JPH04324078A - Lamination type heat exchanger - Google Patents
Lamination type heat exchangerInfo
- Publication number
- JPH04324078A JPH04324078A JP9514891A JP9514891A JPH04324078A JP H04324078 A JPH04324078 A JP H04324078A JP 9514891 A JP9514891 A JP 9514891A JP 9514891 A JP9514891 A JP 9514891A JP H04324078 A JPH04324078 A JP H04324078A
- Authority
- JP
- Japan
- Prior art keywords
- heat exchanger
- refrigerant
- header section
- flat heat
- flow
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 238000003475 lamination Methods 0.000 title 1
- 239000003507 refrigerant Substances 0.000 claims abstract description 146
- 230000001105 regulatory effect Effects 0.000 claims abstract description 17
- 238000005192 partition Methods 0.000 claims description 14
- 239000000758 substrate Substances 0.000 claims description 10
- 238000000465 moulding Methods 0.000 claims description 4
- 239000000463 material Substances 0.000 claims description 3
- 238000004080 punching Methods 0.000 claims description 3
- 238000001816 cooling Methods 0.000 abstract description 13
- 238000009826 distribution Methods 0.000 abstract description 9
- 210000003128 head Anatomy 0.000 abstract 3
- 238000001125 extrusion Methods 0.000 abstract 1
- 210000001061 forehead Anatomy 0.000 abstract 1
- 238000000034 method Methods 0.000 abstract 1
- 238000000638 solvent extraction Methods 0.000 abstract 1
- 238000009827 uniform distribution Methods 0.000 abstract 1
- 239000007788 liquid Substances 0.000 description 16
- 238000004891 communication Methods 0.000 description 13
- 230000000694 effects Effects 0.000 description 9
- 238000011144 upstream manufacturing Methods 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 239000003595 mist Substances 0.000 description 3
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 3
- 238000005259 measurement Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 239000011521 glass Substances 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- 230000008016 vaporization Effects 0.000 description 1
- 238000009834 vaporization Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
- F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/03—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits
- F28D1/0308—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits the conduits being formed by paired plates touching each other
- F28D1/0325—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another
- F28D1/0333—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another the plates having integrated connecting members
- F28D1/0341—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another the plates having integrated connecting members with U-flow or serpentine-flow inside the conduits
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
Description
【０００１】0001
【産業上の利用分野】本発明は、空調機等に用いられる
積層形熱交換器に係り、特にカーエアコン用の蒸発器と
用いるのに好敵な積層熱形交換器に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a laminated heat exchanger used in air conditioners and the like, and more particularly to a laminated heat exchanger suitable for use with evaporators for car air conditioners.
【０００２】0002
【従来の技術】従来の装置として、特開平２ー１７１５
９１号公報に記載のように、冷媒流路となるべきＵ字形
の浅いくぼみ部を有する２枚の伝熱管板を組み合わせて
形成した偏平伝熱管と冷却される空気側の伝熱フィンと
を交互に多数積層した構造とし、Ｕ字形流路の両端部に
は隣接する伝熱管を相互に連通させるように冷媒入口、
出口タンク部が設けられている積層形熱交換器が開示さ
れている。しかし、上記従来の技術では、蒸発器へ送ら
れてきた冷媒は入口パイプ、冷媒流入口を経てミスト状
になって冷媒入口タンク部に連なる偏平伝熱管群内に分
岐流入するが、冷媒流入口からミスト状になって流入し
た冷媒液滴は、大部分が慣性力によって入口タンク部の
反流入口端まで到達し、反流入口端側伝熱管には液冷媒
が大量に流れ込む結果となり、このため中央部の伝熱管
は、逆に冷媒が不足するといった冷媒分配不均一の問題
を生じていた。これを解決しようとしたものに、特開昭
６３−３１５３号公報に記載されているように、入口タ
ンク部の内面に冷媒流入口より長手方向に流れる冷媒の
流通面積を減少させる絞り穴を設けたものが開示されて
いる。[Prior Art] As a conventional device, Japanese Patent Application Laid-Open No. 2-1715
As described in Publication No. 91, flat heat exchanger tubes formed by combining two heat exchanger tube plates each having a shallow U-shaped recess to serve as a refrigerant flow path and heat exchanger fins on the air side to be cooled are alternately used. The U-shaped flow path has a refrigerant inlet and a refrigerant inlet at both ends to allow adjacent heat transfer tubes to communicate with each other.
A stacked heat exchanger is disclosed that is provided with an outlet tank section. However, in the conventional technology described above, the refrigerant sent to the evaporator passes through the inlet pipe and the refrigerant inlet, becomes a mist, and branches into a group of flat heat transfer tubes connected to the refrigerant inlet tank. Most of the refrigerant droplets that flowed in in the form of a mist reach the opposite end of the inlet tank due to inertia, resulting in a large amount of liquid refrigerant flowing into the heat exchanger tube on the side opposite the inlet. Therefore, the heat exchanger tubes in the center had the problem of uneven refrigerant distribution, such as a shortage of refrigerant. In an attempt to solve this problem, as described in Japanese Patent Application Laid-Open No. 63-3153, a throttle hole is provided on the inner surface of the inlet tank section to reduce the flow area of the refrigerant flowing in the longitudinal direction from the refrigerant inlet. have been disclosed.
【０００３】0003
【発明が解決しようとする課題】しかし、上記特開昭６
３−３１５３号公報に開示される単なる絞り穴では、穴
部で生じる細い噴流によってタンクの中心部を流れる液
滴が加速され、絞り部の下流側端へ液滴が大量に流れ込
んでしまうという点について配慮がされていない。また
、絞り穴の下流側には穴径の段差によって死水領域が形
成されるという点についても配慮がされておらず、絞り
穴の直ぐ下流側に位置する伝熱管内への冷媒流入量が不
足してしまうという問題も生じる。[Problem to be solved by the invention] However, the above-mentioned Japanese Patent Application Laid-Open No. 6
The problem with the simple throttle hole disclosed in Publication No. 3-3153 is that the droplets flowing in the center of the tank are accelerated by the thin jet generated in the hole, and a large amount of droplets flow into the downstream end of the throttle part. No consideration has been given to Furthermore, no consideration was given to the fact that a dead water region is formed due to the difference in hole diameter on the downstream side of the throttle hole, and the amount of refrigerant flowing into the heat transfer tube located immediately downstream of the throttle hole is insufficient. There is also the problem of doing so.
【０００４】このため、上記従来の熱交換器では一部の
伝熱管内に液冷媒が多く流れ込み冷媒分配が不均一とな
って出口空気温度がばらつき冷房能力が大幅に低下する
といった問題点があった。[0004] For this reason, the conventional heat exchanger described above has the problem that a large amount of liquid refrigerant flows into some of the heat transfer tubes, making the refrigerant distribution uneven, resulting in variations in the outlet air temperature and a significant reduction in cooling capacity. Ta.
【０００５】本発明の第１の目的は、伝熱管に流れ込む
冷媒の流量分配を均一化することによって冷房能力を向
上できる積層形熱交換器を提供することにある。[0005] A first object of the present invention is to provide a laminated heat exchanger that can improve cooling capacity by equalizing the flow rate distribution of refrigerant flowing into heat transfer tubes.
【０００６】本発明の第２の目的は、成形が容易であっ
て、伝熱管に流れ込む冷媒の流量分配を均一化できる積
層形熱交換器を提供することにある。A second object of the present invention is to provide a laminated heat exchanger that is easy to mold and can uniformize the flow rate distribution of the refrigerant flowing into the heat transfer tubes.
【０００７】[0007]
【課題を解決するための手段】上記第１の目的を達成す
るために、本発明の積層形熱交換器は、偏平伝熱管群の
空気流入側に前方ヘッダ部、空気流出側に後方ヘッダ部
を設けるとともに、後方ヘッダ部に形成された偏平伝熱
管内に冷媒を分岐して流入させるための入口ヘッダ部内
に整流部材を配置したものである。[Means for Solving the Problems] In order to achieve the first object, the laminated heat exchanger of the present invention has a front header section on the air inflow side of the flat heat transfer tube group and a rear header section on the air outflow side. At the same time, a rectifying member is arranged in the inlet header section for branching and flowing the refrigerant into the flat heat exchanger tubes formed in the rear header section.
【０００８】又、偏平伝熱管群の空気流入側に前方ヘッ
ダ部、空気流出側に後方ヘッダ部を設けるとともに、前
方ヘッダ部に形成された偏平伝熱管内に冷媒を分岐して
流入させるための入口ヘッダ部内に整流部材を配置した
ものである。Further, a front header section is provided on the air inflow side of the flat heat exchanger tube group, and a rear header section is provided on the air outflow side, and a refrigerant is provided for branching and flowing into the flat heat exchanger tubes formed in the front header section. A flow regulating member is placed inside the inlet header.
【０００９】又、偏平伝熱管群の空気流入側に前方ヘッ
ダ部、空気流出側に後方ヘッダ部を設けるとともに、前
方ヘッダ部が仕切り板によって二分割されているもので
あって、後方ヘッダ部に形成された偏平伝熱管内に冷媒
を分岐して流入させるための入口ヘッダ部内に整流部材
を配置したものである。[0009] Also, a front header section is provided on the air inflow side of the flat heat exchanger tube group, and a rear header section is provided on the air outflow side, and the front header section is divided into two by a partition plate. A rectifying member is disposed within the inlet header section for branching and flowing the refrigerant into the formed flat heat transfer tube.
【００１０】又、偏平伝熱管群の空気流入側に前方ヘッ
ダ部、空気流出側に後方ヘッダ部を設けるとともに、前
方ヘッダ部あるいは後方ヘッダに形成された偏平伝熱管
内に冷媒を分岐して流入させるための入口ヘッダ部内が
、流入された冷媒を環状流として分配されるように形成
したものである。In addition, a front header section is provided on the air inflow side of the flat heat exchanger tube group, and a rear header section is provided on the air outflow side, and the refrigerant is branched and flows into the flat heat exchanger tubes formed in the front header section or the rear header. The inside of the inlet header is formed so that the inflowing refrigerant is distributed as an annular flow.
