JP2002107091A - Heat exchanger - Google Patents
Heat exchangerInfo
- Publication number
- JP2002107091A JP2002107091A JP2000301083A JP2000301083A JP2002107091A JP 2002107091 A JP2002107091 A JP 2002107091A JP 2000301083 A JP2000301083 A JP 2000301083A JP 2000301083 A JP2000301083 A JP 2000301083A JP 2002107091 A JP2002107091 A JP 2002107091A
- Authority
- JP
- Japan
- Prior art keywords
- main body
- cooling water
- peripheral surface
- tube
- longitudinal direction
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
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
- F28F1/02—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
Abstract
Description
【０００１】[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。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a so-called shell and tube type heat exchanger for cooling a high-temperature gas body with cooling water.
【０００２】[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６２−１１８９６
５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。2. Description of the Related Art A heat exchanger as a so-called shell-and-tube type oil cooler is disclosed in Japanese Utility Model Laid-Open Publication No. 62-11896.
No. 5 is known. As shown in FIG. 4, FIG. 5, or FIG. 6, headers 12 are provided at both ends of a cylindrical (or rectangular cross-section) main body 10, and the header plate 12 has a large number of circular tubes 11 or flat tubes 3. Penetrates, and the opening side of the duct 13 is fitted around the periphery of the header plate 12. Then, high-temperature oil moves in the longitudinal direction of the main body 10 from an oil pipe 15 a protruding from one end of the outer periphery of the main body 10, and flows out from an oil pipe 15 b protruding from the other end of the main body 10.
【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。The cooling water pipe 20a of one duct 13
The cooling water flows into each circular tube 11 or the flat tube 3 from the other, flows in the longitudinal direction, and flows out from the other cooling water pipe 20b. In the main body 10, a heat exchanger is performed between the oil and the cooling water. In such a heat exchanger, it is difficult for the oil flowing from one oil pipe 15a to the other oil pipe 15b to uniformly flow on the outer surface of each tube. Therefore, FIG.
As described above, the buffers 14 are arranged in a zigzag pattern inside the main body 10 to circulate the oil in a meandering manner.
【０００４】[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。In order to uniformly distribute the fluid on the outer surface of the tube, a buffer 14 as shown in FIG.
Although the stagnation of the fluid is improved to some extent, it cannot be said that it is sufficient. That is, there is a disadvantage that the fluid also stagnates at the base of the buffer 14 and the inner surface of the main body 10, and the heat exchange performance cannot be sufficiently exhibited. In particular, when flowing a high-temperature gas body into a tube and cooling the outer surface of the tube with cooling water, if drift occurs in the cooling water on the outer surface of the tube, not only the heat exchange performance cannot be sufficiently obtained, but also local boiling. Causes various problems such as local heating and further drift. Further, when the buffer 14 is provided, there is a disadvantage that the flow resistance increases by that much. Then, this invention makes it a subject to solve such a problem.
【０００５】[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
くされた一対の環状膨出空間部(5) を有する熱交換器で
ある。According to the present invention, a main body (1) comprising a rectangular cylindrical body and a pair of header plates (2) for closing both open ends of the main body (1) are provided. , The body
(1) At least a pair of inner surfaces facing each other, the outer peripheral planes thereof are aligned in parallel, and both ends thereof are the header plate.
(2), a number of flat tubes (3) through which a heat exchange medium to be cooled flows, and cooling water inlets and outlets (2) provided on the outer surfaces of both ends in the longitudinal direction of the main body (1). 4), wherein a slight gap is formed between the outermost peripheral surface of the tube group composed of the large number of flat tubes (3) and the inner peripheral plane of the main body (1). The distance between the inner peripheral surface of both ends in the longitudinal direction and the outermost peripheral surface of the tube group (S1) (S2)
This is a heat exchanger having a pair of annular bulging spaces (5) wider than those (S5) and (S6) in the middle part in the longitudinal direction.
【０００６】請求項２に記載の本発明は、請求項１にお
いて、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)より小に形成された熱
交換器である。According to a second aspect of the present invention, in the first aspect, an interval between an inner peripheral surface of the main body (1) and an outer peripheral surface of the flat tube (3) facing the intermediate portion in the longitudinal direction of the main body (1).
(S6) is a heat exchanger formed to be smaller than the interval (S3) between adjacent outer peripheral planes of the aligned flat tubes (3).
【０００７】[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。Next, an embodiment of the present invention will be described with reference to the drawings. 1 is a partially cutaway front view of the heat exchanger of the present invention, FIG. 2 is a sectional view taken along the line II-II of FIG.
