JP2020020514A

JP2020020514A - Multiple coil type heat exchanger

Info

Publication number: JP2020020514A
Application number: JP2018143958A
Authority: JP
Inventors: 中島　竜一; Ryuichi Nakajima; 竜一中島; 宗一仲川; Soichi Nakagawa
Original assignee: NISSHIN CORP KK
Current assignee: NISSHIN CORP KK
Priority date: 2018-07-31
Filing date: 2018-07-31
Publication date: 2020-02-06
Anticipated expiration: 2038-07-31
Also published as: JP6409147B1

Abstract

To provide a multiple coil type heat exchanger capable of being easily assembled and manufactured, reducing occurrence of bending and breakage of heat transfer tubes, and securing high volume efficiency.SOLUTION: An overflow discharge cylinder 15 and an intermediate cylinder 4 are disposed in a heat exchange tank 1, a heat exchange portion 5 in which a number of heat transfer tubes 2 are wound like a multiple coil is formed in an annular space 10b at an outer side of the intermediate cylinder 4, and a liquid circulation portion 10c is disposed at a lower end side of the intermediate cylinder 4. The overflow discharge cylinder 15 is communicated with a second fluid lead-out port 14 at a lower end side, and an inlet header 3A and an outlet header 3B for a first fluid L1 and a second fluid introduction port 13 are disposed in a manner of facing an upper portion of the annular space 10b. An introduced second fluid L2 exchanges heat with the first fluid L1 distributed and raised in each heat transfer tube 2 from the inlet header 3A in a process of falling in the annular space 10b at the outer side, then flows into an internal space 10a from the liquid circulation portion 10c, flows down into the overflow discharge cylinder 15 from an overflow port 15a, and is directed to the second fluid lead-out port 14.SELECTED DRAWING: Figure 1

Description

本発明は、熱交換槽内にコイル状に巻回された多数本の伝熱チューブが内外多重に配置した多重コイル型熱交換器に関する。 The present invention relates to a multi-coil heat exchanger in which a number of heat transfer tubes wound in a coil shape in a heat exchange tank are multiplexed inside and outside.

熱交換器として、熱交換する流体の種類と組合わせ、用途、処理量、要求される熱交換効率、処理ラインや装置部への組付け形態等に応じ、極めて多種多様な形式及び構造のものが存在する。これらの内、コイル型熱交換器は、第１流体を通す伝熱管がコイル状に巻回されたものであり、被処理流体を流通又は収容する容器内に組み込んだ形でシェル＆コイル式熱交換器と称される。特に、複数本の伝熱管を内外多重のコイル状に巻回した多重コイル型熱交換器は、高い熱交換効率が得られ、大きな熱交換処理量に対応して大型化し易いという利点がある。 Heat exchangers of a wide variety of types and structures, depending on the type and combination of the fluids to be heat-exchanged, the application, the amount of processing, the required heat exchange efficiency, the type of assembly to the processing line and equipment, etc. Exists. Among these, the coil heat exchanger is a shell and coil type heat exchanger in which a heat transfer tube through which a first fluid passes is wound in a coil shape, and is incorporated in a container that circulates or accommodates the fluid to be treated. Called exchanger. In particular, a multi-coil heat exchanger in which a plurality of heat transfer tubes are wound in a multi-layered inner / outer coil form has the advantage that a high heat exchange efficiency can be obtained and the size can be easily increased in response to a large heat exchange throughput.

本出願人は先に、液体を処理対象とする多重コイル型熱交換器として、熱交換効率が高く、第２流体量が多くなっても連続的処理を行うことができ、また第２流体の導入量が変動しても各別なコントロールを行う必要がなく、設備コスト及び稼働コストを著しく低減できるものを提案している（特許文献１）。 The present applicant has previously described a multi-coil type heat exchanger for processing liquid, which has high heat exchange efficiency and can perform continuous processing even when the amount of the second fluid is large. Even if the introduction amount fluctuates, it is not necessary to perform individual control, and a device capable of significantly reducing equipment costs and operating costs has been proposed (Patent Document 1).

上記提案に係る多重コイル型熱交換器は、密閉型の熱交換槽内に、下端側が第２流体出口に連通した溢流排出筒と、これを同心状に取囲む中間筒とを備え、中間筒の外側の環状空間内に複数本の伝熱チューブを内外多重のコイル状に巻回した主熱交換部が形成され、該中間筒の下端側に内側空間と外側の環状空間とを連通する液流通部を有している。また、各伝熱チューブは、主熱交換部の上部から中間筒内の上部に臨む出口ヘッダーに接続すると共に、該主熱交換部の下部から前記液流通部を経て環状空間の上部に臨む入口ヘッダーに接続し、該中間筒の内側で副熱交換部を形成している。そして、第１流体を入口ヘッダーに連続供給する一方、環状空間の上部に臨む第２流体入口から第２流体を導入することにより、該第２流体が環状空間を下降して前記液流通部より中間筒内に入って上昇する過程で、主熱交換部及び副熱交換部の伝熱チューブ内を流れる第１流体と熱交換し、溢流排出筒に流入して第２流体出口より導出するようになっている。 The multi-coil heat exchanger according to the above proposal includes, in a closed heat exchange tank, an overflow discharge cylinder whose lower end communicates with the second fluid outlet, and an intermediate cylinder concentrically surrounding the overflow discharge cylinder. A main heat exchange portion formed by winding a plurality of heat transfer tubes in an inner and outer multiplex coil shape is formed in the outer annular space of the tube, and communicates the inner space and the outer annular space to the lower end side of the intermediate tube. It has a liquid circulation part. Further, each heat transfer tube is connected to an outlet header facing the upper part of the intermediate tube from the upper part of the main heat exchange part, and the inlet part facing the upper part of the annular space from the lower part of the main heat exchange part via the liquid flowing part. It is connected to a header and forms a sub heat exchange section inside the intermediate tube. Then, while the first fluid is continuously supplied to the inlet header, the second fluid is introduced from the second fluid inlet facing the upper part of the annular space, so that the second fluid descends through the annular space and flows from the liquid flow portion. In the process of ascending into the intermediate cylinder and ascending, it exchanges heat with the first fluid flowing through the heat transfer tubes of the main heat exchange section and the sub heat exchange section, flows into the overflow discharge cylinder, and is derived from the second fluid outlet. It has become.

