizing Heat transfer with significantly different temperatures depending on the cut length Since heat conduction between the two can be cut off, and a large number of other uncut parts can be taken, the decrease in fin efficiency can be minimized. It can be remarkably shortened and heat exchange performance can be improved.
[0018]
The invention according to claim 2 is the invention according to claim 1, wherein the ratio of the row pitch Pr to the step pitch Ph of the heat transfer tubes is arranged so that Pr / Ph ≦ 0.7. In a thin heat exchanger in which heat tubes are arranged at a high density, the heat transfer tube length for lowering the refrigerant to a predetermined temperature can be remarkably shortened, and the heat exchange performance can be improved.
[0019]
The invention according to claim 3 is the invention according to claim 1, wherein the fin is further provided with a cut-and-raised portion, and the ratio of the occupied area As of the raised portion and the total fin area Af is As / Af ≦ 0. When the number of cuts is large, the heat transfer coefficient of the fin is improved and the pressure loss of the airflow is increased. Therefore, it is desirable that the occupation area of the cut and raised does not increase beyond a certain amount. Moreover, when there are many cuts and raisings, the cutting part for cutting and raising will increase and fin efficiency will fall. Therefore, heat conduction between heat transfer tubes having different temperature differences is hindered by cutting and raising, and the rate of decrease in fin efficiency due to the provision of the cut portions between the rows is reduced. Therefore, the occupation area of the cut and raised is set to a certain amount or less as described above, and a continuous cutting portion is provided only between the rows of the inlet heat transfer tubes and the outlet heat transfer tubes, thereby reducing the pressure loss of the air flow and heat exchange performance. Can also be improved.
[0020]
The invention according to claim 4 is the same as that according to claim 1, wherein the length L of the cut portion is such that L ≧ Ph × 4 from the refrigerant outlet heat transfer tube in the opposite direction of the refrigerant flow. In addition, by cutting the region where the refrigerant becomes the supercooling liquid between the rows when used as a condenser, it is possible to prevent the heat from flowing into the entire supercooling liquid, thereby further improving the heat exchange performance.
[0021]
The invention according to claim 5 is the invention according to claim 1, wherein the invention is further bent at least once, and the downward end portion is not provided with a cut portion between the rows. When used as an evaporator, the condensate discharge at the downward end is not hindered by the cut part between the rows. The heat exchange performance can also be improved when used as a heat exchanger.
[0022]
【Example】
Embodiments of the heat exchanger according to the present invention will be described below with reference to the drawings.
[0023]
FIG. 1 is a plan view of a fin according to an embodiment of the present invention. FIG. 2 is a perspective view of the heat exchanger of the same embodiment. FIG. 3 is a refrigerant circuit diagram of the embodiment.
[0024]
1 and 2, reference numeral 11 denotes a heat transfer tube, which is arranged in two rows and 14 rows by a row pitch Ph and a row pitch Pr, and constitutes a refrigerant circuit as shown in FIG. Reference numerals 11a and 11b denote refrigerant inlet heat transfer tubes on the rear row side with respect to the air flow 15. 11c is a refrigerant | coolant exit heat exchanger tube, and exists in the front row side with respect to the airflow 15.
[0025]
12 is a fin in which the heat transfer tube 11 is inserted and adhered, and a continuous cutting portion 13 is provided between the heat transfer tubes 11a, 11b and 11c with a length L≈Ph × 6. Further, the fin 12 is provided with the cut-and-raised portion 14 with respect to the area Af of the fin 12 so that the occupied area As of As 14 is As / Af = 0.17.
[0026]
Reference numeral 16 denotes a heat exchanger mainly composed of fins 12 and heat transfer tubes 11, which are bent into a substantially Λ shape and separated.
[0027]
The operation of the heat exchanger 16 configured as described above will be described below.
First, the case where the heat exchanger 16 is used as a condenser will be described.
[0028]
The high-temperature and high-pressure gas refrigerant that has flowed in from the heat transfer tubes 11a and 11b radiates heat to the airflow 15 through the fins 12 and flows out from the heat transfer tube 11c as a substantially constant temperature gas-liquid two-phase refrigerant or low-temperature supercooled liquid refrigerant. . At this time, the refrigerant is a supercooled liquid between the heat transfer tube 11d and the heat transfer tube 11c.
[0029]
