JP2003519355A - Evaporator - Google Patents

Evaporator

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Publication number
JP2003519355A
JP2003519355A JP2001549980A JP2001549980A JP2003519355A JP 2003519355 A JP2003519355 A JP 2003519355A JP 2001549980 A JP2001549980 A JP 2001549980A JP 2001549980 A JP2001549980 A JP 2001549980A JP 2003519355 A JP2003519355 A JP 2003519355A
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JP
Japan
Prior art keywords
evaporator
tube
tubes
fluid
brazed
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
Application number
JP2001549980A
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Japanese (ja)
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JP4869529B2 (en
Inventor
プランション ローラン
Original Assignee
ヴァレオ クリマチザション
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
    • 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
    • F28D1/0316—Assemblies of conduits in parallel
    • 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
    • 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
    • F28F9/0202—Header boxes having their inner space divided by partitions
    • F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions
    • F28F9/0209—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only transversal partitions

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

(57)【要約】 本発明は、空気流と冷媒流体の間で熱交換するための熱交換器用の蒸発器であって、平らな管１が、波形スペーサ２と交互の配置され、このスペーサにより、管同士の間の距離をｄに保持し、スペーサの波形の間の間隙を介して、管の幅方向の空気流の通路を形成し、管の両端が、対向する２個の流体箱とそれぞれ連通し、蒸発器内で、冷媒流体のために、少なくとも２つの移動路を確保している。本発明の特徴は、幅方向における蒸発器の寸法が、20 mmと55 mmの間であり、距離ｄが、4.0 mmと7.6 mm の間である。 (57) The present invention is an evaporator for a heat exchanger for exchanging heat between an air flow and a refrigerant fluid, wherein flat tubes 1 are alternately arranged with corrugated spacers 2, and this spacer Thus, the distance between the tubes is maintained at d, an air flow passage in the width direction of the tubes is formed through the gap between the corrugations of the spacers, and both ends of the tubes are opposed to two fluid boxes. And at least two movement paths are secured for the refrigerant fluid in the evaporator. A feature of the present invention is that the evaporator dimension in the width direction is between 20 mm and 55 mm, and the distance d is between 4.0 mm and 7.6 mm.

Description

【発明の詳細な説明】Detailed Description of the Invention

【０００１】[0001]

【発明の属する技術分野】TECHNICAL FIELD OF THE INVENTION

本発明は、空気流と冷媒流体の間で熱交換するために、この冷媒流体を液相か
ら気相に変化させる蒸発器に関し、特にモータ車両の乗車室の空調装置に設けら
れ、管バンクを有し、この管バンクが、一列の平らな管と、距離ｄで、管同士を
互いに離隔するための波形スペーサとよりなり、このスペーサの波形の間の間隙
を介して、管の幅方向の空気流の通路を形成し、各管の両端が、管バンクに対し
て、互いに反対方向に設けられた２個の流体箱とそれぞれ連通し、蒸発器内の冷
媒流体のための少なくとも２本の移動路を形成している蒸発器に関する。The present invention relates to an evaporator that changes a refrigerant fluid from a liquid phase to a vapor phase in order to exchange heat between an air flow and a refrigerant fluid, and more particularly to an evaporator provided in an air conditioner in a passenger compartment of a motor vehicle, The bank of tubes comprises a row of flat tubes and corrugated spacers for separating the tubes from each other at a distance d, with a gap between the corrugations of the spacers in the width direction of the tubes. An air flow passage is formed, and both ends of each tube communicate with two fluid boxes provided in opposite directions to the tube bank, respectively, and at least two tubes for refrigerant fluid in the evaporator are formed. It relates to an evaporator forming a moving path.

【０００２】 このような蒸発器は、Ｕ字型蒸発器とは異なる正面循環型蒸発器と呼ばれてい
る。Ｕ字型蒸発器は、２本の枝管が１個の流体箱の各チャンバとそれぞれ連通し
ているＵ字型管を冷媒流体が循環している。移動路の数とは、蒸発器の入口と出
口の間で、１つの流体箱から他の流体箱までの管内での冷媒流体の移動の回数を
意味している。入口と出口が２個の流体箱にそれぞれ設けられている場合、その
数は奇数となり、同一の流体箱にある場合に、偶数となる。Such an evaporator is called a front circulation type evaporator, which is different from the U-shaped evaporator. In the U-shaped evaporator, the refrigerant fluid circulates through the U-shaped pipe in which the two branch pipes are in communication with the respective chambers of one fluid box. The number of moving paths means the number of times the refrigerant fluid moves in a pipe from one fluid box to another between the inlet and the outlet of the evaporator. When the inlet and the outlet are provided in each of the two fluid boxes, the number is odd, and when they are in the same fluid box, the number is even.

【０００３】 その技術に応じて、流体箱は管に追加されるか、あるいは管と同一の部材に形
成される。Depending on the technology, the fluid box is either added to the tube or formed in the same piece as the tube.

【０００４】 正面循環型のものは、Ｕ字型のものと比べて、各移動路に使用される所定の数
の管に対して、冷媒流体の通過する管の長さを減少させ、それにより、液相と気
相の分離のみならず、圧力ヘッドの損失と冷媒流体の対応する加熱を減少させる
という利点がある。そこで、空気流との熱交換は、１本の移動路の種々の管の間
の、より低く、かつより均一な冷媒流体温度により、高められる。The front circulation type reduces the length of the pipe through which the refrigerant fluid passes, for a given number of pipes used in each moving path, as compared with the U-shaped type, thereby , And has the advantage of not only separating the liquid and gas phases, but also reducing the pressure head loss and the corresponding heating of the refrigerant fluid. There, heat exchange with the air stream is enhanced by the lower and more uniform refrigerant fluid temperature between the various tubes of a single path.