また、この多重コイル型熱交換器では、大きな熱交換処理量に対応して大型化する場合、十数本から数十本といった多数本の伝熱チューブを用いるが、これら伝熱チューブ群を主熱交換部において内外多重のコイル状に保持させる上で、中間筒の周囲に複数枚の支持板を放射状に配置させ、これら支持板に設けた多数のチューブ挿通孔に各伝熱チューブを順次通してコイル状に巻き込んでいる。なお、伝熱チューブには通常、ＰＦＡ（パーフルオロアルコキシエチレン）やＰＴＦＥ（ポリテトラフルオロエチレン）の如き熱可塑性フッ素樹脂製のものが使用される。 In addition, in the multi-coil heat exchanger, when the heat exchanger is increased in size to cope with a large heat exchange processing amount, a large number of heat transfer tubes, such as ten to several tens, are used. A plurality of support plates are radially arranged around the intermediate cylinder in order to hold the heat transfer unit in a multiplexed coil shape inside and outside, and each heat transfer tube is sequentially passed through a number of tube insertion holes provided in these support plates. Rolled into a coil. The heat transfer tube is usually made of a thermoplastic fluororesin such as PFA (perfluoroalkoxyethylene) or PTFE (polytetrafluoroethylene).

特許第５８８３１６８号公報Japanese Patent No. 5883168

しかしながら、前記提案に係る多重コイル型熱交換器は、優れた熱交換性能を発揮し得るものであるが、その大型化及び量産化を進める段階で、組立製作面や容積効率面等で多分に改良の余地があることが判明した。すなわち、この多重コイル型熱交換器の組立製作では、主熱交換部及び副熱交換部の形成に際し、中間筒の周囲に放射状に配置した支持板に対し、最内側のコイル部を構成する伝熱チューブから順次、各支持板のチューブ挿通孔に挿通しながらコイル状に巻き込んでゆき、巻込み完了後のチューブ両端を入口ヘッダーと出口ヘッダーに連通接続する。しかるに、入口ヘッダー側への接続は中間筒の外側から下端の液流通部を潜らせた上で、該中間筒内を略垂直に引き上げて入口ヘッダーに繋ぐ形になるため、主熱交換部での水平に近い周回姿勢から中間筒内の略垂直姿勢への方向転換部分でチューブの折れやへしゃげが発生し易く、第１流体の流路の閉塞や狭まりによって熱交換性能が低下することになり、またチューブに生じた折れやへしゃげは修正が困難であるから、その解消のためには発生部位まで巻き込んだチューブを外して巻き直すという、非常に手間及び時間を要する作業が必要となる。一方、中間筒内の副熱交換部では、外側の主熱交換部に比してチューブ長が短いために得られる熱交換作用は僅かであるにも関わらず、第２流体の流路面積を確保しつつ多数本の伝熱チューブを配設する上で中間筒の内径を大きくすることになり、それだけ熱交換槽が大型化して熱交換器としての容積効率の低下を招く。 However, the multi-coil type heat exchanger according to the above proposal can exhibit excellent heat exchange performance, but in the stage of increasing its size and mass production, it is likely that it will be difficult to assemble and manufacture and volume efficiency. It turned out that there was room for improvement. That is, in assembling and manufacturing this multi-coil type heat exchanger, when forming the main heat exchange part and the sub heat exchange part, the transfer forming the innermost coil part with respect to the support plate radially arranged around the intermediate cylinder is performed. The coil is wound in a coil shape while being inserted into the tube insertion hole of each support plate sequentially from the heat tube, and both ends of the tube after completion of the winding are connected to the inlet header and the outlet header. However, since the connection to the inlet header side is made to dive from the outside of the intermediate cylinder to the lower end of the liquid flow section, and then pulled up almost vertically inside the intermediate cylinder and connected to the inlet header, the main heat exchange section The tube is likely to be bent or shaved at the part of the intermediate cylinder that changes direction from a nearly horizontal orbiting position to a substantially vertical position, and the heat exchange performance is degraded due to blockage or narrowing of the first fluid flow path. In addition, it is difficult to correct the folds and whiskers that occur on the tube, so removing the tube that has been rolled up to the site of occurrence and rewinding it is necessary to resolve the problem, which requires a lot of trouble and time. Becomes On the other hand, in the sub heat exchange portion in the intermediate cylinder, the heat exchange effect obtained because the tube length is shorter than the outer main heat exchange portion is small, but the flow area of the second fluid is reduced. In arranging a large number of heat transfer tubes while securing, the inner diameter of the intermediate tube is increased, and accordingly, the heat exchange tank is enlarged and the volume efficiency of the heat exchanger is reduced.

本発明は、上述の事情に鑑みて、熱交換槽内にコイル状に巻回された多数本の伝熱チューブが内外多重に配置した多重コイル型熱交換器として、組立製作が容易であって、伝熱チューブの折れやへしゃげを生じにくい上、高い容積効率を確保できるものを提供することを目的としている。 In view of the above circumstances, the present invention is easy to assemble and manufacture as a multi-coil type heat exchanger in which a number of heat transfer tubes wound in a coil shape in a heat exchange tank are arranged in an inner and outer multiplex. It is another object of the present invention to provide a heat transfer tube that is less likely to be bent or shaved and that can ensure high volumetric efficiency.

上記目的を達成するための手段を図面の参照符号を付して示せば、請求項１の発明に係る多重コイル型熱交換器は、熱交換槽１内に、上下方向に沿う溢流排出筒１５と、該溢流排出筒１５を同心状に取囲む中間筒４とを備えると共に、この中間筒４の外側の環状空間１０ｂ内に、フッ素系樹脂からなる多数本の伝熱チューブ２が該中間筒４周りに多重コイル状に巻回して熱交換部５を形成し、中間筒４の外周に複数枚の支持板６が放射状に配置して取り付けられ、該中間筒４の下端側に内側空間１０ａと外側の環状空間１０ｂとを連通する液流通部１０ｃを有し、溢流排出筒１５は、上端側に溢流口１５ａを備えて、下端側が第２流体導出口１４に連通し、環状空間１０ｂの上部に臨んで第１流体Ｌ１の入口ヘッダー３Ａ及び出口ヘッダー３Ｂと第２流体導入口１３が設けられ、熱交換部５における各伝熱チューブ２は、支持板６に設けた多数のチューブ挿通孔６０を通してコイル状に巻回保持されて上下方向に沿うコイル状をなし、その下端部（端部２ａ）が入口ヘッダー３Ａに、上端部が出口ヘッダー３Ｂに、各々環状空間１０ｂを通して連通接続され、第２流体導入口１３より熱交換槽１内に導入された第２流体Ｌ２が外側の環状空間１０ｂを降下する過程で、入口ヘッダー３Ａより各伝熱チューブ２に分配して上昇する第１流体Ｌ１と熱交換したのち、液流通部１０ｃから内側空間１０ａへ流入し、溢流口１５ａより溢流排出筒１５内に流下して第２流体導出口１４に向かうように構成されてなる。 Means for achieving the above object are indicated by reference numerals in the drawings, and a multi-coil type heat exchanger according to the invention of claim 1 is provided in a heat exchange tank 1 with an overflow discharge tube extending vertically. 15 and an intermediate tube 4 concentrically surrounding the overflow discharge tube 15, and in the annular space 10 b outside the intermediate tube 4, a number of heat transfer tubes 2 made of a fluororesin are provided. The heat exchange portion 5 is formed by winding around the intermediate cylinder 4 in a multi-coil shape, and a plurality of support plates 6 are radially arranged and mounted on the outer periphery of the intermediate cylinder 4. The overflow discharge cylinder 15 has an overflow port 15a on the upper end side, and the lower end side communicates with the second fluid outlet 14, and has a liquid circulation portion 10c that communicates the space 10a with the outer annular space 10b. The inlet header 3A and the outlet header 3 of the first fluid L1 facing the upper part of the annular space 10b. And the second fluid inlet 13 are provided, and each heat transfer tube 2 in the heat exchange section 5 is wound and held in a coil shape through a number of tube insertion holes 60 provided in the support plate 6, and is formed in a coil shape along the vertical direction. The lower end (end 2a) is connected to the inlet header 3A and the upper end is connected to the outlet header 3B through the annular space 10b, respectively, and introduced into the heat exchange tank 1 from the second fluid inlet 13. In the process in which the second fluid L2 descends in the outer annular space 10b, the heat is exchanged with the first fluid L1 which is distributed from the inlet header 3A to each heat transfer tube 2 and rises, and then from the liquid flowing portion 10c to the inner space 10a. It is configured to flow in, flow down from the overflow port 15 a into the overflow discharge tube 15, and head toward the second fluid outlet 14.

