JPS58160798A - Heat exchanger - Google Patents
Heat exchangerInfo
- Publication number
- JPS58160798A JPS58160798A JP4266682A JP4266682A JPS58160798A JP S58160798 A JPS58160798 A JP S58160798A JP 4266682 A JP4266682 A JP 4266682A JP 4266682 A JP4266682 A JP 4266682A JP S58160798 A JPS58160798 A JP S58160798A
- Authority
- JP
- Japan
- Prior art keywords
- hole
- heat exchanger
- circular
- wall surface
- tube
- 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.)
- Pending
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
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/04—Arrangements for sealing elements into header boxes or end plates
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
Description
【発明の詳細な説明】
本発明は蒸気発生器等のように管板を有する熱交換4に
係り、特に失色な熱過渡条件で運転される熱交換器の管
板部の熱応力を低減させるのに好適な熱交換器に関する
。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a heat exchanger 4 having a tube plate, such as a steam generator, and particularly to reduce thermal stress in the tube plate portion of a heat exchanger operated under discoloring thermal transient conditions. The present invention relates to a heat exchanger suitable for.
従来の蒸気発生IIII等の熱交換器の管板部の構造は
、管板部に多数の孔部が形成されこの孔部より器内中心
部に向って多数の伝熱管が配設されるようになっている
。従って伝熱管内を流れる流体は管板に形成され九孔部
の内壁面に直接接触する状ゆでR,sすることになる。The structure of the tube plate of a conventional heat exchanger such as a steam generator III is such that a large number of holes are formed in the tube plate and a large number of heat transfer tubes are arranged from these holes toward the center of the vessel. It has become. Therefore, the fluid flowing inside the heat transfer tube is boiled so as to directly contact the inner wall surface of the nine holes formed in the tube plate.
このため多数の孔部を有する看板の中央部付近はll1
ili@状態の流体の温度変化に早く追従するが、管板
の周辺部分は孔部が形成されておらず、また4造的に4
肉部となっているので管板の孔部を流れる流体の温度変
化に対して追従性が悪い。この結果管板の中央部付近と
周辺部との間に大睡な温度差によって大きな熱応力を生
じる問題がある。Therefore, the area near the center of a signboard with many holes is ll1
Although it quickly follows the temperature change of the fluid in the ili@ state, there are no holes in the peripheral part of the tube sheet, and
Since it is a fleshy part, it has poor ability to follow the temperature change of the fluid flowing through the hole in the tube sheet. As a result, there is a problem in that large thermal stress is generated due to a large temperature difference between the central portion and the peripheral portion of the tube sheet.
本発明の目的は、大傘な熱過渡条件下で運転される熱交
換部の管板部に発生する熱応力を低減させることができ
る熱交換器を提供することKToる。An object of the present invention is to provide a heat exchanger capable of reducing thermal stress generated in a tube sheet portion of a heat exchange section operated under severe thermal transient conditions.
上記目的を達成するためには、管板の周辺部のIIFA
度変化追従性を良くする手段と、管板の中央部付近の温
度変化追従性を悪くする手段等が考えられる。本発明F
i熱交換器の構造!i!1度上の問題・を生じることな
く熱応力低減の効果の大きい*=Jtを採用したもので
ある。In order to achieve the above objective, it is necessary to
Possible means include improving the ability to follow temperature changes and making the ability to follow temperature changes worse near the center of the tube sheet. Present invention F
Structure of i heat exchanger! i! *=Jt is adopted, which is highly effective in reducing thermal stress without causing any higher problems.
部ち本発明は管板の孔部内にこの孔部内壁面と間隙をも
って円管を配設し、この円管の外周面と孔部内壁面との
間における流体の流れを防止する丸めのシール機構を設
けたものである。However, the present invention provides a rounded seal mechanism in which a circular tube is disposed in a hole of a tube plate with a gap between the inner wall surface of the hole and the outer circumferential surface of the circular tube and the inner wall surface of the hole. It was established.
以下添付図面によって本@明の実施例を説明する。第1
図及び第2図は本発明の一実施例を示し、図において管
板1には多数の孔2が形成され各々の孔2から器内中心
側に多数の伝熱管3が延設されている。これらの各々の
孔2の内壁面と間隙をもって円管4が挿入されている。Embodiments of this invention will be described below with reference to the accompanying drawings. 1st
2 and 2 show an embodiment of the present invention, in which a large number of holes 2 are formed in a tube plate 1, and a large number of heat exchanger tubes 3 extend from each hole 2 toward the center of the vessel. . A circular tube 4 is inserted into each of these holes 2 with a gap between the inner wall surface and the inner wall surface.