FIG. 3 is a sectional view taken along the line III-III. This heat exchanger includes a main body 1 formed of an elongated rectangular cylindrical body, a pair of header plates 2 closing both ends in a longitudinal direction thereof, and a large number of flat tubes whose both ends are penetrated through flat holes of each header plate 2 in a liquid-tight manner. 3 and a pair of ducts 7 on which the header plate 2 is fitted.
【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Ｓ
５，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。As shown in FIG. 3, a number of flat tubes 3 are arranged at regular intervals in the main body 1 in parallel with the plane. A slight distance S is set between the outermost periphery of the group of flat tubes constituted by a number of flat tubes 3 and the inner surface of the main body 1.
5, S6 are formed. Further, a space S3 which is sufficiently larger than the spaces S5 and S6 is formed between the planes of the adjacent flat tubes 3. Further, the interval between the end portions of the flat tubes 3 arranged in a plurality of rows is S4, and the interval is slightly larger than that of S3.
【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。Next, both ends in the longitudinal direction of the main body 1 are slightly swelled outward, and an annular swelling space portion 5 is formed therein as shown in FIGS. is there. One end of the cooling water pipe 15 is connected to the lower surface side of the outer periphery of the annular bulging space 5, and one end of the cooling water pipe 15 is connected to the entrance of the other annular bulging space 5 at a position 180 ° different therefrom. Have been. In addition, the direction of these entrances can be arbitrarily directed. An inner fin 8 having a rectangular waveform or a normal waveform is inserted into the flat tube 3, and the contact portions thereof are brazed. Each component is preferably made of a stainless steel material, and the space between the header plate 2 and the end of the flat tube 3 and the space between the header plate 2 and the duct 7 are welded and fixed in a liquid-tight manner.
【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。Then, a high-temperature gas body 19 is supplied from one of the ducts 7.
Is introduced, 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 flows from left to right in FIG. 1, but the gas body 19 may flow in the opposite direction. In addition, cooling water flows into the annular bulging space portion 5 of the main body 1 from the cooling water pipe 15 from the inlet / outlet mounting direction such as the lower surface side, flows from the left end to the right end in the drawing, and the cooling water pipe at the upper end side. From 15 it drains. And gas body by cooling water 18
19 is cooled in the main body 1.
【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Ｓ
３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。In FIG. 2, the cooling water flowing from the entrance 4
The bypass tube 18 bypasses the outer surface of the flat tube 3 facing the entrance 4 and smoothly circulates around the outer circumference of the group of flat tubes 3 including the annular bulging space 5 having a relatively large gap. Between the flat tube 3 and the inner surface of the main body 1. Next, the air flows 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. The cooling water that has passed through the annular bulging space 5 circulates through a relatively narrow space S6 between the inner surface of the main body 1 and the outer surface of the outermost flat tube 3 facing the cooling water. Is a slightly larger spacing S
It circulates between the three. However, the water-side temperature distribution in each part of the cross section is substantially the same.
【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。This is because the cooling water flowing between the spaces S3 receives heat radiation from the two opposed flat tubes 3, whereas the cooling water flowing between the outermost flat tubes 3 and the main body 1 does not. Since heat is radiated from only one flat tube 3, less cooling water is sufficient, and as a result, the temperature rise of the cooling water in each part becomes almost the same. Next, at the cross point 9 between the ends of the flat tubes 3 arranged in two rows, the cooling water is heated by the four flat tubes 3. However, the space S4 in that portion is large, and the cooling water flow rate is larger than in the other portions. As a result, the water temperature rise near the crossroads 9 is almost the same as in the other portions.
【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。As described above, at the inlet and outlet of the cooling water of the main body 1,
By providing the annular bulging space portion 5 having a relatively large gap, the cooling water can be sufficiently distributed to each part in the cross section of the annular bulging space portion 5 and the main body 1
In the middle part, the distance between the inner surface and the flat tube 3 is slightly smaller than that of the other parts, so that the cooling water is not unnecessarily bypassed along the inner surface of the main body 1 and at that part, Since the amount of heat received on the water side is also small, it is possible to perform uniform heat reception even if the flow path is narrowed. When the gas body 19 has a particularly high temperature, the space between the flat tube 3 and the header plate 2 or between the both ends of the main body 1 and the duct 7 is formed by a TIG welding or Ni brazing structure. Nickel brazing is preferably performed between the inner fin 8 and the inner fin 8.