請求項２の発明は、上記請求項１の多重コイル型熱交換器において、熱交換部５の多重コイル間に上下方向に沿うチューブ配設用間隙ｄを有し、このチューブ配設用間隙ｄを通して入口ヘッダー３Ａから垂下する各伝熱チューブ２の端部２ａが該熱交換部５の下部へ引き込まれてなるものとしている。 According to a second aspect of the present invention, in the multi-coil heat exchanger of the first aspect, a gap d for arranging tubes extending vertically between the multiple coils of the heat exchange section 5 is provided. The end portion 2a of each heat transfer tube 2 hanging from the inlet header 3A is drawn into the lower portion of the heat exchange section 5.

請求項３の発明は、上記請求項２の多重コイル型熱交換器において、熱交換部５における多重コイルの隣接するチューブ間隔が、チューブ配設用間隙ｄを除いて、チューブ外径以下で略等しく設定されてなるものとしている。 According to a third aspect of the present invention, in the multi-coil type heat exchanger according to the second aspect, the interval between adjacent tubes of the multiple coils in the heat exchange section 5 is substantially equal to or less than the outer diameter of the tube, except for the tube arrangement gap d. It is assumed that they are set equal.

次に、本発明の効果について、図面の参照符号を付して説明する。まず、請求項１の発明に係る多重コイル型熱交換器によれば、第２流体導入口１３より熱交換槽１内に導入された第２流体Ｌ２は、外側の環状空間１０ｂを降下する過程で、熱交換部５において内外多重のコイル部Ｃ１〜Ｃ１４を構成する多数本の伝熱チューブ２間を極めて大きな接触面積で通過することにより、これら伝熱チューブ２内を螺旋状に上昇しつつ流れる第１流体Ｌ１と能率よく熱交換したのち、液流通部１０ｃから内側空間１０ａへ流入し、溢流口１５ａより溢流排出筒１５内に流下して第２流体導出口１４より排出されるから、第２流体量の多い連続的処理でも非常に高い熱交換効率が得られる。 Next, the effects of the present invention will be described with reference numerals in the drawings. First, according to the multi-coil heat exchanger according to the first aspect of the present invention, the process in which the second fluid L2 introduced into the heat exchange tank 1 from the second fluid inlet 13 descends in the outer annular space 10b. In the heat exchange section 5, the heat transfer tube 2 passes through a large number of heat transfer tubes 2 constituting the inner and outer multiple coil portions C1 to C14 with an extremely large contact area. After efficiently exchanging heat with the flowing first fluid L1, it flows into the inner space 10a from the liquid circulation part 10c, flows down into the overflow discharge tube 15 from the overflow port 15a, and is discharged from the second fluid outlet port 14. Therefore, a very high heat exchange efficiency can be obtained even in a continuous process with a large amount of the second fluid.

そして、この多重コイル型熱交換器の熱交換部５では、各コイル部Ｃ１〜Ｃ１４を構成する伝熱チューブ２は、中間筒４の外側の環状空間１０ｂを通して上部の入口ヘッダー３Ａ及び出口ヘッダー３Ｂに連通接続されている。これにより、特に入口ヘッダー３Ａから熱交換部５の下部への配設部分では、入口ヘッダー３Ａから垂下する各伝熱チューブ２の端部２ａは、隣接する支持板６，６間の開きを利用して、緩やかにしの字状にカーブを描く形で水平に近い向きとして容易に支持板６の各コイル部における最下位のチューブ挿通孔６０へ挿通できるから、チューブの折れやへしゃげが発生せず、第１流体の流路の閉塞や狭まりによる熱交換性能の低下が回避される。また、中間筒４の内側は、伝熱チューブ２群を配設することなく、熱交換部５での熱交換を経た第２流体Ｌ２が内側空間１０ａを上昇するだけの流路断面積を確保できればよい。従って、中間筒４の内径を小さくでき、それだけ熱交換槽１を径小化して熱交換器としての容積効率を高め得る。 And in the heat exchange part 5 of this multi-coil type heat exchanger, the heat transfer tubes 2 constituting each of the coil parts C1 to C14 pass through the annular space 10b outside the intermediate cylinder 4 and the upper inlet header 3A and the outlet header 3B. Is connected to the Thereby, especially in the portion provided from the inlet header 3A to the lower part of the heat exchange section 5, the end 2a of each heat transfer tube 2 hanging from the inlet header 3A utilizes the opening between the adjacent support plates 6,6. Then, it can be easily inserted into the lowermost tube insertion hole 60 in each coil portion of the support plate 6 in a direction close to horizontal in a shape of drawing a curve in a gentle V shape, so that the tube breaks and squashes occur. Without this, a decrease in heat exchange performance due to blockage or narrowing of the flow path of the first fluid is avoided. Further, the inside of the intermediate tube 4 secures a flow path cross-sectional area enough for the second fluid L2 that has undergone heat exchange in the heat exchange unit 5 to ascend the inner space 10a without disposing the heat transfer tube 2 group. If possible. Therefore, the inner diameter of the intermediate cylinder 4 can be reduced, and the diameter of the heat exchange tank 1 can be reduced accordingly, and the volumetric efficiency as a heat exchanger can be increased.