この円f4は第2図に示すように円周方向に沿って溝4
Aが形成されこれらの溝4Aにピストンリング5が嵌合
されている。これによって孔2の内壁面と円管4との間
がシールされることになる。ま友管板lxシ上部に突出
し九円管4の外周は支持板6と溶接によって固定されて
いる。第1図において支持板6の外周面の3111所か
ら上方に延びる支持フレーム7が設けられ、この支持フ
レーム7の上端部から両方に延びる係止部材8が固定さ
れている。この係止部材8は7ランク部9に設けられた
段部に係合した状態で熱交換器内に設置されるようにな
っている。This circle f4 is a groove 4 along the circumferential direction as shown in FIG.
A piston ring 5 is fitted into these grooves 4A. This results in a seal between the inner wall surface of the hole 2 and the circular tube 4. The outer periphery of the nine-round tube 4 protruding from the top of the tube plate lx is fixed to the support plate 6 by welding. In FIG. 1, a support frame 7 is provided extending upward from a position 3111 on the outer peripheral surface of the support plate 6, and a locking member 8 extending in both directions from the upper end of the support frame 7 is fixed. This locking member 8 is installed in the heat exchanger in a state where it is engaged with a stepped portion provided on the seventh rank portion 9.
このような構成からなる熱5e換器において、伝熱管3
内を上昇する高温の流体は円f4内を通った後氷室lO
に至る。このよりな篇温の流体の流通時において、孔2
の内壁面と円管4の軸方向における熱膨張差は、円管4
が軸方向に延び、この場合ピストンリングの摺動により
吸収可能となる。In the heat exchanger having such a configuration, the heat exchanger tube 3
The high temperature fluid rising inside the ice chamber lO after passing through the circle f4
leading to. During the flow of fluid with a higher temperature, the hole 2
The difference in thermal expansion between the inner wall surface of the circular tube 4 and the axial direction of the circular tube 4 is
extends in the axial direction, in which case it can be absorbed by sliding of the piston ring.
ま丸孔2の内11面と円管4の半径方向における熱膨g
kMがピストンリング4Aの弾性変形によシ補償される
、従って伝熱管3から孔部内に流入する高温流体が孔2
の内全面と円管4との外壁面との間隙内に流入すること
がない。このことから孔2の内壁面と円管4とのり内は
気体が介在しているので断熱層としての役割りを果丸し
、流体に大きな熱過度が生じ走時も熱過渡が円管4及び
円管4と孔2との間隙を通って管板内に達するまでに時
間を要するため管板1の中央部付近の金属温度変化を管
板1の周辺部の金員温度変化の程度に近付けることが可
能となる。従って大きな熱過渡条件で運転する場合にも
管板lの中央付近と周辺部付近との温度差による熱応力
の発生を抑制することがいる。Thermal expansion g in the radial direction of the inner 11 surfaces of the round hole 2 and the circular tube 4
kM is compensated by the elastic deformation of the piston ring 4A. Therefore, the high temperature fluid flowing into the hole from the heat transfer tube 3 flows into the hole 2.
It does not flow into the gap between the inner surface of the tube 4 and the outer wall surface of the circular tube 4. As a result, since gas exists between the inner wall surface of the hole 2 and the inside of the circular tube 4, it serves as a heat insulating layer, and a large thermal excess is generated in the fluid, causing thermal transients during travel to the circular tube 4. Since it takes time to pass through the gap between the circular tube 4 and the hole 2 and reach the inside of the tube sheet, the metal temperature change near the center of the tube sheet 1 is adjusted to the same degree as the metal temperature change at the periphery of the tube sheet 1. It is possible to get closer. Therefore, even when operating under large thermal transient conditions, it is possible to suppress the generation of thermal stress due to the temperature difference between the center and peripheral portions of the tube sheet l.
本実施例において伝熱管3内の探傷横置及び補修作業等
においては円管4、支持板6、支持フレーム7及び係止
部材8を一体として図中上方に持ち上げて脱着させるこ
とがで色るので補修作業が支障となることはない。また
伝熱[3から円管4内に導入される流体の流速はかなり
高いために円管4のブレが生じる虞れがあるが、ピスト
ンリング4Aによって円管4のプレをも防止する仁とが
で色る。In this embodiment, during horizontal flaw detection and repair work in the heat transfer tube 3, the circular tube 4, support plate 6, support frame 7, and locking member 8 can be lifted upward in the figure as one body and removed. Therefore, repair work will not be a hindrance. In addition, since the flow rate of the fluid introduced into the circular tube 4 from the heat transfer [3] is quite high, there is a risk that the circular tube 4 may shake, but the piston ring 4A prevents the circular tube 4 from deflecting. It's colored.
