JPS5811392A - Supporting structure of heat transmitting pipe for heat exchanger of heat - Google Patents

Abstract

PURPOSE:To reduce a stress generated in the heat transmitting pipe or the support fixture therefor due to a thermal expansion caused by the temperature difference between the heat transmitting pipes each other by a method wherein an annular spacer is changed into the spiral spacer. CONSTITUTION:The spiral spacers 40, 41, 42, 43, inclined into reverse directions each other in each layers, are utilized as the spacers, and whereby primary side fluid, flowed down through respective sub channels, is collided against the upper parts of the spiral spacers 40, 41, 42, 43 and tries to flow along the inclined directions of the spiral spacers, thereby generating a whirling current finally. Accordingly, the primary side fluid moves to the peripheral direction subsequently through the sub channel and flows down through the outside of the heat transmitting pipes. Here, a space constituted at the center of the four pieces of the heat transmitting pipes adjoining each other, for example, the pipes, 31, 32, 33, 34, is referred as the sub channel.

Description

【発明の詳細な説明】 本発胛は、直管式熱交換器の伝熱管支持構造に係り、伝
熱管支持構造を前記伝熱管の軸方向に対しである角度を
有するらせん状にすることによシ、伝熱管外を流れる流
体を熱交換器内において周方向に旋回させ、前記伝熱管
の温度を一様化する構造に関するものである。Detailed Description of the Invention The present invention relates to a heat exchanger tube support structure for a straight tube heat exchanger, and the heat exchanger tube support structure is formed into a spiral shape having a certain angle with respect to the axial direction of the heat exchanger tube. This invention relates to a structure in which the fluid flowing outside the heat exchanger tube is swirled in the circumferential direction within the heat exchanger to uniformize the temperature of the heat exchanger tube.

従来の熱交換器を第１図に従って説明する。外胴１は、
１次流体入ロノズル２と１次流体出口ノズル６とを有す
る。２次側上部鏡板３は、上管板４と一体化され、内部
に２次側上部ブレナム５を形成シ、上方に２次流体出口
ノズル７を有する。A conventional heat exchanger will be explained with reference to FIG. The outer body 1 is
It has a primary fluid inlet nozzle 2 and a primary fluid outlet nozzle 6. The secondary upper end plate 3 is integrated with the upper tube plate 4, forms a secondary upper blemish 5 inside, and has a secondary fluid outlet nozzle 7 above.

伝熱管９は、上端を上管板４、下端を下管板８に接続さ
れ、それぞれの管板近傍に熱遮蔽板１１を内包している
６ また、伝熱管９の外側を囲んで上部に入口窓１２、及び
下部に出口窓１３を有する外部シュラクトｌＯが設置さ
れている。２次流体入口管１５は、２次側上部鏡板３、
上管板４及び下管板８を貫通して２次側下部プレナム１
４に下端開口部を有する。The heat exchanger tube 9 has an upper end connected to the upper tube plate 4 and a lower end connected to the lower tube plate 8, and includes a heat shield plate 11 near each tube plate 6. Also, a heat shield plate 11 is included in the upper part surrounding the outside of the heat exchanger tube 9. An external shracto 10 is installed which has an entrance window 12 and an exit window 13 at the bottom. The secondary fluid inlet pipe 15 is connected to the secondary side upper end plate 3,
The secondary lower plenum 1 passes through the upper tube plate 4 and the lower tube plate 8.
4 has a lower end opening.

１次側高温流体は、１次流体入ロノズル２よシ外胴１内
に導入され、外部シュラウド１０に設けられている入口
窓１？から外部シュラクト１０内に流入し、伝熱管９内
を上昇する２次流体き熱交換しながら下降し、外部シュ
ラウド１０の下部に設けられた出口窓１３を通り、１次
流抹出ロノズル６よシ機器外へ流出する。The primary high temperature fluid is introduced into the outer shell 1 through the primary fluid inlet nozzle 2, and is introduced into the outer shell 1 through the inlet window 1 provided in the outer shroud 10. The secondary fluid flows into the outer shroud 10, rises in the heat transfer tube 9, descends while exchanging heat, passes through the outlet window 13 provided at the lower part of the outer shroud 10, and enters the primary flow discharge nozzle 6. leaks out of the equipment.