請求項２の発明によれば、熱交換部５の多重コイル間に上下方向に沿うチューブ配設用間隙ｄを有し、入口ヘッダー３Ａから垂下する多数本の伝熱チューブ２の端部２ａが環状になる該チューブ配設用間隙ｄを通して周方向に分配して熱交換部５の下部へ引き込まれる形になるから、その引き込み部分で各コイル部の巻き形を歪めずに均整な内外多重コイルの形態を確保できると共に、熱交換部５の組み立てる際の作業性も向上する。 According to the second aspect of the present invention, the multiple coils of the heat exchanging section 5 have a vertically arranged tube arrangement gap d between the multiple coils, and the end portions 2a of the multiple heat transfer tubes 2 hanging from the inlet header 3A are formed. Since it is circumferentially distributed and drawn into the lower part of the heat exchange unit 5 through the tube disposing gap d which is annular, the winding shape of each coil unit is not distorted at the drawn-in portion, and the uniform inner and outer multiple coils are formed. And the workability when assembling the heat exchange unit 5 is also improved.

請求項３の発明によれば、熱交換部５における多重コイルＣ１〜Ｃ１４の隣接するチューブ間隔が、チューブ配設用間隙ｄを除いて、チューブ外径以下で略等しく設定されるから、熱交換部５のチューブ配置密度が均等化すると共に、各伝熱チューブ２に対する第２流体Ｌ２の接触度合が充分に高まるから、該熱交換部５全体により均一で高い熱交換が行われるという利点がある。 According to the third aspect of the present invention, the interval between adjacent tubes of the multiple coils C1 to C14 in the heat exchange section 5 is set substantially equal to or less than the outer diameter of the tube except for the tube arrangement gap d. Since the tube arrangement density of the section 5 is equalized and the degree of contact of the second fluid L2 with each heat transfer tube 2 is sufficiently increased, there is an advantage that uniform and high heat exchange is performed in the entire heat exchange section 5. .

本発明の実施形態に係る多重コイル型熱交換器の縦断側面図である。It is a vertical section side view of a multiple coil type heat exchanger concerning an embodiment of the present invention. 同熱交換器の平面図である。It is a top view of the same heat exchanger. 同熱交換器の横断面図である。It is a cross-sectional view of the same heat exchanger. 同熱交換器の伝熱チューブの配設状態を例示する要部の正面図である。It is a front view of the principal part which illustrates the arrangement state of the heat transfer tube of the same heat exchanger. 同熱交換器における第１流体と第２流体の全体的な流れを示す模式縦断側面図である。FIG. 4 is a schematic vertical sectional side view showing the overall flow of a first fluid and a second fluid in the heat exchanger. 同熱交換部の異なる構成例を示す模式縦断側面図である。It is a schematic vertical side view which shows the example of a different structure of the same heat exchange part.

以下に、本発明に係る多重コイル型熱交換器の実施形態について、図面を参照して具体的に説明する。 Hereinafter, embodiments of a multi-coil heat exchanger according to the present invention will be specifically described with reference to the drawings.

この多重コイル型熱交換器は、図１及び図２に示すように、上方に開放した大径円筒状の槽本体１１と蓋板１２とからなる熱交換槽１内に、中心部に位置して溢流排出筒１５が垂直に立設されると共に、槽内空間１０を中央空間１０ａと外側の環状空間１０ｂとに区画する中間筒４が該溢流排出筒１５を同心状に取囲むように配置しており、その外側の環状空間１０ｂに、ＰＦＡ（パーフルオロアルコキシエチレン）やＰＴＦＥ（ポリテトラフルオロエチレン）の如き熱可塑性フッ素樹脂からなる多数本の伝熱チューブ２を内外多重のコイル状に巻回した熱交換部５が形成されている。なお、溢流排出筒１５の上端は中間筒４の上端よりも低い位置に設定され、熱交換部５の上部側は溢流排出筒１５の上端よりも低位にある。 As shown in FIGS. 1 and 2, this multi-coil type heat exchanger is located at the center in a heat exchange tank 1 composed of a large-diameter cylindrical tank body 11 and a cover plate 12 opened upward. The overflow discharge tube 15 is vertically erected, and the intermediate tube 4 that partitions the in-tank space 10 into a central space 10a and an outer annular space 10b surrounds the overflow discharge tube 15 concentrically. And a plurality of heat transfer tubes 2 made of a thermoplastic fluororesin such as PFA (perfluoroalkoxyethylene) or PTFE (polytetrafluoroethylene) in an outer annular space 10b. The heat exchange part 5 wound around is formed. Note that the upper end of the overflow discharge tube 15 is set at a position lower than the upper end of the intermediate tube 4, and the upper side of the heat exchange unit 5 is lower than the upper end of the overflow discharge tube 15.

蓋板１２の径方向両側位置には、各々シールプレート３３を介してポルト止めしたカップ状の上プレート３１と下プレート３２との間で、槽内空間１０に対して隔絶した第１流体Ｌ１用の入口ヘッダー３Ａ及び出口ヘッダー３Ｂが設けられている。そして、両ヘッダー３Ａ，３Ｂには熱交換部５の各伝熱チューブ２の両端が各々連通接続している。また、蓋板１２には第２流体Ｌ２用の複数（図では３つ）の導入口１３が槽内空間１０の外側の環状空間１０ｂに臨んで設けられる一方、槽体１１の底壁部１１ａには溢流排出筒１３内に連通する第２流体Ｌ２用の導出口１４が設けられている。図１中の符号１６は熱交換槽１の側方外部に取り付けられた液面計であって、ＰＦＡの如き透明性フッ素系樹脂の垂直パイプからなり、その上下端が配管１６ａ，１６ｂを介して槽内空間１０の天井側と底部側に連通している。 The first fluid L1 for the first fluid L1 isolated from the inner space 10 between the cup-shaped upper plate 31 and the lower plate 32, each of which is ported via a seal plate 33, is provided at both radial positions of the lid plate 12. Are provided with an inlet header 3A and an outlet header 3B. Both ends of each heat transfer tube 2 of the heat exchange section 5 are connected to the headers 3A and 3B, respectively. A plurality of (three in the figure) inlets 13 for the second fluid L2 are provided in the cover plate 12 so as to face the annular space 10b outside the inner space 10 of the tank, while the bottom wall 11a of the tank body 11 is provided. Is provided with an outlet 14 for the second fluid L2 communicating with the overflow discharge tube 13. Reference numeral 16 in FIG. 1 denotes a liquid level gauge attached to the side outside of the heat exchange tank 1, which is composed of a vertical pipe made of a transparent fluororesin such as PFA, and whose upper and lower ends are connected via pipes 16a and 16b. It communicates with the ceiling side and the bottom side of the space 10 inside the tank.

