JP2002286329A

JP2002286329A - Evaporator

Info

Publication number: JP2002286329A
Application number: JP2001092233A
Authority: JP
Inventors: Yoshihiro Sasaki; 美弘佐々木; Akinari Narahara; 明成奈良原; Tatsu Asanuma; 達浅沼; Kazuhiro Kojima; 一浩小島; Yoshiaki Koga; 美章古賀
Original assignee: Calsonic Kansei Corp
Current assignee: Marelli Corp
Priority date: 2001-03-28
Filing date: 2001-03-28
Publication date: 2002-10-03

Abstract

PROBLEM TO BE SOLVED: To cool air passing through a core section 6a sufficiently and substantially uniformly even when a superheating region is likely to be enlarged by bringing an evaporator 1a into a thin size or the like. SOLUTION: The number of the back and forth movements of a refrigerant flowing in an air downstream section of a core section 6a in the direction of the length of first and second heat transfer pipe devices 14 at the air downstream section is increased above the number of the back and forth movements of a refrigerant flowing in an air upstream side section of the core section 6a, in the direction of the length of the first and second heat transfer tube devices 14. Further, the widths of the foregoing first and a third linear flow passages 31, 42 in the direction of the thickness of the core section 6a are made larger than those of the foregoing second and a fourth linear flow passages 32, 43.

Description

DETAILED DESCRIPTION OF THE INVENTION

【０００１】[0001]

【発明の属する技術分野】この発明に係るエバポレータ
は、空気調和装置、特に自動車用空気調和装置に組み込
んで、車室内を空気調和する為の空気を冷却する。BACKGROUND OF THE INVENTION An evaporator according to the present invention is incorporated in an air conditioner, in particular, an air conditioner for an automobile, to cool air for air conditioning in a vehicle interior.

【０００２】[0002]

【従来の技術】自動車用空気調和装置には、内部で冷媒
を蒸発させ、外部を流通する空気を冷却するエバポレー
タを組み込んでいる。又、この様な、自動車用空気調和
装置に組み込むエバポレータとして従来から、例えば特
開昭６２−７９８号公報、実開平７−１２７７８号公
報、特開平９−３１８１９５号公報等に記載されている
様な、複数枚の金属板を互いに積層して成る、所謂積層
型エバポレータが知られている。この積層型エバポレー
タは、それぞれが２枚の金属板を最中状に組み合わせて
成る伝熱管素子を複数個、互いに積層する事により構成
している。図６は、この様に従来から知られている積層
型エバポレータの１例を略示している。2. Description of the Related Art An air conditioner for a vehicle incorporates an evaporator for evaporating a refrigerant inside and cooling air flowing outside. Such evaporators to be incorporated into an air conditioner for automobiles have been described in, for example, JP-A-62-798, JP-A-7-12778, and JP-A-9-318195. In addition, a so-called laminated evaporator in which a plurality of metal plates are laminated on each other is known. This laminated evaporator is configured by laminating a plurality of heat transfer tube elements each of which is formed by combining two metal plates in the middle. FIG. 6 schematically shows an example of such a conventionally known laminated evaporator.

【０００３】このエバポレータ１は、それぞれの片面に
凹部を形成した金属板を２枚１組とし、互いの凹部同士
を整合させた状態で最中状に重ね合わせて互いに気密且
つ液密に接合する事により、内側に扁平で互いに独立し
た２本の直線状流路２、２を有する複数の第一伝熱管素
子（図示せず）と、内側に扁平で中間部で１８０度折り
返したＵ字形流路３、３を有する複数の第二伝熱管素子
（図示せず）とを備える。そして、上記複数の第一伝熱
管素子を、隣り合う第一伝熱管素子同士の間にフィン
（図示せず）を設けた状態で重ね合わせて第一部分４を
構成すると共に、上記複数の第二伝熱管素子を、隣り合
う第二伝熱管素子同士の間にフィンを設けた状態で重ね
合わせて第二部分５を構成している。そして、上記第一
部分４と第二部分５とを、上記各第一、第二伝熱管素子
の重ね合わせ方向に重ね合わせる事により、コア部６を
構成している。[0003] The evaporator 1 is a set of two metal plates each having a concave portion formed on one surface thereof, and superposed in the middle while the concave portions are aligned with each other, and joined to each other in a gas-tight and liquid-tight manner. Accordingly, a plurality of first heat transfer tube elements (not shown) each having two flat linear passages 2 and 2 which are flat and independent from each other, and a U-shaped flow which is flat and has a 180-degree folded back at an intermediate portion. A plurality of second heat transfer tube elements (not shown) having passages (3) and (3). Then, the plurality of first heat transfer tube elements are overlapped in a state where fins (not shown) are provided between adjacent first heat transfer tube elements to constitute the first portion 4, and the plurality of second heat transfer tube elements are formed. The second portion 5 is formed by superposing the heat transfer tube elements with fins provided between adjacent second heat transfer tube elements. The core portion 6 is configured by overlapping the first portion 4 and the second portion 5 in the overlapping direction of the first and second heat transfer tube elements.

【０００４】又、上記各第一、第二伝熱管素子の上下両
端部のそれぞれ２個所位置で合計４個所位置に、タンク
空間を設けている。これら複数のタンク空間のうち、上
記各第一伝熱管素子に設けたタンク空間は、上記各直線
状流路２、２の上下両端部に接続している。又、上記複
数のタンク空間のうち、上記各第二伝熱管素子の下端部
に設けた１対のタンク空間は、上記各Ｕ字形流路３、３
の両端部に接続している。これに対して、上記各第二伝
熱管素子の上端部に設けた１対のタンク空間は、上記各
Ｕ字形流路とは独立して設けている。そして、上記各タ
ンク空間のうち、上記各第一、第二伝熱管素子を重ね合
わせた状態で、隣り合うタンク空間同士を互いに連通さ
せる事により、入口タンク部７と中間タンク部８、８と
出口タンク部９とを構成している。そして、上記コア部
６の上端部に設けた入口タンク部７の長さ方向一端部に
冷媒送り込み管１０の下流端部を、同じく出口タンク部
９の長さ方向一端部に冷媒取り出し管１１の上流端部
を、それぞれ接続している。[0004] In addition, tank spaces are provided at a total of four positions, two at the upper and lower ends of each of the first and second heat transfer tube elements. Of these plurality of tank spaces, the tank space provided in each of the first heat transfer tube elements is connected to upper and lower ends of each of the linear flow paths 2 and 2. Further, of the plurality of tank spaces, a pair of tank spaces provided at the lower end of each of the second heat transfer tube elements is provided with a corresponding one of the U-shaped flow paths 3 and 3.
Are connected to both ends. On the other hand, a pair of tank spaces provided at the upper end of each of the second heat transfer tube elements is provided independently of each of the U-shaped flow paths. Then, in each of the tank spaces, the first and second heat transfer tube elements are overlapped, and the adjacent tank spaces are communicated with each other, so that the inlet tank portion 7 and the intermediate tank portions 8 and 8 are connected to each other. An outlet tank section 9 is constituted. The downstream end of the refrigerant feed pipe 10 is provided at one longitudinal end of the inlet tank 7 provided at the upper end of the core 6, and the refrigerant take-out pipe 11 is provided at one longitudinal end of the outlet tank 9. The upstream ends are respectively connected.

【０００５】又、上記各第一、第二伝熱管素子にそれぞ
れ設けた各直線状流路２、２及び各Ｕ字形流路３、３の
上流側、下流側各半部の、上記コア部６の厚さ方向（図
６の表裏方向）に関する幅は、互いに同じにしている。
上述の様な従来のエバポレータ１の場合、上記コア部６
の厚さ方向片側部分（図６の表側部分）に設けた複数の
流路２、３内を流れる冷媒が、この厚さ方向片側部分
で、上記各第一、第二伝熱管素子の長さ方向（図６の上
下方向）に関して逆方向に折り返す回数（１回）が、上
記コア部６の厚さ方向他側部分（図６の裏側部分）に設
けた複数の流路２、３内を流れる冷媒が、この厚さ方向
他側部分で、上記各伝熱管素子の長さ方向に関して逆方
向に折り返す回数（１回）と同じになる。In addition, the core portions of the upstream and downstream halves of the straight flow paths 2 and 2 and the U-shaped flow paths 3 and 3 provided in the first and second heat transfer tube elements, respectively. 6 have the same width in the thickness direction (the front-back direction in FIG. 6).
In the case of the conventional evaporator 1 as described above, the core 6
Refrigerant flowing through the plurality of flow paths 2 and 3 provided on one side portion in the thickness direction (the front side portion in FIG. 6) has the length of the first and second heat transfer tube elements in the one side portion in the thickness direction. The number of turns (one time) in the direction opposite to the direction (vertical direction in FIG. 6) is determined by the inside of the plurality of flow paths 2 and 3 provided on the other side in the thickness direction of the core part 6 (the back side in FIG. 6). The number of times (one time) that the flowing refrigerant is folded in the direction opposite to the length direction of each heat transfer tube element at the other side in the thickness direction is the same.

【０００６】エバポレータ１の使用時には、冷媒送り込
み管１０に設けた冷媒送り込み口１２を通じてコア部６
の内部に液状若しくは気液混合状態の冷媒を送り込む。
このコア部６に送り込まれた冷媒は、このコア部６の厚
さ方向片側部分に存在する一部の直線状流路２、２内及
びＵ字形流路３、３の上流側半部内を流れた後、上記コ
ア部６の厚さ方向他側部分に存在するＵ字形流路３、３
の下流側半部内及び残部の直線状流路２、２内を流れ
る。上記冷媒が上記コア部６内を流れる間に、この冷媒
は上記コア部６の外部を、図７の矢印α方向に通過する
空気調和用の空気と熱交換を行なって蒸発する。又、上
記コア部６内で蒸発したガス状の冷媒は、出口タンク部
９から冷媒取り出し管１１に設けた冷媒取り出し口１３
を通じて外部に取り出され、図示しないコンプレッサに
送られる。この結果、上記空気調和用の空気は、上記熱
交換により冷却される。When the evaporator 1 is used, the core portion 6 passes through a refrigerant inlet 12 provided in the refrigerant inlet pipe 10.
A liquid or a gas-liquid mixed state refrigerant is sent into the inside of the container.
The refrigerant sent into the core 6 flows through some of the straight flow paths 2 and 2 and the upstream half of the U-shaped flow paths 3 and 3 existing on one side in the thickness direction of the core 6. After that, the U-shaped flow paths 3, 3, 3
In the downstream half and the remaining straight flow paths 2, 2. While the refrigerant flows through the core portion 6, the refrigerant evaporates by performing heat exchange with the air for air conditioning passing in the direction of arrow α in FIG. The gaseous refrigerant evaporated in the core portion 6 is supplied from the outlet tank portion 9 to the refrigerant outlet 13 provided in the refrigerant outlet pipe 11.
And then sent to a compressor (not shown). As a result, the air conditioning air is cooled by the heat exchange.

