JP6666703B2 - Heat exchanger - Google Patents

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JP6666703B2
JP6666703B2 JP2015239567A JP2015239567A JP6666703B2 JP 6666703 B2 JP6666703 B2 JP 6666703B2 JP 2015239567 A JP2015239567 A JP 2015239567A JP 2015239567 A JP2015239567 A JP 2015239567A JP 6666703 B2 JP6666703 B2 JP 6666703B2
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重雄 蔦木
重雄 蔦木
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株式会社Ｉｈｉプラント
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Description

本発明は、熱交換器に関するものである。   The present invention relates to a heat exchanger.

下記特許文献１には、液化天然ガス（以下、ＬＮＧと称する）を運搬するＬＮＧ運搬体上におけるＬＮＧの再ガス化方法及び装置が開示されている。ＬＮＧの再ガス化は、オープンラック式やシェルアンドチューブ方式等の熱交換器を用いる。オープンラック式の熱交換器は、熱交換媒体として海水を取り込む大型の熱交換器であり、パイプ等の海水腐食、海水から異物を取り除くフィルタの設置等の問題があり、ＬＮＧ気化器に適さないケースもある。この場合、ＬＮＧ気化用の熱交換器には、通常、熱交換媒体を閉ループ内で循環させるシェルアンドチューブ方式の熱交換器が用いられている。   Patent Document 1 listed below discloses a method and apparatus for regasifying LNG on an LNG carrier that carries liquefied natural gas (hereinafter, referred to as LNG). For regasification of LNG, a heat exchanger such as an open rack type or a shell and tube type is used. The open rack type heat exchanger is a large heat exchanger that takes in seawater as a heat exchange medium, and has problems such as seawater corrosion of pipes and the installation of a filter that removes foreign matter from seawater, and is not suitable for LNG vaporizers. There are cases. In this case, a shell and tube type heat exchanger that circulates a heat exchange medium in a closed loop is usually used as a heat exchanger for vaporizing LNG.

特表２００５−５２１８４９号公報JP-T-2005-521849

ところで、ＬＮＧを再ガス化するシェルアンドチューブ方式の熱交換器は、熱交換媒体としてエチレングリコール水溶液（以下、ＥＧＷと称する）を用いるものが主流である。しかしながら、ＥＧＷの凝固点は３６％重量濃度で約−２２℃であり、ＥＧＷが極低温（約−１６２℃）のＬＮＧと熱交換すると、本体部（シェル）の内部で凍結する懸念があった。このため、従来では、熱交換効率を犠牲にした設計（例えばＬＮＧとＥＧＷを並行流とする等）がなされていた。   By the way, shell-and-tube type heat exchangers for regasifying LNG mainly use an ethylene glycol aqueous solution (hereinafter referred to as EGW) as a heat exchange medium. However, the freezing point of the EGW is about -22 ° C at a 36% weight concentration, and there is a concern that when the EGW exchanges heat with very low temperature (about -162 ° C) LNG, it freezes inside the main body (shell). For this reason, conventionally, a design that sacrificed heat exchange efficiency (for example, LNG and EGW are made to flow in parallel) has been made.

本発明は、上記問題点に鑑みてなされたものであり、熱交換媒体の凍結を防止し、熱交換効率の改善を図ることができる熱交換器の提供を目的とする。   The present invention has been made in view of the above problems, and has as its object to provide a heat exchanger capable of preventing freezing of a heat exchange medium and improving heat exchange efficiency.

上記の課題を解決するために、本発明は、流体が流通する複数の伝熱管を収容する本体部と、前記本体部の内部に形成された、前記複数の伝熱管の間を熱交換媒体が流通する熱交換流路を分割する隔壁と、前記隔壁によって分割された前記熱交換流路のうち、前記複数の伝熱管の下流側の第１熱交換流路に、第１凝固点を有する第１熱交換媒体を供給する第１熱交換媒体供給部と、前記隔壁によって分割された前記熱交換流路のうち、前記複数の伝熱管の上流側の第２熱交換流路に、前記第１凝固点よりも低い第２凝固点を有する第２熱交換媒体を供給する第２熱交換媒体供給部と、有する、という構成を採用する。   In order to solve the above-described problems, the present invention provides a heat exchange medium between a plurality of heat transfer tubes formed in a main body that accommodates a plurality of heat transfer tubes through which a fluid flows, and the plurality of heat transfer tubes. A partition that divides the flowing heat exchange channel, and a first heat exchange channel downstream of the plurality of heat transfer tubes among the heat exchange channels divided by the partition, having a first freezing point. A first heat exchange medium supply unit for supplying a heat exchange medium; and a first heat exchange point in a second heat exchange flow path upstream of the plurality of heat transfer tubes among the heat exchange flow paths divided by the partition. And a second heat exchange medium supply unit that supplies a second heat exchange medium having a lower second freezing point.