熱交換部５は、中間筒４の外周に放射状に等配して取り付けた４枚の略縦長矩形の支持板６を利用して、これら支持板６に設けた多数のチューブ挿通孔６０に各伝熱チューブ２を下から上へ向けてコイル状に挿通することにより、内外のコイル重ね数を１４重に設定したものであり、最内側の第１コイル部Ｃ１から第９コイル部Ｃ９までの伝熱チューブ群５１と、第１０コイル部Ｃ１０から最外側の第１４コイル部Ｃ１４までの伝熱チューブ群５２とに分画されている。その内側の伝熱チューブ群５１は、各コイル部Ｃ１〜Ｃ９を各々１本の伝熱チューブ２にて形成している。一方、外側の伝熱チューブ群５２では、図１のチューブ断面で白黒に分けて図示するように、各コイル部Ｃ１０〜Ｃ１４を各々２本（白と黒）の伝熱チューブ２にて２条巻きに形成している。 The heat exchange unit 5 uses four substantially vertically long rectangular support plates 6 that are radially and evenly mounted on the outer periphery of the intermediate cylinder 4, and each of the heat exchange units 5 has a plurality of tube insertion holes 60 provided in the support plate 6. By inserting the heat transfer tube 2 in a coil shape from bottom to top, the number of inner and outer coil overlaps is set to 14 times, and the innermost first coil portion C1 to the ninth coil portion C9 The heat transfer tube group 51 is divided into a heat transfer tube group 52 and a heat transfer tube group 52 from the tenth coil portion C10 to the outermost fourteenth coil portion C14. The heat transfer tube group 51 on the inner side has each of the coil portions C1 to C9 formed by one heat transfer tube 2. On the other hand, in the outer heat transfer tube group 52, each of the coil portions C10 to C14 is divided into two (white and black) heat transfer tubes 2 as shown in FIG. It is formed into a roll.

そして、内側の伝熱チューブ群５１と外側の伝熱チューブ群５２との間、つまり第９コイル部Ｃ９と第１０コイル部Ｃ１０との間には、伝熱チューブ２の外径に略相当する幅のチューブ配設用間隙ｄが全体として環状に構成されており、図３に示すように、該チューブ配設用間隙ｄを通して入口ヘッダー３Ａから垂下する全部（図では１９本）の伝熱チューブ２が周方向に分配する形で熱交換媒部５の下部まで引き込まれている。なお、内側の伝熱チューブ群５１と外側の伝熱チューブ群５２においては、上下及び斜め左右に隣接する伝熱チューブ２同士の間隔がチューブ外径以下で略等しくなっている。 The outer diameter of the heat transfer tube 2 substantially corresponds between the inner heat transfer tube group 51 and the outer heat transfer tube group 52, that is, between the ninth coil portion C9 and the tenth coil portion C10. As shown in FIG. 3, all (19 in the figure) heat transfer tubes hanging from the inlet header 3 </ b> A through the tube disposing gap d are formed. 2 are drawn down to the lower part of the heat exchange medium portion 5 in a form of distribution in the circumferential direction. Note that, in the inner heat transfer tube group 51 and the outer heat transfer tube group 52, the intervals between the heat transfer tubes 2 adjacent vertically and diagonally right and left are substantially equal to each other below the tube outer diameter.

ここで、図４で示すように、入口ヘッダー３Ａから垂下する各伝熱チューブ２ａは、隣接する支持板６，６間の開き、つまり１／４周分の間隔を利用して、緩やかにしの字状にカーブを描く形で水平に近い向きとして、一つの支持板６の各コイル部における最下位のチューブ挿通孔６０へ挿通し、以降は４枚の支持板６のチューブ挿通孔６０を順次通して熱交換媒部５の上部までコイル状に巻き上げて、その上端側を出口ヘッダー３ｂに連通接続している。なお、この熱交換媒部５の組み立てにおける各伝熱チューブ２の巻回操作は、最内側の第１コイル部Ｃ１から開始される。 Here, as shown in FIG. 4, each heat transfer tube 2a hanging down from the inlet header 3A is loosened by using an opening between the adjacent support plates 6 and 6, that is, an interval of 1/4 rotation. It is inserted in the lowermost tube insertion hole 60 in each coil portion of one support plate 6 in a substantially horizontal direction so as to draw a curve in the shape of a letter, and thereafter the tube insertion holes 60 of the four support plates 6 are sequentially inserted. The upper end of the heat exchanger is wound up in a coil shape up to the upper portion of the heat exchange medium portion 5 and the upper end side thereof is connected to the outlet header 3b. The winding operation of each heat transfer tube 2 in assembling the heat exchange medium section 5 is started from the innermost first coil section C1.

熱交換部５における内側の伝熱チューブ群５１では、最内側の第１コイル部Ｃ１のコイル巻き数が３８であり、この第１コイル部Ｃ１から第６コイル部Ｃ６までは順次にコイル巻き数を２ずつ減じると共に、第６コイル部Ｃ６から第９コイル部Ｃ９までは順次にコイル巻き数を１ずつ減じることで、最外側の第９コイル部Ｃ９のコイル巻き数が２５になっている。一方、外側の伝熱チューブ群５２では、最内側の第１０コイル部Ｃ１０及び第１１コイル部Ｃ１１のコイル巻き数が４２（チューブ一本当りでは半分の２１巻き）、第１２コイル部Ｃ１２のコイル巻き数が４０（チューブ一本当り２０巻き）、第１３コイル部Ｃ１３及び最外側の第１４コイル部Ｃ１４のコイル巻き数が３８（チューブ一本当り１９巻き）になっている。すなわち、第１〜第１４コイル部Ｃ１〜Ｃ１４を形成する計１９本の伝熱チューブ２は、熱交換部５の内から外へコイル径が増大するのに対応してコイル巻き数を減じることにより、略等しい長さに設定されている。 In the inner heat transfer tube group 51 in the heat exchange section 5, the number of coil turns of the innermost first coil section C1 is 38, and the number of coil turns is sequentially from the first coil section C1 to the sixth coil section C6. And the number of coil turns of the outermost ninth coil part C9 is 25 by sequentially reducing the number of coil turns by one from the sixth coil part C6 to the ninth coil part C9. On the other hand, in the outer heat transfer tube group 52, the number of coil turns of the innermost tenth coil part C10 and the eleventh coil part C11 is 42 (21 turns, which is half per tube), and the number of coil turns of the twelfth coil part C12 is The number of turns is 40 (20 turns per tube), and the number of turns of the thirteenth coil part C13 and the outermost fourteenth coil part C14 is 38 (19 turns per tube). In other words, a total of 19 heat transfer tubes 2 forming the first to fourteenth coil portions C1 to C14 are required to reduce the number of coil turns in accordance with an increase in the coil diameter from inside to outside of the heat exchange portion 5. , The lengths are set to be substantially equal.

