JP4536237B2 - Heat exchanger - Google Patents

Heat exchanger Download PDF

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Publication number
JP4536237B2
JP4536237B2 JP2000301083A JP2000301083A JP4536237B2 JP 4536237 B2 JP4536237 B2 JP 4536237B2 JP 2000301083 A JP2000301083 A JP 2000301083A JP 2000301083 A JP2000301083 A JP 2000301083A JP 4536237 B2 JP4536237 B2 JP 4536237B2
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Prior art keywords
main body
flat tubes
cooling water
longitudinal direction
peripheral surface
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JP2000301083A
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JP2002107091A (en
Inventor
利光 栗和田
俊道 小林
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T.RAD CO., L T D.
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T.RAD CO., L T D.
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    • 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
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F28D7/1684—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits having a non-circular cross-section
    • 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

Description

【０００１】
【発明の属する技術分野】
本発明は、高温のガス体を冷却水により冷却する熱交換器であって、いわゆるシェルアンドチューブ型のものに関する。
【０００２】
【従来の技術】
いわゆるシェルアンドチューブ型のオイルクーラとしての熱交換器が、実開昭６２−１１８９６５号で知られている。これは図４、図５または図６に示す如く、円筒（または断面方形）の本体10の両端にヘッダプレート12が設けられ、そのヘッダプレート12に多数の円形のチューブ11または偏平チューブ３の両端が貫通し、ヘッダプレート12の周縁にダクト13の開口側が被嵌されるものである。そして、本体10の外周の一端に突設されたオイルパイプ15ａから本体10内を高温のオイルが長手方向に移動し、本体10の他端に突設されたオイルパイプ15ｂからそれが流出する。
【０００３】
そして一方のダクト13の冷却水パイプ20ａから各円形のチューブ11または偏平チューブ３内に冷却水が流入し、それが長手方向に流通して他方の冷却水パイプ20ｂから流出する。そして本体10内で、オイルと冷却水との間で熱交換器が行われるものである。
このような熱交換器において、一方のオイルパイプ15ａから他方のオイルパイプ15ｂに流通するオイルは、各チューブ外面を均一に流通させることは難しい。そこで、従来図４の如く本体10の内部にバッファ14を千鳥状に配置し、オイルを蛇行状に流通させる工夫が行われていた。
【０００４】
【発明が解決しようとする課題】
チューブ外面側の流体を均一に流通させるために図４に示すようなバッファ14を設けても、ある程度流体の停滞は改善するものの充分とはいえない。即ち、バッファ14と本体10の内面の付根部にはやはり流体の停滞が生じ、熱交換性能を充分に発揮できない欠点があった。特に、高温のガス体をチューブ内に流し、その外面側を冷却水で冷却する場合、チューブの外面側の冷却水に偏流が生じると、その熱交換性能を充分引き出せないだけではなく、局部沸騰に起因する局部加熱や、さらなる偏流等の様々な問題を引き起こす。
