JP4318037B2 - Heat exchanger - Google Patents

Heat exchanger Download PDF

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JP4318037B2
JP4318037B2 JP2004145551A JP2004145551A JP4318037B2 JP 4318037 B2 JP4318037 B2 JP 4318037B2 JP 2004145551 A JP2004145551 A JP 2004145551A JP 2004145551 A JP2004145551 A JP 2004145551A JP 4318037 B2 JP4318037 B2 JP 4318037B2
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casing
outer periphery
tank
fluid
inlet
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JP2005326098A (en
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耐事 坂井
忠道 青山
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T.RAD CO., L T D.
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    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
    • Y02E60/30—Hydrogen technology
    • Y02E60/50—Fuel cells

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Description

本発明は、排熱回収器や燃料電池改質器その他高温ガスが流通する高温度用熱交換器に関する。   The present invention relates to an exhaust heat recovery device, a fuel cell reformer and other high temperature heat exchangers through which high temperature gas flows.

一例として、燃料電池に供給される水素は、高温度用熱交換器である改質器で生成している。係る熱交換器として、下記特許文献に記載された発明が知られている。
この発明は、本出願人自身が開発したものであって、偏平チューブを定間隔に並列してコアを構成し、そのコアの外周に断面方形の内筒を被嵌すると共に、その外側に円形のケーシングを被嵌し、各チューブの両端をチューブプレートに貫通固定する。また、ケーシングの長手方向両端位置に低温流体の一対の出入口を設ける。さらに、一対のチューブプレートの外周に高温流体の出入口用タンクを設けたものである。そして、低温流体はケーシング内に導かれ、各チューブの外面側を流通する。また、高温流体は各チューブ内に流通し、両流体間に熱交換が行われるものである。
このように内筒を断面方形に形成し、外筒を円筒状に形成することにより、耐圧性の高い熱交換器を得る。 As an example, hydrogen supplied to the fuel cell is generated by a reformer that is a high-temperature heat exchanger. As such a heat exchanger, the invention described in the following patent document is known.
The present invention has been developed by the applicant of the present invention. The core is configured by arranging flat tubes in parallel at regular intervals, and an inner cylinder having a square cross section is fitted on the outer periphery of the core, and a circular shape is formed on the outside The casing is fitted, and both ends of each tube are fixed to the tube plate. In addition, a pair of inlets and outlets for the cryogenic fluid are provided at both ends in the longitudinal direction of the casing. Furthermore, a high-temperature fluid inlet / outlet tank is provided on the outer periphery of the pair of tube plates. The low-temperature fluid is guided into the casing and circulates on the outer surface side of each tube. Further, the high-temperature fluid flows through each tube, and heat exchange is performed between the two fluids.
Thus, a heat exchanger with high pressure resistance is obtained by forming the inner cylinder in a square cross section and forming the outer cylinder in a cylindrical shape.

特開２００４−０６０９３２号公報JP 2004-060932 A

前記の熱交換器において、各チューブの外面側を流通する低温流体は、ケーシングの一端部の流入口から他端部の流出口に流通するが、各チューブの各部を均一に流通し難いに欠点がある。これは、図９において、低温流体である第２流体７が第２出入口10からケーシング６の端部に供給されると、第２出入口10側に位置する各偏平チューブ１には、その第２流体７が直接供給されるが、第２出入口10から遠い側にある偏平チューブ１には内筒11を迂回して第２流体７が流通する。ところが、方形の内筒11と円筒形のケーシング６との間隔は内筒11の隅部において狭くなり、その部分で流体の圧力損失が大きくなる欠点がある。そのため、第２出入口10からより遠い側に位置する偏平チューブ１を流通する第２流体７の流量が少なくなる欠点がある。
このことは、各偏平チューブ１の各部に第２流体７が均一に流れないことになり、全体として熱交換性能が低下するおそれがある。 In the heat exchanger described above, the low-temperature fluid that circulates on the outer surface side of each tube circulates from the inlet at one end of the casing to the outlet at the other end, but it is difficult to uniformly circulate each part of each tube. There is. In FIG. 9, when the second fluid 7, which is a low temperature fluid, is supplied from the second inlet / outlet 10 to the end of the casing 6, each flat tube 1 positioned on the second inlet / outlet 10 side has its second Although the fluid 7 is directly supplied, the second fluid 7 flows around the inner tube 11 in the flat tube 1 on the side far from the second entrance 10. However, the interval between the rectangular inner cylinder 11 and the cylindrical casing 6 is narrow at the corner of the inner cylinder 11, and there is a drawback that the pressure loss of the fluid increases at that portion. Therefore, there is a drawback that the flow rate of the second fluid 7 flowing through the flat tube 1 located on the farther side from the second inlet / outlet 10 is reduced.
This means that the second fluid 7 does not flow uniformly in each part of each flat tube 1, and the heat exchange performance as a whole may be reduced.