【０００５】 正面循環型のものは、また、すべて同一な管を使用しうるので、製造を自動化
出来、蒸発器の製造を安価にしうる。The front-circulation type can also use the same tube, so that the manufacturing can be automated and the manufacturing of the evaporator can be made inexpensive.

【０００６】[0006]

【発明が解決しようとする課題】[Problems to be Solved by the Invention]

本発明の目的は、性能を最適にした蒸発器、特に移動路の数を４〜６とした蒸
発器を提供することにある。An object of the present invention is to provide an evaporator with optimized performance, particularly an evaporator having 4 to 6 moving paths.

【０００７】[0007]

【課題を解決するための手段】[Means for Solving the Problems]

本発明は、上記の蒸発器であって、管の幅方向の寸法lを20 mm と 55 mmの間
、距離dを4.0 mmと7.6 mmの間としたものである。 空気流の方向の上記寸法は、この方向における蒸発器の大きさを減少させ、材
料を節約する。しかし、２つの流体の間の熱交換の表面積を減少させる傾向があ
る。この傾向は、距離dを減少させることにより、埋め合わせられる。これらの
２つの寸法を組み合わせることにより、モータ車両の乗客室の空調のために、従
来使用されている蒸発器に比べ、性能のレベルを低下せずに、全体の大きさを減
少させ、材料を節約しうる。The present invention is the above-mentioned evaporator, wherein the width dimension l of the tube is between 20 mm and 55 mm and the distance d is between 4.0 mm and 7.6 mm. The above dimensions in the direction of air flow reduce the size of the evaporator in this direction and save material. However, it tends to reduce the surface area of heat exchange between the two fluids. This tendency is offset by reducing the distance d. The combination of these two dimensions results in a reduction in overall size and a reduction in material without compromising the level of performance compared to the evaporators conventionally used for air conditioning passenger compartments of motor vehicles. Can save.

【０００８】 本発明によれば、以下のような寸法にするとよい。 (1) 管の全厚さを1.0 mmと2.7 mmの間にする。 (2) 管の壁の厚さを0.2 mmと0.45 mmの間にする。管の曲がり部の場合、0.2 mm
と0.7 mmとの間にする。 (3) 管の内壁同士の間の距離を0.6 mmと1.8 mmの間にする。 (4) 波長に対応するスペーサの波形の半分を1.0 mmと1.8 mmの間にする。According to the present invention, the following dimensions are preferable. (1) The total tube thickness is between 1.0 mm and 2.7 mm. (2) The wall thickness of the pipe is between 0.2 mm and 0.45 mm. 0.2 mm for bends in pipe
Between 0.7 mm and 0.7 mm. (3) The distance between the inner walls of the pipe is between 0.6 mm and 1.8 mm. (4) Half the waveform of the spacer corresponding to the wavelength is between 1.0 mm and 1.8 mm.

【０００９】 管と流体箱は、積載したポーチの形状に形成し、各ポーチは、２枚の薄板金属
をカップ状に打抜き、その凹面は互いに向き合わせ、ともにろう付けされて、周
縁部において、漏れを防止している。各ポーチは管を形成し、各端部において、
厚さを増加し、流体箱の一部を形成している。The tube and the fluid box are formed in the shape of a loaded pouch, each pouch being punched out of two sheets of sheet metal in a cup shape, the concave surfaces of which are opposed to each other and brazed together, at the peripheral edge, Prevents leakage. Each pouch forms a tube and at each end,
It has increased thickness and forms part of the fluid box.

【００１０】 流体箱は、管の端部に設けた孔を有する独立した構成要素である。管は、孔の
端部で、漏れを防止するように、ろう付けされている。 各管は、２枚の打抜きされた薄板金属プレートから形成されている。これらの
プレートは、端部において、漏れを防止し、また管の内側に突出する中間部を固
めるために、ろう付けされている。The fluid box is a separate component that has holes at the ends of the tubes. The tubes are brazed at the ends of the holes to prevent leakage. Each tube is formed from two stamped sheet metal plates. These plates are brazed at the ends to prevent leaks and to solidify the inwardly projecting middle of the tube.

【００１１】 各管は、２枚の打抜きされた薄板金属プレートから形成されている。それによ
り、端部において漏れを防止し、管は、プレートの内面にろう付けされたインサ
ートにより固められている。 管は、押出し成形により形成される。管は、折り畳まれ、長手方向にろう付け
された接続部により閉塞された薄板金属から形成される。 少なくとも１個の流体箱は、容積を定める２個の部材より形成され、部材の１
つは孔を備えている。少なくとも１つの内部仕切壁は、容積を別々のチャンバに
分け、各チャンバは、複数の管よりなるグループと連通している。Each tube is formed from two stamped sheet metal plates. Thereby preventing leakage at the ends and the tube is cemented by an insert brazed to the inner surface of the plate. The tube is formed by extrusion. The tube is formed from sheet metal that is folded and closed by longitudinally brazed connections. At least one fluid box is formed from two volume-defining members, one of which is
One has a hole. At least one internal partition divides the volume into separate chambers, each chamber communicating with a group of tubes.