【００１１】又、互いに平行で、かつ長手方向に連通す
る前方タンク部、後方タンク部を備え、二つのタンク部
を連通し、少なくても一回蛇行して流れる冷媒通路部を
形成した偏平伝熱管を複数枚積層し、前方ヘッダ部ある
いは後方ヘッダ部に偏平伝熱管内に冷媒を分岐して流入
させるための入口ヘッダ部を、前方ヘッダ部に冷媒出口
部を設けて、前方ヘッダ部と後方ヘッダ部との間に一つ
又は複数の流路群を形成するとともに、入口ヘッダ部内
に整流部材を配置したものである。[0011] Also, the flat transmission includes a front tank part and a rear tank part which are parallel to each other and communicate with each other in the longitudinal direction, and which connects the two tank parts and forms a refrigerant passage part that meanderes at least once. A plurality of heat tubes are stacked, and an inlet header section is provided in the front header section or rear header section for branching the refrigerant into the flat heat exchanger tubes, and a refrigerant outlet section is provided in the front header section. One or more flow path groups are formed between the header and the header, and a flow regulating member is arranged within the inlet header.
【００１２】又、偏平伝熱管群の上部および下部にヘッ
ダ部が形成され、、空気流出側に後方ヘッダ部を設ける
とともに、前方ヘッダ部が仕切り板によって二分割され
ているものであって、後方ヘッダ部に形成された偏平伝
熱管内に冷媒を分岐して流入させるための入口ヘッダ部
内に整流部材を配置したものである。Further, header portions are formed at the upper and lower portions of the flat heat exchanger tube group, and a rear header portion is provided on the air outflow side, and the front header portion is divided into two by a partition plate. A rectifying member is disposed within the inlet header section for branching and flowing the refrigerant into the flat heat exchanger tubes formed in the header section.
【００１３】又、偏平伝熱管群の上部および下部にヘッ
ダ部が形成され、下部のヘッダ部に形成された偏平伝熱
管内に冷媒を分岐して流入させるための入口ヘッダ部内
に整流部材を配置したものである。Further, header sections are formed at the upper and lower portions of the flat heat exchanger tube group, and a rectifying member is disposed within the inlet header section for branching and flowing the refrigerant into the flat heat exchanger tubes formed at the lower header section. This is what I did.
【００１４】上記第２の目的を達成するために、本発明
の積層形熱交換器は、偏平伝熱管群の空気流入側に前方
ヘッダ部、空気流出側に後方ヘッダ部を設けるとともに
、偏平伝熱管内に冷媒を分岐して流入させるための入口
ヘッダ部が、個々に整流板が形成される複数枚の偏平伝
熱管で形成したものである。In order to achieve the second object, the laminated heat exchanger of the present invention is provided with a front header section on the air inflow side of the flat heat transfer tube group and a rear header section on the air outflow side. The inlet header section for branching and flowing the refrigerant into the heat tube is formed of a plurality of flat heat transfer tubes each having a rectifying plate formed thereon.
【００１５】又、整流板が、接合リブ部を残して流路凹
み部を素材平板に押出し、流路凹み部よりさらに深く押
し出して流路端にタンク部を形成し、タンク部には残余
基板を残して眼鏡状開口を打ち抜き、この残余基板をタ
ンク部とは反対方向に押し出すようにプレス成形して形
成したものである。[0015] Also, the rectifier plate pushes out the concave portion of the flow path onto the flat material plate, leaving the joint rib portion, and pushes it out deeper than the concave portion of the flow path to form a tank portion at the end of the flow path, and the tank portion is filled with the remaining substrate. This is formed by punching out a spectacle-shaped opening, leaving the remaining substrate, and press-molding the remaining substrate in such a way as to push it out in the opposite direction to the tank part.
【００１６】[0016]
【作用】第１に、偏平伝熱管内に冷媒を分岐して流入さ
せるための入口ヘッダ部内に配置した整流部材によって
、タンク中心部の流れが周辺部に案内されるので、入口
パイプから流入したタンク中心部のミスト状の冷媒の液
滴がタンクの周辺部に散らばり、慣性力によって反入口
パイプ側端まで液滴が到達するのが抑えられ、一端側の
伝熱管内に液冷媒が多く流れ込むのを防ぐことができる
。この結果、冷媒分配が略均一となり冷房能力が大幅に
向上する。[Function] First, the flow in the center of the tank is guided to the periphery by the rectifying member placed in the inlet header section for branching the refrigerant into the flat heat transfer tube, so that the flow from the inlet pipe is The mist-like refrigerant droplets in the center of the tank are scattered around the tank, and the inertial force prevents the droplets from reaching the opposite end of the inlet pipe, allowing more liquid refrigerant to flow into the heat transfer tube at one end. can be prevented. As a result, the refrigerant distribution becomes substantially uniform, and the cooling capacity is greatly improved.
【００１７】又、入口ヘッダ部が、個々に整流板が形成
される複数枚の偏平伝熱管で形成しても、タンク中心部
の流れが周辺部に案内されるので、入口パイプから流入
したタンク中心部のミスト状の冷媒の液滴がタンクの周
辺部に散らばり、慣性力によって反入口パイプ側端まで
液滴が到達するのが抑えられ、一端側の伝熱管内に液冷
媒が多く流れ込むのを防ぐことができる。Furthermore, even if the inlet header section is formed of a plurality of flat heat transfer tubes each having a rectifying plate formed thereon, the flow from the center of the tank is guided to the periphery, so that the flow from the inlet pipe into the tank The mist-like refrigerant droplets in the center are scattered around the tank, and the inertial force prevents the droplets from reaching the opposite end of the inlet pipe, allowing more liquid refrigerant to flow into the heat transfer tube at one end. can be prevented.
【００１８】第２に、偏平伝熱管内に冷媒を分岐して流
入させるための入口ヘッダ部が、個々に整流板が形成さ
れる複数枚の偏平伝熱管で形成しているので、偏平伝熱
管とともに整流板を同時に成形することができ、熱交換
器の成形が容易となる。Second, since the inlet header section for branching and injecting the refrigerant into the flat heat exchanger tube is formed by a plurality of flat heat exchanger tubes each having a rectifying plate formed thereon, the flat heat exchanger tube In addition, the current plate can be molded at the same time, making it easy to mold the heat exchanger.
【００１９】[0019]
【実施例】以下、本発明の第１の実施例を図１から図１
５により説明する。[Embodiment] A first embodiment of the present invention will be described below from FIG. 1 to FIG.
5 will be explained.
【００２０】図１は本発明に係る積層形熱交換器の全体
構成を示す斜視図、図２及び図３は偏平伝熱管１を構成
する伝熱管板の斜視図、図４及び図５は偏平伝熱管１を
構成する端部伝熱管板の斜視図、図６はインナーフィン
３の斜視図、図７はインナーフィン３の要部を拡大した
斜視図、図８は図１に示す積層形熱交換器のヘッダ部の
横断面図、図９は整流部材１００の取付け状態を示した
斜視図、図１０は図１で示す後方ヘッダ部５の縦断面図
である。FIG. 1 is a perspective view showing the overall structure of a laminated heat exchanger according to the present invention, FIGS. 2 and 3 are perspective views of a heat exchanger tube plate constituting a flat heat exchanger tube 1, and FIGS. 6 is a perspective view of the inner fin 3, FIG. 7 is an enlarged perspective view of the main parts of the inner fin 3, and FIG. 8 is the laminated heat exchanger plate shown in FIG. 1. FIG. 9 is a cross-sectional view of the header section of the exchanger, FIG. 9 is a perspective view showing the installed state of the rectifying member 100, and FIG. 10 is a longitudinal cross-sectional view of the rear header section 5 shown in FIG. 1.
【００２１】図１から図３に示すように、本実施例に係
る積層形熱交換器１０は、上方に２つのタンク部を有す
る偏平伝熱管１と、空気側のフィン８とを交互に多数積
層して一端側に前方ヘッダ部４、他端側に後方ヘッダ部
５を形成し、図９に示すように後方ヘッダ部５内には整
流部材１００が配置されている。偏平伝熱管１及びフィ
ン８の積層方向の両端部に配置された偏平伝熱管１Ａ、
１Ｂの外側にはサイドフィン８ａを介してサイドプレー
ト２０が設けられており、偏平伝熱管１Ａ、１Ｂに固着
されている。As shown in FIGS. 1 to 3, the laminated heat exchanger 10 according to this embodiment has a plurality of flat heat exchanger tubes 1 having two upper tank portions and a large number of fins 8 on the air side alternately. They are stacked to form a front header section 4 at one end and a rear header section 5 at the other end, and a flow regulating member 100 is disposed within the rear header section 5 as shown in FIG. 1A of flat heat exchanger tubes arranged at both ends of the flat heat exchanger tube 1 and the fins 8 in the stacking direction;
A side plate 20 is provided on the outside of 1B via side fins 8a, and is fixed to flat heat exchanger tubes 1A and 1B.
【００２２】偏平伝熱管１を構成している伝熱管板１ａ
、１ｂは、図２及び図３に示すように、密閉された流路
を形成するため全周が接合されたリブ４０部と、このリ
ブ４０に連なる流路仕切り部６を残して、冷媒流路とな
るべきＵ字形くぼみ部２を素材平板に押し出し、これ加
えてタンク部４ａ、タンク部５ａを押し出して成形され
ている。タンク部４ａ、タンク部５ａにはそれぞれ連通
孔５０ａ、５０ｂが打ち抜かれている。また、伝熱管板
１ａ、１ｂの反タンク側端部には、積層して組立てたと
き偏平伝熱管１の間隔を保持するための折り返し部１１
が設けられている。Heat exchanger tube plate 1a constituting flat heat exchanger tube 1
, 1b, as shown in FIGS. 2 and 3, the refrigerant flow is controlled by leaving a rib 40 part whose entire circumference is joined to form a sealed flow path and a flow path partition part 6 connected to this rib 40. The U-shaped recess 2, which will serve as a channel, is extruded into a flat plate of material, and in addition, the tank portion 4a and the tank portion 5a are extruded to form the tank. Communication holes 50a and 50b are punched out in the tank portion 4a and the tank portion 5a, respectively. Further, at the ends of the heat exchanger tube plates 1a and 1b on the opposite side from the tank, a folded part 11 is provided to maintain the spacing between the flat heat exchanger tubes 1 when stacked and assembled.
is provided.