また、第２出入口10に近い側の偏平チューブ１と遠い側の偏平チューブ１とでは、その熱膨張に差が生じ、耐久性に問題を起こすおそれがある。
なお、第２出入口10を図９の位置より９０°回転した位置に配置することにより、偏平チューブ１の各部に流通する第２流体７の流量をより均一にすることも考えられる。その場合であっても、内筒11の隅部とケーシング６の内面との隙間が少ない部分において、第２流体７の流通に伴う圧力損失が大きくなり、第２流体７の円滑な供給がし難い欠点がある。このような圧力損失は、第２流体７の入口側のみならず出口側においても生じる。 Further, there is a possibility that a difference in thermal expansion occurs between the flat tube 1 on the side close to the second entrance 10 and the flat tube 1 on the far side, causing a problem in durability.
It is also conceivable that the flow rate of the second fluid 7 flowing through each part of the flat tube 1 is made more uniform by arranging the second inlet / outlet 10 at a position rotated by 90 ° from the position of FIG. Even in such a case, the pressure loss accompanying the circulation of the second fluid 7 increases in a portion where the gap between the corner of the inner cylinder 11 and the inner surface of the casing 6 is small, and the second fluid 7 is smoothly supplied. There are difficult drawbacks. Such pressure loss occurs not only on the inlet side of the second fluid 7 but also on the outlet side.

次に、図１０は従来型熱交換器の変形例で、図において下側のタンクに連通する第１出入口９が、そのタンクの側部に設けられたものである。このような場合、第１出入口９と第２出入口10との取付け位置に段差が生じ配管周りが複雑化し、全体としてコンパクト性に欠ける欠点がある。
そこで、本発明は上記各種の問題点を解決することを課題とする。 Next, FIG. 10 shows a modification of the conventional heat exchanger, in which a first inlet / outlet port 9 communicating with the lower tank in the figure is provided at the side of the tank. In such a case, a difference in level is caused at the attachment position between the first entrance 9 and the second entrance 10 and the surroundings of the piping become complicated, and there is a disadvantage that the overall compactness is lacking.
Accordingly, an object of the present invention is to solve the various problems described above.

請求項１に記載の本発明は、定間隔に並列された多数の偏平チューブ(1) の集合体からなり、その集合体の横断面外周が略方形に形成されたコア(2) と、
そのコア(2) の両端に位置し、夫々の偏平チューブの両端が連通固定される一対のチューブプレート(3) と、
少なくとも一方の前記チューブプレート(3) の外周から、前記偏平チューブ(1) の延長方向に延在して、内部に第１流体(4) が導かれる第１タンク(5) と、
その第１タンク(5) の外周および前記コア(2) の外周に被嵌された円筒形のケーシング(6) と、
そのケーシング(6) の両端部外周に開口し、第２流体(7) が導かれる一対の第２出入口(10)と、
前記第１タンク(5) の外周に周方向に凹陥され、それと前記ケーシング(6) の内面との間に形成されて前記第２流体(7) を導く誘導路(8) と、
を具備し、各偏平チューブ(1) の内部に前記第１流体(4) が流通し、その外面側に前記第２流体(7) が流通するように構成された熱交換器である。 The present invention according to claim 1 comprises a core (2) comprising an assembly of a number of flat tubes (1) arranged in parallel at regular intervals, the outer periphery of the assembly being formed into a substantially rectangular shape,
A pair of tube plates (3) located at both ends of the core (2) and connected to and fixed at both ends of each flat tube;
A first tank (5) extending from the outer periphery of at least one of the tube plates (3) in the extending direction of the flat tube (1) and into which the first fluid (4) is guided;
A cylindrical casing (6) fitted on the outer periphery of the first tank (5) and the outer periphery of the core (2);
A pair of second inlets / outlets (10) that open to the outer periphery of both ends of the casing (6) and through which the second fluid (7) is guided;
A guide channel (8) recessed in the circumferential direction on the outer periphery of the first tank (5) and formed between the inner surface of the casing (6) and guiding the second fluid (7);
The heat exchanger is configured such that the first fluid (4) flows through each flat tube (1), and the second fluid (7) flows through the outer surface thereof.