【００１２】 少なくとも１つの流体箱は、孔を有するマニホルドプレートと、このプレート
に接続された、少なくとも２個のタンクから形成されている。そこで、管のグル
ープと連通するチャンバを形成している。 少なくとも１つの流体箱は、少なくとも１つの打抜きされた薄板金属部材から
形成され、中心線の両側に、孔を有するマニホルドプレートとタンクを形成する
。このタンクは、端縁において折り畳まれ、流体箱のチャンバを形成する。At least one fluid box is formed from a manifold plate having holes and at least two tanks connected to the plate. There, a chamber is formed that communicates with the group of tubes. The at least one fluid box is formed from at least one stamped sheet metal member to form a manifold plate with holes on either side of the centerline and a tank. The tank is folded at the edges to form the chamber of the fluid box.

【００１３】[0013]

【発明の実施の形態】DETAILED DESCRIPTION OF THE INVENTION

図１は、本発明による蒸発器の管列の部分断面図であり、平行な２本の平らな
管１が断面で示され、それらの管1の間に、波形のスペーサ２が設けられている
。本発明における最適な寸法を定めるために、管の幅、即ち矢印F１で示される
空気流の方向における蒸発器の寸法をｌ、スペーサで離隔された２本の管同士の
間の距離をｄ、管の全厚さ、即ち管の積載方向の寸法をEe、管の壁厚をe1、管の
内部の厚さEI、即ちEe − 2e1とする。FIG. 1 is a partial cross-sectional view of a tube row of an evaporator according to the invention, in which two parallel flat tubes 1 are shown in cross section, between which a corrugated spacer 2 is provided. There is. In order to determine the optimum dimension in the present invention, the width of the tube, that is, the dimension of the evaporator in the direction of the air flow indicated by the arrow F1, is l, the distance between two tubes separated by a spacer is d, The total thickness of the tube, that is, the dimension in the loading direction of the tube is E e , the wall thickness of the tube is e 1 , and the inner thickness E I of the tube, that is, E e −2e 1 .

【００１４】 図２は、スペーサ２の部分側面図で、ほぼ正弦曲線に対応している。曲線の山
を含む、２つの平面の間の距離dが、この図にも示されている。スペーサの壁厚e 2 、波長の半分p/2が示されている。[0014]   FIG. 2 is a partial side view of the spacer 2, which substantially corresponds to a sine curve. Mountain of curves
The distance d between the two planes including is also shown in this figure. Spacer wall thickness e 2 , Half the wavelength p / 2 is shown.

【００１５】 本発明による好適な寸法は、以下の通りである。 20 mm ≦ l ≦ 55 mm 4.0 mm ≦ d ≦ 7.6 mm 1.0 mm ≦ Ee ≦ 2.7 mm 0.2 mm ≦ e1 ≦ 0.7 mm 0.6 mm ≦ Ei ≦ 1.8 mm 1.0 mm ≦ p/2 ≦ 1.8 mm 0.05 mm ≦ e2 ≦ 0.1 mmThe preferred dimensions according to the invention are as follows: 20 mm ≤ l ≤ 55 mm 4.0 mm ≤ d ≤ 7.6 mm 1.0 mm ≤ E e ≤ 2.7 mm 0.2 mm ≤ e 1 ≤ 0.7 mm 0.6 mm ≤ E i ≤ 1.8 mm 1.0 mm ≤ p / 2 ≤ 1.8 mm 0.05 mm ≤ e 2 ≤ 0.1 mm

【００１６】 図３は、他の変数を等しく、空気流量を一定とした時の、距離dに対する、本
発明の蒸発器の熱交換容量の変化を示している。ｄが4 mmである時に、最大にな
ることを示している。しかし、距離dを減少させると、空気流の圧力ヘッドを増
加させ、送風機の一定速度のおける空気量を減少させる。これが、その値を、4.
0 mmと7.6 mmの間にしなくてならない理由である。FIG. 3 shows changes in the heat exchange capacity of the evaporator of the present invention with respect to the distance d when other variables are made equal and the air flow rate is constant. It is shown that it becomes maximum when d is 4 mm. However, decreasing the distance d increases the pressure head of the air flow and reduces the amount of air at a constant speed of the blower. This is the value of 4.
That is why it must be between 0 mm and 7.6 mm.

【００１７】 壁厚e1は、材料を過剰に消耗せず、耐圧性と耐食性を好適に保つように選択さ
れる。図４のグラフは、管の内面の厚さEiの関数としての蒸発器の熱交換容量の
変化を示している。この厚さが小さい時には、冷媒流体の圧力ヘッドの損失を招
き、熱交換を妨害する温度を上昇させる。反対に、この厚さが大きいと、流体の
速度を低下させ、管の壁との熱交換を限定する。上記の範囲は、最適な結果を与
えるものである。The wall thickness e 1 is selected so as not to excessively consume the material and to keep pressure resistance and corrosion resistance suitable. The graph in FIG. 4 shows the change in evaporator heat exchange capacity as a function of the tube inner surface thickness E i . When this thickness is small, it causes the loss of pressure head of the refrigerant fluid and raises the temperature which hinders heat exchange. Conversely, a large thickness slows the velocity of the fluid and limits heat exchange with the wall of the tube. The above range gives the optimum results.