【００２３】伝熱管板１ａ，１ｂを組み合わせて形成さ
れるＵ字形冷媒流路２内に、図４、図５に示すインナー
フィン３を配置して構成された偏平伝熱管１を、互いの
連通孔５１ａ、５１ｂが重なり合うようにタンク部４ａ
、４ｂを連ねて多数積層して、図１に示すように長手方
向の連通孔を有する前方ヘッダ部４、後方ヘッダ部５を
構成する。隣接する偏平管１の間にできる空間部には冷
却される空気側の伝熱フィン８が介在されて固着されて
いる。A flat heat exchanger tube 1 configured by arranging inner fins 3 shown in FIGS. 4 and 5 is placed in a U-shaped refrigerant flow path 2 formed by combining heat exchanger tube plates 1a and 1b, so that they communicate with each other. Tank part 4a so that holes 51a and 51b overlap
, 4b are stacked in a row to form a front header section 4 and a rear header section 5 having longitudinal communication holes as shown in FIG. Heat transfer fins 8 on the air side to be cooled are interposed and fixed in the space formed between adjacent flat tubes 1.
【００２４】積層方向の一端には偏平伝熱管１Ａが、他
端には偏平伝熱管１Ｂが配置されている。偏平伝熱管１
Ａ、１Ｂは、伝熱管板１ａ、１ｂと図２及び図３に示す
伝熱管板１ｃ、１ｄを各々組み合わせて形成されるＵ字
形冷媒流路内に、図６に示すインナーフィン３を配置し
て構成する。このインナーフィン３は、図７に示すよう
にフィン長手方向に沿う所定のピッチの断続的な切り欠
きＣを有するもので、これにより流れが乱され伝熱が促
進される。また、この切り欠きＣ部を介してフィンを横
切る方向へも冷媒が流れ、Ｕ字形冷媒流路２内の流れの
Ｕターンが円滑におこなわれる。又、図１０に示すよう
に、伝熱管板１ｄ側に設けられるインナーフィン３ａの
フィン高さｈは偏平伝熱管１内に配置されているインナ
ーフィン３の略１／２に設定されている。伝熱管板１ｃ
、１ｄには、伝熱管板１ａ、１ｂと同じく連通孔５１ａ
が設けられており、平らな板状になっている。伝熱管板
１ｃは右端に配置され、連通孔５１ａに連なるように、
入口パイプ６が接続されている。ここで、伝熱管板１ｃ
の連通孔５１ａを冷媒流入口１０６と呼ぶ。伝熱管板１
ｄは左端に配置され、連通孔５１ａに連なるように、出
口パイプ７が接続されている。A flat heat exchanger tube 1A is placed at one end in the stacking direction, and a flat heat exchanger tube 1B is placed at the other end. Flat heat exchanger tube 1
In A and 1B, inner fins 3 shown in FIG. 6 are arranged in a U-shaped refrigerant flow path formed by combining heat transfer tube sheets 1a and 1b and heat transfer tube sheets 1c and 1d shown in FIGS. 2 and 3, respectively. Configure. As shown in FIG. 7, the inner fin 3 has intermittent notches C at a predetermined pitch along the longitudinal direction of the fin, which disturbs the flow and promotes heat transfer. Further, the refrigerant also flows in a direction across the fins through this notch C, and a U-turn in the flow within the U-shaped refrigerant flow path 2 is smoothly performed. Further, as shown in FIG. 10, the fin height h of the inner fins 3a provided on the heat exchanger tube plate 1d side is set to approximately 1/2 of the inner fins 3 disposed inside the flat heat exchanger tube 1. Heat exchanger tube plate 1c
, 1d has a communication hole 51a like the heat exchanger tube plates 1a and 1b.
It is in the shape of a flat plate. The heat exchanger tube plate 1c is arranged at the right end so as to be connected to the communication hole 51a.
An inlet pipe 6 is connected. Here, heat exchanger tube plate 1c
The communication hole 51a is called a refrigerant inlet 106. Heat exchanger tube plate 1
d is arranged at the left end, and the outlet pipe 7 is connected so as to be continuous with the communication hole 51a.
【００２５】図８において、積層方向の中央部に位置し
ている偏平伝熱管１の連通孔５０ａは仕切り板Ｓによっ
て閉塞されており、空気流Ａの上流側に配置されている
前方ヘッダ部４は、仕切り板Ｓによって４Ａ、４Ｂの二
つに分割されている。ヘッダ４Ａに連なる複数の偏平伝
熱管群で構成された第１の流路群１０８には、後方ヘッ
ダ部５Ａが連通しており、ヘッダ４Ｂに連なる複数の偏
平伝熱管群で構成された第２の流路群１０９には後方ヘ
ッダ部５Ｂが連通している。また後方ヘッダ５Ａ、５Ｂ
の中間に位置し、前記仕切り板Ｓによって連通孔５０ａ
が閉塞されている偏平伝熱管１の連通孔５０ｂには冷媒
流入口１０７が形成されている。冷媒流入口１０６、１
０７から冷媒が流入するヘッダには、それぞれ入口ヘッ
ダ４Ａ、５Ｂが形成され、第１の流路群および第２の流
路群を流下した冷媒が合流するヘッダにはそれぞれ出口
ヘッダ４Ｂ、５Ａが形成されている。In FIG. 8, the communication hole 50a of the flat heat exchanger tube 1 located at the center in the stacking direction is closed by a partition plate S, and the front header section 4 located on the upstream side of the air flow A is closed. is divided into two parts, 4A and 4B, by a partition plate S. The rear header section 5A is in communication with the first flow path group 108, which is made up of a plurality of flat heat exchanger tube groups connected to the header 4A, and the second flow path group 108 is made up of a plurality of flat heat exchanger tube groups connected to the header 4B. A rear header section 5B communicates with the flow path group 109. Also rear header 5A, 5B
The communication hole 50a is located in the middle of the partition plate S.
A refrigerant inlet 107 is formed in the communication hole 50b of the flat heat exchanger tube 1, which is closed. Refrigerant inlet 106, 1
The headers into which the refrigerant flows from 07 are formed with inlet headers 4A and 5B, respectively, and the headers into which the refrigerant flowing down the first flow path group and the second flow path group join are formed with outlet headers 4B and 5A, respectively. It is formed.
【００２６】冷媒流入口１０７からみて入口ヘッダ５Ｂ
の奥側であって、最奥端に位置する伝熱管板１ｄには整
流部材１００が配置されている。整流部材１００は、図
９に示すように長手方向に段差のついた中空状の箱体で
、左端開口部には突起１０１が形成されている。伝熱管
板１ｄには図６に示すように、凹状に成形した基板部１
０３を残してスリット穴１０２が穿たれている。このス
リット穴１０２に前記突起１０１を図９に示す要領で挿
入した後、図９、図１０に示すように突起１０１の先端
を折り曲げて、整流部材１００を伝熱管板１ｄに固着さ
せる。Inlet header 5B viewed from refrigerant inlet 107
A rectifying member 100 is arranged on the heat exchanger tube plate 1d located at the innermost end of the tube. As shown in FIG. 9, the flow regulating member 100 is a hollow box shaped with a step in the longitudinal direction, and a projection 101 is formed at the left end opening. As shown in FIG. 6, the heat exchanger tube plate 1d has a substrate portion 1 formed into a concave shape.
A slit hole 102 is bored except for 03. After inserting the protrusion 101 into the slit hole 102 as shown in FIG. 9, the tip of the protrusion 101 is bent as shown in FIGS. 9 and 10 to fix the flow regulating member 100 to the heat exchanger tube plate 1d.
【００２７】なお、整流部材１００の幅は、ヘッダ５Ｂ
内に流入する冷媒の流れ方向に対して、下流側の幅Ｗ２
が上流側の幅Ｗ１に比べて大きくなるように２段階に設
定されているが、このように２段階に限られるものでは
なく、楔形状に滑らかにＷ寸法を変えても良く、冷媒分
配等に応じて適宜段数やＷ寸法を増減してもよい。Note that the width of the rectifying member 100 is the same as that of the header 5B.
Width W2 on the downstream side with respect to the flow direction of the refrigerant flowing into the
Although the W dimension is set in two stages so that the width W1 is larger than the width W1 on the upstream side, it is not limited to two stages as shown above, and the W dimension may be changed smoothly into a wedge shape, and the refrigerant distribution etc. The number of stages and W dimension may be increased or decreased as appropriate.
【００２８】次に本実施例に示す積層型熱交換器内の冷
媒の流れについて説明する。Next, the flow of refrigerant in the laminated heat exchanger shown in this embodiment will be explained.
【００２９】図８に本実施例の積層形熱交換器内の冷媒
の流れを冷媒の流れ９で模式的に示す。図８において、
蒸発器へ送られてきた気液二相状態の冷媒は、冷媒の流
れ９に示したように、入口パイプ６に設けられた小孔６
ａより流入口１０６を介してミスト状となって入口ヘッ
ダ４Ａ内に流入する。入口ヘッダ４Ａ内に流入した冷媒
は、仕切板Ｓによって隣接するヘッダ４Ｂへの流入が阻
止されるので、第１の流路群内をＵ字形流路にそって流
れ、出口ヘッダ５Ａ内に流入する。この出口ヘッダ５Ａ
から冷媒流入口１０７を介して隣接する入口ヘッダ５Ｂ
内に流入した気液二相状態の冷媒は冷媒の流れ９に示し
たように、第２の流路群内をＵ字形流路にそって流れ出
口ヘッダ４Ｂ内に流入し、出口パイプ７を経て外部に流
出する。なお、前記第１の、第２の流路群内を冷媒が流
れる間に、液冷媒の有する蒸発潜熱によって管外を流れ
る空気が冷却されて空気温度が低下する。FIG. 8 schematically shows the flow of refrigerant in the laminated heat exchanger of this embodiment as a refrigerant flow 9. In FIG. In Figure 8,
The gas-liquid two-phase refrigerant sent to the evaporator passes through a small hole 6 provided in the inlet pipe 6, as shown in the refrigerant flow 9.
a, flows into the inlet header 4A through the inlet 106 in the form of a mist. The refrigerant that has flowed into the inlet header 4A is prevented from flowing into the adjacent header 4B by the partition plate S, so it flows along the U-shaped flow path within the first flow path group and flows into the outlet header 5A. do. This exit header 5A
from the adjacent inlet header 5B via the refrigerant inlet 107.
The refrigerant in the gas-liquid two-phase state flows through the second flow path group along the U-shaped flow path into the outlet header 4B, as shown in the refrigerant flow 9, and flows into the outlet header 4B through the outlet pipe 7. After that, it flows out to the outside. Note that while the refrigerant flows through the first and second flow path groups, the air flowing outside the tube is cooled by the latent heat of vaporization of the liquid refrigerant, and the air temperature decreases.