また、本発明においては、前記第２熱交換流路における熱交換によって凝縮した前記第２熱交換媒体を気化させる気化器を有し、前記第２熱交換媒体供給部は、前記気化器によって気化した前記第２熱交換媒体を、再び前記第２熱交換流路に供給する第２熱交換媒体循環流路を有する、という構成を採用する。   Further, in the present invention, there is provided a vaporizer for vaporizing the second heat exchange medium condensed by heat exchange in the second heat exchange flow path, wherein the second heat exchange medium supply unit is vaporized by the vaporizer. And a second heat exchange medium circulation channel for supplying the second heat exchange medium to the second heat exchange channel again.

また、本発明においては、前記気化器は、前記凝縮した前記第２熱交換媒体を貯溜する貯溜部と、前記貯溜部に貯溜された前記第２熱交換媒体の液面に挿し込まれ、前記気化した前記第２熱交換媒体の前記第２熱交換流路への逆流を阻止する水封板と、を有する、という構成を採用する。   Further, in the present invention, the vaporizer is inserted into a storage section for storing the condensed second heat exchange medium, and a liquid level of the second heat exchange medium stored in the storage section, A water seal plate for preventing the vaporized second heat exchange medium from flowing back into the second heat exchange channel.

また、本発明においては、前記気化器は、前記第２熱交換流路の底部に接続されており、前記第２熱交換流路は、前記第２熱交換媒体を回流させると共に、前記凝縮した前記第２熱交換媒体を前記底部に導く傾斜を備える複数のバッフルプレートを有する、という構成を採用する。   Further, in the present invention, the vaporizer is connected to a bottom of the second heat exchange flow path, and the second heat exchange flow path circulates the second heat exchange medium and condenses the second heat exchange medium. A configuration is employed in which a plurality of baffle plates having an inclination for guiding the second heat exchange medium to the bottom are provided.

また、本発明においては、前記第１熱交換媒体供給部は、前記第１熱交換流路において熱交換した後の前記第１熱交換媒体を、再び前記第１熱交換流路に供給する第１熱交換媒体循環流路と、前記第１熱交換媒体循環路において前記第１熱交換媒体を加熱する第１熱交換媒体加熱部と、前記第１熱交換媒体加熱部によって加熱された前記第１熱交換媒体の一部を、前記第２熱交換媒体を気化させる熱交換媒体として前記気化器に供給するバイパス流路と、を有する、という構成を採用する。   Further, in the present invention, the first heat exchange medium supply unit supplies the first heat exchange medium after the heat exchange in the first heat exchange flow path to the first heat exchange flow path again. 1 heat exchange medium circulation channel, a first heat exchange medium heating unit for heating the first heat exchange medium in the first heat exchange medium circulation channel, and the first heat exchange medium heating unit heated by the first heat exchange medium heating unit. And a bypass flow path for supplying a part of the heat exchange medium to the vaporizer as a heat exchange medium for vaporizing the second heat exchange medium.

また、本発明においては、前記隔壁は、前記第１熱交換流路及び前記第２熱交換流路の少なくともいずれか一方に突出し、前記第１熱交換媒体と前記第２熱交換媒体との伝熱を促進させる突起部を有する、という構成を採用する。   Further, in the present invention, the partition wall protrudes into at least one of the first heat exchange channel and the second heat exchange channel, and transfers the first heat exchange medium and the second heat exchange medium. A configuration having a protrusion for promoting heat is employed.

本発明では、複数の伝熱管を収容する本体部の内部に形成された熱交換流路を隔壁によって分割し、複数の伝熱管の下流側（流体の流出側（高温））においては、第１凝固点を有する第１熱交換媒体によって熱交換し、複数の伝熱管の上流側（流体の流入側（低温））においては、第１凝固点より低い第２凝固点を有する第２熱交換媒体によって熱交換する。このように、流体が低温である複数の伝熱管の上流側においては、凝固点の低い第２熱交換媒体を使用することにより、熱交換媒体の凍結を防止することができる。このため、熱交換媒体の凍結の懸念が解消され、熱交換効率の改善を図ることが可能となる。
したがって、本発明では、熱交換媒体の凍結を防止し、熱交換効率の改善を図ることができる熱交換器が得られる。 In the present invention, the heat exchange flow passage formed inside the main body that houses the plurality of heat transfer tubes is divided by the partition wall, and the first heat transfer passage is located downstream of the plurality of heat transfer tubes (the fluid outflow side (high temperature)). Heat is exchanged by the first heat exchange medium having a freezing point, and on the upstream side (inflow side (low temperature) of the fluid) of the plurality of heat transfer tubes, heat is exchanged by the second heat exchange medium having a second freezing point lower than the first freezing point. I do. As described above, by using the second heat exchange medium having a low freezing point on the upstream side of the plurality of heat transfer tubes where the fluid has a low temperature, freezing of the heat exchange medium can be prevented. For this reason, the fear of freezing of the heat exchange medium is eliminated, and the heat exchange efficiency can be improved.
Therefore, in the present invention, a heat exchanger capable of preventing freezing of the heat exchange medium and improving heat exchange efficiency is obtained.