【００１８】 図５と図６は、空気流量を一定とし、波長に対応するスペーサの波形の半分p/
2に対する、蒸発器の熱交換容量の変化、及び空気流に及ぼす圧力ヘッドの損失
の変化をそれぞれ示している。In FIGS. 5 and 6, the air flow rate is constant and half the p / p of the waveform of the spacer corresponding to the wavelength.
2 shows the change in the heat exchange capacity of the evaporator and the change in the loss of the pressure head on the air flow for 2 respectively.

【００１９】 図７において、記号○と▼で示された曲線は、それぞれ、p/2 = 1.4 mmと、 p/2 = 1.7 mmの時の空気流量に対する、全空調装置における空気による圧力ヘッ
ドの損失の変化を示してしる。記号■で示された曲線は、空気流量に対する、送
風機により生成された逆圧の変化を示している。圧力ヘッドの損失の曲線と逆圧
曲線の交点は、蒸発器と送風機の組み合わせの空気の操作点を示している。そこ
で、蒸発器を流れる空気量が得られ、それによる機能が低下する。p/2の種々の
値への接近を繰り返すことによって、その送風機の最適値が決定される。いろい
ろな送風機と空調ボックスで実施することにより、本発明により提案された値が
得られる。In FIG. 7, the curves indicated by the symbols ○ and ▼ are the pressure heads by air in all air conditioners for the air flow rates when p / 2 = 1.4 mm and p / 2 = 1.7 mm, respectively. It shows the change in loss. The curve indicated by the symbol {circle around (1)} shows the change in the back pressure generated by the blower with respect to the air flow rate. The intersection of the pressure head loss curve and the back pressure curve represents the air operating point of the evaporator and blower combination. Then, the amount of air flowing through the evaporator is obtained, and the function due to this is reduced. By iteratively approaching different values of p / 2, the optimum value for the blower is determined. By working with different blowers and air conditioning boxes, the values proposed by the invention are obtained.

【００２０】 図１に示した管１は、２枚のプレート１aと１bを互いにろう付けし、プレス加
工して、長手方向の２個の端部リブ１cと、複数の中間リブ1dを形成する。１枚
のプレートの端部リブ１cが別のプレートの端部リブにろう付けされ、管の外側
への漏れを完全に防止している。１枚のプレートの各中間リブ１dは、別のプレ
ートのリブ1ｄにろう付けされ、管を強固にし、管内の流体のための循環路1eを
形成している。中間リブ１dを、管の一端から他端には延びず、また循環路を形
成しない突起で、全部若しくは一部を置き換えてもよい。In the tube 1 shown in FIG. 1, two plates 1a and 1b are brazed to each other and pressed to form two longitudinal end ribs 1c and a plurality of intermediate ribs 1d. . The end ribs 1c of one plate are brazed to the end ribs of another plate to completely prevent leakage to the outside of the tube. Each intermediate rib 1d of one plate is brazed to the rib 1d of another plate to stiffen the tube and form a circulation path 1e for the fluid in the tube. The intermediate rib 1d may be wholly or partly replaced with a protrusion that does not extend from one end of the tube to the other end and does not form a circulation path.

【００２１】 図８は、本発明による蒸発器10の実施例の長手方向の断面図を示している。管
と２個の流体ボックスは、複数のポーチ11から形成され、図の左から右へと積載
されている。各ポーチ11は、プレス加工されたカップ12,13の形状の２枚の金属
薄板プレートよりなっている。カップ12,13は同一の形状で、凹面を互いに向き
合わせている。２個のカップによりポーチを形成して、ポーチの容積を定めるべ
く、ろう付けすることにより、流体を密閉している。各カップは、上部14と、下
部15と、より長い中間部16より構成されている。２個のカップの中間部16により
、管バンクの１本の管を形成している。FIG. 8 shows a longitudinal sectional view of an embodiment of the evaporator 10 according to the invention. The tube and the two fluid boxes are formed from a plurality of pouches 11 and are stacked from left to right in the figure. Each pouch 11 comprises two thin metal plates in the shape of pressed cups 12,13. The cups 12 and 13 have the same shape, and the concave surfaces face each other. The two pouches form a pouch and the fluid is sealed by brazing to define the pouch volume. Each cup consists of an upper part 14, a lower part 15 and a longer middle part 16. The middle part 16 of the two cups forms one tube of the tube bank.

【００２２】 カップの上部は、容積17を定める。この容積17は、ポーチの容積の一部をなし
、管の上部と連通している。複数の上部14は、上部流体箱18を形成する。各容積
17は、カップ19の底の孔を介して、隣接する少なくとも１つの容積と連通し、流
体箱の１つのチャンバを形成する。同様に、カップの下部15は、管の下端と連通
する容積20を定め、それらは一体となって、少なくとも１つのチャンバを構成す
る下部流体箱21を形成する。少なくとも２本の移動路で流体を循環させるために
、２個の流体箱は、少なくとも３つのチャンバを有していなくてはならない。図
示の実施例で、流体のための入口22と出口23は、それぞれ下部流体箱と上部流体
箱に設けられ、移動路の数が奇数、少なくとも３つになっている。波形スペーサ
２は、カップ11,12の中間部16の外面にろう付けされている。The upper part of the cup defines a volume 17. This volume 17 forms part of the volume of the pouch and communicates with the top of the tube. The plurality of upper portions 14 form an upper fluid box 18. Each volume
17 communicates with at least one adjacent volume through a hole in the bottom of cup 19 and forms one chamber of the fluid box. Similarly, the lower portion 15 of the cup defines a volume 20 in communication with the lower end of the tube, which together form a lower fluid box 21 which constitutes at least one chamber. The two fluid boxes must have at least three chambers in order to circulate the fluid in at least two paths. In the illustrated embodiment, an inlet 22 and an outlet 23 for the fluid are provided in the lower and upper fluid boxes, respectively, with an odd number of passages, at least three. The corrugated spacer 2 is brazed to the outer surface of the intermediate portion 16 of the cups 11 and 12.