請求項２に記載の本発明は、請求項１において、
少なくとも一方の前記チューブプレート(3) の周縁が方形に形成され、前記第１タンク(5) の外周がタンクの内面側に凹陥する断面弧状の弧状曲面(5a)の筒状に形成され、その筒状の先端縁が前記ケーシング(6) に接続され、その弧状曲面(5a)とケーシング(6) の内面との間に前記誘導路(8) が形成される熱交換器である。 The present invention according to claim 2 is the method according to claim 1,
The peripheral edge of at least one of the tube plates (3) is formed in a square shape, and the outer periphery of the first tank (5) is formed in a cylindrical shape having an arcuate curved surface (5a) having a cross-sectional arc shape recessed on the inner surface side of the tank, The heat exchanger has a cylindrical tip edge connected to the casing (6), and the induction path (8) is formed between the arcuate curved surface (5a) and the inner surface of the casing (6).

請求項３に記載の本発明は、請求項１において、
少なくとも一方の前記チューブプレート(3) の周縁部が略方形に形成され、前記第１タンク(5) の外周の少なくとも一部に、タンクの内面側に凹陥する断面弧状の弧状曲面(5a)が筒状に形成され、その筒状の先端縁が前記ケーシング(6) の一端を閉塞する蓋部(6a)に接続され、そのケーシング(6) の一端部外周に前記第１タンク(5) に連通する第１出入口(9) が開口し、その第１出入口(9) から周方向に離間し且つ、前記弧状曲面(5a)外周に対向する位置で、ケーシング(6) の端部に第２出入口(10)が開口され、前記弧状曲面(5a)と前記ケーシング(6) の内面との間に前記誘導路(8) が設けられ、
前記第１出入口(9) と、前記第２出入口(10)とが、ケーシング(6) の軸線方向の同一位置に存在する熱交換器である。 The present invention according to claim 3 provides the method according to claim 1,
A peripheral edge of at least one of the tube plates (3) is formed in a substantially square shape, and an arcuate curved surface (5a) having an arcuate cross section that is recessed on the inner surface side of the tank is formed on at least a part of the outer periphery of the first tank (5). A cylindrical tip end is connected to a lid (6a) that closes one end of the casing (6), and an outer periphery of one end of the casing (6) is connected to the first tank (5). The communicating first doorway (9) opens, is spaced apart from the first doorway (9) in the circumferential direction, and is opposed to the outer circumference of the arcuate curved surface (5a), at the end of the casing (6). The doorway (10) is opened, the guide path (8) is provided between the arcuate curved surface (5a) and the inner surface of the casing (6),
The first inlet / outlet (9) and the second inlet / outlet (10) are heat exchangers present at the same position in the axial direction of the casing (6).

請求項４に記載の本発明は、請求項１において、
前記コア(2) の外周が、断面方形の内筒(11)で被嵌され、その内筒の両端部の対向面で且つ、前記偏平チューブ(1) の平面に直交する面に、前記第２流体(7) の出入口部(12)が開口され、
前記第２出入口(10)が、内筒(11)の前記出入口部(12)の存在しない閉塞面に対向して開口する熱交換器である。 The present invention according to claim 4 provides the method according to claim 1,
The outer periphery of the core (2) is fitted with an inner cylinder (11) having a square cross section, and is opposed to the opposite surfaces of both ends of the inner cylinder and on the surface perpendicular to the plane of the flat tube (1). The inlet / outlet part (12) of the two fluid (7) is opened,
The second inlet / outlet (10) is a heat exchanger that opens to face a closed surface where the inlet / outlet part (12) of the inner cylinder (11) does not exist.