さらにはバッファ14を設けると、その分だけ流通抵抗が増大する欠点があった。
そこで本発明は、係る問題点を解決することを課題とする。
【０００５】
【課題を解決するための手段】
請求項１に記載の本発明は、矩形筒体よりなる本体(1) と、
その本体(1) の両開口端を閉塞する一対のヘッダプレート(2) と、
前記本体(1) の少なくとも対向する一対の内面に、夫々の外周の平面が平行に整列され、その両端が前記ヘッダプレート(2) に液密に貫通され、内部に被冷却用熱交換媒体が流通する多数の偏平チューブ(3) と、
前記本体(1) の長手方向両端部外面に設けられた冷却水の出入口(4) と、
を具備し、前記多数の偏平チューブ(3) で構成するチューブ群の最外周表面と前記本体(1) の内周平面とに僅かの隙間が形成され、
前記本体(1) の長手方向両端部の内周面と、前記チューブ群の最外周表面との間隔(S1)(S2)が、長手方向の中間部におけるそれら(S5)(S6)よりも広くされ、
前記本体(1)の長手方向中間部であって、その内周面とそれに対向する偏平チューブ(3) の外周との間隔(S6)が、整列された前記偏平チューブ(3)どうしの隣り合う外周平面間における間隔(S3)より小に形成され、
それらの偏平チューブ(3)は、その断面の長手方向に複数列に並列され、その列間の隙間となる並列された偏平チューブ(3)の端部間隔(S4)が、前記偏平チューブ(3)どうしの隣り合う外周平面間における間隔(S3)より僅かに大に形成された熱交換器である。
【０００７】
【発明の実施の形態】
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一部破断正面図であり、図２は図１のII−II矢視断面図、図３は同 III− III矢視断面図である。
この熱交換器は、細長い矩形筒体からなる本体１と、その長手方向両端を閉塞する一対のヘッダプレート２と、各ヘッダプレート２の偏平孔に両端が液密に貫通された多数の偏平チューブ３と、ヘッダプレート２を被嵌する一対のダクト７とを有する。
【０００８】
本体１の内部には図３に示す如く、その平面に平行に多数の偏平チューブ３が定間隔に並列されている。そして多数の偏平チューブ３によって構成する偏平チューブ群の最外周と本体１の内面とは僅かの間隔Ｓ５，Ｓ６が形成されている。また、隣り合う偏平チューブ３の平面間は前記間隔Ｓ５，Ｓ６よりも充分大きな間隔Ｓ３が形成されている。さらに複数列に並列された偏平チューブ３の端部間隔はＳ４とされ、その間隔は前記Ｓ３のそれよりも僅かに大に形成されている。
【０００９】
次に、本体１の長手方向両端部は外方に僅かに膨出され、そこに図１及び図２に示す如く環状膨出空間部５が形成され、その膨出量はＳ７である。そしてその環状膨出空間部５の外周において下面側に冷却水パイプ15の一端が接続され、それと１８０°異なった位置の他方の環状膨出空間部５の出入口に冷却水パイプ15の一端が接続されている。なお、これらの出入口の方向は任意に向けることができる。偏平チューブ３の内部には矩形波状または通常の波形のインナーフィン８が挿入されて、その接触部間がろう付けされている。そして各部品は好ましくはステンレス鋼材からなり、ヘッダプレート２と偏平チューブ３の端部との間、およびヘッダプレート２とダクト７との間は液密に溶接固定されてる。
【００１０】
そして一方のダクト７から高温のガス体19が導入され、各偏平チューブ３を長手方向に流通して他方のダクト７からそれが流出する。なお、この例では高温のガス体19が図１において、左方から右方に流通しているが、その逆向きにガス体19を流通させてもよい。また、下面側等の出入口取付方向からの冷却水パイプ15から冷却水が本体１の環状膨出空間部５に流入し、図において左端部から右端部を流通し、上端側等の冷却水パイプ15からそれが流出する。そして冷却水18によりガス体19が本体１内で冷却される。
【００１１】
図２において出入口４から流入した冷却水18は、その出入口４に対向する偏平チューブ３の外表面を迂回し且つ、比較的隙間の大きな環状膨出空間部５を含む偏平チューブ３群の外周を円滑に流通して、各偏平チューブ３間及び偏平チューブ３と本体１の内面との間に供給される。次いで各偏平チューブ３間及び偏平チューブ３と本体１の内面との間を偏平チューブの長手方向に流通する。そして、環状膨出空間部５を通過した冷却水は、本体１の内面とそれに対向する最外側の偏平チューブ３の外面との間では、比較的狭い間隔Ｓ６を流通し、各偏平チューブ３間はそれよりも僅かに広い間隔Ｓ３間を流通する。しかしながら、横断面の各部における水側温度分布は略同一である。
【００１２】