【００２３】 図９と図10は、図８と類似する図であるが、流体箱とは別に製造された管１を
備える蒸発器に関する。これは、例えば、図８のカップ12,13に類似するカップ
を組み立てるが、上部14と下部15を含んでいない。管を押出し成形したり、ある
いは薄板金を畳んで、長手方向の接続部をろう付けすることによって製造される
。9 and 10 are views similar to FIG. 8 but for an evaporator with a tube 1 manufactured separately from the fluid box. This assembles, for example, a cup similar to cups 12, 13 of FIG. 8, but does not include top 14 and bottom 15. Manufactured by extruding the tube or folding the sheet metal and brazing the longitudinal connections.

【００２４】 図９の蒸発器30の上部流体箱31と下部流体箱32は、複数の孔34を有するマニホ
ルドプレート33を備えている。これらの孔34に管１の端部が挿入され、周縁リム
35が、管のバンクに係止されている。上部マニホルドプレートは、タンク37のカ
バーとなっている。タンク37の端縁38は、リム35にろう付けされている。端縁38
とリム35により、流体箱の容積が定められる。The upper fluid box 31 and the lower fluid box 32 of the evaporator 30 of FIG. 9 include a manifold plate 33 having a plurality of holes 34. The ends of the pipe 1 are inserted into these holes 34 and the peripheral rim
35 is locked in the bank of tubes. The upper manifold plate serves as a cover for the tank 37. The edge 38 of the tank 37 is brazed to the rim 35. Edge 38
The rim 35 defines the volume of the fluid box.

【００２５】 この容積内には、もう一つのタンク37が設けられ、その端縁40はプレート33に
ろう付けされている。下部マニホルドプレート33は、２個のタンク41,42に共通
するカバーをなしている。これらのタンク41,42は、管の積載方向に並べられて
いる。タンク41,42の端縁43,44は、接触する中央で互いにろう付けされ、端部で
、プレート33の周縁リム35にろう付けされている。In this volume, another tank 37 is provided, the edge 40 of which is brazed to the plate 33. The lower manifold plate 33 forms a cover common to the two tanks 41 and 42. These tanks 41 and 42 are arranged in the pipe loading direction. The edges 43,44 of the tanks 41,42 are brazed to each other in the center of contact and at the ends to the peripheral rim 35 of the plate 33.

【００２６】 タンク39により、流体箱31の容積を、タンク39の内側と外側にそれぞれ設けた
２つのチャンバ45,46に分けている。チャンバ45,46は、それぞれ、中央部の複数
の管と、その回りの複数の管と連通している。タンク41,42は、マニホルドプレ
ート33とともに、下部流体箱の２つのチャンバ47,48を定め、これらのチャンバ4
7,48は、それぞれ、管バンクの積載方向に延びる、２つのグループの管と連通し
ている。The tank 39 divides the volume of the fluid box 31 into two chambers 45 and 46 provided inside and outside the tank 39, respectively. Each of the chambers 45 and 46 communicates with a plurality of tubes in the central portion and a plurality of tubes around it. The tanks 41, 42, together with the manifold plate 33, define two chambers 47, 48 of the lower fluid box, these chambers 4
7, 48 communicate with two groups of pipes, each extending in the stacking direction of the pipe bank.

【００２７】 流体は、タンク37,39の側壁に形成された孔49を介して、チャンバ45に流入し
、中央部の複数の管を介して、頂部から底部に循環し、チャンバ47,48に送られ
る。そこから、他の管を介して、底部から頂部へと送られ、チャンバ46に到達し
、タンク37の孔50を介して排出される。このようにして、蒸発器内の流体の循環
は２つの移動路により行われる。The fluid flows into the chamber 45 through the holes 49 formed in the side walls of the tanks 37 and 39, circulates from the top to the bottom through a plurality of tubes in the central portion, and enters the chambers 47 and 48. Sent. From there, it is routed from the bottom to the top via another tube, reaches the chamber 46 and is discharged via the hole 50 in the tank 37. In this way, the circulation of the fluid in the evaporator is carried out by the two moving paths.

【００２８】 図10の蒸発器50においては、下部流体箱32の構造は図９のものと同一であるの
で、下部構造については述べない。上部流体箱51は、マニホルドプレート33につ
いては、図９の流体箱31と類似しているが、２つではなく、３つのタンク52,53,
54が設けられている点で異なっている。タンク52,53,54は、管の積載方向に並べ
られ、それぞれ、プレート33と、チャンバ55,56,57を定めている。In the evaporator 50 of FIG. 10, since the structure of the lower fluid box 32 is the same as that of FIG. 9, the lower structure will not be described. The upper fluid box 51 is similar to the fluid box 31 of FIG. 9 with respect to the manifold plate 33, but with three tanks 52,53, rather than two.
The difference is that 54 is provided. The tanks 52, 53, 54 are arranged in the loading direction of the tubes and define the plate 33 and the chambers 55, 56, 57, respectively.