【００３０】以下、本実施例による作用、効果を図１１
から図１４に基づいて説明する。図１１は、整流部材１
００が配置されている本実施例の積層形熱交換器の入口
ヘッダ５Ｂ内の冷媒の流動状況を模式的に示す図で、本
実施例との比較のため、従来の装置である絞りを設けた
場合の積層形熱交換器の冷媒の流れを図１２に示してい
る。図１１において、冷媒流入口１０６から気液二相状
態の冷媒が入口ヘッダ５Ｂ内に流入するが、冷却能力の
大きい冷媒の液滴は、ヘッダタンクの中心部を流れる冷
媒の液滴の慣性力によって入口ヘッダ５Ｂの最も奥部へ
大量に流れ込もうとする。 この時、従来の絞り穴３
０を設けた積層形熱交換器では、図１２に示すように、
絞り穴３０によって中心部の流れが加速されてしまうと
いう点について考慮されていないため、冷媒の液滴の慣
性力によって入口ヘッダ５Ｂの最も奥部へ大量に流れ込
もうとするのを阻止できないという問題がある。また、
絞り部３０のすぐ下流のタンク部には死水領域３２が生
じるという点についても考慮されていないため、このタ
ンク部に連通している伝熱管内への冷媒流入量が不足し
、この部分の出口空気温度が局所的に高くなるという問
題もある。The functions and effects of this embodiment will be explained below with reference to FIG. 11.
This will be explained based on FIG. FIG. 11 shows the rectifying member 1
This is a diagram schematically showing the flow condition of the refrigerant in the inlet header 5B of the laminated heat exchanger of this embodiment in which 00 is arranged.For comparison with this embodiment, a conventional device with a throttle is provided. FIG. 12 shows the flow of refrigerant in the laminated heat exchanger in this case. In FIG. 11, refrigerant in a gas-liquid two-phase state flows into the inlet header 5B from the refrigerant inlet 106, but droplets of the refrigerant with a large cooling capacity are caused by the inertia of the refrigerant droplets flowing through the center of the header tank. This causes a large amount of water to flow into the innermost part of the entrance header 5B. At this time, the conventional aperture hole 3
In the laminated heat exchanger equipped with 0, as shown in Fig. 12,
Since no consideration is given to the fact that the flow in the center is accelerated by the throttle hole 30, it is impossible to prevent the refrigerant droplets from flowing in large quantities to the innermost part of the inlet header 5B due to the inertial force. There's a problem. Also,
Since no consideration is given to the fact that a dead water region 32 occurs in the tank section immediately downstream of the throttle section 30, the amount of refrigerant flowing into the heat transfer tubes communicating with this tank section is insufficient, and the outlet of this section There is also the problem of locally high air temperatures.
【００３１】これに対して、本実施例では、図１１に示
すように入口ヘッダ５Ｂの奥側に整流部材１００を配置
しているので、この整流部材１００によってヘッダタン
クの中心部の流れがヘッダタンク内の周辺部に案内され
るので、ミスト状の冷媒の液滴がヘッダタンク内に略均
一に散らばり、一端側の伝熱管内に液冷媒が多く流れ込
むのを防ぐことができる。従って、入口ヘッダ５Ｂに連
なる第２の流路群１０９を構成している各々の伝熱管内
へ、冷媒がほぼ均一に分配される。図１３に示すように
、整流部材１００の配置をその先端が左端から７番目の
タンクに位置するように設定した場合、出口空気温度は
、上記した従来の積層形熱交換器に比べて、図１４に示
すようにほぼ均一化され冷房能力が大幅に向上する。On the other hand, in this embodiment, as shown in FIG. 11, a rectifying member 100 is arranged at the rear side of the inlet header 5B, so that the flow in the center of the header tank is diverted by this rectifying member 100. Since the liquid refrigerant is guided to the periphery of the tank, droplets of the mist-like refrigerant are almost uniformly scattered within the header tank, and it is possible to prevent a large amount of liquid refrigerant from flowing into the heat transfer tube at one end. Therefore, the refrigerant is distributed almost uniformly into each of the heat transfer tubes forming the second flow path group 109 connected to the inlet header 5B. As shown in FIG. 13, when the arrangement of the rectifier member 100 is set so that its tip is located in the seventh tank from the left end, the outlet air temperature is lower than that of the conventional laminated heat exchanger described above. As shown in 14, the cooling capacity is almost uniform and the cooling capacity is greatly improved.
【００３２】なお、上記したものでは、整流部材１００
の配置をその先端が図１３に示すように、左端から７番
目のタンクに位置するように設定したが、整流部材１０
０の先端位置は、蒸発器の寸法仕様等によって適宜選定
できるものである。また、本実施例では、整流部材１０
０は薄板からなる中空箱体で構成したが、中実体として
も良い。[0032] In the above, the rectifying member 100
As shown in FIG.
The position of the tip of 0 can be appropriately selected depending on the dimensional specifications of the evaporator, etc. Further, in this embodiment, the rectifying member 10
0 is constructed of a hollow box made of a thin plate, but it may also be a solid body.
【００３３】また、整流部材１００を、第１５図に示す
ように入口ヘッダ４Ａ内にのみに配置してもよいが、あ
るいは入口ヘッダ４Ａと入口ヘッダ５Ｂの両方に配置し
てもよい。Further, the flow regulating member 100 may be disposed only in the inlet header 4A as shown in FIG. 15, or may be disposed in both the inlet header 4A and the inlet header 5B.
【００３４】次に、本発明の第２の実施例を図１６及び
図１７に示す。第１の実施例では、前方ヘッダ部４の中
間部に仕切り板Ｓを配置して冷媒通路を第１の、第２の
流路群に区分けしているが、第２の実施例では、図１６
に示すように、前方ヘッダ４、後方ヘッダ５に連なる伝
熱管群は全体として一つの流路群で構成されいる。そし
て、前方ヘッダ４に出口パイプ６が接続され、後方ヘッ
ダ５には、冷媒流入口１０６に連なるパイプ連通孔６ａ
を介して入口パイプ６が接続される。この場合には、後
方ヘッダ５によって入口ヘッダ５が形成され、前方ヘッ
ダ４によって出口ヘッダ４が形成されている。入口ヘッ
ダ５内には、冷媒流入口１０６からみて最も奥側（図１
６の左端側）に整流部材１００が配置されている。この
整流部材１００の形状は、第１の実施例では段差のつい
た角柱状のものを例にとり示したが、タンク穴５０ａ、
５０ｂの寸法や蒸発器の寸法仕様等の諸条件によって適
宜選定できるものであり、角部のない形状としてもよく
、また、図１７に示すように段差のない形状としてもよ
い。Next, a second embodiment of the present invention is shown in FIGS. 16 and 17. In the first embodiment, a partition plate S is arranged in the middle part of the front header section 4 to divide the refrigerant passage into the first and second flow path groups. 16
As shown, the heat exchanger tube group connected to the front header 4 and the rear header 5 is constituted as one flow path group as a whole. An outlet pipe 6 is connected to the front header 4, and a pipe communication hole 6a connected to the refrigerant inlet 106 is provided in the rear header 5.
An inlet pipe 6 is connected via the inlet pipe 6. In this case, the rear header 5 forms the entrance header 5, and the front header 4 forms the exit header 4. Inside the inlet header 5, there is a
A rectifying member 100 is arranged on the left end side of 6). The shape of the flow regulating member 100 is exemplified as a prismatic shape with steps in the first embodiment, but
It can be appropriately selected depending on various conditions such as the dimensions of the evaporator 50b and the dimensional specifications of the evaporator, and may have a shape without corners, or a shape without steps as shown in FIG. 17.
【００３５】次に、本発明の第３の実施例を図１８から
図２９により説明する。本実施例では、棒状の整流部材
１００の代わりに図１８及び図１９に示すように、整流
板１２０を冷媒の流れ方向に沿って複数配置している。
この整流板１２０は、図２及び図３に示す伝熱管板１ｂ
に皿状タンク部４ｂを設け、図１８に示すように連通孔
５１ｂを横断するように一体成形されている。この整流
板１２０を一体成形した伝熱管板１２１は、伝熱管板１
２１の皿状タンク部４ｂの底に、残余基板部１１０を残
して眼鏡状の開口を打ち抜き、この残余基板部１１０を
タンク部４ｂとは反対方向に太鼓状に押し出すようにプ
レス成形して、連通孔５１ｂを確保するとともに整流板
１２０を形成する。このようにして形成された伝熱管板
１２１と前記伝熱管板１ａとを組み合わせて構成した偏
平伝熱管１Ｃを、所定の枚数だけ積層し入口ヘッダ５Ｂ
を構成する。図１９に示す積層形熱交換器では、図１８
に示す整流板１２０は、図１９に示すように上流側の板
幅がＷ１で、下流側の板幅がＷ２であり、Ｗ２＞Ｗ１に
設定された２種類の整流板１２０ａ（板幅がＷ１）、１
２０ｂ（板幅がＷ２）を複数配置したものであり、図２
０に示す積層形熱交換器では、図１８に示す整流板１２
０は、幅が一定のものを複数枚の配置したものである。Next, a third embodiment of the present invention will be explained with reference to FIGS. 18 to 29. In this embodiment, instead of the rod-shaped flow regulating member 100, as shown in FIGS. 18 and 19, a plurality of flow regulating plates 120 are arranged along the flow direction of the refrigerant. This current plate 120 is a heat exchanger tube plate 1b shown in FIGS. 2 and 3.
A dish-shaped tank portion 4b is provided in the tank portion 4b, and as shown in FIG. 18, the tank portion 4b is integrally molded so as to cross the communication hole 51b. The heat exchanger tube plate 121 integrally formed with this rectifying plate 120 is a heat exchanger tube plate 1
A spectacle-shaped opening is punched out at the bottom of the dish-shaped tank section 4b of No. 21, leaving the remaining substrate section 110, and the remaining substrate section 110 is press-molded so as to be extruded into a drum shape in the direction opposite to the tank section 4b. The communication hole 51b is secured and the current plate 120 is formed. A predetermined number of flat heat exchanger tubes 1C constructed by combining the thus formed heat exchanger tube plate 121 and the heat exchanger tube plate 1a are stacked to form an inlet header 5B.