なぜならば、間隔Ｓ３間を流通する冷却水は、対向する二つの偏平チューブ３の放熱を受けるのに対し、最外側の偏平チューブ３と本体１との間を流通する冷却水には一つの偏平チューブ３のみから放熱を受けるので、より少ない冷却水で充分たり、結果として各部における冷却水の水温上昇が同一に近くなる。
次に、二列に配列された偏平チューブ３の端部間における十字交差点９では、４本の偏平チューブ３によって冷却水が加熱される。しかしながら、その部分における間隔Ｓ４は大きく冷却水流量は他の部分よりも大であるから、結果として十字交差点９の近傍においてもその水温上昇は他の部分と同一に近くなる。
【００１３】
このように本体１の冷却水の出入口部に、比較的隙間の大きな環状膨出空間部５を設けることにより、その環状膨出空間部５の横断面における各部分に冷却水を充分に行き渡らせることができると共に、本体１の中間部においてはその内面と偏平チューブ３との間隔を他の部分よりも僅かに小とし、必要以上に冷却水が本体１の内面に沿ってバイパスすることがないようにし且つ、その部分では水側受熱量も少ないため流路を狭くしても均一なる受熱を行うことが可能となる。
なお、ガス体19が特に高温の場合には、偏平チューブ３とヘッダプレート２との間または本体１の両端とダクト７との間をティグ溶接またはＮｉろう付け構造とすると共に、偏平チューブ３とインナーフィン８との間はニッケルろう付けとすることが好ましい。
【００１４】
【発明の作用・効果】
本発明によれば、本体１の長手方向両端部に比較的隙間の大きな環状膨出空間部５を有するため、その両端部における各部分の冷却水圧力を均一にして、各偏平チューブ３の外周を流通する冷却水の流量を等しくし、各部の熱交換能力を最大限に引き出すことができる。逆に言えば、環状膨出空間部５が本体１の両端部に存在しない場合には、同一の横断面において出入口４からより遠い位置の冷却水圧力は低下し、その分だけ偏平チューブ３の外周の冷却水の流量が減少するおそれがある。しかしながら、本発明では環状膨出空間部５の存在により各部の冷却水の流量を均一にし得る。
また、このように構成することにより単位容積当たりの熱交換効率を向上させることができる。そしてコンパクトで搭載効率の良い熱交換器を提供できる。
【００１５】
さらに、本体１の長手方向の中間部においてその内周面とそれに対向する偏平チューブの外周との間隔が、整列された偏平チューブ３どうしの隣り合う外周平面の間隔より小に形成されたものである。それにより、長手方向中間部において本体１の内周面に沿う冷却水の熱交換量と、各偏平チューブ３間を流通する冷却水の温度分布を略均一にすることができる。
なぜならば、本体１の内周面に沿う冷却水はその内周面に沿う一つのみの偏平チューブから放熱を受けるが、隣接する各偏平チューブ間を流通する冷却水は対向する二つの偏平チューブから放熱を受ける。そのため、より熱交換量の多い部分を流通する流路断面をより大きくすることにより、各部の冷却水の温度上昇を略等しくでき、熱交換をより円滑に行い得る。それと共に、本体１の内面に沿って冷却水がバイパスされることを防止できる。
さらに、それらの偏平チューブ３は、その断面の長手方向に複数列に並列され、その列間の隙間となる並列された偏平チューブ３の端部間隔S4が、前記偏平チューブ３どうしの隣り合う外周平面間における間隔S3より僅かに大に形成されたから、二列に配列された偏平チューブ３の端部間における十字交差点９（図３）では、４本の偏平チューブ３によって加熱されても、その部分における間隔S4が大きいので、冷却水流量が他の部分より大きく、結果として十字交差点９の近傍の水温上昇を他の部分と同一近くにできる効果がある。
【図面の簡単な説明】
【図１】本発明の熱交換器の一部破断正面図。
【図２】図１のII−II矢視断面図。
【図３】図１の III− III矢視断面図。
【図４】従来型熱交換器の正面略図。
【図５】同熱交換器においてダクト13を取り除いた状態の側面図。
【図６】他の従来型熱交換器の分解斜視図。
【符号の説明】
１ 本体
２ ヘッダプレート
３ 偏平チューブ
４ 出入口
５ 環状膨出空間部
６ 出入口
７ ダクト
８ インナーフィン
９ 十字交差点
10 本体
11 チューブ
12 ヘッダプレート
13 ダクト
14 バッファ
15 冷却水パイプ
15ａ オイルパイプ
15ｂ オイルパイプ
16 フランジ
17 フィン
18 冷却水
19 ガス体
20 パイプ
20ａ 冷却水パイプ
20ｂ 冷却水パイプ[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a so-called shell and tube type heat exchanger that cools a high-temperature gas body with cooling water.