【００２９】 タンク52の孔58を介して、流体はチャンバ55に流入し、第１のグループの管を
介して、頂部から底部に循環し、下部のチャンバ47に到達する。そこから、第２
グループの管を介して、底部から頂部へと循環し、チャンバ56へと到達する。さ
らに第３グループの管を介して、頂部から底部へと循環し、チャンバ48へ到達す
る。最後に、第４グループの管を介して、流体は、底部から頂部へと循環し、チ
ャンバ48からチャンバ57へと送られ、タンク54の孔59を介して、蒸発器から排出
される。循環は、４種類の移動路により行われる。Through the holes 58 in the tank 52, the fluid flows into the chamber 55, circulates from the top to the bottom via the first group of tubes and reaches the lower chamber 47. From there, the second
It circulates from the bottom to the top through the tubes of the group and reaches the chamber 56. It then circulates from the top to the bottom and reaches the chamber 48 via a third group of tubes. Finally, via the fourth group of tubes, the fluid circulates from the bottom to the top, is routed from chamber 48 to chamber 57 and out of the evaporator via hole 59 in tank 54. Circulation is performed by four types of moving paths.

【００３０】 図11は、流体箱の少なくとも一部を形成することにより、図９,10に示したよ
うなスペーサと管のバンクに設けられる、打ち抜きされた薄板状片60を示してい
る。この薄板状片60は、図示のように、水平線Lの左右にそれぞれ設けた２個の
部分61,62を有し、それぞれ、上向きと下向きに打抜きされることにより、一方
にはタンクを、他方には周縁リム64と孔63を有するマニホルドプレートが形成さ
れる。FIG. 11 shows a stamped lamella 60 provided in a bank of spacers and tubes as shown in FIGS. 9 and 10 by forming at least part of a fluid box. As shown in the figure, the thin plate-like piece 60 has two portions 61 and 62 provided on the left and right sides of the horizontal line L, respectively, and by punching upward and downward respectively, a tank is provided on one side and a portion on the other side. A manifold plate having a peripheral rim 64 and a hole 63 is formed therein.

【００３１】 矢印F2で示すように、線Lの回りに、180°回転させることによって、プレート
62は、タンク61に嵌められるようになる。リム62は、タンクの全周壁65と接触し
、これらをろう付けすることにより、流体密封性が確保される。このようにして
作られた部材は、１個のチャンバ、若しくは複数のチャンバよりなる流体箱を形
成するように、数個を並置して用いられる。必要に応じて、流体のための入口孔
若しくは出口孔66が設けられる。By rotating 180 ° about line L, as indicated by arrow F2, the plate
62 can be fitted into the tank 61. The rim 62 contacts the entire peripheral wall 65 of the tank, and by brazing these, the fluid tightness is secured. The members manufactured in this way are used in parallel so as to form one chamber or a fluid box composed of a plurality of chambers. Inlet or outlet holes 66 for fluid are provided as needed.

【００３２】 言うまでもないが、流体箱の容積が、マニホルドプレート及びタンクのような
２つの部材により定められ、２つ以上のチャンバに分割される例において、この
ような分割は、仕切壁のような公知の方法で行われる。 管を固める、公知の別の方法として、波形片によりろう付けした波形インサー
トのようなものをプレートの内壁にろう付けしてもよい。Needless to say, in the example where the volume of the fluid box is defined by two members such as a manifold plate and a tank and is divided into two or more chambers, such division is such as a partition wall. It is performed by a known method. Another known method of hardening the tube is to braze the inner wall of the plate, such as a corrugated insert brazed with corrugated pieces.

【図面の簡単な説明】[Brief description of drawings]

【図１】 蒸発器の部分断面図。[Figure 1]   The partial cross section figure of an evaporator.

【図２】 蒸発器の部分断面図。[Fig. 2]   The partial cross section figure of an evaporator.

【図３】 蒸発器の作用に対する寸法の影響を示すグラフ。[Figure 3]   6 is a graph showing the effect of dimensions on the operation of an evaporator.

【図４】 蒸発器の作用に対する寸法の影響を示すグラフ。[Figure 4]   6 is a graph showing the effect of dimensions on the operation of an evaporator.

【図５】 蒸発器の作用に対する寸法の影響を示すグラフ。[Figure 5]   6 is a graph showing the effect of dimensions on the operation of an evaporator.

【図６】 蒸発器の作用に対する寸法の影響を示すグラフ。[Figure 6]   6 is a graph showing the effect of dimensions on the operation of an evaporator.

【図７】 蒸発器の作用に対する寸法の影響を示すグラフ。[Figure 7]   6 is a graph showing the effect of dimensions on the operation of an evaporator.

【図８】 蒸発器の別の実施例の長手方向の断面図。[Figure 8]   FIG. 6 is a longitudinal cross-sectional view of another embodiment of the evaporator.

【図９】 蒸発器のさらに別の実施例の長手方向の断面図。[Figure 9]   FIG. 6 is a longitudinal sectional view of still another embodiment of the evaporator.

【図１０】 蒸発器のもう一つの別の実施例の長手方向の断面図。[Figure 10]   FIG. 6 is a longitudinal cross-sectional view of another alternative embodiment of an evaporator.