各支持板６は上端内側の係止突片６１を中間筒４の上部に設けたスリット状係止孔（図示省略）に挿嵌係止する一方、該中間筒４は下端周縁部を各支持板６の下部内側に設けた上向き切欠部６２に嵌合している。これにより、各支持板６と中間筒４とが一体化すると共に、図１に示すように、該中間筒４の下端が槽体１１の底壁部１１ａから離れて配置することで、槽内空間１０の中央空間１０ａと外側の環状空間１０ｂとを連通する液流通部１０ｃが構成されている。また、４枚の支持板６は、各々上部側が吊り具６３（図２参照）を介して蓋板１２に吊持されている。従って、中間筒４及び４枚の支持板６と熱交換部５の各伝熱チューブ２は、蓋板１２に一体化したユニットとして、熱交換槽１の槽本体１１に対して着脱可能になっている。 Each support plate 6 inserts and locks the locking projection 61 on the inner side of the upper end into a slit-shaped locking hole (not shown) provided at the upper part of the intermediate cylinder 4, while the intermediate cylinder 4 supports the lower peripheral edge of the intermediate cylinder 4. It is fitted in an upward cutout 62 provided inside the lower part of the plate 6. Thereby, each support plate 6 and the intermediate cylinder 4 are integrated, and the lower end of the intermediate cylinder 4 is separated from the bottom wall portion 11a of the tank body 11 as shown in FIG. A liquid circulation unit 10c is provided to communicate the central space 10a of the space 10 with the outer annular space 10b. The upper sides of the four support plates 6 are each suspended from the lid plate 12 via a suspender 63 (see FIG. 2). Accordingly, the heat transfer tubes 2 of the intermediate cylinder 4 and the four support plates 6 and the heat exchange section 5 are detachable from the tank body 11 of the heat exchange tank 1 as a unit integrated with the cover plate 12. ing.

なお、熱交換槽１の槽本体１１及び蓋板１２と入口及び出口ヘッダー３Ａ，３Ｂは、ＳＵＳ３０４の如きステンレス鋼製であり、槽本体１１及び蓋板１２の内側表面にはＰＴＦＥ樹脂のライニングが施されている。また、中間筒４、支持板６、溢流排出筒１５、吊り具６３はＰＦＡ又はＰＴＦＥ樹脂製である。 The tank body 11 and the cover plate 12 and the inlet and outlet headers 3A and 3B of the heat exchange tank 1 are made of stainless steel such as SUS304, and the inside surfaces of the tank body 11 and the cover plate 12 are lined with PTFE resin. It has been subjected. The intermediate tube 4, the support plate 6, the overflow discharge tube 15, and the hanging members 63 are made of PFA or PTFE resin.

上記構成の多重コイル型熱交換器において、第２流体Ｌ２として例えば高温の酸廃水等の被処理液を用い、第１流体Ｌ１である冷却水との熱交換によって低温化させる場合について説明する。図５に示すように、まず入口ヘッダー３Ａに連続的に導入される第１流体Ｌ１の冷却水は、該入口ヘッダー３Ａに連通する複数本（例示は１９本）の伝熱チューブ２に分配されて、各伝熱チューブ２内を熱交換部５の下端から螺旋状に上昇したのち、該熱交換部５の上端から出口ヘッダー３Ｂ内へ流入し、該出口ヘッダー３Ｂから合流状態で導出される。一方、第２流体Ｌ２の被処理液は、導入口１３から中間筒４の外側の環状空間１０ａへ連続的に導入され、該環状空間１０ｂを下降したのち、下部の液流通部１０ｃより中間筒４の内側に入って中央空間１０ａを上昇し、溢流排出筒１５の上端からオーバーフローして該溢流排出筒１５内へ流入して導出口１４より導出されるが、熱交換部５では多重コイル状に巻回した多数本の伝熱チューブ２間を通過することで、これら伝熱チューブ２内を流れる第１流体Ｌ１の冷却水と非常に効率よく熱交換して低温化されると共に、溢流口１５ａより溢流排出筒１５内に流下して第２流体導出口１４より排出されるから、第２流体ｌ２の被処理液量が多い連続的処理でも非常に高い熱交換効率が得られる。 In the multi-coil heat exchanger having the above-described configuration, a case will be described in which a liquid to be treated such as a high-temperature acid wastewater is used as the second fluid L2 and the temperature is lowered by heat exchange with the cooling water as the first fluid L1. As shown in FIG. 5, first, the cooling water of the first fluid L1 continuously introduced into the inlet header 3A is distributed to a plurality of (19 in illustration) heat transfer tubes 2 communicating with the inlet header 3A. Then, after spirally ascending from the lower end of the heat exchange section 5 through each heat transfer tube 2, the heat flows into the outlet header 3B from the upper end of the heat exchange section 5 and is extracted from the outlet header 3B in a merged state. . On the other hand, the liquid to be treated of the second fluid L2 is continuously introduced from the inlet 13 into the annular space 10a outside the intermediate cylinder 4 and descends through the annular space 10b. 4, rises in the central space 10 a, overflows from the upper end of the overflow discharge tube 15, flows into the overflow discharge tube 15, and is drawn out from the outlet 14. By passing between a number of heat transfer tubes 2 wound in a coil shape, heat exchange with the cooling water of the first fluid L1 flowing through the heat transfer tubes 2 is performed very efficiently, and the temperature is lowered. Since the liquid flows down from the overflow port 15a into the overflow discharge tube 15 and is discharged from the second fluid outlet port 14, an extremely high heat exchange efficiency can be obtained even in a continuous process in which the amount of the liquid to be treated of the second fluid 12 is large. Can be

そして、この多重コイル型熱交換器の熱交換部５において、入口ヘッダー３Ａから垂下する各伝熱チューブ２の端部２ａは、緩やかにしの字状にカーブを描く形で、水平に近い向きで支持板６の各コイル部における最下位のチューブ挿通孔６０へ挿通できるから、チューブの折れやへしゃげが発生せず、第１流体Ｌ１の流路の閉塞や狭まりによる熱交換性能の低下が回避される。また、中間筒４の内側には伝熱チューブ２群を配設することなく、その内側空間１０ａは熱交換部５での熱交換を経た第２流体Ｌ２が上昇するだけの流路断面積を確保できればよいから、中間筒４の内径を小さくでき、それだけ熱交換槽１を径小化して熱交換器としての容積効率を高め得る。 Then, in the heat exchange section 5 of the multi-coil heat exchanger, the end 2a of each heat transfer tube 2 hanging from the inlet header 3A is drawn in a gently curved shape in a direction close to horizontal. Since the lowermost tube insertion hole 60 in each coil portion of the support plate 6 can be inserted into the lowermost tube insertion hole, the tube does not bend or shrink, and the heat exchange performance is reduced due to blockage or narrowing of the flow path of the first fluid L1. Be avoided. Further, without disposing the heat transfer tube 2 group inside the intermediate cylinder 4, the inner space 10 a has a flow path cross-sectional area enough for the second fluid L 2 having undergone heat exchange in the heat exchange unit 5 to rise. Since it is sufficient to secure the diameter, the inner diameter of the intermediate cylinder 4 can be reduced, and the diameter of the heat exchange tank 1 can be reduced accordingly, and the volume efficiency as a heat exchanger can be increased.