【０００７】[0007]

【発明が解決しようとする課題】上記エバポレータ１の
内部から冷媒取り出し管１０を通じてコンプレッサに向
け送り出された冷媒が、十分に気化し切っていないと、
液状若しくは気液混合状態の冷媒がコンプレッサに送り
込まれる、所謂リキッドバックが発生して、このコンプ
レッサの故障を招く可能性がある。この為に従来から、
この様なリキッドバックの発生を防止すべく、エバポレ
ータ１の内部に設けた複数の流路２、３の一部で、冷媒
取り出し管１１から冷媒が流出する直前の部分である、
上記コア部６の厚さ方向他側部分に存在する直線状流路
２、２の一部に、冷媒を十分に気化し切る為の、所謂ス
ーパーヒート領域を設けている。If the refrigerant sent from the inside of the evaporator 1 to the compressor through the refrigerant outlet pipe 10 is not sufficiently vaporized,
A so-called liquid back, in which a refrigerant in a liquid or gas-liquid mixed state is sent to the compressor, may occur, leading to a failure of the compressor. For this reason,
In order to prevent the occurrence of such liquid back, a part of the plurality of flow paths 2 and 3 provided inside the evaporator 1 is a part immediately before the refrigerant flows out from the refrigerant outlet pipe 11.
A so-called superheat area is provided in a part of the linear flow paths 2 and 2 existing on the other side in the thickness direction of the core part 6 for sufficiently vaporizing the refrigerant.

【０００８】一方、近年、自動車用空気調和装置の小型
化が望まれており、これに伴って、エバポレータ１の厚
さを小さくする事が望まれている。但し、この様な要請
に応えるべく、上述した従来のエバポレータ１の厚さを
小さくした場合には、上記スーパーヒート領域が上記コ
ア部６の厚さ方向他側部分に存在する流路２、３のほぼ
総ての部分に迄拡大する為、このコア部６を通過する空
気を、十分に且つ均一に冷却する事が難しくなる。即
ち、上記スーパーヒート領域は、上記リキッドバックの
発生を防止し、エバポレータ１を組み込んだ自動車用空
気調和装置の信頼性を確保する為に必要であるが、スー
パーヒート領域は乾き度が高い部分である為、このスー
パーヒート領域部分の外部を通過する空気と、この部分
の内部を流れる冷媒との間での熱交換は十分に行なわれ
ない。この為、エバポレータ１全体に対してスーパーヒ
ート領域が占める割合が大きくなった場合には、このエ
バポレータ１を通過する空気を十分に冷却する事が難し
くなる。On the other hand, in recent years, it has been desired to reduce the size of the air conditioner for automobiles, and accordingly, it has been desired to reduce the thickness of the evaporator 1. However, when the thickness of the above-described conventional evaporator 1 is reduced in order to meet such a demand, the superheat region is formed in the flow paths 2, 3, 3, and 4 on the other side in the thickness direction of the core 6. , The air passing through the core portion 6 is difficult to sufficiently and uniformly cool. That is, the superheat region is necessary to prevent the occurrence of the liquid back and to secure the reliability of the automotive air conditioner incorporating the evaporator 1, but the superheat region is a portion where the dryness is high. For this reason, heat exchange between the air passing outside the superheat region and the refrigerant flowing inside the portion is not sufficiently performed. Therefore, when the ratio of the superheat region to the entire evaporator 1 increases, it becomes difficult to sufficiently cool the air passing through the evaporator 1.

【０００９】又、従来構造の場合には、コア部６の厚さ
方向片側部分に設けた複数の流路２、３内を流れる冷媒
が、この厚さ方向片側部分で、各第一、第二伝熱管素子
の長さ方向に関して逆方向に折り返す回数（１回）を、
上記コア部６の厚さ方向他側部分に設けた複数の流路
２、３内を流れる冷媒が、この厚さ方向他側部分で、上
記各第一、第二伝熱管素子の長さ方向に関して逆方向に
折り返す回数（１回）と同じにしている。この為、上記
コア部６の第一部分４と第二部分５とのそれぞれの厚さ
方向他側部分で、各直線状流路２、２同士の間及び各Ｕ
字形流路３、３の下流側半部同士の間で偏流が生じる可
能性がある。特に、従来構造の場合には、上記コア部６
の厚さ方向他側部分にそれぞれ存在する、各直線状流路
２、２及び各Ｕ字形流路３、３の下流側半部の、上記コ
ア部６の厚さ方向に関する幅を、上記コア部６の厚さ方
向片側部分にそれぞれ存在する、各直線状流路２、２及
び各Ｕ字形流路３、３の上流側半部の、上記コア部６の
厚さ方向に関する幅と同じか、場合によってはこれより
も大きくしている。この様に上記コア部６の厚さ方向他
側部分に存在する各直線状流路２、２及び各Ｕ字形流路
３、３の下流側半部の、上記コア部６の厚さ方向に関す
る幅が比較的大きくなっていると、上記偏流が生じる程
度が著しくなる。この様に第一部分４と第二部分５との
厚さ方向他側部分毎に著しい偏流が生じた場合には、上
記コア部６を厚さ方向に通過した空気で、このコア部６
を通過する部分毎に大きな温度差を生じる。そして、こ
のコア部６を通過する空気を均一に冷却できないと、自
動車室内への吹き出し空気の温度にむらを生じて、乗員
にとって快適な冷房状態を実現しにくくなる。本発明
は、この様な事情に鑑みて、エバポレータを薄くする等
により、スーパーヒート領域が拡大する傾向となった場
合でも、コア部を通過する空気を十分に、且つ、ほぼ均
一に冷却できる構造を実現すべく発明したものである。Further, in the case of the conventional structure, the refrigerant flowing through the plurality of flow paths 2 and 3 provided on one side in the thickness direction of the core portion 6 is divided into the first and second channels by the one side in the thickness direction. The number of turns (one time) in the opposite direction with respect to the length direction of the two heat transfer tube elements is as follows:
Refrigerant flowing through the plurality of flow paths 2 and 3 provided on the other side in the thickness direction of the core portion 6 passes through the lengthwise direction of the first and second heat transfer tube elements at the other side in the thickness direction. Is the same as the number of turns (one time) in the reverse direction. For this reason, at the other side in the thickness direction of each of the first portion 4 and the second portion 5 of the core portion 6, between each of the straight flow paths 2 and between each of
A drift may occur between the downstream halves of the U-shaped channels 3,3. In particular, in the case of the conventional structure, the core 6
The width in the thickness direction of the core portion 6 of the downstream half of each of the straight flow paths 2 and 2 and each of the U-shaped flow paths 3 and 3, respectively, which is present on the other side in the thickness direction of the core, The width of the upstream half of each of the straight flow paths 2 and 2 and each of the U-shaped flow paths 3 and 3 existing on one side in the thickness direction of the section 6 is the same as the width in the thickness direction of the core section 6 And in some cases even larger. In this way, the downstream half of each of the linear flow paths 2 and 2 and each of the U-shaped flow paths 3 and 3 existing on the other side in the thickness direction of the core section 6 relates to the thickness direction of the core section 6. If the width is relatively large, the degree of occurrence of the drift becomes significant. In this manner, when a significant drift occurs at the other portion in the thickness direction between the first portion 4 and the second portion 5, the air passing through the core portion 6 in the thickness direction causes the core portion 6 to flow.
A large temperature difference is generated for each portion passing through. If the air passing through the core portion 6 cannot be cooled uniformly, the temperature of the air blown into the vehicle cabin will be uneven, making it difficult to achieve a comfortable cooling state for the occupant. In view of such circumstances, the present invention provides a structure that can sufficiently and substantially uniformly cool air passing through a core portion even when a superheat region tends to expand due to a thin evaporator or the like. It was invented in order to realize.

【００１０】[0010]

【課題を解決するための手段】本発明のエバポレータ
は、従来から知られているエバポレータと同様に、内側
に冷媒を流す為の扁平な流路を有する複数の伝熱管素子
と、隣り合う伝熱管素子同士の間に設けられた複数のフ
ィンとから成るコア部と、このコア部の両側に上記複数
の流路と連通する状態で設けられた複数のタンク部と、
これら複数のタンク部の一部に冷媒を送り込む為の冷媒
送り込み口と、上記複数のタンク部の一部から冷媒を取
り出す為の冷媒取り出し口とを備える。An evaporator according to the present invention comprises a plurality of heat transfer tube elements each having a flat flow path for flowing a refrigerant inside, and a heat transfer tube adjacent to the heat transfer tube, similar to a conventionally known evaporator. A core portion comprising a plurality of fins provided between the elements, and a plurality of tank portions provided on both sides of the core portion so as to communicate with the plurality of flow paths,
A refrigerant inlet for sending refrigerant to a part of the plurality of tanks, and a refrigerant outlet for extracting refrigerant from a part of the tanks are provided.

【００１１】特に、本発明のエバポレータに於いては、
上記冷媒送り込み口から上記コア部の厚さ方向片側部分
に送り込まれた冷媒がこの厚さ方向片側部分に設けた複
数の流路内を流れた後、上記コア部の厚さ方向他側部分
に設けた複数の流路内を流れて、上記冷媒取り出し口か
ら取り出される。又、上記冷媒送り込み口が存在する、
上記コア部の厚さ方向片側部分内を流れる冷媒が、この
厚さ方向片側部分で、上記各伝熱管素子の長さ方向に関
して逆方向に折り返す回数を、上記冷媒取り出し口が存
在する、上記コア部の厚さ方向他側部分内を流れる冷媒
が、この厚さ方向他側部分で、上記各伝熱管素子の長さ
方向に関して逆方向に折り返す回数よりも多くしてい
る。又、上記コア部の厚さ方向に関する流路の幅を、上
記コア部の厚さ方向片側部分に設けた流路で、上記コア
部の厚さ方向他側部分に設けた流路よりも大きくしてい
る。In particular, in the evaporator of the present invention,
After the refrigerant sent from the refrigerant inlet to the thickness direction one side portion of the core portion flows through a plurality of flow paths provided in the thickness direction one side portion, the refrigerant flows into the thickness direction other side portion of the core portion. It flows through the plurality of channels provided and is taken out from the coolant outlet. Also, the refrigerant inlet is present,
Refrigerant flowing in the thickness direction one side portion of the core portion, the number of times that the thickness direction one side portion is folded in the opposite direction with respect to the length direction of each heat transfer tube element, the refrigerant outlet is present, the core The refrigerant flowing in the other side portion in the thickness direction of the portion has a larger number of turns than the number of turns in the direction opposite to the length direction of each heat transfer tube element in the other side portion in the thickness direction. Further, the width of the flow path in the thickness direction of the core portion, the flow path provided on one side in the thickness direction of the core, is larger than the flow path provided on the other side in the thickness direction of the core. are doing.