【００１４】[0014]
【発明の作用・効果】請求項１に記載の本発明によれ
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。According to the first aspect of the present invention, since the main body 1 has the annular bulging space portions 5 with relatively large gaps at both ends in the longitudinal direction, cooling of each portion at the both ends is achieved. By making the water pressure uniform, the flow rate of the cooling water flowing around the outer circumference of each flat tube 3 is made equal, and the heat exchange capacity of each part can be maximized. Conversely, when the annular bulging space portion 5 does not exist at both ends of the main body 1, the cooling water pressure at a position farther from the entrance 4 in the same cross section decreases, and the flat tube 3 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 5. Further, with such a configuration, the heat exchange efficiency per unit volume can be improved. And a compact heat exchanger with good mounting efficiency can be provided.
【００１５】請求項２に記載の本発明によれば、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。According to the second aspect of the present invention, the main body 1
In the intermediate portion in the longitudinal direction, the distance between the inner peripheral surface and the outer periphery of the flat tube opposed thereto is formed smaller than the distance between the adjacent outer peripheral planes of the aligned flat tubes 3. Thereby, the heat exchange amount of the cooling water along the inner peripheral surface of the main body 1 and the temperature distribution of the cooling water flowing between the flat tubes 3 can be made substantially uniform in the longitudinal middle part. This is because the cooling water along the inner peripheral surface of the main body 1 receives heat radiation from only one flat tube along the inner peripheral surface, but the cooling water flowing between the adjacent flat tubes is two opposed flat tubes. Receive heat radiation from For this reason, by increasing the cross-section of the flow passage that circulates a portion having 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, it is possible to prevent the cooling water from being bypassed along the inner surface of the main body 1.
【図面の簡単な説明】[Brief description of the drawings]
【図１】本発明の熱交換器の一部破断正面図。FIG. 1 is a partially cutaway front view of a heat exchanger of the present invention.
【図２】図１のII−II矢視断面図。FIG. 2 is a sectional view taken along the line II-II of FIG.
【図３】図１の III− III矢視断面図。FIG. 3 is a sectional view taken along the line III-III in FIG. 1;
【図４】従来型熱交換器の正面略図。FIG. 4 is a schematic front view of a conventional heat exchanger.
【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。FIG. 5 is a side view of the heat exchanger with the duct 13 removed.
【図６】他の従来型熱交換器の分解斜視図。FIG. 6 is an exploded perspective view of another conventional heat exchanger.
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 DESCRIPTION OF SYMBOLS 1 Main body 2 Header plate 3 Flat tube 4 Entrance 5 Annular bulging space 6 Entrance 7 Duct 8 Inner fin 9 Crossing intersection 10 Main body 11 Tube 12 Header plate 13 Duct 14 Buffer 15 Cooling water pipe 15a Oil pipe 15b Oil pipe 16 Flange 17 Fin 18 Cooling water 19 Gas body 20 Pipe 20a Cooling water pipe 20b Cooling water pipe
Claims (2)
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)よりも広くされた一対の環状
膨出空間部(5) を有する熱交換器。1. A main body (1) made of a rectangular cylindrical body, a pair of header plates (2) for closing both open ends of the main body (1), and at least a pair of inner surfaces opposed to each other of the main body (1). A large number of flat tubes (3) through which the respective outer peripheral planes are aligned in parallel, both ends of which are penetrated in a liquid-tight manner through the header plate (2), and through which a heat exchange medium to be cooled flows; (1) a cooling water inlet / outlet (4) provided on the outer surfaces of both ends in the longitudinal direction, and an outermost peripheral surface of a tube group composed of the large number of flat tubes (3) and the main body (1). A slight gap is formed between the inner peripheral plane and the inner peripheral surface at both ends in the longitudinal direction of the main body (1), and the interval (S1) (S2) between the outermost peripheral surface of the tube group is an intermediate point in the longitudinal direction. A heat exchanger having a pair of annular bulging spaces (5) wider than those (S5) and (S6) in the section.
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)より小に形成された熱交換
器。2. The space (S6) according to claim 1, wherein the space (S6) is an intermediate portion in the longitudinal direction of the main body (1) and an inner peripheral surface thereof and an outer peripheral surface of the flat tube (3) opposed thereto.