本発明の熱交換器は、第１タンク５の外周が周方向に凹陥され、それとケーシング６の内面との間に第２流体７を導く誘導路８が設けられたものであるから、コア２の横断面外周が略方形に形成され且つ、ケーシング６が円筒形に形成されていても、誘導路８を介して第２流体７を円滑に各チューブに均等に導くことができる。また第２流体を円滑に誘導路８に導くことができるので、その流通に伴う圧力損失を減少し熱交換を促進し得る。   In the heat exchanger of the present invention, the outer periphery of the first tank 5 is recessed in the circumferential direction, and the induction path 8 for guiding the second fluid 7 is provided between the outer periphery of the first tank 5 and the inner surface of the casing 6. The second fluid 7 can be smoothly and evenly guided to the respective tubes via the guide path 8 even when the outer periphery of the cross section is formed in a substantially square shape and the casing 6 is formed in a cylindrical shape. Further, since the second fluid can be smoothly guided to the guide path 8, the pressure loss accompanying the circulation can be reduced and heat exchange can be promoted.

上記構成において、ケーシング６の端部に第１出入口９と第２出入口10とを、そのケーシング６の軸線方向の同一位置に設けたものにおいては、第１出入口９と第２出入口10とに接続される配管がコンパクトに収まり、配管を含めて省スペースな熱交換器となり得る。   In the above configuration, in the case where the first entrance 9 and the second entrance 10 are provided at the end of the casing 6 at the same position in the axial direction of the casing 6, the first entrance 9 and the second entrance 10 are connected. The pipes to be stored can be compact and can be a space-saving heat exchanger including the pipes.

上記構成において、コア２の外周を内筒11で被嵌し、その内筒11の端部に出入口部12を設け、その出入口部12の存在しない位置で、第２出入口10をケーシング６の端部に開口したものにおいては、各偏平チューブ１にさらに均等に第２流体７を流通させ熱交換性能を向上できる。   In the above configuration, the outer periphery of the core 2 is fitted with the inner cylinder 11, the inlet / outlet part 12 is provided at the end of the inner cylinder 11, and the second inlet / outlet 10 is connected to the end of the casing 6 at a position where the inlet / outlet part 12 does not exist. In what is opened in the section, the second fluid 7 can be circulated evenly through the flat tubes 1 to improve the heat exchange performance.

次に、図面に基づいて本発明の実施の形態につき説明する。
図１は本発明の熱交換器の要部分解斜視図であり、図２はその組立て状態を示す斜視図、図３は図２における III− III矢視断面図である。
この熱交換器は高温の流体が流通するものであって、ケーシング６と内筒11とコア２とコア２の両端に配置された一対の第１タンク５とを有する。
コア２は、多数の偏平チューブ１を小隙を有して互いに平行に複数列並列したチューブ群を有し、そのチューブ群の外周が略方形（この場合正方形）に形成されている。そしてチューブの両端は、第１タンク５のチューブプレート３に貫通し、その貫通部が気密に固定されている。コア２を被嵌する内筒11は、コア２の外周に相似形でそれより僅かに大きい断面方形（正方形）に形成されている。その内筒11は図１に示す如く、その両側部が上下一対の部分よりもその端部が短くなり、そこに第２流体の出入口部12が形成される。そして、内筒11の上下一対の部材の両端はチューブプレート３に接合されている。 Next, embodiments of the present invention will be described with reference to the drawings.
FIG. 1 is an exploded perspective view of a main part of a heat exchanger according to the present invention, FIG. 2 is a perspective view showing an assembled state thereof, and FIG. 3 is a cross-sectional view taken along line III-III in FIG.
This heat exchanger has a high-temperature fluid flowing therein, and includes a casing 6, an inner cylinder 11, a core 2, and a pair of first tanks 5 disposed at both ends of the core 2.
The core 2 has a tube group in which a large number of flat tubes 1 are arranged in parallel in parallel with each other with a small gap, and the outer periphery of the tube group is formed in a substantially square shape (in this case, a square). Then, both ends of the tube penetrate the tube plate 3 of the first tank 5, and the penetrating portions are fixed in an airtight manner. The inner cylinder 11 to which the core 2 is fitted is formed in a square shape (square) having a similar shape to the outer periphery of the core 2 and slightly larger than that. As shown in FIG. 1, the inner cylinder 11 has both end portions shorter than the pair of upper and lower portions, and a second fluid inlet / outlet portion 12 is formed there. Then, both ends of the pair of upper and lower members of the inner cylinder 11 are joined to the tube plate 3.