Configure. In the laminated heat exchanger shown in Fig. 19, Fig. 18
As shown in FIG. 19, the current plate 120 shown in FIG. 19 has a plate width of W1 on the upstream side and a plate width of W2 on the downstream side. ), 1
20b (board width W2) is arranged, and as shown in Figure 2.
In the laminated heat exchanger shown in FIG.
0 is an arrangement of a plurality of sheets having a constant width.
【００３６】本実施例における積層形熱交換器のヘッダ
タンク内の冷媒の流動状況を図１９及び図２０に模式的
に示す。図１９に示す上流側の板幅をＷ１、下流側の板
幅をＷ２（Ｗ２＞Ｗ１）の整流板を複数枚の配置した場
合のフローパターンと、図２０に示す幅が一定のものを
複数枚の配置した場合のフローパターンは、図示のよう
に同様のものとなっていることが分かる。これらのフロ
ーパターンを、図１１に示す段差付き棒状の整流部材１
００を配置した場合のフローパターン及び図１６に示す
段差無し棒状の整流部材１００を配置した場合のフロー
パターンと比較した場合、それぞれほぼ同様にヘッダタ
ンク中心部を流れる冷媒が整流板によって周辺部に案内
されているのが分かる。また、出口空気温度も図２１及
び図２２に示すように略均一化されており冷房能力の大
幅な向上が認められることが分かる。したがって、棒状
の整流部材１００の代わりに整流板１２０を用いても、
本発明による作用効果は同様であることが分かる。The flow condition of the refrigerant in the header tank of the laminated heat exchanger in this example is schematically shown in FIGS. 19 and 20. Figure 19 shows a flow pattern when a plurality of rectifying plates are arranged, with the upstream side plate width being W1 and the downstream side plate width being W2 (W2>W1), and Fig. 20 showing a plurality of rectifier plates with a constant width. It can be seen that the flow pattern when two sheets are arranged is similar to that shown in the figure. These flow patterns are controlled by a stepped rod-shaped rectifying member 1 shown in FIG.
When comparing the flow pattern when the header tank 00 is arranged and the flow pattern when the straightening member 100 in the shape of a rod without a step shown in FIG. I understand that you are being guided. Furthermore, as shown in FIGS. 21 and 22, the outlet air temperature is also approximately equalized, and it can be seen that the cooling capacity is significantly improved. Therefore, even if the current plate 120 is used instead of the rod-shaped current member 100,
It can be seen that the effects of the present invention are similar.
【００３７】なお、上記の例では、伝熱管板１ｂのタン
ク部に眼鏡状に打ち抜いて開口部を形成した後の残余基
板１１０をさらに太鼓状に成形してなる整流板１２０を
ヘッダタンク内に配置しているが、図２３及び図２４に
示すように残余基板１１０を皿状に成形してなる皿状の
整流体１２５をタンク内に配置しても良い。伝熱管板１
ａ、１ｂのタンク部４ｂに皿状の整流体１２５を一体成
形した伝熱管板を４１ａ、４１ｂを組み合わせて構成し
た偏平伝熱管１Ｄを所定の枚数だけ、図２５に示すよう
に積層し、内部に皿状整流体１２５を連ねて、棒状の整
流部が構成されるように入口ヘッダ５Ｂを形成している
。なお、ここでは整流部材入り入口ヘッダ５Ｂを構成す
るのに伝熱管板４１ａ、４１ｂを組み合わせて構成した
偏平伝熱管１Ｄを用いたが、図２６に示すように、伝熱
管板４１ａの代わりに伝熱管板１ａと伝熱管板４１ｂを
組み合わせて構成した偏平伝熱管１Ｅを用いても良い。
この場合は、皿状整流体１２５が一つ飛びに並んだ構造
の整流部が入口ヘッダ５Ｂ内に構成される。In the above example, the rectifier plate 120, which is formed by further forming the remaining substrate 110 into a drum shape after punching out the tank portion of the heat exchanger tube plate 1b in the shape of glasses to form an opening, is placed inside the header tank. However, as shown in FIGS. 23 and 24, a dish-shaped flow regulator 125 formed by molding the remaining substrate 110 into a dish shape may be arranged in the tank. Heat exchanger tube plate 1
A predetermined number of flat heat exchanger tubes 1D, which are constructed by combining heat exchanger tube plates 41a and 41b with a dish-shaped fluid regulator 125 integrally molded in the tank portion 4b of a and 1b, are stacked as shown in FIG. The inlet header 5B is formed by connecting the dish-shaped flow regulators 125 to form a rod-shaped flow regulator. Here, a flat heat exchanger tube 1D constructed by combining heat exchanger tube plates 41a and 41b was used to configure the inlet header 5B containing a rectifying member, but as shown in FIG. You may use the flat heat exchanger tube 1E comprised by combining the heat tube plate 1a and the heat exchanger tube plate 41b. In this case, a flow rectifier having a structure in which dish-shaped flow rectifiers 125 are arranged one after another is configured in the inlet header 5B.
【００３８】図２７に他の変形例を示す。図２７に示す
実施例では、幅Ｗ２の整流部材１２０ｂの代わりに所定
の寸法Ｌだけ冷媒の流れにほぼ直交する方向に位置をず
らせて形成された整流板１２０ｃを交互に配置すること
によって、冷媒の流れ方向から見た整流板１２０ｃの投
影寸法がＷ２となるように幅Ｗ１の整流板１２０ｃを配
置したものである。こうすることによっても、幅Ｗ２の
整流板を実質的に配置したのと同様の効果が得られる。FIG. 27 shows another modification. In the embodiment shown in FIG. 27, instead of the rectifying member 120b having the width W2, rectifying plates 120c formed by shifting the position by a predetermined dimension L in a direction substantially perpendicular to the flow of the refrigerant are arranged alternately. The current plate 120c having a width W1 is arranged so that the projected dimension of the current plate 120c viewed from the flow direction is W2. By doing so, the same effect as that obtained by substantially arranging a rectifier plate having the width W2 can be obtained.
【００３９】又、本実施例として伝熱管板のタンク部に
一体成形された整流板１２０を入口ヘッダ５Ｂ内に複数
並べて整流部を構成しても良いことを示したが、本実施
例の変形例として、整流板１２０の断面形状は、図２８
及び図２９に示すような形状を適宜選定できる。In addition, although it has been shown in this embodiment that a plurality of rectifying plates 120 integrally formed in the tank portion of the heat exchanger tube plate may be arranged in the inlet header 5B to form a rectifying section, modifications of this embodiment are possible. As an example, the cross-sectional shape of the current plate 120 is shown in FIG.
And shapes as shown in FIG. 29 can be selected as appropriate.
【００４０】図２８に示す実施例では、整流板１２０ｅ
の断面形状を流れ方向に頂部を向けた山形状に形成して
いる。このように、整流板１２０ｅの断面形状を流れ方
向に頂部を向けた山形状に形成することにより、流れが
滑らかになり、液滴の衝突による衝撃音や渦流れによる
音の発生が軽減される。又、断面を山形に形成したので
、構造強度が増し、部材の板厚を薄くできる効果も有す
る。したがって、本実施例では、冷媒の流動音の軽減や
板厚を薄くできる効果がある。In the embodiment shown in FIG. 28, the current plate 120e
The cross-sectional shape is formed into a mountain shape with the top facing the flow direction. In this way, by forming the cross-sectional shape of the current plate 120e into a mountain shape with the top facing the flow direction, the flow becomes smooth, and the generation of impact noise due to collision of droplets and noise due to vortex flow is reduced. . Furthermore, since the cross section is formed into a chevron shape, the structural strength is increased and the thickness of the member can be reduced. Therefore, this embodiment has the effect of reducing refrigerant flow noise and reducing the plate thickness.
【００４１】図２９に示す実施例では、山形に形成した
整流板１２０ｆの山形頂部にスリットを設け、整流板１
２０ｆの下流側の負圧域にスリット部から冷媒を流入さ
せるようにしたものである。したがって、スリット部か
ら流入する冷媒によって、整流板１２０ｆの下流側に形
成される負圧の大きさの大きさが軽減されるので、整流
板１２０ｆの下流側の渦流れも抑えられ、渦流れによる
音の発生がさらに軽減されるという効果がある。In the embodiment shown in FIG. 29, a slit is provided at the top of the chevron-shaped rectifying plate 120f, and the rectifying plate 1
The refrigerant is made to flow into the negative pressure area downstream of 20f from the slit portion. Therefore, the magnitude of the negative pressure formed on the downstream side of the baffle plate 120f is reduced by the refrigerant flowing in from the slit part, so the vortex flow on the downstream side of the baffle plate 120f is also suppressed, and the eddy flow due to the vortex flow is suppressed. This has the effect of further reducing sound generation.
【００４２】本発明の第４の実施例を図３０から図３２
に示す。上記した実施例は、冷媒流路をＵ字形に形成す
ることによって、偏平伝熱管流路の両端に連通する二つ
のヘッダタンクが、偏平伝熱管の一端側に並列に配置さ
れた積層形熱交換器を示したものであるが、本実施例で
は、Ｕ字形流路とする代わりに直線状の流路を形成し、
上下にヘッダタンクを配置した積層形熱交換器を構成し
ている。A fourth embodiment of the present invention is shown in FIGS. 30 to 32.
Shown below. The above embodiment is a laminated heat exchanger in which two header tanks communicating with both ends of a flat heat transfer tube flow path are arranged in parallel at one end of the flat heat transfer tube by forming the refrigerant flow path in a U-shape. However, in this example, a straight flow path is formed instead of a U-shaped flow path,
It consists of a stacked heat exchanger with header tanks placed above and below.