[0002]
[Prior art]
A heat exchanger as a so-called shell and tube type oil cooler is known from Japanese Utility Model Laid-Open No. 62-118965. As shown in FIG. 4, FIG. 5, or FIG. 6, header plates 12 are provided at both ends of a cylindrical (or square) main body 10, and a plurality of circular tubes 11 or flat tubes 3 are provided on the header plate 12. And the opening side of the duct 13 is fitted around the periphery of the header plate 12. Then, hot oil moves in the longitudinal direction from the oil pipe 15a protruding at one end of the outer periphery of the main body 10 and flows out from the oil pipe 15b protruding from the other end of the main body 10.
[0003]
Then, the cooling water flows into the circular tubes 11 or the flat tubes 3 from the cooling water pipe 20a of one duct 13, flows in the longitudinal direction, and flows out from the other cooling water pipe 20b. And in the main body 10, a heat exchanger is performed between oil and cooling water.
In such a heat exchanger, it is difficult to distribute the oil flowing from one oil pipe 15a to the other oil pipe 15b uniformly on the outer surface of each tube. Thus, conventionally, as shown in FIG. 4, the buffer 14 is arranged in a staggered manner inside the main body 10 to circulate the oil in a meandering manner.
[0004]
[Problems to be solved by the invention]
Even if the buffer 14 as shown in FIG. 4 is provided in order to allow the fluid on the tube outer surface side to flow uniformly, the stagnation of the fluid is improved to some extent, but it is not sufficient. That is, the buffer 14 and the base portion of the inner surface of the main body 10 still have a stagnation of fluid, and there is a defect that the heat exchange performance cannot be sufficiently exhibited. In particular, when a high-temperature gas body is flowed into the tube and the outer surface side is cooled with cooling water, if there is a drift in the cooling water on the outer surface side of the tube, not only can the heat exchange performance be sufficiently brought out, but also local boiling Causes various problems such as local heating and further drift.
Furthermore, when the buffer 14 is provided, there is a disadvantage that the flow resistance increases accordingly.
Then, this invention makes it a subject to solve the problem which concerns.
[0005]
[Means for Solving the Problems]
The present invention according to claim 1 comprises a main body (1) comprising a rectangular cylinder,
A pair of header plates (2) closing both open ends of the body (1);
The at least one pair of opposed inner surfaces of the main body (1) have parallel outer peripheral planes, both ends of which are liquid-tightly penetrated by the header plate (2), and a heat exchange medium for cooling is contained therein. A number of flat tubes (3) in circulation;
Cooling water inlet / outlet (4) provided on the outer surfaces of both ends in the longitudinal direction of the main body (1),
A slight gap is formed between the outermost peripheral surface of the tube group constituted by the multiple flat tubes (3) and the inner peripheral plane of the main body (1),
The distance (S1) (S2) between the inner peripheral surface of both ends in the longitudinal direction of the main body (1) and the outermost peripheral surface of the tube group is wider than those (S5) (S6) in the intermediate portion in the longitudinal direction. It is,
The intermediate portion in the longitudinal direction of the main body (1), and the interval (S6) between the inner peripheral surface and the outer periphery of the flat tube (3) facing it is adjacent to the aligned flat tubes (3). Formed smaller than the interval (S3) between the outer peripheral planes ,
These flat tubes (3) are juxtaposed in a plurality of rows in the longitudinal direction of the cross section, and the end spacing (S4) of the parallel flat tubes (3) that forms gaps between the rows is the flat tube (3 ) A heat exchanger formed slightly larger than the interval (S3) between adjacent outer peripheral planes .
[0007]
DETAILED DESCRIPTION OF THE INVENTION
Next, embodiments of the present invention will be described with reference to the drawings.
1 is a partially cutaway front view of a heat exchanger according to the present invention, FIG. 2 is a sectional view taken along the line II-II in FIG. 1, and FIG. 3 is a sectional view taken along the line III-III.
This heat exchanger includes a main body 1 made of an elongated rectangular cylinder, a pair of header plates 2 that close both ends in the longitudinal direction, and a number of flat tubes in which both ends are liquid-tightly penetrated into the flat holes of each header plate 2. 3 and a pair of ducts 7 to which the header plate 2 is fitted.