また、内筒11の外周とケーシング６の内周との間には、ケーシング６の軸線方向に離間して一対の第１バッフルプレート13，第２バッフルプレート14が配置されている。そして第２バッフルプレート14は、図３に示す如く、その内周が内筒11に溶接され、第１バッフルプレート13の内周は溶接されることなく、そこに非溶接部19が形成される。
ケーシング６の軸線方向中間部には波形曲折部15が設けられ、それによって各部品の熱膨張差を吸収する。さらにケーシング６の長手方向両端部であって、チューブプレート３に近接した位置には一対の第２出入口10が設けられ、それが内筒11内に連通する。
なお、コア２の偏平チューブ１内にはインナーフィン16が挿通され、その外面側にはアウターフィン17が設けられている（図１）。 A pair of first baffle plates 13 and second baffle plates 14 are arranged between the outer periphery of the inner cylinder 11 and the inner periphery of the casing 6 so as to be separated from each other in the axial direction of the casing 6. As shown in FIG. 3, the inner periphery of the second baffle plate 14 is welded to the inner cylinder 11, and the inner periphery of the first baffle plate 13 is not welded, and a non-welded portion 19 is formed there. .
A corrugated bent portion 15 is provided at an intermediate portion in the axial direction of the casing 6, thereby absorbing the thermal expansion difference of each component. Further, a pair of second entrances 10 are provided at both ends in the longitudinal direction of the casing 6 and in the vicinity of the tube plate 3, and communicate with the inner cylinder 11.
An inner fin 16 is inserted into the flat tube 1 of the core 2 and an outer fin 17 is provided on the outer surface side (FIG. 1).

ここにおいて、本発明の特徴とするところは、第１タンク５の外周形状である。この例では、第１タンク５は内筒11の外周に整合するチューブプレート３の周縁から筒状に突出され、その筒状の開口端の縁部が、ケーシング６の開口縁に溶接されている。この第１タンク５の筒状部外周は、内面側に凹陥する断面弧状の弧状曲面５ａを周方向に有し、その弧状曲面５ａとケーシング６の内周との間に誘導路８を形成する。即ち、第２出入口10から流入した第２流体７が弧状曲面５ａに沿って流通し、第２出入口10から遠い側の内筒11の出入口部12からも流入し、各偏平チューブ１外周を均一に流通する。そして、内筒11の出入口部12の両側からそれが流出し、第２出入口10に導かれる。このとき第２出入口10より遠い側を通る第２流体７は、第１タンク５の弧状曲面５ａを流通して円滑に第２出入口10に導かれる。これは、出入口部12から流出した第２流体７がその内筒11の方形の隅部を通ることなく、略円筒形の弧状曲面５ａを円滑に流通することを意味する。それによって、第２流体７の流通に伴う圧力損失を低減し、各偏平チューブ１外周を略均等に第２流体７を流通させることができる。   Here, the feature of the present invention is the outer peripheral shape of the first tank 5. In this example, the first tank 5 protrudes in a cylindrical shape from the peripheral edge of the tube plate 3 aligned with the outer periphery of the inner cylinder 11, and the edge of the cylindrical opening end is welded to the opening edge of the casing 6. . The outer periphery of the cylindrical portion of the first tank 5 has an arcuate curved surface 5 a having a cross-sectional arc shape that is recessed on the inner surface side, and a guide path 8 is formed between the arcuate curved surface 5 a and the inner periphery of the casing 6. . That is, the second fluid 7 flowing in from the second inlet / outlet 10 flows along the arcuate curved surface 5a and also flows in from the inlet / outlet portion 12 of the inner cylinder 11 on the side far from the second inlet / outlet 10, so that the outer periphery of each flat tube 1 is uniform. To circulate. Then, it flows out from both sides of the inlet / outlet portion 12 of the inner cylinder 11 and is guided to the second inlet / outlet 10. At this time, the second fluid 7 passing through the side farther from the second inlet / outlet 10 flows through the arcuate curved surface 5a of the first tank 5 and is smoothly guided to the second inlet / outlet 10. This means that the second fluid 7 flowing out from the inlet / outlet part 12 smoothly flows through the substantially cylindrical arcuate curved surface 5a without passing through the square corners of the inner cylinder 11. Thereby, the pressure loss accompanying the distribution | circulation of the 2nd fluid 7 can be reduced, and the 2nd fluid 7 can be distribute | circulated substantially uniformly in each flat tube 1 outer periphery.