【００１２】更に、請求項２に記載したエバポレータの
場合には、上記コア部のうちの少なくとも幅方向一部
は、複数の第一伝熱管素子を、隣り合う第一伝熱管素子
同士の間にフィンを設けた状態で重ね合わせて成る第一
部分と、複数の第二伝熱管素子を、隣り合う第二伝熱管
素子同士の間にフィンを設けた状態で重ね合わせて成る
第二部分とを、互いに幅方向に重ね合わせる事により構
成している。そして、このうちの第一部分を構成する上
記各第一伝熱管素子は、それぞれの片面の長さ方向一端
部に互いに独立した状態で設けられた第一、第二深凹部
と、同じく長さ方向他端部に互いに独立した状態で設け
られた第三、第四深凹部と、同じく中間部に設けられて
このうちの第一、第三深凹部同士を連通させる第一浅凹
部と、同じく中間部に設けられて上記第二、第四深凹部
同士を連通させる第二浅凹部とを備えた１対の第一金属
板を、それぞれの凹部同士を対向させた状態で最中状に
重ね合わせて互いに接合する事により、上記第一深凹部
同士が突き合わされた部分に第一タンク空間を、上記第
二深凹部同士が突き合わされた部分に第二タンク空間
を、上記第三深凹部同士が突き合わされた部分に第三タ
ンク空間を、上記第四深凹部同士が突き合わされた部分
に第四タンク空間を、上記第一浅凹部同士が突き合わさ
れた部分に上記第一、第三タンク空間同士を連通させる
第一直線状流路を、上記第二浅凹部同士が突き合わされ
た部分に上記第二、第四タンク空間同士を連通させる第
二直線状流路を、それぞれ設けたものである。又、上記
第二部分を構成する上記各第二伝熱管素子は、それぞれ
の片面の長さ方向一端部に互いに独立した状態で設けら
れた第五、第六深凹部と、同じく長さ方向他端部に設け
られた第七深凹部と、同じく中間部に設けられて上記第
五、第七深凹部同士を連通させる第三浅凹部と、同じく
中間部に設けられて上記第六、第七深凹部同士を連通さ
せる第四浅凹部とを備えた１対の第二金属板を、それぞ
れの凹部同士を対向させた状態で最中状に重ね合わせて
互いに接合する事により、上記第五深凹部同士が突き合
わされた部分に第五タンク空間を、上記第六深凹部同士
が突き合わされた部分に第六タンク空間を、上記第七深
凹部同士が突き合わされた部分に第七タンク空間を、上
記第三浅凹部同士が突き合わされた部分に上記第五、第
七タンク空間同士を連通させる第三直線状流路を、上記
第四浅凹部同士が突き合わされた部分に上記第六、第七
タンク空間同士を連通させる第四直線状流路を、それぞ
れ設けたものである。そして、上記各第一伝熱管素子に
より構成する第一部分と、上記各第二伝熱管素子により
構成する第二部分とを互いに重ね合わせた状態で、互い
に隣り合う上記各第一〜第七タンク空間同士を、一部を
除いて互いに連通する事により、複数のタンク部を構成
している。そして、上記冷媒送り込み口を通じて、上記
コア部の厚さ方向片側部分内に送り込まれた冷媒が、こ
のコア部の厚さ方向片側部分にそれぞれ存在する、上記
複数のタンク部の一部と、上記各第一、第三直線状流路
とを流れた後、上記コア部の厚さ方向他側部分にそれぞ
れ存在する、上記複数のタンク部の残部と、上記各第
二、第四直線状流路とを流れて、上記冷媒取り出し口か
ら取り出される。Further, in the case of the evaporator according to the second aspect, at least a part of the core portion in the width direction includes a plurality of first heat transfer tube elements between adjacent first heat transfer tube elements. A first portion formed by overlapping with fins provided, and a plurality of second heat transfer tube elements, a second portion formed by overlapping with fins provided between adjacent second heat transfer tube elements, They are constructed by overlapping each other in the width direction. Each of the first heat transfer tube elements constituting the first portion of the first and second deep recesses provided independently of each other at one end in the longitudinal direction on one surface of each of the first heat transfer tube elements, and also in the longitudinal direction. Third and fourth deep recesses provided independently of each other at the other end, and first shallow recesses provided at the middle portion and communicating between the first and third deep recesses, similarly at the middle portion A pair of first metal plates provided with a second shallow recess provided in the portion and communicating the second and fourth deep recesses in the middle with the respective recesses facing each other. By joining together, the first tank space is a part where the first deep recesses abut each other, the second tank space is a part where the second deep recesses abut each other, and the third deep recesses are each other. The third tank space is placed in the abutted part, The butted portion has a fourth tank space, and the first shallow recess has a butted portion formed with the first and third tank spaces. A second linear flow path that connects the second and fourth tank spaces to each other is provided in the joined portion. The second heat transfer tube elements constituting the second portion are provided with fifth and sixth deep recesses provided independently at one end in the longitudinal direction on one surface of each of the second heat transfer tube elements. A seventh deep recess provided at an end portion, a third shallow recess also provided at the middle portion to communicate the fifth and seventh deep recesses, and the sixth and seventh recesses also provided at the middle portion. A pair of second metal plates provided with a fourth shallow recess that allows the deep recesses to communicate with each other are superimposed in the middle with the respective recesses facing each other and joined together to form the fifth deep plate. The fifth tank space in the portion where the recesses are abutted, the sixth tank space in the portion where the sixth deep recesses are abutted, the seventh tank space in the portion where the seventh deep recesses are abutted, The above-mentioned fifth and seventh tanks are placed in the portion where the above-mentioned third shallow recesses abut each other. The third straight flow path that communicates between them, the fourth straight flow path that communicates the sixth and seventh tank spaces with each other where the fourth shallow recesses abut each other, is there. The first to seventh tank spaces adjacent to each other in a state where the first portion formed by each of the first heat transfer tube elements and the second portion formed by each of the second heat transfer tube elements are overlapped with each other. The plurality of tanks are connected to each other except for a part, thereby constituting a plurality of tank units. And, through the refrigerant inlet, the refrigerant fed into the thickness direction one side portion of the core portion is present in the thickness direction one side portion of the core portion, respectively, a part of the plurality of tank portions, After flowing through each of the first and third linear flow paths, the remaining parts of the plurality of tank parts, which are present on the other side in the thickness direction of the core part, and the respective second and fourth linear flow paths And the refrigerant is taken out from the refrigerant outlet.

【００１３】[0013]

【作用】上述の様に構成する本発明のエバポレータによ
れば、コア部の厚さ方向片側部分に設けた複数の流路
で、冷媒の流れ方向に関して互いに並列に設けた流路の
本数を少なくできる。この為、上記コア部の厚さ方向片
側部分に設けた流路内を流れる冷媒の流速を高める事が
できて、これら各流路内を流れる冷媒と上記コア部の厚
さ方向片側部分の外部を通過する空気との間での熱交換
を効率良く行なわせる事ができる。しかも、本発明の場
合には、上記コア部の厚さ方向に関する流路の幅を、上
記コア部の厚さ方向片側部分に設けた流路で、上記コア
部の厚さ方向他側部分に設けた流路よりも大きくしてい
る。この為、使用時にスーパーヒート領域が上記コア部
の厚さ方向他側部分のほぼ全体に迄拡大した場合でも、
上記コア部を厚さ方向に通過する空気を、このコア部の
厚さ方向片側部分を通過する間に十分に冷却できる。According to the evaporator of the present invention configured as described above, the number of channels provided in parallel with each other in the flow direction of the refrigerant is reduced by the plurality of channels provided on one side in the thickness direction of the core. it can. For this reason, it is possible to increase the flow velocity of the refrigerant flowing in the flow path provided on one side in the thickness direction of the core portion, and to increase the flow rate of the refrigerant flowing in each flow path and the outside of the thickness direction one side portion of the core portion. Heat can be efficiently exchanged with the air passing through. Moreover, in the case of the present invention, the width of the flow path in the thickness direction of the core portion is set to the flow path provided on one side in the thickness direction of the core portion, and the width of the flow path in the thickness direction of the core portion is changed to the other side in the thickness direction. It is larger than the provided channel. For this reason, even when the superheat area is expanded to almost the entire other part in the thickness direction of the core part during use,
The air passing through the core in the thickness direction can be sufficiently cooled while passing through one side in the thickness direction of the core.

【００１４】又、本発明の場合には、上記コア部の厚さ
方向片側部分内を流れる冷媒が、この厚さ方向片側部分
で、各伝熱管素子の長さ方向に関して逆方向に折り返す
回数を、上記コア部の厚さ方向他側部分内を流れる冷媒
が、この厚さ方向他側部分で、上記各伝熱管素子の長さ
方向に関して逆方向に折り返す回数よりも多くしてい
る。この為、上記コア部の厚さ方向他側部分に設けた流
路で、上記冷媒の流れ方向に関して互いに並列に設けた
流路の本数を多くできる。従って、スーパーヒート領域
が拡大して、これら各流路の殆どの部分をガス状の冷媒
が流れる場合でも、エバポレータの圧力損失の増大を小
さく抑える事ができる。しかも、本発明の場合には、上
記コア部の厚さ方向に関する、このコア部の厚さ方向他
側部分に設けた流路の幅が比較的小さくなる為、上記コ
ア部の厚さ方向他側部分で、上記冷媒の流れ方向に関し
て互いに並列に設けた流路同士の間で、冷媒の偏流が生
じる程度を小さくできる。従って、上記コア部を厚さ方
向に通過後の空気の温度分布をほぼ均一にできて、乗員
にとって快適な冷房状態を実現できる。Further, in the case of the present invention, the number of times that the refrigerant flowing through one side in the thickness direction of the core portion is folded back in the opposite direction with respect to the length direction of each heat transfer tube element in the one side portion in the thickness direction. The number of times that the refrigerant flowing in the other side in the thickness direction of the core portion is folded back in the opposite direction in the length direction of each of the heat transfer tube elements in the other side portion in the thickness direction. Therefore, the number of flow paths provided in parallel with each other in the flow direction of the refrigerant can be increased in the flow paths provided on the other side in the thickness direction of the core portion. Therefore, even when the superheat region is expanded and the gaseous refrigerant flows through most of these flow paths, the increase in the pressure loss of the evaporator can be suppressed to a small value. Moreover, in the case of the present invention, the width of the flow path provided on the other side in the thickness direction of the core portion with respect to the thickness direction of the core portion is relatively small. In the side part, the degree of occurrence of the drift of the refrigerant can be reduced between the flow paths provided in parallel with each other in the flow direction of the refrigerant. Therefore, the temperature distribution of the air after passing through the core in the thickness direction can be made substantially uniform, and a cooling state that is comfortable for the occupant can be realized.