【図１１】 蒸発器流体箱の製造に使用される部材の斜視図。FIG. 11   FIG. 6 is a perspective view of a member used to manufacture an evaporator fluid box.

【符号の説明】[Explanation of symbols]

1 管 1a,1b プレート 10,30 蒸発器 11 ポーチ 12,13,19 カップ 14 上部 15 下部 16 中間部 17,20 容積 18,31 上部流体箱 21,32 下部流体箱 33 マニホルドプレート 34 孔 35 リム 37,41,42,52,53,54,61 タンク 45,46,47,48,55,56,57 チャンバ 1 tube 1a, 1b plate 10,30 evaporator 11 pouch 12,13,19 cups 14 top 15 bottom 16 Middle part 17,20 volume 18,31 Upper fluid box 21,32 Lower fluid box 33 Manifold plate 34 holes 35 rims 37,41,42,52,53,54,61 tanks 45,46,47,48,55,56,57 chambers

───────────────────────────────────────────────────── フロントページの続き (51)Int.Cl.7 識別記号 ＦＩ テーマコート゛(参考） Ｆ２８Ｄ 1/053 Ｆ２８Ｄ 1/053 Ａ Ｆ２８Ｆ 1/30 Ｆ２８Ｆ 1/30 Ａ 3/10 3/10 9/02 ３０１ 9/02 ３０１Ｅ ─────────────────────────────────────────────────── ─── Continued Front Page (51) Int.Cl. 7 Identification Code FI Theme Coat (Reference) F28D 1/053 F28D 1/053 A F28F 1/30 F28F 1/30 A 3/10 3/10 9/02 301 9/02 301E

Claims (16)