次に、図４〜図７は本発明の第２の実施の形態を示し、図４はその要部分解斜視図、図５はその組立て状態を示す縦断面図であり、図６は図５のＡ−Ａ矢視断面図、図７は同Ｂ−Ｂ矢視断面図である。
この例が前記第１の実施の形態と異なる点は、図４において上側に位置するチューブプレート３が円形に形成され、そのチューブプレート３とケーシング６の上端閉塞面との間が波形曲折部15で連結されていること、及び図５において、下側の第２出入口10及び第１出入口９の夫々の軸線が同一の高さに存在することである。さらに、第２出入口10の開口に対向した位置に第１タンク５の弧状曲面５ａが形成されていること、及び第１タンク５のチューブプレート３がケーシング６の内面に接合されていることである。 Next, FIG. 4 to FIG. 7 show a second embodiment of the present invention, FIG. 4 is an exploded perspective view of an essential part thereof, FIG. 5 is a longitudinal sectional view showing an assembled state thereof, and FIG. A-A cross-sectional view of FIG. 7, FIG. 7 is a cross-sectional view of the BB arrow.
This example is different from the first embodiment in that the tube plate 3 located on the upper side in FIG. 4 is formed in a circular shape, and the waved bent portion 15 is formed between the tube plate 3 and the upper end closing surface of the casing 6. And in FIG. 5, the axes of the lower second entrance 10 and the first entrance 9 are at the same height. Furthermore, the arcuate curved surface 5 a of the first tank 5 is formed at a position facing the opening of the second entrance 10, and the tube plate 3 of the first tank 5 is joined to the inner surface of the casing 6. .

そして図５において、下側の第２出入口10から流入した第２流体７は、弧状曲面５ａに沿って第１タンク５の外周を流通し、コア２の各偏平チューブ１外面側に均等に供給される。そしてコア２の上端部とチューブプレート３との間を流通し、一部波形曲折部15の外周を流通して上側の第２出入口10からそれが流出する。
また、上側の第１出入口９から流入した第１流体４は各偏平チューブ１内を流通し、下側の第１タンク５から第１出入口９に流出する。その間、第１流体４と第２流体７との熱交換が行われる。
そして特に、第２流体７はその流入側の第２出入口10において、第１タンク５の弧状曲面５ａに導かれ、次いでチューブプレート３側に回り込み各偏平チューブ１を均等に流通する。 In FIG. 5, the second fluid 7 flowing in from the lower second inlet / outlet 10 circulates on the outer periphery of the first tank 5 along the arcuate curved surface 5 a and is evenly supplied to the outer surface side of each flat tube 1 of the core 2. Is done. And it distribute | circulates between the upper end part of the core 2, and the tube plate 3, and distribute | circulates the outer periphery of the partial waveform bending part 15, and it flows out out of the upper 2nd entrance / exit.
The first fluid 4 flowing in from the upper first inlet / outlet 9 flows through each flat tube 1 and flows out from the lower first tank 5 to the first inlet / outlet 9. Meanwhile, heat exchange between the first fluid 4 and the second fluid 7 is performed.
In particular, the second fluid 7 is guided to the arcuate curved surface 5a of the first tank 5 at the second inlet / outlet 10 on the inflow side thereof, and then circulates to the tube plate 3 side to circulate through the flat tubes 1 evenly.