【００１５】更に、請求項２に記載したエバポレータの
場合には、コア部を構成する伝熱管素子の種類が２種類
で済む為、コスト低減を図れる。更に、上記コア部の厚
さ方向片側部分に設けた流路と、同じく厚さ方向他側部
分に設けた流路とを、複数の第七タンク空間により連通
させている。この為、圧力損失が増大する原因となる、
サイドタンク部を設ける必要がなくなり、エバポレータ
を大型化する事なく、圧力損失の更なる低減を図れて、
十分な性能確保を図れる。Further, in the case of the evaporator according to the second aspect, since only two types of heat transfer tube elements are required to constitute the core portion, the cost can be reduced. Further, a flow path provided on one side in the thickness direction of the core portion and a flow path provided on the other side in the thickness direction are communicated by a plurality of seventh tank spaces. For this reason, it causes the pressure loss to increase,
There is no need to provide a side tank, and the pressure loss can be further reduced without increasing the size of the evaporator.
Sufficient performance can be ensured.

【００１６】[0016]

【発明の実施の形態】図１〜５は、本発明の実施の形態
の１例を示している。本発明のエバポレータ１ａは、そ
れぞれが複数ずつの第一伝熱管素子１４、１４と、第二
伝熱管素子１５、１５と、コルゲート型のフィン１６、
１６とを積層して成るコア部６ａを有する。そして、こ
のコア部６ａの幅方向片側部分（図１、５の表側部分）
を、上記複数の第一伝熱管素子１４、１４を、隣り合う
第一伝熱管素子１４、１４同士の間にフィン１６を設け
た状態で重ね合わせた第一部分１７により、同じく幅方
向他側部分（図１、５の裏側部分）を、上記複数の第二
伝熱管素子１５、１５を、隣り合う第二伝熱管素子１
５、１５同士の間にフィン１６を設けた状態で重ね合わ
せた第二部分１８により、それぞれ構成している。又、
上記第一伝熱管素子１４と第二伝熱管素子１５とは、そ
れぞれの片面に凹部を形成した第一、第二金属板１９、
２０をそれぞれ２枚１組とし、互いの凹部同士を対向さ
せた状態で最中状に重ね合わせて互いに気密且つ液密に
接合する事により造ったもので、内側に冷媒を流す為の
扁平な流路を有する。又、上記第一、第二伝熱管素子１
４、１５の内部構造は、互いに異ならせている。1 to 5 show an example of an embodiment of the present invention. The evaporator 1a of the present invention includes a plurality of first heat transfer tube elements 14, 14, a plurality of second heat transfer tube elements 15, 15, corrugated fins 16,
16 are laminated. Then, one side portion in the width direction of the core portion 6a (the front side portion in FIGS. 1 and 5).
The first portion 17 in which the plurality of first heat transfer tube elements 14 are overlapped with the adjacent first heat transfer tube elements 14 provided with fins 16 is also used in the other portion in the width direction. (The back side portions in FIGS. 1 and 5), the plurality of second heat transfer tube elements 15, 15
Each of the second portions 18 is overlapped with a fin 16 provided between the fifth and the fifth 15, and is constituted by each. or,
The first heat transfer tube element 14 and the second heat transfer tube element 15 have first and second metal plates 19 each having a recess on one surface thereof.
20 is a set of two sheets each, and is made by superimposing them in the middle in a state where the recesses are opposed to each other and joining them air-tightly and liquid-tightly. It has a channel. Also, the first and second heat transfer tube elements 1
The internal structures of 4 and 15 are different from each other.

【００１７】上記第一、第二金属板１９、２０は、芯材
（比較的融点が高いアルミニウム合金）の両面にろう材
（Siを多く含み、比較的融点が低いアルミニウム合金）
を積層した、所謂両面クラッド材としている。前記エバ
ポレータ１ａを造る場合には、上記第一、第二の金属板
１９、２０と、フィン１６と、冷媒送り込み口１２を有
する冷媒送り込み管１０と、冷媒取り出し口１３を有す
る冷媒取り出し管１１とを組み合わせ、加熱炉中で加熱
して、上記ろう材により上記各部材１９、２０、１６、
１０、１１を、互いにろう付け接合する。この状態で、
上記コア部６ａの幅方向片側部分は、複数の上記第一伝
熱管素子１４とフィン１６とを重ね合わせた第一部分１
７となり、同じく幅方向他側部分は、複数の上記第二伝
熱管素子１５とフィン１６とを重ね合わせた第二部分１
８となる。The first and second metal plates 19 and 20 are made of a brazing material (an aluminum alloy containing a large amount of Si and having a relatively low melting point) on both surfaces of a core material (an aluminum alloy having a relatively high melting point).
, A so-called double-sided clad material. When the evaporator 1a is manufactured, the first and second metal plates 19 and 20, the fins 16, the refrigerant inlet pipe 10 having the refrigerant inlet 12, and the refrigerant outlet pipe 11 having the refrigerant outlet 13 are provided. Are heated in a heating furnace, and each of the members 19, 20, 16,
10 and 11 are brazed to each other. In this state,
One side portion in the width direction of the core portion 6a is a first portion 1 in which a plurality of the first heat transfer tube elements 14 and the fins 16 are overlapped.
7, and the other portion in the width direction is the second portion 1 in which the plurality of second heat transfer tube elements 15 and the fins 16 are overlapped.
It becomes 8.

【００１８】上記コア部６ａの第一部分１７を構成する
各第一伝熱管素子１４、１４は、図３（Ａ）（Ｂ）に詳
示する様な第一金属板１９を２枚、互いの凹部を対向さ
せた状態で最中状に重ね合わせ、一体にろう付けして成
る。アルミニウム合金製の両面クラッド材である素板に
プレス加工を施して成る、上記第一金属板１９は、それ
ぞれの片面の上端部に、互いに独立した第一、第二深凹
部２１、２２を設けている。又、それぞれの片面の下端
部に、互いに独立した第三、第四深凹部２３、２４を設
けている。更に、中間部には、上記第一、第三深凹部２
１、２３同士を連通させる第一浅凹部２５と、この第一
浅凹部２５と独立した状態で設けて、上記第二、第四深
凹部２２、２４同士を連通させる第二浅凹部２６とを設
けている。又、本例の場合には、上記第一浅凹部２５の
中間部の幅Ｗ₂₅を、上記第二浅凹部２６の中間部の幅Ｗ
₂₆よりも大きくしている（Ｗ₂₅＞Ｗ₂₆）。Each of the first heat transfer tube elements 14, 14 constituting the first portion 17 of the core portion 6a has two first metal plates 19 as shown in detail in FIGS. They are superposed in the middle with the concave portions facing each other and brazed together. The first metal plate 19, which is formed by pressing a raw plate that is a double-sided clad material made of an aluminum alloy, has first and second deep recesses 21 and 22 that are independent from each other at the upper end of one surface. ing. In addition, third and fourth deep recessed portions 23 and 24 are provided independently at the lower end of each one surface. Further, the first and third deep recesses 2 are provided in the intermediate portion.
A first shallow recess 25 for communicating the first and the third shallow recesses 25 and a second shallow recess 26 for providing the second and the fourth deep recesses 22 and 24 independently of each other. Provided. Further, in the case of this example, the width W ₂₅ of the middle part of the first shallow recess 25 is set to the width W ₂₅ of the middle part of the second shallow recess 26.
₂₆ (W ₂₅ > W ₂₆ ).

【００１９】上記各第一伝熱管素子１４、１４はそれぞ
れ、上述の様な第一金属板１９を１対ずつ、それぞれの
凹部同士を対向させた状態、即ち、第一深凹部２１同
士、第二深凹部２２同士、第三深凹部２３同士、第四深
凹部２４同士、第一浅凹部２５同士、第二浅凹部２６同
士を互いに対向させた状態で最中状に重ね合わせてい
る。そして、上記第一深凹部２１同士が突き合わされた
部分に第一タンク空間２７を、上記第二深凹部２２同士
が突き合わされた部分に第二タンク空間２８を、上記第
三深凹部２３同士が突き合わされた部分に第三タンク空
間２９を、上記第四深凹部２４同士が突き合わされた部
分に第四タンク空間３０を、それぞれ形成している。Each of the first heat transfer tube elements 14 and 14 has a pair of first metal plates 19 as described above, with the respective concave portions facing each other, that is, the first deep concave portions 21 and the first The two deep recesses 22, the third deep recesses 23, the fourth deep recesses 24, the first shallow recesses 25, and the second shallow recesses 26 face each other in a middle state. Then, the first tank space 27 is provided at a portion where the first deep recesses 21 are abutted, the second tank space 28 is provided at a portion where the second deep recesses 22 are abutted, and the third deep recesses 23 are provided with each other. A third tank space 29 is formed at the butted portion, and a fourth tank space 30 is formed at the portion where the fourth deep recesses 24 are butted.

【００２０】又、上記第一浅凹部２５同士が突き合わさ
れた部分を第一直線状流路３１として、上記第一、第三
タンク空間２７、２９同士を連通させている。更に、上
記第二浅凹部２６同士が突き合わされた部分を第二直線
状流路３２として、上記第二、第四タンク空間２８、３
０同士を連通させている。本例の場合、前記コア部６ａ
の厚さ方向（図１、５の左右方向）に関する上記各第一
直線状流路３１の中間部の幅Ｗ₃₁は、同じく上記各第二
直線状流路３２の中間部の幅Ｗ₃₂よりも大きくなってい
る（Ｗ₃₁＞Ｗ₃₂）。尚、上記第一、第二浅凹部２５、２
６内には多数の突起３３、３３を形成している。これら
各突起３３、３３の先端面は、１対の上記第一金属板１
９同士を最中状に組み合わせる際に、これら第一金属板
１９の周縁部及び上記第一、第二浅凹部２５、２６同士
の間部分等と共に、互いに突き合わされてろう付けされ
る。そして、上記各第一伝熱管素子１４、１４の耐圧強
度を確保すると共に、上記第一、第二直線状流路３１、
３２内を流れる冷媒の流れを攪乱する役目を果たす。The first and third tank spaces 27 and 29 are communicated with each other by using a portion where the first shallow recesses 25 abut each other as a first straight flow path 31. Further, a portion where the second shallow recesses 26 abut against each other is defined as a second straight flow path 32, and the second and fourth tank spaces 28, 3
0 are communicated with each other. In the case of this example, the core portion 6a
The width W ₃₁ of the intermediate portion of each of the first linear flow channels 31 in the thickness direction (the horizontal direction of FIGS. 1 and 5) is also larger than the width W ₃₂ of the intermediate portion of each of the second linear flow channels 32. It is larger (W ₃₁ > W ₃₂ ). The first and second shallow recesses 25, 2
A large number of protrusions 33 are formed in 6. The tip surfaces of these projections 33, 33 are paired with the first metal plate 1
When the pieces 9 are combined in the middle, the peripheral portions of the first metal plate 19 and the portions between the first and second shallow recesses 25 and 26 are abutted with each other and brazed. And while ensuring the pressure resistance of each of the first heat transfer tube elements 14, 14, the first and second linear flow paths 31,
It serves to disrupt the flow of the refrigerant flowing through the inside 32.