第3図は本発明の他の実施例を示し、第1図及び第2図
に示す実施例と異なる点は円管11の下端部が円錐状に
拡大した構造となっていることである。この場合円管1
1及びピストンリングに対する流体の流通抵抗を小さく
することができる。FIG. 3 shows another embodiment of the present invention, which differs from the embodiment shown in FIGS. 1 and 2 in that the lower end of the circular tube 11 is expanded into a conical shape. In this case, circular pipe 1
1 and the piston ring can be reduced.
#!4図は本発明の他の実施例を示し、第1図及び第2
図に示す実施例と異なる点は、管板lに形成される孔1
2の口径が拡大され、円管13の内径が伝熱管3の内径
と等しくなるようにしたものである。本実施例によれば
、流体の流通抵抗を小さくすることができると共に円管
13の内径が大きいために伝熱管の探傷慣食等の場合に
おいても円f13を取り外すことなくこの円′#13内
に探傷器等を挿入することができる。#! FIG. 4 shows another embodiment of the present invention, and FIGS.
The difference from the embodiment shown in the figure is that the hole 1 formed in the tube sheet l
The diameter of the heat exchanger tube 2 is enlarged so that the inner diameter of the circular tube 13 becomes equal to the inner diameter of the heat transfer tube 3. According to this embodiment, it is possible to reduce the flow resistance of the fluid, and since the inner diameter of the circular tube 13 is large, even in the case of flaw detection and erosion of heat transfer tubes, there is no need to remove the circle f13. A flaw detector, etc. can be inserted into the
本発明においては、円管に溝を形成し、この溝にピスト
ンリングを嵌合させる代りに円管に直接リングを焼滅め
によって固着させることもできる。In the present invention, instead of forming a groove in the circular tube and fitting the piston ring into the groove, the ring may be directly fixed to the circular tube by burning.
また第1図及び第2図の場合孔2の内壁面と円管との間
隙内に気体を介在させているので管板lの中央部付近に
おける温度追従性が最も低くなる効果があるが、孔2の
内11面と円管4との間隙内において流体が流動しない
状態であれば管板1の中夫付近の温度追従性を低くする
ことができる。このような手段として第1図における支
持フレーム7の代りに円筒状の支持部材とすることによ
って孔2の内Ia面と円管との間隙内に導入してくる流
体は係合部材8のF面で行き止ま抄となる九めに流体の
流通を阻止することができる。従って管板1の中央部付
近のm[追従性を低くすることができる。友だしこの場
合円管4のプレが生じる虞れがあるのでピストンリング
4人の代りに円管4と孔部内壁向との間に架設された支
持部材を設けることが望ましい。In addition, in the case of FIGS. 1 and 2, since gas is interposed in the gap between the inner wall surface of the hole 2 and the circular tube, there is an effect that the temperature followability near the center of the tube sheet l is lowest. If the fluid does not flow within the gap between the inner surface 11 of the hole 2 and the circular tube 4, the temperature followability in the vicinity of the center shaft of the tube plate 1 can be lowered. As such a means, by using a cylindrical support member in place of the support frame 7 in FIG. It is possible to block the flow of fluid at the 9th point where the surface becomes a dead end. Therefore, it is possible to lower the followability of m near the center of the tube sheet 1. However, in this case, there is a risk that the circular tube 4 may bend, so it is desirable to provide a supporting member installed between the circular tube 4 and the inner wall of the hole in place of the four piston rings.
なお孔部内壁面と円管との間隙に設けられるピストンリ
ングや支愕部材弄は、熱膨張率が小さくかつ熱膨張率が
管板1を形成する材質と同等であることが理想的である
が、実用上の面から考えれば熱膨張率が管板1の材質と
同等であることが望ましい。Ideally, the piston ring and support member provided in the gap between the inner wall surface of the hole and the circular pipe should have a small coefficient of thermal expansion and be equivalent to the material forming the tube sheet 1. From a practical point of view, it is desirable that the coefficient of thermal expansion is the same as that of the material of the tube sheet 1.
以上のように本発明によれば、管板の中央部付近におけ
る温度変化追従性を管板の周辺部における温度変化追従
性よりも低くすることができるので管板中央部付近と周
辺部との温度差を小さくすることかで含熱応力の発生を
低減することができるため構造の錐全性を増加する効果
がある。As described above, according to the present invention, the temperature change followability near the center of the tubesheet can be made lower than the temperature change followability near the periphery of the tubesheet. By reducing the temperature difference, the generation of thermal stress can be reduced, which has the effect of increasing the integrity of the structure.