[0008]
As shown in FIG. 3, a large number of flat tubes 3 are arranged in parallel in the main body 1 at regular intervals in parallel to the plane. A slight gap S5, S6 is formed between the outermost periphery of the flat tube group constituted by a large number of flat tubes 3 and the inner surface of the main body 1. Further, an interval S3 sufficiently larger than the intervals S5 and S6 is formed between the planes of the adjacent flat tubes 3. Further, the interval between the ends of the flat tubes 3 arranged in a plurality of rows is S4, and the interval is formed slightly larger than that of S3.
[0009]
Next, both end portions in the longitudinal direction of the main body 1 are slightly bulged outwardly to form an annular bulging space portion 5 as shown in FIGS. 1 and 2, and the bulging amount is S7. One end of the cooling water pipe 15 is connected to the lower surface side on the outer periphery of the annular bulging space 5, and one end of the cooling water pipe 15 is connected to the inlet / outlet of the other annular bulging space 5 at a position 180 ° different from that. Has been. In addition, the direction of these entrances and exits can be made arbitrarily. An inner fin 8 having a rectangular wave shape or a normal wave shape is inserted into the flat tube 3 and the contact portions are brazed. Each component is preferably made of a stainless steel material, and is fixed in a fluid-tight manner between the header plate 2 and the end of the flat tube 3 and between the header plate 2 and the duct 7.
[0010]
A high-temperature gas body 19 is introduced from one duct 7, flows through each flat tube 3 in the longitudinal direction, and flows out from the other duct 7. In this example, the high-temperature gas body 19 is circulated from left to right in FIG. 1, but the gas body 19 may be circulated in the opposite direction. Further, cooling water flows from the cooling water pipe 15 from the inlet / outlet mounting direction on the lower surface side and the like into the annular bulging space portion 5 of the main body 1 and flows from the left end portion to the right end portion in the drawing, and the cooling water pipe on the upper end side and the like. From 15 it flows out. The gas body 19 is cooled in the main body 1 by the cooling water 18.
[0011]
In FIG. 2, the cooling water 18 flowing in from the inlet / outlet 4 bypasses the outer surface of the flat tube 3 facing the inlet / outlet 4, and surrounds the outer periphery of the group of flat tubes 3 including the annular bulging space 5 having a relatively large gap. It flows smoothly and is supplied between the flat tubes 3 and between the flat tubes 3 and the inner surface of the main body 1. Subsequently, it circulates between the flat tubes 3 and between the flat tubes 3 and the inner surface of the main body 1 in the longitudinal direction of the flat tubes. And the cooling water which passed the cyclic | annular expansion | swelling space part 5 distribute | circulates comparatively narrow space | interval S6 between the inner surface of the main body 1, and the outer surface of the outermost flat tube 3 facing it, and between each flat tube 3 Circulates between the slightly larger intervals S3. However, the water temperature distribution in each part of the cross section is substantially the same.
[0012]
This is because the cooling water flowing between the spaces S3 receives heat from the two opposing flat tubes 3, whereas the cooling water flowing between the outermost flat tube 3 and the main body 1 has one flatness. Since heat is received only from the tube 3, less cooling water is sufficient, and as a result, the temperature rise of the cooling water in each part is almost the same.
Next, the cooling water is heated by the four flat tubes 3 at the cross intersection 9 between the ends of the flat tubes 3 arranged in two rows. However, since the interval S4 in that portion is large and the cooling water flow rate is larger than that in the other portions, as a result, even in the vicinity of the crossing intersection 9, the water temperature rise is almost the same as that in the other portions.
[0013]
As described above, by providing the annular bulging space portion 5 having a relatively large gap at the cooling water inlet / outlet portion of the main body 1, the cooling water is sufficiently distributed to each part in the cross section of the annular bulging space portion 5. In addition, in the middle part of the main body 1, the distance between the inner surface and the flat tube 3 is slightly smaller than other parts, and cooling water does not bypass the inner surface of the main body 1 more than necessary. In addition, since the amount of heat received on the water side is small at that portion, uniform heat reception can be performed even if the flow path is narrowed.
When the gas body 19 is particularly hot, a TIG welding or Ni brazing structure is used between the flat tube 3 and the header plate 2 or between both ends of the main body 1 and the duct 7. It is preferable to use nickel brazing between the inner fins 8.