【００２１】一方、上記コア部６ａの第二部分１８を構
成する、前記各第二伝熱管素子１５、１５は、図４
（Ａ）（Ｂ）に詳示する様な第二金属板２０を２枚、最
中状に重ね合わせ、互いにろう付けして成る。やはりア
ルミニウム合金製の両面クラッド材である素板にプレス
加工を施して成る、上記第二金属板２０は、それぞれの
片面の上端部に、互いに独立した第五、第六深凹部３
４、３５を設けている。又、それぞれの片面の下端部
に、上記第二金属板２０の幅方向に長い、第七深凹部３
６を設けている。更に、中間部には、上記第五、第七深
凹部３４、３６同士を連通させる第三浅凹部３７と、上
記第六、第七深凹部３５、３６同士を連通させる第四浅
凹部３８とを設けている。又、本例の場合には、上記第
三浅凹部３７の中間部の幅Ｗ₃₇を、上記第四浅凹部３８
の中間部の幅Ｗ₃₈よりも大きくしている（Ｗ₃₇＞
Ｗ₃₈）。On the other hand, each of the second heat transfer tube elements 15, 15 constituting the second portion 18 of the core portion 6 a is shown in FIG.
(A) Two second metal plates 20, as shown in detail in (B), are superposed in the middle and brazed together. The second metal plate 20, which is also formed by pressing a base plate which is also a double-sided clad material made of an aluminum alloy, has fifth and sixth deep recesses 3 independent of each other at the upper end of one surface.
4 and 35 are provided. Further, a seventh deep concave portion 3 which is long in the width direction of the second metal plate 20 is provided at a lower end portion of each one surface.
6 are provided. Further, in the middle part, a third shallow recess 37 for communicating the fifth and seventh deep recesses 34 and 36 with each other, and a fourth shallow recess 38 for communicating the sixth and seventh deep recesses 35 and 36 with each other. Is provided. In the case of this example, the width W ₃₇ of the intermediate portion of the third shallow recess 37 is set to the fourth shallow recess 38.
Is made larger than the width W ₃₈ of the intermediate portion (W _37>
W ₃₈ ).

【００２２】上記各第二伝熱管素子１５、１５はそれぞ
れ、上述の様な第二金属板２０を１対ずつ、それぞれの
凹部同士を対向させた状態、即ち、第五深凹部３４同
士、第六深凹部３５同士、第七深凹部３６同士、第三浅
凹部３７同士、第四浅凹部３８同士を互いに対向させた
状態で最中状に重ね合わせている。そして、上記第五深
凹部３４同士が突き合わされた部分に第五タンク空間３
９を、上記第六深凹部３５同士が突き合わされた部分に
第六タンク空間４０を、上記第七深凹部３６同士が突き
合わされた部分に第七タンク空間４１を、それぞれ形成
している。Each of the second heat transfer tube elements 15 and 15 has a pair of the second metal plates 20 as described above, with the respective concave portions facing each other, that is, the fifth deep concave portions 34 and the fifth deep concave portions 34. The six deep recesses 35, the seventh deep recesses 36, the third shallow recesses 37, and the fourth shallow recesses 38 are superposed in the middle while facing each other. The fifth tank space 3 is formed in a portion where the fifth deep recesses 34 are abutted.
9, a sixth tank space 40 is formed at a portion where the sixth deep recesses 35 abut each other, and a seventh tank space 41 is formed at a portion where the seventh deep recesses 36 abut each other.

【００２３】又、上記第三浅凹部３７同士が突き合わさ
れた部分を第三直線状流路４２として、上記第五、第七
タンク空間３９、４１同士を連通させている。更に、上
記第四浅凹部３８同士が突き合わされた部分を第四直線
状流路４３として、上記第六、第七タンク空間４０、４
１同士を連通させている。本例の場合、前記コア部６ａ
の厚さ方向に関する上記各第三直線状流路４２の中間部
の幅Ｗ₄₂は、同じく上記各第四直線状流路４３の中間部
の幅Ｗ₄₃よりも大きくなっている（Ｗ₄₂＞Ｗ₄₃）。尚、
上記第三、第四浅凹部３７、３８内にも、前述した第一
金属板１９に設けた第一、第二浅凹部２５、２６の場合
と同様に、多数の突起３３、３３を形成している。The portion where the third shallow recesses 37 abut each other is used as a third straight flow path 42 to connect the fifth and seventh tank spaces 39 and 41 to each other. Further, a portion where the fourth shallow recesses 38 abut each other is defined as a fourth linear flow path 43, and the sixth and seventh tank spaces 40, 4
1 communicates with each other. In the case of this example, the core portion 6a
Width W ₄₂ is also larger than the width W ₄₃ of the intermediate portion of the respective fourth straight flow channel 43 (W ₄₂ in the thickness direction about the respective third straight flow path 42 middle portion of> W ₄₃ ). still,
A large number of projections 33 are formed in the third and fourth shallow recesses 37 and 38 as in the case of the first and second shallow recesses 25 and 26 provided in the first metal plate 19 described above. ing.

【００２４】前記コア部６ａは、それぞれが前述した様
に構成する複数の第一伝熱管素子１４、１４及びフィン
１６、１６から成る第一部分１７と、それぞれが上述し
た様に構成する複数の第二伝熱管素子１７、１７及びフ
ィン１６、１６から成る第二部分１８とを、上記第一部
分１７と第二部分１８との間にフィン１６、１６を設け
た状態で互いに重ね合わせる事により構成している。そ
して、エバポレータ１ａを自動車用空気調和装置の一部
に組み付けた状態で、上記各第一伝熱管素子１４、１４
内の第二直線状流路３２、３２と、上記各第二伝熱管素
子１５、１５内の第四直線状流路４３、４３とを空気調
和用の空気の流通方向αに関して風上側（図１、５の右
側）に位置させている。これに対して、上記各第一伝熱
管素子１４、１４内の第一直線状流路３１、３１と、上
記各第二伝熱管素子１５、１５内の第三直線状流路４
２、４２とは、上記空気の流通方向αに関して風下側
（図１、５の左側）に位置させている。The core portion 6a has a first portion 17 including a plurality of first heat transfer tube elements 14, 14 and fins 16, 16 each configured as described above, and a plurality of first portions 17 each configured as described above. The second heat transfer tube elements 17 and 17 and the second portion 18 including the fins 16 and 16 are configured to overlap each other with the fins 16 and 16 provided between the first portion 17 and the second portion 18. ing. Then, in a state where the evaporator 1a is assembled to a part of the automotive air conditioner, the first heat transfer tube elements 14, 14
The second straight flow passages 32, 32 in the inside and the fourth straight flow passages 43, 43 in the second heat transfer tube elements 15, 15 are arranged on the windward side with respect to the flow direction α of the air for air conditioning (FIG. 1, 5). On the other hand, the first straight passages 31 in the first heat transfer tube elements 14 and the third straight passages 4 in the second heat transfer tube elements 15
2 and 42 are located on the leeward side (the left side in FIGS. 1 and 5) with respect to the air flow direction α.

【００２５】そして、この様に上記各第一伝熱管素子１
４、１４と上記各第二伝熱管素子１５、１５とを重ね合
わせた状態で、上記第一部分１７のうちで、上記第二部
分１８と反対側の幅方向片半部（図１、５の表側半部）
を構成する上記各第一伝熱管素子１４、１４の第一タン
ク空間２７同士を互いに連通して、入口タンク部４４を
構成している。この為、上記第一部分１７の幅方向片半
部で上記各第一伝熱管素子１４、１４を構成する第一金
属板１９に形成した第一深凹部２１の底部には、上記第
一部分１７の幅方向片半部の幅方向他端（図１、５の裏
側端）に位置する１枚の第一金属板１９を除き、冷媒を
通過させる為の通孔４５を形成している。この様にして
構成した、上記入口タンク部４４の長さ方向一端部（図
１、５の表側端部）には、前記冷媒送り込み管１０の下
流端を接続している。The first heat transfer tube element 1
In a state where the second heat transfer tube elements 15 and 15 are overlapped with each other, the first half portion 17 of the first portion 17 is opposite to the second portion 18 in the width direction half (see FIGS. 1 and 5). Front half)
The first tank spaces 27 of the first heat transfer tube elements 14 and 14 are connected to each other to form an inlet tank portion 44. For this reason, at the bottom of the first deep concave portion 21 formed in the first metal plate 19 constituting each of the first heat transfer tube elements 14 in the widthwise half of the first portion 17, the first portion 17 Except for one first metal plate 19 located at the other end in the width direction of one half in the width direction (the back end in FIGS. 1 and 5), a through hole 45 for allowing the refrigerant to pass through is formed. The downstream end of the refrigerant feed pipe 10 is connected to one end of the inlet tank 44 in the longitudinal direction (the front end in FIGS. 1 and 5).

【００２６】又、上記第一部分１７を構成する上記各第
一伝熱管素子１４、１４の第三タンク空間２９同士を互
いに連通して、第一折り返しタンク部４６を構成してい
る。この為、上記第一部分１７の上記各第一伝熱管素子
１４、１４を構成する第一金属板１９に形成した第三深
凹部２３の底部には、上記第一部分１７の幅方向両端に
位置する２枚の第一金属板１９を除き、冷媒を通過させ
る為の通孔４５を形成している。The third tank spaces 29 of the first heat transfer tube elements 14 constituting the first portion 17 are connected to each other to form a first folded tank portion 46. For this reason, at the bottom of the third deep recess 23 formed in the first metal plate 19 constituting each of the first heat transfer tube elements 14, 14 of the first portion 17, they are located at both ends in the width direction of the first portion 17. Except for the two first metal plates 19, a through hole 45 for allowing a refrigerant to pass therethrough is formed.

【００２７】又、上記第一部分１７のうちで、上記第二
部分１８と同じ側の幅方向他半部（図１、５の裏側半
部）を構成する上記各第一伝熱管素子１４、１４の第一
タンク空間２７と、上記第二部分１８を構成する上記各
第二伝熱管素子１５、１５の第五タンク空間３９とを互
いに連通して、第二折り返しタンク部４７を構成してい
る。この為、上記第一部分１７の幅方向他半部を構成す
る第一金属板１９に形成した第一深凹部２１の底部と、
上記第二部分１８を構成する第二金属板２０に形成した
第五深凹部３５の底部とには、上記第二部分１８の幅方
向他端（図１、５の裏側端）に位置する１枚の第二金属
板２０を除き、冷媒を通過させる為の通孔４５を形成し
ている。The first heat transfer tube elements 14, 14 constituting the other half of the first portion 17 in the width direction on the same side as the second portion 18 (the back half in FIGS. 1 and 5). The first tank space 27 and the fifth tank space 39 of each of the second heat transfer tube elements 15 constituting the second portion 18 communicate with each other to form a second folded tank portion 47. . For this reason, the bottom of the first deep recess 21 formed in the first metal plate 19 constituting the other half in the width direction of the first portion 17,
The bottom of the fifth deep recess 35 formed in the second metal plate 20 constituting the second portion 18 is located at the other end in the width direction of the second portion 18 (the back end in FIGS. 1 and 5). Except for the two second metal plates 20, a through hole 45 for allowing a refrigerant to pass therethrough is formed.