次に、図８は本発明のさらに他の実施の形態を示し、この例が図５のものと大きくことなる点は、ケーシング６の外面側に波形曲折部15が設けられていることである。   Next, FIG. 8 shows still another embodiment of the present invention, and this example is greatly different from that of FIG. 5 in that a corrugated bent portion 15 is provided on the outer surface side of the casing 6. .

本発明の熱交換器の第１の実施の形態の示す要部分解斜視図。The principal part disassembled perspective view which 1st Embodiment of the heat exchanger of this invention shows. 同熱交換器の組立て状態を示す斜視図。The perspective view which shows the assembly state of the same heat exchanger. 図２の III− III矢視断面図。III-III arrow sectional drawing of FIG. 本発明の熱交換器の第２の実施の形態の示す要部分解斜視図。The principal part disassembled perspective view which 2nd Embodiment of the heat exchanger of this invention shows. 同熱交換器の組立て状態を示す縦断面図。The longitudinal cross-sectional view which shows the assembly state of the same heat exchanger.

図５のＡ−Ａ矢視断面図。AA arrow sectional drawing of FIG. 図５のＢ−Ｂ矢視断面図。BB arrow sectional drawing of FIG. 本発明の熱交換器の第３の実施の形態の示す縦断面図。The longitudinal cross-sectional view which shows 3rd Embodiment of the heat exchanger of this invention. 従来型熱交換器の第２流体７の流れを示す説明図。Explanatory drawing which shows the flow of the 2nd fluid 7 of a conventional heat exchanger. 従来型熱交換器の他の例を示す縦断面図。The longitudinal cross-sectional view which shows the other example of the conventional heat exchanger.

符号の説明Explanation of symbols

１ 偏平チューブ
２ コア
３ チューブプレート
４ 第１流体
５ 第１タンク
５ａ 弧状曲面
６ ケーシング
６ａ 蓋部
７ 第２流体
８ 誘導路
９ 第１出入口
10 第２出入口 DESCRIPTION OF SYMBOLS 1 Flat tube 2 Core 3 Tube plate 4 1st fluid 5 1st tank 5a Arc-shaped curved surface 6 Casing 6a Cover part 7 2nd fluid 8 Guideway 9 1st entrance / exit
10 Gate 2

11 内筒
12 出入口部
13 第１バッフルプレート
14 第２バッフルプレート
15 波形曲折部
16 インナーフィン
17 アウターフィン
18 溶接部
19 非溶接部
11 Inner cylinder
12 Entrance / exit
13 First baffle plate
14 Second baffle plate
15 Waveform bend
16 Inner fin
17 Outer fin
18 Welded part
19 Non-welded part

Claims (4)