At this time, since the fins 12 are provided with the cut-and-raised parts 14, the heat exchange performance is efficiently improved without significantly reducing the fin efficiency and without significantly increasing the pressure loss of the air flow 15. . Moreover, since the cutting portion 13 can block heat conduction between the heat transfer tubes 11a and 11b through which the high-temperature gas refrigerant flows and the low-temperature supercooled liquid heat transfer tubes 11d to 11c, the transfer for lowering the refrigerant to a predetermined temperature is possible. The length of the heat pipe 11 can be remarkably shortened, and the heat exchange performance can be improved. By taking many other uncut portions, it is possible to minimize a decrease in fin efficiency.
[0030]
Further, since the ratio of the stage pitch Ph to the row pitch Pr is Pr / Ph = 0.6, the thin heat exchanger 16 can be configured. Here, FIG. 4 shows a characteristic diagram regarding fin efficiency in the case of cutting between rows, as disclosed in JP-A-2-166394. As shown in the figure, the fin efficiency is greatly reduced if the rows are separated when Pr / Ph ≦ 0.7 or less. Therefore, in this embodiment, the heat exchange performance is not lowered in this portion because the fin efficiency is prevented from being lowered without cutting the rows between the heat transfer tubes 11 having substantially the same refrigerant temperature.
[0031]
Next, a case where the heat exchanger 16 is used as an evaporator will be described.
Condensed water adhering to the surface of the fin 12 while the air flow 15 is cooled falls downward in the heat exchanger 16. In the present embodiment, the lower end portions of the fins 12 are not provided with the cutting portions 13 between the rows, so that the fall of the condensed water from above is not prevented, and the pressure loss of the airflow 15 is minimized. be able to.
[0032]
【The invention's effect】
As described above, according to the first aspect of the present invention, a plurality of heat transfer tube groups of at least 10 stages in a plurality of rows constituting a connected refrigerant circuit in which the refrigerant flows inside, and the heat transfer tube group are inserted. It is composed of a large number of fins through which the airflow flows, and the pipe of the heat transfer tube is configured by providing a refrigerant inlet heat transfer tube in the leeward row with respect to the airflow, and providing a refrigerant outlet heat transfer tube in the leeward row, Heat conduction between a heat transfer tube through which at least a high-temperature gas refrigerant flows and a heat transfer tube through which a low-temperature supercooled liquid flows only in the fin direction between the rows of the refrigerant inlet heat transfer tubes and the refrigerant outlet heat transfer tubes The cutting section that is continuously cut in a plurality of stages so as to cut off the heat is provided leaving the non-cut sections in a plurality of stages , and the length of the heat transfer tube for lowering the refrigerant to a predetermined temperature can be remarkably shortened. , Heat exchange performance can be improved.
[0033]
In addition to the invention described in claim 1, the invention described in claim 2 is such that the ratio of the row pitch Pr to the step pitch Ph of the heat transfer tubes is arranged so that Pr / Ph ≦ 0.7. Heat exchange performance can be improved in a thin heat exchanger in which heat tubes are arranged at high density.
[0034]
In the invention according to claim 3, in addition to the invention according to claim 1, the fin is provided with a cut and raised, and the ratio of the occupied area As of the cut and raised to the total fin area Af is As / Af ≦ 0. 3, the pressure loss of the airflow is small, and the heat exchange performance can be improved.
[0035]
In addition to the invention described in claim 1, the length L of the cutting part is such that L ≧ Ph × 4 from the refrigerant outlet heat transfer tube in the opposite direction of the refrigerant flow. In addition, the heat exchange performance can be further improved by cutting the region where the refrigerant becomes the supercooled liquid when used as a condenser, between the rows.
[0036]
In addition to the invention of claim 1, the invention according to claim 5 is bent at least once and the downward end portion is not provided with a cutting portion between the rows, and the heat exchanger is Even when used as an evaporator, an increase in air pressure loss can be suppressed, and heat exchange performance can be improved both when used as a condenser and as an evaporator.
[Brief description of the drawings]
FIG. 1 is a plan view of a fin of an embodiment of a heat exchanger according to the present invention. FIG. 2 is a perspective view of the heat exchanger of the embodiment. FIG. 3 is a refrigerant circuit diagram of the heat exchanger of the embodiment. [Characteristics of fin efficiency when the rows of heat exchangers of the same embodiment are cut] [FIG. 5] Plan view of fins of conventional heat exchanger [Explanation of symbols]
11 Heat Transfer Tubes 11a, 11b Refrigerant Inlet Heat Transfer Tube 11c Refrigerant Outlet Heat Transfer Tube 12 Fin 13 Cutting Section 14 Cut Up 15 Air Flow 16 Heat Exchanger