また、実施形態のように、熱交換部５の多重コイル間に上下方向に沿うチューブ配設用間隙ｄを設け、入口ヘッダー３Ａから垂下する多数本の伝熱チューブ２の端部２ａが環状になる該チューブ配設用間隙ｄを通して周方向に分配して熱交換部５の下部へ引き込まれるようにすれば、その引き込み部分で各コイル部の巻き形を歪めずに均整な内外多重コイルの形態を確保できると共に、熱交換部５の組み立てる際の作業性も向上するという利点がある。加えて、該チューブ配設用間隙ｄを除いて、隣接する伝熱チューブ２，２のチューブ間隔をチューブ外径以下で略等しくすれば、該熱交換部５のチューブ配置密度も均等化して各伝熱チューブ２に対する第２流体Ｌ２の接触度合が充分に高まるから、より高い熱交換効率が得られる。 Further, as in the embodiment, a gap d for arranging tubes is provided along the vertical direction between the multiple coils of the heat exchange unit 5, and the end portions 2a of the plurality of heat transfer tubes 2 hanging from the inlet header 3A are formed in an annular shape. By distributing in the circumferential direction through the tube disposing gap d and being drawn into the lower part of the heat exchange section 5, the winding form of each coil section is not distorted at the drawn-in portion, and the form of uniform inner and outer multiple coils is formed. And the workability at the time of assembling the heat exchange unit 5 is also improved. In addition, if the interval between adjacent heat transfer tubes 2 and 2 is substantially equal to or less than the tube outer diameter except for the tube arrangement gap d, the tube arrangement density of the heat exchange unit 5 is also equalized, and Since the degree of contact of the second fluid L2 with the heat transfer tube 2 is sufficiently increased, higher heat exchange efficiency can be obtained.

更に、この多重コイル型熱交換器では、熱交換部５において各伝熱チューブ２が支持板６によって安定した巻回状態を保持しているため、変動のない高い熱交換効率が維持される一方、熱交換部５を構築する際に、各伝熱チューブ２を支持板６のチューブ挿通孔６０に順次通してゆくだけで、同じ巻きピッチで一定した巻き径に容易に設定できるという利点がある。更に、実施形態では、中間筒４及び支持板６と巻回した多数の伝熱チューブ２とが蓋板１２に一体化したユニットになっているから、熱交換器の組立てに際して該ユニットをシェル１Ａの槽体１１内に挿入するだけで熱交換部５を簡単に配設できると共に、劣化等で一部の伝熱チューブ２を交換する際にもユニットごと取り出して容易に交換操作を行えるという利点もある。 Furthermore, in this multi-coil heat exchanger, since the heat transfer tubes 2 in the heat exchange section 5 maintain a stable winding state by the support plate 6, high heat exchange efficiency without fluctuation is maintained. When the heat exchange unit 5 is constructed, there is an advantage that a constant winding diameter can be easily set at the same winding pitch only by sequentially passing each heat transfer tube 2 through the tube insertion hole 60 of the support plate 6. . Further, in the embodiment, since the intermediate tube 4, the support plate 6, and the wound heat transfer tube 2 are integrated into the lid plate 12, the unit is integrated into the shell 1A when assembling the heat exchanger. The advantage is that the heat exchange part 5 can be easily arranged simply by inserting the heat exchange tube 5 into the tank body 11 and the unit can be easily taken out and replaced when replacing some of the heat transfer tubes 2 due to deterioration or the like. There is also.

なお、実施形態の多重コイル型熱交換器では、熱交換部５における内外のコイル重ね数が１４重と多いが、該熱交換部５の内側から外側へ向けてコイル径の拡大に対応して各伝熱チューブ２のコイル巻き数が減じることで、各伝熱チューブ２の長さが熱交換部５全体で均等化されているから、各伝熱チューブ２における圧損が均一化し、熱交換部５全体として各伝熱チューブ２を通過する第１流体Ｌ１の流速及び流量が均等化することに加え、内側の１条巻きの伝熱チューブ群５１に対して外側が２条巻きの伝熱チューブ群５２になっているから、内側の伝熱チューブ群５１における最外周（第９コイル部Ｃ９）のコイル部幅に対し、その外側の伝熱チューブ群５２における最内周（第１０コイル部Ｃ１０）のコイル部幅が広くなり、熱交換部５全体として充分なコイル部幅を確保でき、もって極めて高い熱交換効率が得られる。 In the multi-coil heat exchanger of the embodiment, the number of inner and outer coils in the heat exchanging section 5 is as large as 14 times, but it is necessary to cope with an increase in the coil diameter from the inside to the outside of the heat exchanging section 5. Since the number of coil turns of each heat transfer tube 2 is reduced, the length of each heat transfer tube 2 is equalized in the entire heat exchange unit 5. 5 as a whole, the flow rate and the flow rate of the first fluid L1 passing through each heat transfer tube 2 are equalized, and the heat transfer tubes with two turns on the outside are arranged for the heat transfer tube group 51 with one turn on the inside. Since it is a group 52, the innermost circumference of the outermost heat transfer tube group 52 (the tenth coil part C10) is larger than the outermost circumference (ninth coil part C9) of the inner heat transfer tube group 51 with respect to the coil width. ) The coil part width becomes wider and heat exchange 5 as a whole can secure a sufficient coil unit widths, with extremely high heat exchange efficiency is obtained.