However, the heat exchanger is formed to be smaller than the interval (S3) between the adjacent flat tubes (3) arranged adjacent to each other.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2000301083A JP4536237B2 (en) | 2000-09-29 | 2000-09-29 | Heat exchanger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2000301083A JP4536237B2 (en) | 2000-09-29 | 2000-09-29 | Heat exchanger |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP2002107091A true JP2002107091A (en) | 2002-04-10 |
| JP4536237B2 JP4536237B2 (en) | 2010-09-01 |
Family
ID=18782667
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2000301083A Expired - Fee Related JP4536237B2 (en) | 2000-09-29 | 2000-09-29 | Heat exchanger |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP4536237B2 (en) |
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2003201923A (en) * | 2002-01-07 | 2003-07-18 | Denso Corp | Exhaust heat exchanger |
| WO2004011869A1 (en) * | 2002-07-25 | 2004-02-05 | Toyo Radiator Co., Ltd. | Heat exchanger |
| JP2004077024A (en) * | 2002-08-19 | 2004-03-11 | Denso Corp | Exhaust heat exchanger device |
| US7303002B2 (en) | 2004-09-08 | 2007-12-04 | Usui Kokusai Sangyo Kaisha Limited | Fin structure, heat-transfer tube having the fin structure housed therein, and heat exchanger having the heat-transfer tube assembled therein |
| 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 |
| US7527088B2 (en) | 2001-07-10 | 2009-05-05 | Denso Corporation | Exhaust gas heat exchanger |
| JP2009216285A (en) * | 2008-03-10 | 2009-09-24 | Showa Denko Kk | Double-tube heat exchanger |
| US7614443B2 (en) | 2005-09-09 | 2009-11-10 | Usui Kokusai Sangyo Kaisha Limited | Heat exchanger tube |
| WO2012093286A2 (en) * | 2010-12-15 | 2012-07-12 | Grundfos Holding A/S | Heat transfer system |
| RU175917U1 (en) * | 2017-02-20 | 2017-12-22 | ФЕДЕРАЛЬНОЕ ГОСУДАРСТВЕННОЕ БЮДЖЕТНОЕ ОБРАЗОВАТЕЛЬНОЕ УЧРЕЖДЕНИЕ ВЫСШЕГО ОБРАЗОВАНИЯ "Брянский государственный технический университет" | Tubular heat exchanger |
| EP3546877A4 (en) * | 2016-11-25 | 2020-06-17 | IHI Corporation | Pressure container |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2000097578A (en) * | 1998-07-24 | 2000-04-04 | Modine Mfg Co | Heat exchanger and, especially, exhaust gas heat exchanger |
Family Cites Families (2)
| 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 |
-
2000
- 2000-09-29 JP JP2000301083A patent/JP4536237B2/en not_active Expired - Fee Related
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2000097578A (en) * | 1998-07-24 | 2000-04-04 | Modine Mfg Co | Heat exchanger and, especially, exhaust gas heat exchanger |
Cited By (18)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7527088B2 (en) | 2001-07-10 | 2009-05-05 | Denso Corporation | Exhaust gas heat exchanger |
| JP2003201923A (en) * | 2002-01-07 | 2003-07-18 | Denso Corp | Exhaust heat exchanger |
| WO2004011869A1 (en) * | 2002-07-25 | 2004-02-05 | Toyo Radiator Co., Ltd. | Heat exchanger |
| US7267160B2 (en) | 2002-07-25 | 2007-09-11 | T.Rad Co., Ltd. | Heat exchanger |
| CN100414246C (en) * | 2002-07-25 | 2008-08-27 | 株式会社T.Rad | Heat exchanger |
| JP2004077024A (en) * | 2002-08-19 | 2004-03-11 | Denso Corp | Exhaust heat exchanger device |
| US7303002B2 (en) | 2004-09-08 | 2007-12-04 | Usui Kokusai Sangyo Kaisha Limited | Fin structure, heat-transfer tube having the fin structure housed therein, and heat exchanger having the heat-transfer tube assembled therein |
| DE102006041985B4 (en) * | 2005-09-09 | 2011-06-30 | Usui Kokusai Sangyo Kaisha Ltd., Shizuoka | heat exchanger tube |
| US7614443B2 (en) | 2005-09-09 | 2009-11-10 | Usui Kokusai Sangyo Kaisha Limited | Heat exchanger tube |
| 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 |
| WO2012093286A3 (en) * | 2010-12-15 | 2012-11-08 | Grundfos Holding A/S | Heat transfer system |
| US9151541B2 (en) | 2010-12-15 | 2015-10-06 | Grundfos Holding A/S | Heat transfer system |
| EP3546877A4 (en) * | 2016-11-25 | 2020-06-17 | IHI Corporation | Pressure container |
| US11177046B2 (en) | 2016-11-25 | 2021-11-16 | Ihi Corporation | Pressure vessel |
| EP3974761A1 (en) * | 2016-11-25 | 2022-03-30 | IHI Corporation | 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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