第1図は本発明の一実施例を示す要部の縦断面図、II
2図#′i#!1図の要部拡大図、第3図及び第4図は
それぞれ本@明の他の実施例を示す要部の縦断面図でる
る。
l・・・管板、2・・・孔、3・・・伝熱管、4・・・
円管、5・・・ピストンリング、6・・・支持板、7・
・・支持フレーム、第 1 図
第 21¥1
第 3 図
6FIG. 1 is a vertical sectional view of the main part showing one embodiment of the present invention, II
Figure 2#'i#! FIG. 1 is an enlarged view of the main part, and FIGS. 3 and 4 are longitudinal sectional views of the main part showing other embodiments of the present invention. l...tube sheet, 2...hole, 3...heat exchanger tube, 4...
Circular tube, 5... Piston ring, 6... Support plate, 7.
...Support frame, Fig. 1 Fig. 21¥1 Fig. 3 Fig. 6
Claims (1)
に延設された伝熱管とを備え九熱交1llI器において
、前記孔部内にこの孔部内壁面と間隙をもって円管を配
設し、この円管の外周面と孔部内壁面との間との間にお
ける液体の流れを防止する九めのシール機構を設は九こ
とを特徴とする熱交換器。 2、シー/L?機構が、円管と孔部内411面との間隙
に設けられたピストンリングである特許請求の範囲第1
項記載の熱交換器。 3、シール機構が、管板より延設され九フランジの内面
に沿って設けられ九支持部材と7ランジとの密接構造物
である特許請求の範囲第1項記載の熱交換器。 4、円管と孔部内壁面との間に支持部材を設けた特許請
求の範囲@3項記載の熱交換器。[Claims] 1. In a nine-heat exchanger equipped with a tube plate in which a large number of holes are formed and a heat transfer tube extending into the container from the holes, A heat exchanger characterized in that a circular pipe is arranged with a gap between the wall surface and a sealing mechanism that prevents liquid from flowing between the outer peripheral surface of the circular pipe and the inner wall surface of the hole. vessel. 2. C/L? Claim 1, wherein the mechanism is a piston ring provided in the gap between the circular tube and the 411 surface inside the hole.
Heat exchanger as described in section. 3. The heat exchanger according to claim 1, wherein the sealing mechanism is a close structure between the supporting member and the flange, which extends from the tube plate and is provided along the inner surface of the flange. 4. The heat exchanger according to claim 3, wherein a support member is provided between the circular tube and the inner wall surface of the hole.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP4266682A JPS58160798A (en) | 1982-03-19 | 1982-03-19 | Heat exchanger |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP4266682A JPS58160798A (en) | 1982-03-19 | 1982-03-19 | Heat exchanger |
Publications (1)
Publication Number | Publication Date |
---|---|
JPS58160798A true JPS58160798A (en) | 1983-09-24 |
Family
ID=12642335
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP4266682A Pending JPS58160798A (en) | 1982-03-19 | 1982-03-19 | Heat exchanger |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS58160798A (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2562505A1 (en) | 2011-08-25 | 2013-02-27 | Nuovo Pignone S.p.A. | Integrated pressure compensating heat exchanger and method |
US20150068716A1 (en) * | 2012-05-15 | 2015-03-12 | Behr Gmbh & Co. Kg | Exhaust gas heat exchanger |
CN111256495A (en) * | 2018-11-30 | 2020-06-09 | 比亚迪股份有限公司 | Heat exchanger, thermal management system of vehicle and vehicle |
-
1982
- 1982-03-19 JP JP4266682A patent/JPS58160798A/en active Pending
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2562505A1 (en) | 2011-08-25 | 2013-02-27 | Nuovo Pignone S.p.A. | Integrated pressure compensating heat exchanger and method |
US9863723B2 (en) | 2011-08-25 | 2018-01-09 | Silvio Giachetti | Integrated pressure compensating heat exchanger and method |
US20150068716A1 (en) * | 2012-05-15 | 2015-03-12 | Behr Gmbh & Co. Kg | Exhaust gas heat exchanger |
US9791214B2 (en) * | 2012-05-15 | 2017-10-17 | Mahle International Gmbh | Exhaust gas heat exchanger |
CN111256495A (en) * | 2018-11-30 | 2020-06-09 | 比亚迪股份有限公司 | Heat exchanger, thermal management system of vehicle and vehicle |
CN111256495B (en) * | 2018-11-30 | 2021-12-07 | 比亚迪股份有限公司 | Heat exchanger, thermal management system of vehicle and vehicle |
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