[0014]
[Operation and effect of the invention]
According to the present invention, since the annular bulging space 5 having a relatively large gap is provided at both longitudinal ends of the main body 1, the cooling water pressure at each portion at the both ends is made uniform, and the outer periphery of each flat tube 3. The flow rate of the cooling water flowing through can be made equal, and the heat exchange capacity of each part can be maximized. In other words, when the annular bulging space 5 is not present at both ends of the main body 1, the cooling water pressure at a position farther from the inlet / outlet 4 in the same cross section is reduced, and the flat tube 3 is correspondingly reduced. There is a possibility that the flow rate of the cooling water on the outer periphery may decrease. However, in the present invention, the flow rate of the cooling water in each part can be made uniform by the presence of the annular bulging space part 5.
Moreover, the heat exchange efficiency per unit volume can be improved by comprising in this way. A compact and efficient mounting heat exchanger can be provided.
[0015]
Furthermore, the interval between the inner peripheral surface of the main body 1 and the outer periphery of the flat tube opposite to the inner peripheral surface is formed smaller than the interval between the adjacent outer peripheral planes of the aligned flat tubes 3. is there. Thereby, the heat exchange amount of the cooling water along the inner peripheral surface of the main body 1 in the longitudinal intermediate portion and the temperature distribution of the cooling water flowing between the flat tubes 3 can be made substantially uniform.
This is because the cooling water along the inner peripheral surface of the main body 1 receives heat from only one flat tube along the inner peripheral surface, but the cooling water flowing between the adjacent flat tubes is opposed to two flat tubes. Receive heat dissipation. Therefore, by increasing the cross-section of the flow path through the portion with a larger amount of heat exchange, the temperature rise of the cooling water in each portion can be made substantially equal, and heat exchange can be performed more smoothly. At the same time, bypassing of the cooling water along the inner surface of the main body 1 can be prevented.
Furthermore, the flat tubes 3 are arranged in parallel in a plurality of rows in the longitudinal direction of the cross section, and the end portion interval S4 of the parallel flat tubes 3 which becomes a gap between the rows is the outer periphery adjacent to the flat tubes 3. Since it is formed slightly larger than the space S3 between the planes, even if heated by the four flat tubes 3 at the crossing point 9 (FIG. 3) between the ends of the flat tubes 3 arranged in two rows, Since the interval S4 in the portion is large, the cooling water flow rate is larger than that in the other portions, and as a result, there is an effect that the water temperature rise in the vicinity of the cross intersection 9 can be made the same as that in the other portions.
[Brief description of the drawings]
FIG. 1 is a partially broken front view of a heat exchanger according to the present invention.
FIG. 2 is a cross-sectional view taken along the line II-II in FIG.
3 is a cross-sectional view taken along arrow III-III in FIG.
FIG. 4 is a schematic front view of a conventional heat exchanger.
FIG. 5 is a side view of the heat exchanger with a duct 13 removed.
FIG. 6 is an exploded perspective view of another conventional heat exchanger.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Main body 2 Header plate 3 Flat tube 4 Entrance / exit 5 Annular expansion space 6 Entrance / exit 7 Duct 8 Inner fin 9 Cross intersection
10 Body
11 tubes
12 Header plate
13 Duct
14 buffers
15 Cooling water pipe
15a Oil pipe
15b Oil pipe
16 Flange
17 fins
18 Cooling water
19 Gas body
20 pipes
20a Cooling water pipe
20b Cooling water pipe

Claims (1)

矩形筒体よりなる本体(1) と、