【００４３】図３０に本実施例の積層形熱交換器の流路
構造を模式的に縦断面図として示す。図３０に示す実施
例では、上部に設けられたヘッダ２０４Ａ、２０４Ｂの
中間部に仕切り板Ｓを設け、上部のヘッダと下部のヘッ
ダとの間に複数の偏平伝熱管２０１からなる二つの流路
群を構成し、双方のヘッダ間で一回Ｕタ−ンして冷媒を
流すようにしたものである。上部のヘッダ２０４Ａ内に
流入した冷媒は、複数の偏平伝熱管２０１内を分岐して
流下し、出口ヘッダ２０５Ａに至り、出口ヘッダ２０５
Ａに隣接している入口ヘッダ２０５Ｂ内へ冷媒流入口１
０７ａを介して流入する。冷媒流入口１０７ａの奥側に
は整流部材１００が配置されているので、冷媒流入口１
０７ａを介して入口ヘッダ２０５Ｂ内へ流入した冷媒は
、入口ヘッダ２０５Ｂに連なる複数の偏平伝熱管２０１
内へほぼ均一に分配され、冷房能力が向上する。なお、
本実施例では、上部のヘッダタンクに仕切り板Ｓを設け
た場合であるが、これとは反対に下部のヘッダタンクに
仕切り板Ｓを設け、上部のヘッダタンク内に整流部材を
配置する構成としてもよい。FIG. 30 schematically shows the flow path structure of the laminated heat exchanger of this example as a longitudinal sectional view. In the embodiment shown in FIG. 30, a partition plate S is provided in the middle part of the headers 204A and 204B provided at the upper part, and two flow channels made of a plurality of flat heat exchanger tubes 201 are provided between the upper header and the lower header. The refrigerant is configured as a group and makes one U-turn between both headers to allow the refrigerant to flow. The refrigerant that has flowed into the upper header 204A branches and flows down through the plurality of flat heat exchanger tubes 201, reaches the outlet header 205A, and then flows through the plurality of flat heat exchanger tubes 201.
Refrigerant inlet 1 into inlet header 205B adjacent to A
07a. Since the rectifying member 100 is arranged on the back side of the refrigerant inlet 107a, the refrigerant inlet 1
The refrigerant that has flowed into the inlet header 205B through 07a flows through the plurality of flat heat exchanger tubes 201 connected to the inlet header 205B.
It is distributed almost evenly throughout the air, improving cooling capacity. In addition,
In this example, the partition plate S is provided in the upper header tank, but on the contrary, a structure in which the partition plate S is provided in the lower header tank and the flow regulating member is arranged in the upper header tank is also possible. Good too.
【００４４】図３１に本実施例の積層形熱交換器の流路
構造を模式的に縦断面図として示す。上部に設けられた
入口ヘッダ２０４Ａと出口ヘッダ２０４Ｂとの間は、仕
切り板Ｓによって仕切られており、底部には出口ヘッダ
２０５Ｂが設けられ、入口ヘッダ２０４Ａの冷媒流入口
１０６ａに隣接して整流部材１００ａが配置されている
。また、入口ヘッダ２０５Ｂ内には整流部材１００が二
分割され、冷媒流入口１０７ａに隣接して整流部材１０
０ｂが、奥側に整流部材１００ｃが配置されている。
この実施例は、特に冷媒流量が少なく液冷媒の割合
が多い冷媒９０が流入してくる蒸発器に好適である。即
ち、入口パイプ６０から流入口１０６ａを介して入口ヘ
ッダ２０４Ａ内へ流入した液冷媒の割合が多い冷媒９０
は、重力の作用によって液滴が落下して流入口１０６ａ
に近接した偏平伝熱管２０１内へ多く流入しようとする
。ところが、流入口１０６ａに近接して配置され整流部
材１００ａの整流作用によって、流入口１０６ａに近接
した偏平伝熱管２０１内へ多く流入するのが抑えられる
。よって、冷媒は入口ヘッダ２０４Ａに連なる伝熱管内
へ略均一に分配される。FIG. 31 schematically shows the flow path structure of the laminated heat exchanger of this example as a longitudinal sectional view. A partition plate S separates the inlet header 204A and the outlet header 204B provided at the top, and an outlet header 205B is provided at the bottom, and a flow regulating member is provided adjacent to the refrigerant inlet 106a of the inlet header 204A. 100a is arranged. Further, the rectifying member 100 is divided into two parts in the inlet header 205B, and the rectifying member 100 is arranged adjacent to the refrigerant inlet 107a.
0b, the rectifying member 100c is arranged on the back side. This embodiment is particularly suitable for an evaporator into which a refrigerant 90 having a small refrigerant flow rate and a high proportion of liquid refrigerant flows into the evaporator. That is, the refrigerant 90 has a large proportion of liquid refrigerant that has flowed into the inlet header 204A from the inlet pipe 60 through the inlet 106a.
The droplets fall due to the action of gravity and flow into the inlet 106a.
A large amount of heat tends to flow into the flat heat exchanger tube 201 near the . However, due to the rectifying action of the rectifying member 100a disposed close to the inlet 106a, a large amount of heat is prevented from flowing into the flat heat exchanger tube 201 close to the inlet 106a. Therefore, the refrigerant is distributed substantially uniformly into the heat transfer tubes connected to the inlet header 204A.
【００４５】次に、入口ヘッダ２０４Ａに連なる伝熱管
内を、空気と熱交換しながら気相冷媒の割合を増し流下
した冷媒は、冷媒流入口１０７ａを介して入口ヘッダ２
０５Ｂ内へ環状流となって流入する。冷媒流入口１０７
ａから流入した冷媒噴流は液冷媒の割合が多く、その外
周側には冷媒液滴が多く集まって流れているが、この冷
媒液滴がヘッダ部の内面に突き出しているタンク接合リ
ブ１５０によって塞き止められて、冷媒流入口１０７ａ
に隣接した伝熱管内へ冷媒液滴が大量に流入しようとす
る。一方、噴流中心部の冷媒液滴は慣性力によって入口
ヘッダ２０５Ｂの奥側（図３４の左端側）へ多く流れよ
うとする。冷媒流入口１０７ａに近接して配置された整
流部１００ｃの正流作用によって、液冷媒は２０５Ｂに
連なる伝熱管内へ略均一に分配される。以上述べたよう
に、本実施例によれば、熱交換器全体として冷媒分配が
均一化され、出口空気温度も均一となるので、冷房能力
が大幅に向上する。Next, the refrigerant flowing down the heat exchanger tube connected to the inlet header 204A while exchanging heat with air and increasing the proportion of gas phase refrigerant flows into the inlet header 2 via the refrigerant inlet 107a.
It flows into 05B as an annular flow. Refrigerant inlet 107
The refrigerant jet that flows in from a has a large proportion of liquid refrigerant, and many refrigerant droplets gather on the outer circumference and flow, but these refrigerant droplets are blocked by the tank joint rib 150 protruding from the inner surface of the header part. The refrigerant inlet 107a is blocked.
A large amount of refrigerant droplets attempt to flow into the heat transfer tube adjacent to the . On the other hand, many of the refrigerant droplets at the center of the jet tend to flow toward the back of the inlet header 205B (toward the left end in FIG. 34) due to inertial force. Due to the forward flow action of the rectifier 100c disposed close to the refrigerant inlet 107a, the liquid refrigerant is distributed almost uniformly into the heat transfer tubes connected to the refrigerant inlet 205B. As described above, according to this embodiment, the refrigerant distribution is made uniform throughout the heat exchanger, and the outlet air temperature is also made uniform, so that the cooling capacity is significantly improved.
【００４６】図３２に本実施例の積層形熱交換器の流路
構造を模式的に縦断面図として示す。図３２に示す積層
形熱交換器では、上下に配置された入口および出口ヘッ
ダタンク２０５、２０６のそれぞれの中央部に入口、出
口部を設け、左右に分けて冷媒を流すようにしたもので
は、入口、出口部を設け、左右に分けた冷媒を流すよう
にしたもので、入口ヘッダタンクの左右の奥側にはそれ
ぞれ整流部材１００が配置されている。整流部材１００
の作用効果は、図３０に示す実施例と同様である。
以上述べたように本実施例によれば、熱交換器全体とし
て冷媒分配が均一化され出口空気温度も均一になるので
、冷房能力が大幅に向上する。FIG. 32 schematically shows the flow path structure of the laminated heat exchanger of this example as a longitudinal sectional view. In the laminated heat exchanger shown in FIG. 32, an inlet and an outlet are provided in the center of each of the upper and lower inlet and outlet header tanks 205 and 206, and the refrigerant is divided into left and right parts. An inlet and an outlet are provided to allow the refrigerant to flow divided into left and right sides, and rectifying members 100 are arranged at the left and right rear sides of the inlet header tank, respectively. Rectifying member 100
The functions and effects are similar to those of the embodiment shown in FIG.
As described above, according to this embodiment, the refrigerant distribution is made uniform throughout the heat exchanger and the outlet air temperature is also made uniform, so that the cooling capacity is significantly improved.
【００４７】なお、以上述べた実施例は、入口ヘッダタ
ンク内に整流部材を設けることによって冷媒の流れを整
流して、入口ヘッダタンクに連なる伝熱管内へ冷媒を均
一に分配しようとするものであり、このような技術思想
を実現できる技術手段であれば上述した実施例に限られ
るものではない。[0047] In the embodiments described above, the flow of refrigerant is rectified by providing a rectifying member in the inlet header tank, and the refrigerant is uniformly distributed into the heat transfer tubes connected to the inlet header tank. However, the present invention is not limited to the above-mentioned embodiments as long as it is a technical means that can realize such a technical idea.
【００４８】[0048]
【発明の効果】以上説明したように、本発明の積層形熱
交換器によれば、第１に、偏平伝熱管内に冷媒を分岐し
て流入させるための入口ヘッダ部内に配置した整流部材
によって、タンク中心部の流れが周辺部に案内されるの
で、入口パイプから流入したタンク中心部のミスト状の
冷媒の液滴がタンクの周辺部に散らばり、慣性力によっ
て反入口パイプ側端まで液滴が到達するのが抑えられ、
一端側の伝熱管内に液冷媒が多く流れ込むのを防ぐこと
ができる。この結果、ヘッダに連なる伝熱管内へ冷媒を
均一に分配できるので、出口空気温度が均一化され冷房
能力を向上できるという効果を奏する。As explained above, according to the laminated heat exchanger of the present invention, firstly, the rectifying member disposed within the inlet header section for branching and inflowing the refrigerant into the flat heat exchanger tubes. , as the flow in the center of the tank is guided to the periphery, the mist-like refrigerant droplets in the center of the tank that flowed in from the inlet pipe are scattered around the periphery of the tank, and due to inertia, the droplets spread to the end opposite to the inlet pipe. is suppressed from reaching the
It is possible to prevent a large amount of liquid refrigerant from flowing into the heat transfer tube at one end. As a result, the refrigerant can be uniformly distributed into the heat transfer tubes connected to the header, resulting in the effect that the outlet air temperature can be made uniform and the cooling capacity can be improved.