一方、２次側低温流体祉、２次流体入口管１５より機器
内に流入し、２次側下部プレナム１４に至り反転して下
管板８に設けられている伝熱管内に流れ込み、１次流体
と熱交換しながら上昇し、２次側上部プレナム５に至り
、２次流体出口ノズル７より機器外へ流出する。On the other hand, the secondary side cold fluid flows into the equipment from the secondary fluid inlet pipe 15, reaches the secondary side lower plenum 14, turns around, flows into the heat transfer tube provided on the lower tube plate 8, and flows into the primary It rises while exchanging heat with the fluid, reaches the secondary side upper plenum 5, and flows out of the device from the secondary fluid outlet nozzle 7.

また従来の伝熱管支持金具構造を第２図および第３図に
示す。伝熱管群９は前記伝熱管群９を周方向に等分割す
る仕切板２２に固定されたリング状スペーサ２０にさら
に固定された伝熱管支持金具２１で同心円配置で固定さ
れる。Further, the conventional heat exchanger tube support metal structure is shown in FIGS. 2 and 3. The heat exchanger tube group 9 is fixed in a concentric arrangement by a heat exchanger tube support fitting 21 further fixed to a ring-shaped spacer 20 fixed to a partition plate 22 that equally divides the heat exchanger tube group 9 in the circumferential direction.

このような伝熱管群９の配置においては、隣シ合う４本
の伝熱管例えば３１，３２，３３．３４あるいは、３３
，３４，３５．３６の中央に構成される空間（以後これ
をサブチャンネをと言う。）に沿って流れようとする。In such an arrangement of the heat exchanger tube group 9, four adjacent heat exchanger tubes, for example, 31, 32, 33.34 or 33.
, 34, 35, and 36 (hereinafter referred to as a subchannel).

これは、伝熱管群９が直管であるため伝熱管群９の外側
を流れる１次側流体は周方向あるいは半径方向に流れよ
うとする速度成分を持ち得ないからである。これらのサ
ブチャンネルを流れる１次側流体の流量は、入口窓１２
から管束部に流入した直後の流量配分によってほぼ決定
され、以後その流量を維持しｆｃまま各々のサブチャン
ネルを流下しようとする。このような流動状況において
は、各サブチャンネルを流れる１次側流体温度は下記の
（１）式によシ表わされる。This is because the heat exchanger tube group 9 is a straight tube, so the primary fluid flowing outside the heat exchanger tube group 9 cannot have a velocity component that tends to flow in the circumferential direction or the radial direction. The flow rate of the primary fluid flowing through these subchannels is controlled by the inlet window 12.
The distribution of the flow rate is determined almost immediately after the flow rate flows into the tube bundle, and from then on, the flow rate is maintained and the flow rate continues to flow down each subchannel at fc. In such a flow situation, the temperature of the primary fluid flowing through each subchannel is expressed by the following equation (1).

”　Ｇｔ　Ｃｐ　ｔΔＴｔ ここに、 ＧＨｓ　ＧＢ　＋　Ｇｓ３　、　ＧＢ４　：伝熱管３１
，３２゜３３．３４を流れる２ 次側流体流量（Ｋｆ／ｎ　ｒ　） Ｇ１　：サブチャンネルを流れる１次側流体流量（Ｋｆ
／ｎｒ） Ｃｐｌ：１次側流体比熱（ｋｃａｔ／に４”Ｃ）Ｃｐｌ
：２次側流体比熱（ｋＣａｔ／ＫｇＣ＞ΔＴ１：１次側
流体温度降下（ｔＺ’）ΔＴ、＝２次側流体温度上昇（
Ｃ） ここで２次側流体流量は各伝熱管に等分配されると仮定
すれば、 Ｇｓｌ”　Ｇ１２　＝　Ｇｓａ　＝　Ｇｓ＜　＝Ｑｔ　
　　　　　　（２）となり、１次側流体、２次側流体の
比熱が等しければ（１）式は結局（３）式で表わされる
。” Gt Cp tΔTt Here, GHs GB + Gs3, GB4: Heat exchanger tube 31
, 32°33.34 Secondary fluid flow rate (Kf/n r ) G1 : Primary fluid flow rate flowing through the subchannel (Kf
/nr) Cpl: Primary fluid specific heat (kcat/4”C) Cpl
: Secondary fluid specific heat (kCat/KgC>ΔT1: Primary fluid temperature drop (tZ') ΔT, = Secondary fluid temperature rise (
C) Here, assuming that the secondary fluid flow rate is equally distributed to each heat transfer tube, Gsl'' G12 = Gsa = Gs< =Qt
(2), and if the specific heat of the primary fluid and the secondary fluid are equal, then equation (1) can be expressed as equation (3).