本発明の多重コイル型熱交換器では、内外のコイル重ね数、各コイル部のコイル巻き数及びチューブ条数は実施形態以外に適宜設定できるが、好ましくは熱交換槽１のサイズと縦横比に応じて熱交換部５全体の伝熱チューブ２の長さが均等化するように設定するのがよい。例えば、内側の伝熱チューブ群を２条以上の複数条巻きコイル部として、外側の伝熱チューブ群を内側よりもチューブ条数が多い多条巻きコイル部としたり、更には図４で例示するように、該熱交換部５を内外３層以上の伝熱チューブ群Ｚ１〜Ｚ３に分画し、隣接する伝熱チューブ群Ｚ１，Ｚ２間及びＺ２，Ｚ３間にチューブ配設用間隙ｄを設けると共に、隣接する内側の伝熱チューブ群に対して外側の伝熱チューブ群のチューブ条数が多くなる構成とすることも可能である。図４に例示する多重コイル型熱交換器でも、熱交換部５の各伝熱チューブ群Ｚ１〜Ｚ３は、内側から外側へコイル巻き数を減じることで外側ほどコイル部幅は狭くなるが、伝熱チューブ群毎に内側から外側へ順次にチューブ条数が増すことにより、極端に狭いコイル部幅になる部位を生じず、熱交換部５全体として充分なコイル部幅を確保して高い熱交換効率を達成できる。また、熱交換部５の伝熱チューブ群の内外の分画数によっては、分画最外部の伝熱チューブ群では各コイル部が５条巻き以上になる場合もある。 In the multi-coil heat exchanger of the present invention, the number of inner and outer coils, the number of coil turns of each coil part, and the number of tubes can be appropriately set other than in the embodiment. Accordingly, it is preferable that the length of the heat transfer tube 2 of the entire heat exchange section 5 is set to be equalized. For example, the inner heat transfer tube group may be a multi-turn coil portion having two or more turns, and the outer heat transfer tube group may be a multi-turn coil portion having more tube turns than the inner heat transfer tube portion. As described above, the heat exchange unit 5 is divided into heat transfer tube groups Z1 to Z3 of three or more layers inside and outside, and a tube arrangement gap d is provided between the adjacent heat transfer tube groups Z1 and Z2 and between Z2 and Z3. At the same time, it is also possible to adopt a configuration in which the number of tubes of the outer heat transfer tube group is larger than that of the adjacent inner heat transfer tube group. In the multi-coil heat exchanger illustrated in FIG. 4, the heat transfer tube groups Z <b> 1 to Z <b> 3 of the heat exchange unit 5 have the coil portion width narrower toward the outside by decreasing the number of coil turns from the inside to the outside. By increasing the number of tubes sequentially from the inside to the outside for each heat tube group, there is no portion having an extremely narrow coil portion width, and a sufficient coil portion width is secured for the entire heat exchange portion 5 to achieve high heat exchange. Efficiency can be achieved. Further, depending on the number of inner and outer heat transfer tube groups of the heat exchange unit 5, each coil unit may have five or more turns in the outermost heat transfer tube group.

１熱交換槽
１０槽内空間
１０ａ内側空間
１０ｂ環状空間
１０ｃ液流通部
１３第２流体導入口
１４第２流体導出口
１５溢流排出筒
１５ａ溢流口
２伝熱チューブ
２ａ端部
３Ａ入口ヘッダー
３Ｂ出口ヘッダー
４中間筒
５熱交換部
５１内側の伝熱チューブ群
５２外側の伝熱チューブ群
６支持板
６０チューブ挿通孔
Ｃ１〜Ｃ１４コイル部
ｄチューブ配設用間隙
Ｌ１第１流体
Ｌ２第２流体 DESCRIPTION OF SYMBOLS 1 Heat exchange tank 10 Inside space of tank 10a Inner space 10b Annular space 10c Liquid circulation part 13 Second fluid inlet 14 Second fluid outlet 15 Overflow discharge tube 15a Overflow port 2 Heat transfer tube 2a End 3A Inlet header 3B Outlet header 4 Intermediate cylinder 5 Heat exchange unit 51 Inner heat transfer tube group 52 Outer heat transfer tube group 6 Support plate 60 Tube insertion holes C1 to C14 Coil unit d Tube arrangement gap L1 First fluid L2 Second fluid

Claims

熱交換槽内に、上下方向に沿う溢流排出筒と、該溢流排出筒を同心状に取囲む中間筒とを備えると共に、この中間筒の外側の環状空間内に、フッ素系樹脂からなる多数本の伝熱チューブが該中間筒周りに多重コイル状に巻回して熱交換部を形成し、
前記中間筒の外周に複数枚の支持板が放射状に配置して取り付けられ、該中間筒の下端側に内側空間と外側の環状空間とを連通する液流通部を有し、
前記溢流排出筒は、上端側に溢流口を備えて、下端側が第２流体導出口に連通し、
前記環状空間の上部に臨んで第１流体の入口ヘッダー及び出口ヘッダーと第２流体導入口が設けられ、
前記熱交換部における各伝熱チューブは、前記支持板に設けた多数のチューブ挿通孔を通してコイル状に巻回保持されて上下方向に沿うコイル状をなし、その下端部が前記入口ヘッダーに、上端部が前記出口ヘッダーに、各々前記環状空間を通して連通接続され、
前記第２流体導入口より熱交換槽内に導入された第２流体が前記外側の環状空間を降下する過程で、前記入口ヘッダーより各伝熱チューブに分配して上昇する第１流体と熱交換したのち、前記液流通部から前記内側空間へ流入し、前記溢流口より溢流排出筒内に流下して第２流体導出口に向かうように構成されてなる多重コイル型熱交換器。 In the heat exchange tank, an overflow discharge tube along the vertical direction and an intermediate tube surrounding the overflow discharge tube concentrically are provided, and an annular space outside the intermediate tube is made of a fluororesin. A number of heat transfer tubes are wound around the intermediate tube in a multi-coil form to form a heat exchange section,
A plurality of support plates are radially arranged and attached to the outer periphery of the intermediate cylinder, and have a liquid circulation part communicating the inner space and the outer annular space at the lower end side of the intermediate cylinder,
The overflow discharge cylinder has an overflow port on the upper end side, and the lower end side communicates with the second fluid outlet,
A first fluid inlet header and an outlet header and a second fluid inlet are provided facing the upper part of the annular space,
Each heat transfer tube in the heat exchange section is wound and held in a coil shape through a number of tube insertion holes provided in the support plate to form a coil along the vertical direction, and the lower end thereof is provided at the entrance header, Parts are communicatively connected to said outlet header, each through said annular space;
In the process where the second fluid introduced into the heat exchange tank from the second fluid introduction port descends through the outer annular space, the second fluid is distributed to each heat transfer tube from the inlet header and exchanges heat with the first fluid. Then, the multi-coil heat exchanger is configured to flow into the inner space from the liquid flow portion, flow down from the overflow port into the overflow discharge tube, and head toward the second fluid outlet.

前記熱交換部の多重コイル間に上下方向に沿うチューブ配設用間隙を有し、このチューブ配設用間隙を通して前記入口ヘッダーから垂下する各伝熱チューブが該熱交換部の下部へ引き込まれてなる請求項１に記載の多重コイル型熱交換器。 There is a gap for arranging tubes along the vertical direction between the multiple coils of the heat exchange section, and each heat transfer tube hanging from the inlet header through the gap for arranging tubes is drawn into the lower part of the heat exchange section. The multi-coil heat exchanger according to claim 1.

前記熱交換部における多重コイルの隣接するチューブ間隔が、前記チューブ配設用間隙を除いて、チューブ外径以下で略等しく設定されてなる請求項２に記載の多重コイル型熱交換器。 3. The multi-coil heat exchanger according to claim 2, wherein the interval between adjacent tubes of the multi-coil in the heat exchange unit is set to be substantially equal to or less than the outer diameter of the tube except for the tube disposing gap.