【００４９】又、入口ヘッダ部が、個々に整流板が形成
される複数枚の偏平伝熱管で形成しても、タンク中心部
の流れが周辺部に案内されるので、入口パイプから流入
したタンク中心部のミスト状の冷媒の液滴がタンクの周
辺部に散らばり、慣性力によって反入口パイプ側端まで
液滴が到達するのが抑えられ、一端側の伝熱管内に液冷
媒が多く流れ込むのを防ぐことができ、この結果、ヘッ
ダに連なる伝熱管内へ冷媒を均一に分配できるので、出
口空気温度が均一化され冷房能力を向上できるという効
果を奏する。Furthermore, even if the inlet header section is formed of a plurality of flat heat exchanger tubes each having a rectifier plate, the flow from the center of the tank is guided to the periphery, so that the flow from the inlet pipe into the tank The mist-like refrigerant droplets in the center are scattered around the tank, and the inertial force prevents the droplets from reaching the opposite end of the inlet pipe, allowing more liquid refrigerant to flow into the heat transfer tube at one end. As a result, the refrigerant can be uniformly distributed into the heat transfer tubes connected to the header, resulting in the effect that the outlet air temperature can be made uniform and the cooling capacity can be improved.
【００５０】第２に、偏平伝熱管内に冷媒を分岐して流
入させるための入口ヘッダ部が、個々に整流板が形成さ
れる複数枚の偏平伝熱管で形成しているので、偏平伝熱
管とともに整流板を同時に成形することができ、熱交換
器の成形が容易となる効果がある。Second, since the inlet header section for branching and injecting the refrigerant into the flat heat exchanger tube is formed by a plurality of flat heat exchanger tubes each having a rectifying plate formed thereon, the flat heat exchanger tube In addition, the current plate can be molded at the same time, which has the effect of facilitating the molding of the heat exchanger.
【００５１】[0051]
【図１】本発明の第１の実施例を示す積層形熱交換器の
全体構成の斜視図である。FIG. 1 is a perspective view of the overall configuration of a laminated heat exchanger showing a first embodiment of the present invention.
【図２】伝熱管板の斜視図である。FIG. 2 is a perspective view of a heat exchanger tube plate.
【図３】伝熱管板の斜視図である。FIG. 3 is a perspective view of a heat exchanger tube plate.
【図４】端部伝熱管板の斜視図である。FIG. 4 is a perspective view of an end heat exchanger tube plate.
【図５】端部伝熱管板の斜視図である。FIG. 5 is a perspective view of an end heat exchanger tube plate.
【図６】インナーフィンの斜視図である。FIG. 6 is a perspective view of the inner fin.
【図７】インナーフィンの要部を拡大した斜視図である
。FIG. 7 is an enlarged perspective view of essential parts of the inner fin.
【図８】ヘッダ部の横断面図である。FIG. 8 is a cross-sectional view of the header section.
【図９】整流部材の取付け状態を示した斜視図である。FIG. 9 is a perspective view showing a state in which the rectifying member is attached.
【図１０】後方ヘッダ部の縦断面図である。FIG. 10 is a longitudinal sectional view of the rear header section.
【図１１】本実施例の流動状況を模式的に示したヘッダ
部の横断面図である。FIG. 11 is a cross-sectional view of the header section schematically showing the flow situation in this example.
【図１２】従来例の流動状況を模式的に示したヘッダ部
の横断面図である。FIG. 12 is a cross-sectional view of a header section schematically showing a flow situation in a conventional example.
【図１３】整流部材の配置状態を示す入り口ヘッダの横
断面図である。FIG. 13 is a cross-sectional view of the entrance header showing the arrangement of the flow regulating members.
【図１４】本実施例の場合の出口空気温度の測定結果を
示す図である。FIG. 14 is a diagram showing measurement results of outlet air temperature in the case of this example.
【図１５】ヘッダ部の横断面図である。FIG. 15 is a cross-sectional view of the header section.
【図１６】本発明の第２の実施例を示すヘッダ部の横断
面図である。FIG. 16 is a cross-sectional view of a header section showing a second embodiment of the present invention.
【図１７】入り口ヘッダの横断面図である。FIG. 17 is a cross-sectional view of the entrance header.
【図１８】本発明の第３の実施例を示す整流板付き伝熱
管板の要部斜視図である。FIG. 18 is a perspective view of a main part of a heat exchanger tube plate with a rectifier plate showing a third embodiment of the present invention.
【図１９】幅が異なる２種類の整流板を配置した入り口
ヘッダの横断面図である。FIG. 19 is a cross-sectional view of an entrance header in which two types of rectifier plates having different widths are arranged.
【図２０】幅が一様な整流板を配置した入り口ヘッダの
横断面図である。FIG. 20 is a cross-sectional view of an entrance header in which a baffle plate having a uniform width is arranged.
【図２１】整流部材を配置状態を示す入り口ヘッダの横
断面図である。FIG. 21 is a cross-sectional view of the entrance header showing a state in which the flow regulating member is arranged.
【図２２】本実施例の場合の出口空気温度の測定結果を
示す図である。FIG. 22 is a diagram showing measurement results of outlet air temperature in the case of this example.
【図２３】皿状の整流体付き伝熱管板の要部の斜視図で
ある。FIG. 23 is a perspective view of a main part of a dish-shaped heat exchanger tube plate with a flow regulator.
【図２４】皿状の整流体付き伝熱管板の要部の斜視図で
ある。FIG. 24 is a perspective view of a main part of a dish-shaped heat exchanger tube plate with a flow regulator.
【図２５】皿状の整流部材が配置された入り口ヘッダの
横断面図である。FIG. 25 is a cross-sectional view of an inlet header in which a dish-shaped flow straightening member is arranged.
【図２６】皿状の整流体を一つ飛びに配置した入り口ヘ
ッダの横断面図である。FIG. 26 is a cross-sectional view of an inlet header in which dish-shaped flow regulators are arranged one after the other.
【図２７】整流部材が配置された入り口ヘッダの横断面
図である。FIG. 27 is a cross-sectional view of an inlet header in which a flow regulating member is arranged.
【図２８】山形に成形した整流板を入り口ヘッダ内に山
形頂部を先頭に一列に配置した横断面図である。FIG. 28 is a cross-sectional view of rectifier plates formed into chevron shapes arranged in a line in an entrance header with the chevron tops at the front.
【図２９】流れに対して迎え角を持った整流板を入り口
ヘッダ内に二列にハの字状に配置した横断面図である。FIG. 29 is a cross-sectional view of two rows of baffle plates arranged in a V-shape inside the entrance header, each having an angle of attack with respect to the flow.
【図３０】本発明の第４の実施例を示す積層形熱交換器
の流路構造を模式的に示す縦断面図である。FIG. 30 is a vertical cross-sectional view schematically showing the flow passage structure of a laminated heat exchanger according to a fourth embodiment of the present invention.
【図３１】積層形熱交換器の流路構造を模式的に示す縦
断面図である。FIG. 31 is a vertical cross-sectional view schematically showing the flow path structure of a laminated heat exchanger.
【図３２】積層形熱交換器の流路構造を模式的に示す縦
断面図である。FIG. 32 is a vertical cross-sectional view schematically showing the flow passage structure of a laminated heat exchanger.
１…偏平伝熱管、１Ａ、１Ｂ…端部偏平伝熱管、１Ｃ、
１Ｄ、１Ｅ…整流板、整流体付き偏平伝熱管、２…冷媒
流路、４…前方ヘッダ、５…後方ヘッダ、４ａ、４ｂ…
タンク部、５Ｂ…入り口ヘッダ、１００…整流部材、１
０７…冷媒流入口、１２０…整流板、１２５…皿状整流
体1... Flat heat exchanger tube, 1A, 1B... End flat heat exchanger tube, 1C,
1D, 1E...straightening plate, flat heat exchanger tube with flow straightener, 2...refrigerant channel, 4...front header, 5...rear header, 4a, 4b...
Tank part, 5B... Entrance header, 100... Rectifying member, 1
07... Refrigerant inlet, 120... Current plate, 125... Dish-shaped flow regulator
Claims (16)
互に積層した積層形熱交換器において、前記偏平伝熱管
群の空気流入側に前方ヘッダ部、空気流出側に後方ヘッ
ダ部を設けるとともに、前記後方ヘッダ部に形成された
前記偏平伝熱管内に冷媒を分岐して流入させるための入
口ヘッダ部内に整流部材を配置したことを特徴とする積
層形熱交換器。1. A stacked heat exchanger in which a plurality of air side fins and flat heat exchanger tubes are alternately stacked, wherein a front header section is provided on the air inflow side of the flat heat exchanger tube group, a rear header section is provided on the air outflow side, and A laminated heat exchanger, characterized in that a rectifying member is disposed within an inlet header section for branching and flowing a refrigerant into the flat heat exchanger tubes formed in the rear header section.
互に積層した積層形熱交換器において、前記偏平伝熱管
群の空気流入側に前方ヘッダ部、空気流出側に後方ヘッ
ダ部を設けるとともに、前記前方ヘッダ部に形成された
前記偏平伝熱管内に冷媒を分岐して流入させるための入
口ヘッダ部内に整流部材を配置したことを特徴とする積
層形熱交換器。2. A laminated heat exchanger in which a plurality of air-side fins and flat heat exchanger tubes are alternately stacked, wherein a front header section is provided on the air inflow side of the flat heat exchanger tube group, and a rear header section is provided on the air outflow side; A laminated heat exchanger, characterized in that a rectifying member is disposed within an inlet header section for branching and flowing a refrigerant into the flat heat exchanger tubes formed in the front header section.