ΔＴ＋”　（Ｇｔ／Ｇｔ）Δ’ｒｔ　　　　　　　　　
（ａ）すなわチ（３）式よ〕、各サブチャンネルを流れ
る１次側流体の流量がそれぞれのサブチャンネル毎に異
なれば、それが直接１次側流体の温度降下量のちがいと
なる。今、伝熱管温度はその外側を流れる１次側流体温
度と内側を流れる２次側流体温度で決まるので１次側流
体温度が各サブチャンネル毎に異なれば伝熱管温度はそ
れぞれ異なってくる。ΔT+” (Gt/Gt)Δ'rt
(a), that is, Equation (3)], if the flow rate of the primary fluid flowing through each subchannel is different for each subchannel, this directly results in a difference in the amount of temperature drop of the primary fluid. Now, the heat exchanger tube temperature is determined by the temperature of the primary fluid flowing outside and the secondary fluid flowing inside, so if the primary fluid temperature differs for each subchannel, the heat exchanger tube temperatures will differ.

しかるに、伝熱管群９はその両端を上管板４および下管
板８で固定されているので、伝熱管群９を構成する伝熱
管の温度が異なれば、伝熱管群９の平均温度に対し、相
対的に温度が高い伝熱管はその温度に相当する分だけ熱
膨張によシ伸びようとし、相対的に温度が低い伝熱管は
その温度に相当する分だけ熱収縮によシ縮もうとする。However, since both ends of the heat exchanger tube group 9 are fixed by the upper tube plate 4 and the lower tube plate 8, if the temperature of the heat exchanger tubes composing the heat exchanger tube group 9 differs, the average temperature of the heat exchanger tube group 9 will differ. A heat exchanger tube whose temperature is relatively high will try to expand by thermal expansion by an amount corresponding to that temperature, and a heat exchanger tube whose temperature is relatively low will try to contract by an amount corresponding to that temperature by thermal contraction. do.

ここで伝熱管群９の平均温度よシ高い温度の伝熱管が伸
びようとしても、伝熱管群９＃−１その両端を下管板４
および下管板８で固定されているため、伝熱管は伸びる
ことが出来ず、伝熱管の軸に直角な方向に変形し、この
伝熱管に曲げ応力が働き、かつ伝熱管支持金具２１に伝
熱管の曲げ応力に相当する反力が加わシ、伝熱管および
伝熱管支持金具２１の強度上の信頼性を低下させる原因
となる。Even if the heat exchanger tubes with a temperature higher than the average temperature of the heat exchanger tube group 9 try to extend, both ends of the heat exchanger tube group 9#-1 are connected to the lower tube plate 4.
Since the heat exchanger tubes are fixed by the upper and lower tube plates 8, the heat exchanger tubes cannot stretch and are deformed in a direction perpendicular to the axis of the heat exchanger tubes. A reaction force corresponding to the bending stress of the heat tube is applied, which causes a decrease in reliability in terms of strength of the heat exchanger tube and the heat exchanger tube support fitting 21.

そこで本発明においては、リング状スペーサを伝熱管の
軸直角方向にある角度だけ傾けたらせん状スペーサとし
、伝熱管を同心円のらせん状スペーサに固定した伝熱管
支持金具で支持する方法を用いる。リング状スペーサを
らせん状スペーサとすることによＬ１次側流体に旋回流
を生ぜしめ、各サブチャンネル間で混合させることによ
シ、１次側流体温度をサブチャンネル間で均一化し、ひ
いては伝熱管平均温度を均一化させるものでｂる。Therefore, in the present invention, a method is used in which the ring-shaped spacer is a spiral spacer tilted by a certain angle in the direction perpendicular to the axis of the heat exchanger tube, and the heat exchanger tube is supported by a heat exchanger tube support fitting fixed to the concentric spiral spacer. By changing the ring spacer to a spiral spacer, a swirling flow is generated in the L primary fluid, and by mixing between each subchannel, the temperature of the primary fluid is made uniform between the subchannels, and the transmission is improved. It makes the average temperature of the heat tube uniform.