【００２８】又、上記第二部分１８を構成する上記各第
二伝熱管素子１５、１５の第七タンク空間４１の風上側
部分と、上記第一部分１７を構成する上記各第一伝熱管
素子１４、１４の第四タンク空間３０とを互いに連通し
て、冷媒移送タンク部４８を構成している。この為、上
記第二部分１８を構成する第二金属板２０に形成した第
七深凹部３６の底部の風上側部分と、上記第一部分１７
を構成する第一金属板１９に形成した第四深凹部２４の
底部とには、前記コア部６ａの両端に位置する２枚の第
一、第二金属板１９、２０を除き、冷媒を通過させる為
の通孔４５を形成している。The windward part of the seventh tank space 41 of each of the second heat transfer tube elements 15, 15 forming the second portion 18 and the first heat transfer tube element 14 forming the first portion 17. , And the fourth tank space 30 are connected to each other to form a refrigerant transfer tank unit 48. For this reason, the windward portion at the bottom of the seventh deep concave portion 36 formed in the second metal plate 20 constituting the second portion 18 and the first portion 17
Except for the two first and second metal plates 19 and 20 located at both ends of the core portion 6a, the refrigerant passes through the bottom of the fourth deep recess 24 formed in the first metal plate 19 constituting A through hole 45 is formed.

【００２９】更に、上記第二部分１８を構成する上記各
第二伝熱管素子１５、１５の第六タンク空間４０と、上
記第一部分１７を構成する上記各第一伝熱管素子１４、
１４の第二タンク空間２８とを互いに連通して、出口タ
ンク部４９を構成している。この為、上記第二部分１８
を構成する第二金属板２０に形成した第六深凹部３５の
底部と、上記第一部分１７を構成する第一金属板１９に
形成した第二深凹部２２の底部とには、前記コア部６ａ
の幅方向他端（図１、５の裏側端）に位置する１枚の第
二金属板２０を除き、冷媒を通過させる為の通孔４５を
形成している。この様にして構成した、上記出口タンク
部４９の長さ方向一端部（図１、５の表側端部）には、
前記冷媒取り出し管１１の上流端を接続している。そし
て、本例の場合には、前記冷媒送り込み口１０が存在す
る、上記コア部６ａの厚さ方向片側部分内を流れる冷媒
が、この厚さ方向片側部分で、上記各第一、第二伝熱管
素子１４、１５の長さ方向（図１、２、５の上下方向）
に関して逆方向に折り返す回数（２回）を、上記冷媒取
り出し口１１が存在する、上記コア部６ａの厚さ方向他
側部分内を流れる冷媒が、この厚さ方向他側部分で、上
記各第一、第二伝熱管素子１４、１５の長さ方向に関し
て逆方向に折り返す回数（０回）よりも多くしている。Further, the sixth tank space 40 of each of the second heat transfer tube elements 15, 15 constituting the second portion 18, and the first heat transfer tube element 14, constituting the first portion 17,
The 14th second tank space 28 is communicated with each other to form an outlet tank portion 49. For this reason, the second part 18
The bottom of the sixth deep recess 35 formed in the second metal plate 20 forming the first portion 17 and the bottom of the second deep recess 22 formed in the first metal plate 19 forming the first portion 17 have the core portion 6a.
Except for one second metal plate 20 located at the other end in the width direction (the back end in FIGS. 1 and 5), a through hole 45 for allowing the refrigerant to pass through is formed. At one end in the length direction of the outlet tank 49 (the front end in FIGS. 1 and 5), the thus configured outlet tank 49 is provided.
The upstream end of the refrigerant outlet pipe 11 is connected. In the case of the present example, the refrigerant flowing in the thickness direction one side portion of the core portion 6a where the refrigerant feed port 10 is present is separated by the thickness direction one side portion into the first and second transmission lines. Length direction of the heat tube elements 14 and 15 (vertical direction in FIGS. 1, 2 and 5)
The number of times (two times) that the coolant flows in the thickness direction other side portion of the core portion 6a where the coolant outlet 11 is present is changed by the number of times (two times) that the refrigerant is taken out in the thickness direction other side portion. First, the number of turns (0 times) in the reverse direction with respect to the length direction of the second heat transfer tube elements 14 and 15 is set.

【００３０】上述の様に構成する本発明のエバポレータ
の使用時には、コンデンサから吐出され、膨張弁を通過
した液状若しくは気液混合状態の冷媒を、前記冷媒送り
込み管１０から前記入口タンク部４４内に送り込む。こ
の入口タンク部４４に送り込まれた冷媒は、図５に実線
矢印イで示す様に、この入口タンク部４４の全体に広が
る。この入口タンク部４４内に広がった冷媒は、続い
て、同図に実線矢印ロで示す様に、前記コア部６ａの幅
方向片側部分に設けた第一部分１７の幅方向片半部の風
下側部分を構成する、各第一伝熱管素子１４、１４内の
第一直線状流路３１を、第一折り返しタンク部４６に向
けて、同図の矢印α方向に流れる空気との間で熱交換を
行ないつつ流れる。When the evaporator of the present invention having the above-described structure is used, the refrigerant in the liquid or gas-liquid mixed state discharged from the condenser and passed through the expansion valve is transferred from the refrigerant supply pipe 10 into the inlet tank 44. Send in. The refrigerant fed into the inlet tank 44 spreads over the entire inlet tank 44 as shown by a solid arrow A in FIG. The refrigerant spread in the inlet tank portion 44 is then leeward of one half in the width direction of the first portion 17 provided on one side in the width direction of the core portion 6a, as shown by a solid arrow B in FIG. The first straight flow path 31 in each of the first heat transfer tube elements 14, which constitute the portion, exchanges heat with the air flowing in the direction of the arrow α in FIG. Flow while doing.

【００３１】この様にして第一折り返しタンク部４６内
に流れ込んだ冷媒は、この第一折り返しタンク部４６内
を同図に実線矢印ハで示す様に、上記第一部分１７の風
下側部分の下端部を、水平方向に流れた後、この第一部
分１７の幅方向他半部で、風下側部分に設けた各第一直
線状流路３１内に流入する。そして、これら各第一直線
状流路３１内に流入した冷媒は、同図に実線矢印ニで示
す様に、上記熱交換をしつつ、下から上に流れた後、前
記第二折り返しタンク部４７に達し、この第二折り返し
タンク部４７内を、同図に実線矢印ホで示す様に流れ
る。そして、この第二折り返しタンク部４７内を流れた
冷媒は、上記コア部６ａの幅方向他側部分に設けた第二
部分１８の第三直線状流路４２内に流入する。これら各
第三直線状流路４２内に流入した冷媒は、同図に実線矢
印ヘで示す様に、上記熱交換をしつつ、上記第二部分１
８の風下側部分を上から下に向けて流れた後、下端部で
第七タンク空間４１内を、同図に実線矢印トで示す様に
流れる。そして、この第三タンク空間４１内から前記冷
媒移送タンク部４８に送られた冷媒は、同図に破線矢印
チで示す様に、この冷媒移送タンク部４８全体に広が
る。この冷媒移送タンク部４８に広がった冷媒は、続い
て、上記第一、第二部分１７、１８の風上側に存在する
第四直線状流路４３及び第二直線状流路３２内を、同図
に破線矢印リ、リで示す様に、下から上に上記熱交換を
しつつ流れて、前記出口タンク部４９に達する。The refrigerant that has flowed into the first turn-back tank portion 46 in this manner flows through the inside of the first turn-back tank portion 46 as shown by a solid line arrow c in FIG. After flowing through the portion in the horizontal direction, it flows into each of the first straight flow channels 31 provided in the leeward portion at the other half in the width direction of the first portion 17. Then, the refrigerant flowing into each of the first linear flow paths 31 flows upward from below while performing the heat exchange as shown by a solid arrow d in FIG. , And flows through the inside of the second folded tank portion 47 as shown by a solid arrow E in FIG. Then, the refrigerant flowing in the second return tank portion 47 flows into the third straight flow path 42 of the second portion 18 provided on the other side in the width direction of the core portion 6a. The refrigerant that has flowed into each of the third linear flow paths 42 performs the above-described heat exchange as shown by the solid arrow in FIG.
After flowing down the leeward part of FIG. 8 from top to bottom, it flows through the inside of the seventh tank space 41 at the lower end as shown by the solid arrows in FIG. Then, the refrigerant sent from the inside of the third tank space 41 to the refrigerant transfer tank portion 48 spreads over the entire refrigerant transfer tank portion 48 as shown by a broken line arrow H in FIG. Subsequently, the refrigerant spread to the refrigerant transfer tank portion 48 flows through the fourth linear flow path 43 and the second linear flow path 32 existing on the windward side of the first and second portions 17 and 18. As indicated by broken arrows in the figure, the heat flows from bottom to top while performing the heat exchange, and reaches the outlet tank 49.

【００３２】そして、この様にして出口タンク部４９に
達した、過熱状態のガス状冷媒は、同図に破線矢印ヌで
示す様に、この出口タンク部４９内を流れた後、前記冷
媒取り出し管１１に流出し、この冷媒取り出し管１１の
下流端に接続した配管を通じて、コンプレッサの吸入口
に送られる。The superheated gaseous refrigerant that has reached the outlet tank 49 in this way flows through the outlet tank 49 as shown by the broken arrow in FIG. The refrigerant flows out to the pipe 11 and is sent to the suction port of the compressor through a pipe connected to the downstream end of the refrigerant take-out pipe 11.

【００３３】前述の様に構成し、上述の様にコア部６ａ
の内部を流れる冷媒とこのコア部６ａの外部を通過する
空気との間で熱交換を行ない、この空気を冷却する、本
発明のエバポレータの場合、風下側に存在する、コア部
６ａの厚さ方向片側部分内を流れる冷媒が、この厚さ方
向片側部分で、各第一、第二伝熱管素子１４、１５の長
さ方向に関して逆方向に折り返す回数（２回）を、風上
側に存在する、上記コア部６ａの厚さ方向他側部分内を
流れる冷媒が、この厚さ方向他側部分で、上記各第一、
第二伝熱管素子１４、１５の長さ方向に関して逆方向に
折り返す回数（０回）よりも多くしている。この為、風
下側に存在する、上記コア部６ａの厚さ方向片側部分に
設けた複数の第一、第三直線状流路３１、４２で、第一
部分１７の幅方向片半部に設けた第一直線状流路３１の
本数と、同じく幅方向他半部に設けた第一直線状流路３
１の本数と、第二部分１８に設けた第三直線状流路４２
の本数とを、それぞれ少なくできる。言い換えれば、上
記複数の第一、第三直線状流路３１、４２で、冷媒の流
れ方向に関して互いに並列に設けた流路３１、４２の本
数を、それぞれ少なくできる。従って、上記コア部６ａ
の厚さ方向片側部分に設けた流路３１、４２内を流れる
冷媒の流速を高める事ができて、これら各流路３１、４
２内を流れる冷媒と、上記コア部６ａの厚さ方向片側部
分の外部を通過する空気との間での熱交換を効率良く行
なわせる事ができる。The core 6a is constructed as described above, and
In the case of the evaporator according to the present invention, which exchanges heat between the refrigerant flowing inside the core and the air passing outside the core 6a to cool the air, the thickness of the core 6a existing on the leeward side The number of times (two times) that the refrigerant flowing in the one-way part in the thickness direction is folded in the opposite direction with respect to the length direction of each of the first and second heat transfer tube elements 14 and 15 in the one-side part in the thickness direction is present on the windward side. The refrigerant flowing in the other portion in the thickness direction of the core portion 6a is separated by the first and second portions in the other portion in the thickness direction.
The number of turns (0 times) in the reverse direction with respect to the length direction of the second heat transfer tube elements 14 and 15 is set larger. For this reason, a plurality of first and third linear flow paths 31 and 42 provided on one side in the thickness direction of the core portion 6a existing on the leeward side are provided on one half in the width direction of the first portion 17. The number of the first linear flow paths 31 and the first linear flow path 3 similarly provided in the other half in the width direction
1 and the third straight channel 42 provided in the second portion 18.
Can be reduced respectively. In other words, in the plurality of first and third linear flow paths 31 and 42, the number of flow paths 31 and 42 provided in parallel with each other in the flow direction of the refrigerant can be reduced. Therefore, the core 6a
Can increase the flow velocity of the refrigerant flowing through the flow paths 31 and 42 provided on one side in the thickness direction.
The heat exchange between the refrigerant flowing inside 2 and the air passing through the outside of one side in the thickness direction of the core 6a can be efficiently performed.