互に積層した積層形熱交換器において、前記偏平伝熱管
群の空気流入側に前方ヘッダ部、空気流出側に後方ヘッ
ダ部を設けるとともに、前記前方ヘッダ部が仕切り板に
よって二分割されているものであって、前記後方ヘッダ
部に形成された前記偏平伝熱管内に冷媒を分岐して流入
させるための入口ヘッダ部内に整流部材を配置したこと
を特徴とする積層形熱交換器。3. A stacked heat exchanger in which a plurality of air side fins and flat heat exchanger tubes are alternately stacked, wherein a front header section is provided on the air inflow side of the flat heat exchanger tube group, and a rear header section is provided on the air outflow side of the flat heat exchanger tube group; , the front header section is divided into two by a partition plate, and a flow straightening member is arranged in the inlet header section for branching and flowing the refrigerant into the flat heat exchanger tubes formed in the rear header section. A laminated heat exchanger characterized by:
互に積層した積層形熱交換器において、前記偏平伝熱管
群の空気流入側に前方ヘッダ部、空気流出側に後方ヘッ
ダ部を設けるとともに、前記前方ヘッダ部あるいは後方
ヘッダに形成された前記偏平伝熱管内に冷媒を分岐して
流入させるための入口ヘッダ部内が、流入された冷媒を
環状流として分配されるように形成されていることを特
徴とする積層形熱交換器。4. A stacked heat exchanger in which a plurality of air-side fins and flat heat exchanger tubes are alternately stacked, wherein a front header section is provided on the air inflow side of the flat heat exchanger tube group, and a rear header section is provided on the air outflow side; The inside of the inlet header section for branching and inflowing the refrigerant into the flat heat exchanger tubes formed in the front header section or the rear header is formed so that the inflowing refrigerant is distributed as an annular flow. A laminated heat exchanger featuring:
方タンク部、後方タンク部を備え、前記二つのタンク部
を連通し、少なくても一回蛇行して流れる冷媒通路部を
形成した偏平伝熱管を複数枚積層し、前記前方ヘッダ部
あるいは後方ヘッダ部に前記偏平伝熱管内に冷媒を分岐
して流入させるための入口ヘッダ部を、前記前方ヘッダ
部に冷媒出口部を設けて、前記前方ヘッダ部と後方ヘッ
ダ部との間に一つ又は複数の流路群を形成するとともに
、前記入口ヘッダ部内に整流部材を配置したことを特徴
とする積層形熱交換器。5. A flat refrigerant comprising a front tank part and a rear tank part which are parallel to each other and communicate with each other in the longitudinal direction, and which connects the two tank parts and forms a refrigerant passage part that meanderes at least once. A plurality of heat exchanger tubes are stacked, an inlet header section for branching and inflowing refrigerant into the flat heat exchanger tubes is provided in the front header section or the rear header section, and a refrigerant outlet section is provided in the front header section. 1. A laminated heat exchanger, characterized in that one or more flow path groups are formed between a front header section and a rear header section, and a flow regulating member is disposed within the inlet header section.
互に積層した積層形熱交換器において、前記偏平伝熱管
群の空気流入側に前方ヘッダ部、空気流出側に後方ヘッ
ダ部を設けるとともに、前記偏平伝熱管内に冷媒を分岐
して流入させるための入口ヘッダ部が、個々に整流板が
形成される複数枚の偏平伝熱管で形成されていることを
特徴とする積層形熱交換器。6. A stacked heat exchanger in which a plurality of air-side fins and flat heat exchanger tubes are alternately stacked, wherein a front header section is provided on the air inflow side of the flat heat exchanger tube group, and a rear header section is provided on the air outflow side; , a laminated heat exchanger characterized in that the inlet header section for branching and flowing the refrigerant into the flat heat exchanger tubes is formed of a plurality of flat heat exchanger tubes each having a rectifying plate formed thereon. .
互に積層した積層形熱交換器において、前記偏平伝熱管
群の上部および下部にヘッダ部が形成され、、空気流出
側に後方ヘッダ部を設けるとともに、前記前方ヘッダ部
が仕切り板によって二分割されているものであって、前
記後方ヘッダ部に形成された前記偏平伝熱管内に冷媒を
分岐して流入させるための入口ヘッダ部内に整流部材を
配置したことを特徴とする積層形熱交換器。7. A stacked heat exchanger in which a plurality of air side fins and flat heat exchanger tubes are alternately stacked, header portions are formed at the upper and lower portions of the flat heat exchanger tube group, and a rear header portion is formed on the air outflow side. and the front header section is divided into two by a partition plate, and a rectifier is provided in the inlet header section for branching and flowing the refrigerant into the flat heat exchanger tubes formed in the rear header section. A laminated heat exchanger characterized by an arrangement of members.
互に積層した積層形熱交換器において、前記偏平伝熱管
群の上部および下部にヘッダ部が形成され、前記下部の
ヘッダ部に形成された前記偏平伝熱管内に冷媒を分岐し
て流入させるための入口ヘッダ部内に整流部材を配置し
たことを特徴とする積層形熱交換器。8. A stacked heat exchanger in which a plurality of air-side fins and flat heat exchanger tubes are alternately stacked, wherein header portions are formed at the upper and lower portions of the flat heat exchanger tube group, and header portions are formed at the lower header portion. A laminated heat exchanger characterized in that a rectifying member is disposed within an inlet header portion for branching and flowing a refrigerant into the flat heat exchanger tube.
流れに沿って除々に大きくした請求項１から８のいずれ
かに記載の積層形熱交換器。9. The laminated heat exchanger according to claim 1, wherein the cross-sectional area of the rectifying member gradually increases along the flow from the inflow direction of the refrigerant.
て、段階的に大きくした請求項１から８のいずれかに記
載の積層形熱交換器。10. The laminated heat exchanger according to claim 1, wherein the width of the rectifying member is increased stepwise along the inflow direction of the refrigerant.
に沿って略一定に形成されている請求項１から８のいず
れかに記載の積層形熱交換器。11. The laminated heat exchanger according to claim 1, wherein the width of the rectifying member is formed to be substantially constant along the longitudinal direction of the inlet header.
から流れに沿って除々に大きくした請求項１から８のい
ずれかに記載の積層形熱交換器。12. The laminated heat exchanger according to claim 1, wherein the cross-sectional area of the baffle plate gradually increases along the flow from the inflow direction of the refrigerant.
凹み部を素材平板に押出し、流路凹み部よりさらに深く
押し出して流路端にタンク部を形成し、タンク部には残
余基板を残して眼鏡状開口を打ち抜き、この残余基板を
タンク部とは反対方向に押し出すようにプレス成形して
形成されるものである請求項６に記載の積層形熱交換器
。13. The current plate extrudes the concave portion of the flow path onto a flat material plate while leaving the joint rib portion, and pushes the concave portion of the flow path deeper than the concave portion to form a tank portion at the end of the flow path, and the tank portion has a remaining portion. 7. The laminated heat exchanger according to claim 6, wherein the laminated heat exchanger is formed by punching out a spectacle-shaped opening while leaving the substrate, and press-molding the remaining substrate in a direction opposite to the tank portion.
頂部を向けた山形形状に形成されている請求項６、１２
又は１３に記載の積層形熱交換器。14. Claims 6 and 12, wherein the cross section of the current plate is formed in a chevron shape with the top facing in the inflow direction of the refrigerant.
Or the laminated heat exchanger according to 13.
が設けられている請求項１４に記載の積層形熱交換器。15. The laminated heat exchanger according to claim 14, wherein a slit is provided at the top of the chevron-shaped rectifier plate.
角方向にずれて配置されている請求項６、１２、１３、
１４又は１５に記載の積層形熱交換器。16. Claims 6, 12, 13, wherein the baffle plate is disposed offset in a direction perpendicular to the inflow direction of the refrigerant.
16. The laminated heat exchanger according to 14 or 15.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3095148A JP2751657B2 (en) | 1991-04-25 | 1991-04-25 | Stacked heat exchanger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3095148A JP2751657B2 (en) | 1991-04-25 | 1991-04-25 | Stacked heat exchanger |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH04324078A true JPH04324078A (en) | 1992-11-13 |
| JP2751657B2 JP2751657B2 (en) | 1998-05-18 |
Family
ID=14129718
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP3095148A Expired - Lifetime JP2751657B2 (en) | 1991-04-25 | 1991-04-25 | Stacked heat exchanger |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2751657B2 (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6227290B1 (en) | 1995-02-16 | 2001-05-08 | Zexel Corporation | Laminated heat exchanger |
| FR2825792A1 (en) * | 2001-06-07 | 2002-12-13 | Valeo Climatisation | Evaporator for motor vehicle air conditioning has stacked plates defining U-shaped flow paths between each pair of plates |
| US6868696B2 (en) * | 2003-04-18 | 2005-03-22 | Calsonic Kansei Corporation | Evaporator |
| WO2007046358A1 (en) * | 2005-10-17 | 2007-04-26 | Calsonic Kansei Corporation | Evaporator |
| CN100351603C (en) * | 2003-09-15 | 2007-11-28 | 汉拏空调株式会社 | Heat exchanger |
| JP2012021682A (en) * | 2010-07-13 | 2012-02-02 | Mitsubishi Electric Corp | Heat exchanger and heat pump system having the same |
| JP2013508657A (en) * | 2009-10-23 | 2013-03-07 | フォイト パテント ゲーエムベーハー | Heat exchanger plate and evaporator having the same |
| CN104990433A (en) * | 2015-06-04 | 2015-10-21 | 中国科学院理化技术研究所 | Plate-fin heat exchanger |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5873526B2 (en) * | 2014-05-07 | 2016-03-01 | 高松機械工業株式会社 | Spindle base cooling tank |
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| JPS633153A (en) * | 1986-06-23 | 1988-01-08 | 株式会社デンソー | Refrigerant evaporator |
| JPH01102660U (en) * | 1987-12-28 | 1989-07-11 |
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Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6227290B1 (en) | 1995-02-16 | 2001-05-08 | Zexel Corporation | Laminated heat exchanger |
| FR2825792A1 (en) * | 2001-06-07 | 2002-12-13 | Valeo Climatisation | Evaporator for motor vehicle air conditioning has stacked plates defining U-shaped flow paths between each pair of plates |
| US6868696B2 (en) * | 2003-04-18 | 2005-03-22 | Calsonic Kansei Corporation | Evaporator |
| CN100351603C (en) * | 2003-09-15 | 2007-11-28 | 汉拏空调株式会社 | Heat exchanger |
| US7461687B2 (en) | 2003-09-15 | 2008-12-09 | Halla Climate Control Corporation | Heat exchanger |
| WO2007046358A1 (en) * | 2005-10-17 | 2007-04-26 | Calsonic Kansei Corporation | Evaporator |
| JP2013508657A (en) * | 2009-10-23 | 2013-03-07 | フォイト パテント ゲーエムベーハー | Heat exchanger plate and evaporator having the same |
| JP2012021682A (en) * | 2010-07-13 | 2012-02-02 | Mitsubishi Electric Corp | Heat exchanger and heat pump system having the same |
| CN104990433A (en) * | 2015-06-04 | 2015-10-21 | 中国科学院理化技术研究所 | Plate-fin heat exchanger |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2751657B2 (en) | 1998-05-18 |
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