その本体(1) の両開口端を閉塞する一対のヘッダプレート(2) と、
前記本体(1) の少なくとも対向する一対の内面に、夫々の外周の平面が平行に整列され、その両端が前記ヘッダプレート(2) に液密に貫通され、内部に被冷却用熱交換媒体が流通する多数の偏平チューブ(3) と、
前記本体(1) の長手方向両端部外面に設けられた冷却水の出入口(4) と、
を具備し、前記多数の偏平チューブ(3) で構成するチューブ群の最外周表面と前記本体(1) の内周平面とに僅かの隙間が形成され、
前記本体(1) の長手方向両端部の内周面と、前記チューブ群の最外周表面との間隔(S1)(S2)が、長手方向の中間部におけるそれら(S5)(S6)よりも広くされ、
前記本体(1)の長手方向中間部であって、その内周面とそれに対向する偏平チューブ(3) の外周との間隔(S6)が、整列された前記偏平チューブ(3) どうしの隣り合う外周平面間における間隔(S3)より小に形成され、
それらの偏平チューブ(3)は、その断面の長手方向に複数列に並列され、その列間の隙間となる並列された偏平チューブ(3)の端部間隔(S4)が、前記偏平チューブ(3)どうしの隣り合う外周平面間における間隔(S3)より僅かに大に形成された熱交換器。A main body (1) made of a rectangular cylinder;
A pair of header plates (2) closing both open ends of the body (1);
The at least one pair of opposed inner surfaces of the main body (1) have parallel outer peripheral planes, both ends of which are liquid-tightly penetrated by the header plate (2), and a heat exchange medium for cooling is contained therein. A number of flat tubes (3) in circulation;
Cooling water inlet / outlet (4) provided on the outer surfaces of both ends in the longitudinal direction of the main body (1),
A slight gap is formed between the outermost peripheral surface of the tube group constituted by the multiple flat tubes (3) and the inner peripheral plane of the main body (1),
The distance (S1) (S2) between the inner peripheral surface of both ends in the longitudinal direction of the main body (1) and the outermost peripheral surface of the tube group is wider than those (S5) (S6) in the intermediate portion in the longitudinal direction. It is,
The intermediate portion in the longitudinal direction of the main body (1), and the interval (S6) between the inner peripheral surface and the outer periphery of the flat tube (3) facing it is adjacent to the aligned flat tubes (3). Formed smaller than the interval (S3) between the outer peripheral planes ,
These flat tubes (3) are juxtaposed in a plurality of rows in the longitudinal direction of the cross section, and the end spacing (S4) of the parallel flat tubes (3) that forms gaps between the rows is the flat tube (3 ) A heat exchanger formed slightly larger than the interval (S3) between adjacent outer peripheral planes .
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JP3956097B2 (en) * 2002-01-07 2007-08-08 株式会社デンソー Exhaust heat exchanger
US7077190B2 (en) 2001-07-10 2006-07-18 Denso Corporation Exhaust gas heat exchanger
JP4151001B2 (en) * 2002-07-25 2008-09-17 株式会社ティラド Heat exchanger
JP2004077024A (en) * 2002-08-19 2004-03-11 Denso Corp Exhaust heat exchanger device
JP2006105577A (en) 2004-09-08 2006-04-20 Usui Kokusai Sangyo Kaisha Ltd Fin structure, heat-transfer tube having the fin structure housed therein, and heat exchanger having the heat-transfer tube assembled therein
JP4756585B2 (en) 2005-09-09 2011-08-24 臼井国際産業株式会社 Heat exchanger tube for heat exchanger
CN100460796C (en) * 2006-05-22 2009-02-11 北京美联桥科技发展有限公司 Multi-tube pass type heat exchanger
JP2009216285A (en) * 2008-03-10 2009-09-24 Showa Denko Kk Double-tube heat exchanger
WO2012093286A2 (en) * 2010-12-15 2012-07-12 Grundfos Holding A/S Heat transfer system
JP7035308B2 (en) 2016-11-25 2022-03-15 株式会社Ihi Pressure vessel
RU175917U1 (en) * 2017-02-20 2017-12-22 ФЕДЕРАЛЬНОЕ ГОСУДАРСТВЕННОЕ БЮДЖЕТНОЕ ОБРАЗОВАТЕЛЬНОЕ УЧРЕЖДЕНИЕ ВЫСШЕГО ОБРАЗОВАНИЯ "Брянский государственный технический университет" Tubular heat exchanger

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JPS6139285U (en) * 1984-08-16 1986-03-12 三菱重工業株式会社 Heat exchanger
JP2000097578A (en) * 1998-07-24 2000-04-04 Modine Mfg Co Heat exchanger and, especially, exhaust gas heat exchanger

Patent Citations (3)

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Publication number Priority date Publication date Assignee Title
JPS58158968U (en) * 1982-04-14 1983-10-22 特殊機化工業株式会社 heat exchanger
JPS6139285U (en) * 1984-08-16 1986-03-12 三菱重工業株式会社 Heat exchanger
JP2000097578A (en) * 1998-07-24 2000-04-04 Modine Mfg Co Heat exchanger and, especially, exhaust gas heat exchanger

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