【００３４】しかも、本発明の場合には、上記コア部６
ａの厚さ方向に関する、このコア部６ａの厚さ方向片側
部分に設けた第一、第三直線状流路３１、４２の幅
Ｗ₃₁、Ｗ ₄₂が、上記コア部６ａの厚さ方向に関する、こ
のコア部６ａの厚さ方向他側部分に設けた第二、第四直
線状流路３２、４３の幅Ｗ₃₂、Ｗ₄₃よりも、それぞれ大
きくなっている（Ｗ₃₁＞Ｗ₃₂、Ｗ₄₂＞Ｗ₄₃）。この為、
使用時にスーパーヒート領域が上記コア部６ａの厚さ方
向他側部分のほぼ全体に迄拡大した場合でも、上記コア
部６ａを厚さ方向に通過する空気を、このコア部６ａの
厚さ方向片側部分を通過する間に十分に冷却できる。Moreover, in the case of the present invention, the core 6
a side in the thickness direction of the core portion 6a with respect to the thickness direction
Width of the first and third straight flow paths 31, 42 provided in the portion
W₃₁, W ₄₂Is related to the thickness direction of the core 6a.
Second and fourth shafts provided on the other side in the thickness direction of the core portion 6a.
Width W of linear flow paths 32 and 43₃₂, W₄₃Each larger than
(W₃₁> W₃₂, W₄₂> W₄₃). Because of this,
When used, the superheat area is the thickness of the core 6a.
Even if the core is expanded to almost the entire other side,
The air passing through the portion 6a in the thickness direction passes through the core portion 6a.
It can be cooled sufficiently while passing through one side in the thickness direction.

【００３５】又、本発明の場合には、上記コア部６ａの
厚さ方向他側部分内を流れる冷媒が、上記コア部６ａの
厚さ方向他側部分で、上記各第一、第二伝熱管素子１
４、１５の長さ方向に関して逆方向に折り返す回数を０
回としている。この為、上記コア部６ａの厚さ方向他側
部分で、上記冷媒の流れ方向に関して互いに並列に設け
た第四、第二直線状流路４３、３２の本数が多くなる。
従って、スーパーヒート領域が拡大して、これら各流路
４３、３２の殆どの部分をガス状の冷媒が流れる場合で
も、エバポレータ１ａの圧力損失の増大を小さく抑える
事ができる。Further, in the case of the present invention, the refrigerant flowing in the other side in the thickness direction of the core portion 6a flows through the first and second transmission lines in the other side portion in the thickness direction of the core portion 6a. Heat tube element 1
The number of turns in the reverse direction with respect to the length direction of 4, 15 is 0.
Times. For this reason, the number of the fourth and second linear flow paths 43 and 32 provided in parallel with each other in the flow direction of the refrigerant at the other side in the thickness direction of the core portion 6a increases.
Therefore, even when the superheat region is expanded and the gaseous refrigerant flows through most of these flow paths 43 and 32, an increase in the pressure loss of the evaporator 1a can be suppressed to a small value.

【００３６】しかも、本発明の場合には、上記コア部６
ａの厚さ方向に関する、このコア部６ａの厚さ方向他側
部分に設けた第四、第二直線状流路４３、３２の幅
Ｗ₃₂、Ｗ ₄₃が、上記コア部６ａの厚さ方向に関する、こ
のコア部６ａの厚さ方向片側部分に設けた第一、第三直
線状流路３１、４２の幅Ｗ₃₁、Ｗ₄₂よりも小さくなって
いる（Ｗ₃₂＜Ｗ₃₁、Ｗ₄₃＜Ｗ₄₂）。従って、上記コア部
６ａの厚さ方向に関する、上記第四、第二直線状流路４
３、３２の幅Ｗ₃₂、Ｗ₄₃は比較的小さくなる為、前記冷
媒移送タンク部４８から複数の第四、第二直線状流路４
３、３２に送られる冷媒が、この冷媒移送タンク部４８
の下流端寄り部分に接続された一部の第二直線状流路３
２内に著しく片寄って流れる事を抑える事ができる。言
い換えれば、上記コア部６ａの厚さ方向他側部分で、上
記冷媒の流れ方向に関して互いに並列に設けた複数の第
四、第二直線状流路４３、３２同士の間で、冷媒の偏流
が生じる程度を小さくできる。従って、上記コア部６ａ
を厚さ方向に通過後の空気の温度分布をほぼ均一にでき
て、乗員にとって快適な冷房状態を実現できる。Moreover, in the case of the present invention, the core 6
The other side in the thickness direction of the core portion 6a with respect to the thickness direction of a
The width of the fourth and second straight flow paths 43 and 32 provided in the portion
W₃₂, W ₄₃Is related to the thickness direction of the core 6a.
The first and third shafts provided on one side in the thickness direction of the core portion 6a
Width W of linear flow paths 31, 42₃₁, W₄₂Smaller than
Yes (W₃₂<W₃₁, W₄₃<W₄₂). Therefore, the core
The fourth and second linear flow paths 4 in the thickness direction
3, 32 width W₃₂, W₄₃Is relatively small.
A plurality of fourth and second linear flow paths 4 from the medium transfer tank portion 48
The refrigerant sent to the refrigerant transfer tanks 3 and 32 is
Part of the second straight flow path 3 connected to the downstream end portion
It is possible to suppress the flow that is significantly deviated in the area 2. Word
In other words, on the other side in the thickness direction of the core portion 6a,
A plurality of second cooling units are provided in parallel with each other in the flow direction of the refrigerant.
Fourth, refrigerant drift between the second linear flow paths 43 and 32
Can be reduced. Therefore, the core 6a
The air temperature distribution after passing through the
As a result, a cooling state that is comfortable for the occupant can be realized.

【００３７】更に、本例の構造によれば、上記コア部６
ａを構成する素子１４、１５の種類が、２種類で済む。
この為、部品製作、部品管理、組立作業が何れも容易に
なって、エバポレータ１ａのコスト低減を図れる。更
に、本例の場合には、比較的高温側のコア部６ａの厚さ
方向他側部分を風上側に、比較的低温側のコア部６ａの
厚さ方向片側部分を風下側に、それぞれ位置させてい
る。従って、このコア部６ａと、このコア部６ａを通過
する空気との間の温度差を、風上側から風下側迄十分に
確保して、上記コア部６ａと空気との熱交換を効率良く
行なわせる事ができる。更に、本例の場合、上記コア部
６ａの厚さ方向片側部分に設けた第一、第三直線状流路
３１、４２と、同じく厚さ方向他側部分に設けた第二、
第四直線状流路３２、４３とを、複数の第七タンク空間
４１により連通させている。この為、圧力損失が増大す
る原因となる、サイドタンク部を設ける必要がなくな
り、エバポレータ１ａを大型化する事なく、圧力損失の
更なる低減を図れて、十分な性能確保を図れる。Further, according to the structure of this embodiment, the core 6
Only two types of elements 14 and 15 constituting a are required.
Therefore, parts production, parts management, and assembly work are all easy, and the cost of the evaporator 1a can be reduced. Further, in the case of this example, the other portion in the thickness direction of the core portion 6a on the relatively high temperature side is located on the windward side, and the one portion in the thickness direction of the core portion 6a on the relatively low temperature side is located on the leeward side. Let me. Therefore, a sufficient temperature difference between the core portion 6a and the air passing through the core portion 6a is secured from the windward side to the leeward side, and the heat exchange between the core portion 6a and the air is efficiently performed. I can make it. Further, in the case of this example, the first and third linear flow paths 31 and 42 provided on one side in the thickness direction of the core portion 6a, and the second and third linear channels 31 and 42 provided on the other side in the thickness direction.
The fourth straight flow paths 32 and 43 are communicated by a plurality of seventh tank spaces 41. Therefore, it is not necessary to provide a side tank portion, which causes an increase in pressure loss, and the pressure loss can be further reduced without increasing the size of the evaporator 1a, and sufficient performance can be ensured.

【００３８】尚、本発明は、上述した様な、コア部６ａ
の厚さ方向片側部分内を流れる冷媒が、この厚さ方向片
側部分で、各第一、第二伝熱管素子１４、１５の長さ方
向に関して逆方向に折り返す回数を２回とすると共に、
上記コア部６ａの厚さ方向他側部分内を流れる冷媒が、
この厚さ方向他側部分で、上記各第一、第二伝熱管素子
１４、１５の長さ方向に関して逆方向に折り返す回数を
０回とした構造に限定するものではない。要は、本発明
では、冷媒送り込み口が存在する、コア部の厚さ方向片
側部分内を流れる冷媒が、この厚さ方向片側部分で、各
伝熱管素子の長さ方向に関して逆方向に折り返す回数
を、冷媒取り出し口が存在する、コア部の厚さ方向他側
部分内を流れる冷媒が、この厚さ方向他側部分で、上記
各伝熱管素子の長さ方向に関して逆方向に折り返す回数
よりも多くした構造であれば良い。It is to be noted that the present invention is not limited to the above-described core portion 6a.
Refrigerant flowing in the thickness direction one-side portion, the thickness direction one-side portion, the number of times in the reverse direction with respect to the length direction of each of the first and second heat transfer tube elements 14, 15 is two times,
The refrigerant flowing in the other part in the thickness direction of the core part 6a is:
The structure is not limited to the structure in which the number of turns in the direction opposite to the length direction of each of the first and second heat transfer tube elements 14 and 15 at the other side in the thickness direction is zero. In short, in the present invention, the number of times that the refrigerant flowing in the thickness direction one-side portion of the core portion where the refrigerant inlet is present is folded back in the thickness direction one-side portion in the opposite direction with respect to the length direction of each heat transfer tube element. The refrigerant outlet is present, the refrigerant flowing in the other side in the thickness direction of the core portion, in the other side in the thickness direction, than the number of turns in the opposite direction with respect to the length direction of each of the heat transfer tube elements. Any structure may be sufficient.