【特許請求の範囲】[Claims] 【請求項１】 空気流と冷媒流体の間で熱交換するために、冷媒流体を液相
から気相に変化させる、特にモータ車両の乗客室のための空調用の蒸発器であっ
て、 波形スペーサ(2)と互い違いに配置された、１列の平らな管(1)よりなる管バン
クを備え、このスペーサ(2)により管同士の間の距離を(ｄ)に保持し、スペーサ(
2)の波形の間の間隙が、管の幅方向(F1)における空気流の通路を形成し、各管の
両端が、それぞれ２つの流体箱(31)(32)と連通し、これら流体箱が、前記管バン
クに対して、互いに対向して設けられ、蒸発器内の冷媒流体に少なくとも２つの
移動路を確保し、また管の幅方向における長さ(l)を20 mmと55 mmの間にし、距
離(d)を4.0 mmと7.6 mmの間にしている蒸発器。1. An evaporator for air conditioning, especially for a passenger compartment of a motor vehicle, for changing a refrigerant fluid from a liquid phase to a vapor phase for heat exchange between an air stream and a refrigerant fluid, the waveform comprising: A tube bank consisting of a row of flat tubes (1), staggered with the spacer (2), is provided, the spacer (2) keeping the distance between the tubes at (d),
The gap between the corrugations of 2) forms a passage for the air flow in the width direction (F1) of the pipe, and both ends of each pipe communicate with two fluid boxes (31) (32), respectively. Are provided so as to face each other with respect to the tube bank, secure at least two moving paths for the refrigerant fluid in the evaporator, and have lengths (l) in the width direction of the tubes of 20 mm and 55 mm. Evaporator with a distance (d) between 4.0 mm and 7.6 mm. 【請求項２】 管の全厚さ(Ee)が、1.0 mmと2.7 mmの間である請求項１記載
の蒸発器。2. Evaporator according to claim 1, wherein the total tube thickness (E e ) is between 1.0 mm and 2.7 mm. 【請求項３】 管の壁厚(e1)が、0.2 mmと0.7 mmの間である請求項１記載の
蒸発器。3. Evaporator according to claim 1, wherein the tube wall thickness (e 1 ) is between 0.2 mm and 0.7 mm. 【請求項４】 管の内壁同士の間の距離(E2)が、0.6 mmと1.8 mmの間である
請求項１〜３のいずれかに記載の蒸発器。4. Evaporator according to claim 1, wherein the distance (E 2 ) between the inner walls of the tubes is between 0.6 mm and 1.8 mm. 【請求項５】 波長に対応するスペーサの波形の半分の長さ(p/2)が、1.0 m
mと1.8 mmの間である請求項１〜４のいずれかに記載の蒸発器。5. The half length (p / 2) of the waveform of the spacer corresponding to the wavelength is 1.0 m
An evaporator according to any of claims 1 to 4, which is between m and 1.8 mm. 【請求項６】 スペーサの壁厚(e2)が、0.05 mmと0.1 mmの間である請求項
１〜５のいずれかに記載の蒸発器。6. The evaporator according to claim 1, wherein the wall thickness (e 2 ) of the spacer is between 0.05 mm and 0.1 mm. 【請求項７】 管と流体箱(18)(21)が、積載したポーチ(11)の形状であり、
各ポーチが、カップの形状に打抜き加工された２枚の薄板金属プレート(12)(13)
より形成され、カップの凹面が互いに向き合っており、端部において、漏れを防
止するように、ろう付けされ、各ポーチが、前記管のひとつを定め、端部におい
て厚さを増加させて、流体箱の部分を形成している請求項１〜６のいずれかに記
載の蒸発器。7. The pipe and fluid box (18) (21) are in the form of a loaded pouch (11),
Each pouch has two thin metal plates stamped into the shape of a cup (12) (13)
Formed, and the concave surfaces of the cups face each other and are brazed at the ends to prevent leakage, and each pouch defines one of the tubes, increasing the thickness at the ends, An evaporator according to any one of claims 1 to 6, which forms a box part. 【請求項８】 流体箱(31)(32)が孔(34)を有し、この孔を介して、管(1)の
端部を流体が流入し、この管がろう付けされることによって、孔の回りの漏れを
防止している請求項１〜６のいずれかに記載の蒸発器。8. The fluid box (31) (32) has a hole (34) through which the fluid flows into the end of the pipe (1) and the pipe is brazed. The evaporator according to any one of claims 1 to 6, wherein leakage around the holes is prevented. 【請求項９】 各管が、打抜き加工された、２枚の薄板金属プレート(1a)(1
b)より形成され、これらのプレートがともにろう付けされることにより、端部に
おける漏れを防止し、また中間部(1d)において、管の内側に突出している請求項
８記載の蒸発器。9. Two thin metal plates (1a) (1) in which each tube is stamped.
Evaporator according to claim 8, characterized in that it is formed from b) and that these plates are brazed together to prevent leakage at the ends and project inside the tube at the intermediate part (1d). 【請求項１０】 各管が、打抜き加工された、２枚の薄板金属プレート(1a)
(1b)より形成され、これらのプレートがともにろう付けされることにより、端部
における漏れが防止され、また管が、プレートの内面にろう付けされたインサー
トにより硬められている請求項８記載の蒸発器。10. Two thin metal plates (1a) in which each tube is stamped.
9. Formed according to claim 8, wherein the plates are brazed together to prevent leakage at the ends and the tube is stiffened by an insert brazed to the inner surface of the plate. Evaporator. 【請求項１１】 管が押出し成形により作られたものである請求項８記載の
蒸発器。11. An evaporator according to claim 8, wherein the tube is made by extrusion. 【請求項１２】 管が、長手方向にろう付けされた接続部により折り畳まれ
、閉塞される請求項８記載の蒸発器。12. The evaporator according to claim 8, wherein the tube is folded and closed by a longitudinally brazed connection. 【請求項１３】 少なくとも１つの流体箱が、容積(45)(46)を定める２個の
部材(33)(37)より形成され、容積の一つが孔(34)を定め、少なくとも１つの内側
固定仕切壁(39)が、容積を２つのチャンバ(45)(46)に分割し、それぞれのチャン
バが、管の１つのグループと連通している請求項８〜12のいずかに記載の蒸発器
。13. At least one fluid box is formed by two members (33) (37) defining a volume (45) (46), one of the volumes defining a hole (34) and at least one inner side. Fixed partition wall (39) divides the volume into two chambers (45) (46), each chamber being in communication with a group of tubes. Evaporator. 【請求項１４】 少なくとも１つの流体箱(32)が、孔(34)を有するマニホル
ドプレート(33)から形成され、少なくとも２個のタンク(41)(42)が、マニホルド
プレートと連結されることにより、各チャンバ(47)(48)を定め、各チャンバが、
１つのグループの管と連通している請求項８〜13のいずかに記載の蒸発器。14. At least one fluid box (32) is formed from a manifold plate (33) having holes (34), and at least two tanks (41) (42) are connected to the manifold plate. By defining each chamber (47) (48), each chamber
An evaporator as claimed in any one of claims 8 to 13 in communication with a group of tubes. 【請求項１５】 少なくとも１個の流体箱が、打抜きされた、少なくとも１
個の薄板金属部材(60)から形成され、この部材の片側に、折り曲げ線(L)、孔(63
)を有するマニホルドプレート(62)、及びタンク(61)を定め、それらを折り曲げ
、ろう付けすることにより、流体箱のチャンバを形成する請求項８〜14のいずれ
かに記載の蒸発器。15. At least one fluid box is stamped, at least one
It is made of individual thin sheet metal members (60), and the bending line (L) and hole (63
15. A vaporizer according to any one of claims 8-14, wherein a manifold plate (62) having a) and a tank (61) are defined and are bent and brazed to form a chamber of the fluid box. 【請求項１６】 移動路の数が、４〜６のいずれかである請求項１〜15のい
ずれかに記載の蒸発器。16. The evaporator according to claim 1, wherein the number of moving paths is 4-6.
JP2001549980A 1999-12-29 2000-12-21 Evaporator Expired - Lifetime JP4869529B2 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FR9916668A FR2803376B1 (en) 1999-12-29 1999-12-29 EVAPORATOR WITH STACKED FLAT TUBES HAVING TWO OPPOSITE FLUID BOXES
FR99/16668 1999-12-29
PCT/FR2000/003630 WO2001050079A2 (en) 1999-12-29 2000-12-21 Evaporator consisting of stacked flat tubes having two opposite fluid boxes

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JP2003519355A true JP2003519355A (en) 2003-06-17
JP4869529B2 JP4869529B2 (en) 2012-02-08

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DE (1) DE10084298B3 (en)
FR (1) FR2803376B1 (en)
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JP4869529B2 (en) 2012-02-08
WO2001050079A3 (en) 2002-02-14
FR2803376A1 (en) 2001-07-06
DE10084298B3 (en) 2013-12-05
FR2803376B1 (en) 2002-09-06
WO2001050079A2 (en) 2001-07-12
US20020179295A1 (en) 2002-12-05
DE10084298T1 (en) 2002-03-28

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