定間隔に並列された多数の偏平チューブ(1) の集合体からなり、その集合体の横断面外周が略方形に形成されたコア(2) と、
そのコア(2) の両端に位置し、夫々の偏平チューブの両端が連通固定される一対のチューブプレート(3) と、
少なくとも一方の前記チューブプレート(3) の外周から、前記偏平チューブ(1) の延長方向に延在して、内部に第１流体(4) が導かれる第１タンク(5) と、
その第１タンク(5) の外周および前記コア(2) の外周に被嵌された円筒形のケーシング(6) と、
そのケーシング(6) の両端部外周に開口し、第２流体(7) が導かれる一対の第２出入口(10)と、
前記第１タンク(5) の外周に周方向に凹陥され、それと前記ケーシング(6) の内面との間に形成されて前記第２流体(7) を導く誘導路(8) と、
を具備し、各偏平チューブ(1) の内部に前記第１流体(4) が流通し、その外面側に前記第２流体(7) が流通するように構成された熱交換器。 A core (2) comprising an assembly of a number of flat tubes (1) arranged in parallel at regular intervals, the outer periphery of the assembly being formed in a substantially rectangular shape,
A pair of tube plates (3) located at both ends of the core (2) and connected to and fixed at both ends of each flat tube;
A first tank (5) extending from the outer periphery of at least one of the tube plates (3) in the extending direction of the flat tube (1) and into which the first fluid (4) is guided;
A cylindrical casing (6) fitted on the outer periphery of the first tank (5) and the outer periphery of the core (2);
A pair of second inlets / outlets (10) that open to the outer periphery of both ends of the casing (6) and through which the second fluid (7) is guided;
A guide channel (8) recessed in the circumferential direction on the outer periphery of the first tank (5) and formed between the inner surface of the casing (6) and guiding the second fluid (7);
A heat exchanger configured such that the first fluid (4) flows through each flat tube (1) and the second fluid (7) flows through the outer surface thereof. 請求項１において、
少なくとも一方の前記チューブプレート(3) の周縁が方形に形成され、前記第１タンク(5) の外周がタンクの内面側に凹陥する断面弧状の弧状曲面(5a)の筒状に形成され、その筒状の先端縁が前記ケーシング(6) に接続され、その弧状曲面(5a)とケーシング(6) の内面との間に前記誘導路(8) が形成される熱交換器。 In claim 1,
The peripheral edge of at least one of the tube plates (3) is formed in a square shape, and the outer periphery of the first tank (5) is formed in a cylindrical shape having an arcuate curved surface (5a) having a cross-sectional arc shape recessed on the inner surface side of the tank, A heat exchanger in which a cylindrical tip edge is connected to the casing (6), and the induction path (8) is formed between the arcuate curved surface (5a) and the inner surface of the casing (6). 請求項１において、
少なくとも一方の前記チューブプレート(3) の周縁部が略方形に形成され、前記第１タンク(5) の外周の少なくとも一部に、タンクの内面側に凹陥する断面弧状の弧状曲面(5a)が筒状に形成され、その筒状の先端縁が前記ケーシング(6) の一端を閉塞する蓋部(6a)に接続され、そのケーシング(6) の一端部外周に前記第１タンク(5) に連通する第１出入口(9) が開口し、その第１出入口(9) から周方向に離間し且つ、前記弧状曲面(5a)外周に対向する位置で、ケーシング(6) の端部に第２出入口(10)が開口され、前記弧状曲面(5a)と前記ケーシング(6) の内面との間に前記誘導路(8) が設けられ、
前記第１出入口(9) と、前記第２出入口(10)とが、ケーシング(6) の軸線方向の同一位置に存在する熱交換器。 In claim 1,
A peripheral edge of at least one of the tube plates (3) is formed in a substantially square shape, and an arcuate curved surface (5a) having an arcuate cross section that is recessed toward the inner surface of the tank is formed on at least a part of the outer periphery of the first tank (5). A cylindrical tip end is connected to a lid (6a) that closes one end of the casing (6), and an outer periphery of one end of the casing (6) is connected to the first tank (5). The communicating first doorway (9) opens, is spaced apart from the first doorway (9) in the circumferential direction, and is opposed to the outer circumference of the arcuate curved surface (5a), at the end of the casing (6). The doorway (10) is opened, the guide path (8) is provided between the arcuate curved surface (5a) and the inner surface of the casing (6),
A heat exchanger in which the first inlet / outlet (9) and the second inlet / outlet (10) are located at the same position in the axial direction of the casing (6). 請求項１において、
前記コア(2) の外周が、断面方形の内筒(11)で被嵌され、その内筒の両端部の対向面で且つ、前記偏平チューブ(1) の平面に直交する面に、前記第２流体(7) の出入口部(12)が開口され、
前記第２出入口(10)が、内筒(11)の前記出入口部(12)の存在しない閉塞面に対向して開口する熱交換器。
In claim 1,
The outer periphery of the core (2) is fitted with an inner cylinder (11) having a square cross section, and is opposed to the opposite surfaces of both ends of the inner cylinder and on the surface perpendicular to the plane of the flat tube (1). The inlet / outlet part (12) of the two fluid (7) is opened,
A heat exchanger in which the second inlet / outlet (10) opens to face a closed surface where the inlet / outlet portion (12) of the inner cylinder (11) does not exist.
JP2004145551A 2004-05-14 2004-05-14 Heat exchanger Expired - Fee Related JP4318037B2 (en)

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JP2010048536A (en) * 2008-08-25 2010-03-04 Denso Corp Heat exchanger
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