【００３９】又、本発明のエバポレータは、上述した様
に、複数のタンク部４４、４６〜４９を、複数の伝熱管
素子１４、１５の一部により構成した構造に限定するも
のではない。本発明のエバポレータは、内側に冷媒を流
す為の扁平な流路を有する複数の伝熱管素子の両端に、
これら各伝熱管素子と別体のタンク部材を設けると共
に、これら各タンク部材の内側にタンク部を設けた構造
でも実施できる。As described above, the evaporator of the present invention is not limited to the structure in which the plurality of tank portions 44, 46 to 49 are constituted by a part of the plurality of heat transfer tube elements 14, 15. The evaporator of the present invention, at both ends of a plurality of heat transfer tube elements having a flat flow path for flowing the refrigerant inside,
A tank member provided separately from these heat transfer tube elements may be provided, and a tank portion may be provided inside each of the tank members.

【００４０】[0040]

【発明の効果】本発明のエバポレータは、以上に述べた
通り構成され作用するので、エバポレータを薄くする等
により、スーパーヒート領域が拡大する傾向となった場
合でも、コア部を通過する空気を十分に、且つ、ほぼ均
一に冷却できる。The evaporator of the present invention is constructed and operates as described above. Therefore, even if the superheat region tends to expand due to a reduction in the thickness of the evaporator or the like, the air passing through the core portion can be sufficiently removed. And can be cooled almost uniformly.

[Brief description of the drawings]

【図１】本発明の実施の形態の１例を示す斜視図。FIG. 1 is a perspective view showing an example of an embodiment of the present invention.

【図２】本発明のエバポレータを構成する２種類の素子
を、それぞれ図１と同方向から見た状態で示す略透視
図。FIG. 2 is a schematic perspective view showing two types of elements constituting the evaporator of the present invention, when viewed from the same direction as FIG.

【図３】図２（Ａ）に示した第一伝熱管素子を構成する
第一金属板を示しており、（Ａ）は図１の矢印α方向か
ら、（Ｂ）は図２と同方向から、それぞれ見た図。3A and 3B show a first metal plate constituting the first heat transfer tube element shown in FIG. 2A, wherein FIG. 3A is in the direction of arrow α in FIG. 1 and FIG. 3B is in the same direction as FIG. From, each figure seen.

【図４】図２（Ｂ）に示した第二伝熱管素子を構成する
第二金属板を示しており、（Ａ）は図１の矢印α方向か
ら、（Ｂ）は図２と同方向から、それぞれ見た図。4A and 4B show a second metal plate constituting the second heat transfer tube element shown in FIG. 2B, wherein FIG. 4A is from the direction of arrow α in FIG. 1 and FIG. From, each figure seen.

【図５】本発明のエバポレータに於ける冷媒の流れ状態
を説明する為の、略透視斜視図。FIG. 5 is a schematic perspective view for explaining a flow state of a refrigerant in the evaporator of the present invention.

【図６】従来構造の１例に於ける冷媒の流れ状態を説明
する為の、略透視斜視図。FIG. 6 is a schematic perspective view for explaining a flow state of a refrigerant in an example of a conventional structure.

[Explanation of symbols]

１、１ａエバポレータ２直線状流路３Ｕ字形流路４第一部分５第二部分６、６ａコア部７入口タンク部８中間タンク部９出口タンク部１０冷媒送り込み管１１冷媒取り出し管１２冷媒送り込み口１３冷媒取り出し口１４第一伝熱管素子１５第二伝熱管素子１６フィン１７第一部分１８第二部分１９第一金属板２０第二金属板２１第一深凹部２２第二深凹部２３第三深凹部２４第四深凹部２５第一浅凹部２６第二浅凹部２７第一タンク空間２８第二タンク空間２９第三タンク空間３０第四タンク空間３１第一直線状流路３２第二直線状流路３３突起３４第五深凹部３５第六深凹部３６第七深凹部３７第三浅凹部３８第四浅凹部３９第五タンク空間４０第六タンク空間４１第七タンク空間４２第三直線状流路４３第四直線状流路４４入口タンク部４５通孔４６第一折り返しタンク部４７第二折り返しタンク部４８冷媒移送タンク部４９出口タンク部 DESCRIPTION OF SYMBOLS 1, 1a Evaporator 2 Linear flow path 3 U-shaped flow path 4 First part 5 Second part 6, 6a Core part 7 Inlet tank part 8 Intermediate tank part 9 Outlet tank part 10 Refrigerant feed pipe 11 Refrigerant take-out pipe 12 Refrigerant feed port Reference Signs List 13 refrigerant outlet 14 first heat transfer tube element 15 second heat transfer tube element 16 fin 17 first part 18 second part 19 first metal plate 20 second metal plate 21 first deep recess 22 second deep recess 23 third deep recess 24 Fourth deep recess 25 First shallow recess 26 Second shallow recess 27 First tank space 28 Second tank space 29 Third tank space 30 Fourth tank space 31 First straight flow path 32 Second straight flow path 33 Projection 34 fifth deep recess 35 sixth deep recess 36 seventh deep recess 37 third shallow recess 38 fourth shallow recess 39 fifth tank space 40 sixth tank space 41 seventh tank empty 42 Third straight flow 43 fourth straight flow passage 44 inlet tank portion 45 through hole 46 first folded tank portion 47 second folding tank unit 48 refrigerant transfer tank 49 outlet tank portion

───────────────────────────────────────────────────── フロントページの続き (72)発明者浅沼達東京都中野区南台５丁目24番15号カルソニックカンセイ株式会社内 (72)発明者小島一浩東京都中野区南台５丁目24番15号カルソニックカンセイ株式会社内 (72)発明者古賀美章東京都中野区南台５丁目24番15号カルソニックカンセイ株式会社内Ｆターム(参考） 3L103 AA05 AA35 BB38 CC18 DD03 DD57 ──────────────────────────────────────────────────続き Continuing on the front page (72) Inventor Tatsu Asanuma 5-24-15 Minamidai, Nakano-ku, Tokyo Calso Nick Kansei Corporation (72) Inventor Kazuhiro Kojima 5-24-15 Minamidai, Nakano-ku, Tokyo Calso Nick Kansei Corporation (72) Inventor Yoshiaki Koga 5-24-15 Minamidai, Nakano-ku, Tokyo Calso F-term in Nick Kansei Corporation (Reference) 3L103 AA05 AA35 BB38 CC18 DD03 DD57

Claims

[Claims]

1. A core section comprising a plurality of heat transfer tube elements having a flat flow path for flowing a refrigerant inside, and a plurality of fins provided between adjacent heat transfer tube elements. A plurality of tanks provided in a state of communicating with the plurality of flow paths on both sides of the plurality of tanks, a refrigerant inlet for feeding a refrigerant to a part of the plurality of tanks, and a part of the plurality of tanks. In an evaporator provided with a refrigerant take-out port for taking out a refrigerant, a plurality of flow paths provided in the thickness direction one side portion of the refrigerant fed from the refrigerant supply port to one thickness direction side portion of the core portion. After flowing through the inside, it flows through a plurality of flow paths provided on the other side in the thickness direction of the core portion, is taken out from the refrigerant outlet, and the thickness of the core portion where the refrigerant inlet is present. Cold flowing in one side part But in this thickness direction side portion,
The number of times the heat transfer tube element is folded in the opposite direction with respect to the length direction, the refrigerant outlet is present, the refrigerant flowing in the thickness direction other side portion of the core portion is the thickness direction other side portion, The number of times the heat transfer tube elements are folded in the opposite direction with respect to the length direction is greater than the number of times, and the width of the flow path in the thickness direction of the core portion is provided on one side in the thickness direction of the core portion. An evaporator characterized in that the flow path is larger than the flow path provided on the other side in the thickness direction of the core portion.

At least a part of the core portion in the width direction includes a first portion formed by stacking a plurality of first heat transfer tube elements with fins provided between adjacent first heat transfer tube elements. A plurality of second heat transfer tube elements, and a second portion formed by overlapping with a fin provided between adjacent second heat transfer tube elements, is configured by overlapping each other in the width direction, The first heat transfer tube elements constituting the first portion of the first and second heat transfer tube elements are provided with first and second deep recesses provided independently of each other at one longitudinal end of one surface thereof, and the other longitudinal end thereof. The third and fourth deep recesses provided independently of each other in the portion, the first shallow recess is also provided in the middle portion and communicates between the first and third deep recesses, and also in the middle portion A second shallow recess provided to communicate the second and fourth deep recesses. A pair of first metal plates provided with each other are superposed in the middle while the respective concave portions are opposed to each other, and are joined to each other. The space, the second tank space at the portion where the second deep recesses are butted, the third tank space at the portion where the third deep recesses are butted, the portion where the fourth deep recesses are butted. The fourth tank space,
In the portion where the first shallow recesses are abutted, the first,
A first linear flow path for communicating the third tank spaces with each other, and a second linear flow path for communicating the second and fourth tank spaces with each other at a portion where the second shallow recesses are abutted, respectively. The second heat transfer tube element constituting the second portion, the fifth, sixth deep recesses provided independently at one longitudinal end of one side of each, the same length, The seventh deep recess provided at the other end in the direction, the fifth shallow recess provided also in the middle, and the third shallow recess communicating with the seventh deep recess, the sixth deep recess also provided in the middle, A pair of second metal plates provided with a fourth shallow recess that allows the seventh deep recesses to communicate with each other are superposed in the middle while the respective recesses are opposed to each other, and are joined to each other. The fifth tank space is placed in the part where the five deep recesses are The sixth tank space in the portion where the deep recesses are abutted, the seventh tank space in the portion where the seventh deep recesses are abutted, the fifth and the fifth in the portion where the third shallow recesses are abutted. A third linear flow path that communicates the seven tank spaces with each other, and a fourth linear flow path that communicates the sixth and seventh tank spaces with each other where the fourth shallow recesses abut each other are provided. Wherein the first portion constituted by each of the first heat transfer tube elements and the second portion constituted by each of the second heat transfer tube elements are superimposed on each other, and the first to seventh portions which are adjacent to each other. A plurality of tank portions are formed by connecting the tank spaces to each other except for a part thereof, and the refrigerant sent into one side in the thickness direction of the core portion through the refrigerant inlet is formed by the core. One side in the thickness direction Respectively, a part of the plurality of tank portions, and after flowing through each of the first and third linear flow paths, each of the plurality of the plurality of tank portions is present on the other side in the thickness direction of the core portion. 2. The evaporator according to claim 1, wherein the evaporator flows through the remaining portion of the tank portion and the second and fourth straight flow paths and is taken out from the refrigerant outlet.