本発明の一実施例を第４図および第５図に示す。An embodiment of the invention is shown in FIGS. 4 and 5.

スペーサとして各層毎に互いに逆方向に傾けたらせん状
スペーサ４Ｇ、４１．４２．４３を用いることによシ、
各々のサブチャンネルを流下して東Ｎ１次側流体はらせ
ん状スペーサ４０，４１゜４２．４３の上部に当たり、
らせん状スペーサ４０，４１，４２．４３の傾いた方向
に流れようとし、結局旋回流を生ずることになる。これ
によって１次側流体はサブチャンネルを順次周方向に移
りつつ伝熱管外を流下するため、従来の熱交換器で見ら
れたようなサブチャンネル毎の１次側流体の流量配分で
伝熱管温度が決定されることなく周方向に均一化され、
伝熱管相互の温度差に起因する熱膨張により伝熱管９８
るいは伝熱管支持金具４０に発生する応力を低減出来る
。By using spiral spacers 4G, 41, 42, 43 tilted in opposite directions for each layer as spacers,
The east N primary side fluid flowing down each subchannel hits the upper part of the spiral spacer 40, 41゜42.43,
It tends to flow in the direction in which the spiral spacers 40, 41, 42, and 43 are inclined, resulting in a swirling flow. As a result, the primary fluid flows down the outside of the heat exchanger tube while sequentially moving through the subchannels in the circumferential direction, so the heat exchanger tube temperature can be adjusted by distributing the flow rate of the primary fluid for each subchannel as seen in conventional heat exchangers. is uniform in the circumferential direction without being determined,
Heat exchanger tubes 98 due to thermal expansion due to temperature difference between the heat exchanger tubes
In addition, the stress generated in the heat exchanger tube support fitting 40 can be reduced.

【図面の簡単な説明】[Brief explanation of the drawing]

第１図は従来の熱交換器の構造概略図、第２図および第
３図は従来の伝熱管支持構造平面図および正面図、第４
図および第５図は本発明による伝熱管支持構造平面図お
よび正面図である。 ２０・・・リング状スづ−サ、２１・・・伝熱管支持金
具、２２・・・仕切板、３０〜３５・・・伝熱管、４０
・・・伝熱あ１０ ８ｚ口 第３図 第４図 ＃愕図Figure 1 is a structural schematic diagram of a conventional heat exchanger, Figures 2 and 3 are a plan view and front view of a conventional heat exchanger tube support structure, and Figure 4 is a schematic diagram of the structure of a conventional heat exchanger.
FIG. 5 is a plan view and a front view of a heat exchanger tube support structure according to the present invention. 20... Ring-shaped spring, 21... Heat exchanger tube support fitting, 22... Partition plate, 30-35... Heat exchanger tube, 40
...Heat transfer A10 8z mouth Figure 3 Figure 4 #Amazing diagram

Claims (1)

【特許請求の範囲】[Claims] １、管板に複数の直管の伝熱管が同心円配置に装着され
、伝熱管間隙には同心円配置にリング状スペーサが設け
られ、各伝熱管が前記スペーサに固着された弾性を有す
る支持金具によシ、各伝熱管単独に弾性支持されてなる
伝熱管支持構造において、前記スペーサを軸方向に対し
ある角度を設けたらせん状に取付けることを特徴きする
熱交換器の伝熱管支持構造。1. A plurality of straight heat exchanger tubes are installed in a concentric arrangement on a tube plate, a ring-shaped spacer is provided in a concentric arrangement in the gap between the heat exchanger tubes, and each heat exchanger tube is attached to an elastic support fitting fixed to the spacer. A heat exchanger tube support structure for a heat exchanger in which each heat exchanger tube is elastically supported independently, wherein the spacer is attached in a spiral shape at a certain angle with respect to the axial direction.