Claims

内部を冷媒が流動する連結された冷媒回路を構成する複数列で少なくとも１０段以上の複数段の伝熱管群と、前記伝熱管群が挿入され、その間を気流が流動する多数のフィンより成り、伝熱管の配管は気流に対して風下側の列に冷媒入り口伝熱管を設け、風上側の列に冷媒出口伝熱管を設けて構成され、前記冷媒入り口伝熱管と前記冷媒出口伝熱管との列間にある前記フィンの段方向にのみ、少なくとも高温のガス冷媒が流れる伝熱管と低温の過冷却液が流れる伝熱管との間の熱伝導を遮断するように複数段連続して切断される切断部を、複数段の切断されない部分を残して設けたことを特徴とする熱交換器。It is composed of a plurality of rows of heat transfer tube groups of at least 10 stages in a plurality of rows constituting a connected refrigerant circuit in which the refrigerant flows inside, and a plurality of fins into which the heat transfer tube groups are inserted, and airflow flows between them. The pipe of the heat transfer tube is configured by providing a refrigerant inlet heat transfer tube in a row on the leeward side with respect to the air flow, and providing a refrigerant outlet heat transfer tube in the row on the windward side, and the row of the refrigerant inlet heat transfer tube and the refrigerant outlet heat transfer tube Cutting that is continuously cut in a plurality of stages so as to cut off heat conduction between at least the heat transfer tube through which the high-temperature gas refrigerant flows and the heat transfer tube through which the low-temperature supercooled liquid flows, only in the step direction of the fins between them A heat exchanger characterized in that the portion is provided leaving a plurality of uncut portions .

伝熱管の列ピッチＰｒと段ピッチＰｈとの比がＰｒ／Ｐｈ≦０．７に配列された請求項１記載の熱交換器。The heat exchanger according to claim 1, wherein the ratio of the row pitch Pr to the step pitch Ph of the heat transfer tubes is arranged so that Pr / Ph≤0.7.

フィンには切り起こしが設けられ、切り起こしの占有面積Ａｓと全フィン面積Ａｆとの比がＡｓ／Ａｆ≦０．３である請求項１記載の熱交換器。The heat exchanger according to claim 1, wherein the fin is provided with a cut and raised, and a ratio of the occupied area As of the cut and raised to the total fin area Af is As / Af ≦ 0.3.

切断部の長さＬは冷媒出口伝熱管から冷媒の流れの反対方向に向けてＬ≧Ｐｈ×４である請求項１記載の熱交換器。2. The heat exchanger according to claim 1, wherein the length L of the cut portion is L ≧ Ph × 4 from the refrigerant outlet heat transfer tube in the direction opposite to the refrigerant flow.

少なくとも１回以上折り曲げられ、下向き端部は列間に切断部を設けていないことを特徴とする請求項１記載の熱交換器。The heat exchanger according to claim 1, wherein the heat exchanger is bent at least once and the downward end portion is not provided with a cut portion between the rows.