本発明の実施形態における熱交換器の構成図である。It is a lineblock diagram of a heat exchanger in an embodiment of the present invention. 本発明の別実施形態における熱交換器の構成図である。It is a lineblock diagram of a heat exchanger in another embodiment of the present invention.

以下、本発明の実施形態について図面を参照して説明する。   Hereinafter, embodiments of the present invention will be described with reference to the drawings.

図１は、本発明の実施形態における熱交換器１の構成図である。
図１に示すように、熱交換器１は、本体部１０と、隔壁２０と、第１熱交換媒体供給部３０と、第２熱交換媒体供給部４０と、を有する。熱交換器１は、熱交換媒体３との熱交換により、流体２を所定温度に加熱するシェルアンドチューブ方式の熱交換器である。本実施形態の流体２は、ＬＮＧであり、熱交換媒体３との熱交換によって、天然ガス（以下、ＮＧと称する）となって本体部１０から排出される。 FIG. 1 is a configuration diagram of a heat exchanger 1 according to an embodiment of the present invention.
As shown in FIG. 1, the heat exchanger 1 has a main body 10, a partition wall 20, a first heat exchange medium supply unit 30, and a second heat exchange medium supply unit 40. The heat exchanger 1 is a shell and tube heat exchanger that heats the fluid 2 to a predetermined temperature by exchanging heat with the heat exchange medium 3. The fluid 2 of the present embodiment is LNG, and is converted into natural gas (hereinafter, referred to as NG) by heat exchange with the heat exchange medium 3 and discharged from the main body 10.

本体部１０は、鉛直方向に立設した略円筒形状を有する。本体部１０は、流体２が流通する複数の伝熱管１１を収容している。複数の伝熱管１１は、鉛直方向に延在しており、その両端部が管板１２によって支持されている。管板１２は、本体部１０の内壁面に固定された円板部材であり、その板面に複数の伝熱管１１の端部を固定する複数の貫通孔が形成されている。本体部１０と、複数の伝熱管１１と、上下の管板１２とによって囲まれた空間は、熱交換媒体３が流通する熱交換流路４となる。   The main body 10 has a substantially cylindrical shape standing upright in the vertical direction. The main body 10 houses a plurality of heat transfer tubes 11 through which the fluid 2 flows. The plurality of heat transfer tubes 11 extend in the vertical direction, and both ends thereof are supported by the tube sheet 12. The tube sheet 12 is a disk member fixed to the inner wall surface of the main body 10, and has a plurality of through holes formed on the plate surface to fix the ends of the plurality of heat transfer tubes 11. The space surrounded by the main body 10, the plurality of heat transfer tubes 11, and the upper and lower tube sheets 12 becomes the heat exchange channel 4 through which the heat exchange medium 3 flows.

本体部１０の底部には、流体２が流入する流体流入口１３が設けられている。また、本体部１０の頂部には、流体２が流出する流体流出口１４が設けられている。流体流入口１３から本体部１０の内部に流入した流体２は、管板１２に支持された複数の伝熱管１１の内部を上昇し、熱交換媒体３と熱交換した後、流体流出口１４を介して本体部１０の頂部から排出される。   The bottom of the main body 10 is provided with a fluid inlet 13 into which the fluid 2 flows. A fluid outlet 14 through which the fluid 2 flows out is provided at the top of the main body 10. The fluid 2 flowing from the fluid inlet 13 into the main body 10 rises inside the plurality of heat transfer tubes 11 supported by the tube sheet 12 and exchanges heat with the heat exchange medium 3. It is discharged from the top of the main body 10 through the main body.

隔壁２０は、本体部１０の内部に設けられ、熱交換流路４を上下に分割するものである。隔壁２０は、本体部１０の中腹部の内壁面に固定された円板部材であり、その板面に複数の伝熱管１１を挿通させる複数の貫通孔が形成されている。隔壁２０の貫通孔と複数の伝熱管１１との間は、溶接等によってシールされている。   The partition wall 20 is provided inside the main body 10 and divides the heat exchange channel 4 into upper and lower portions. The partition wall 20 is a disk member fixed to the inner wall surface of the middle abdomen of the main body 10, and has a plurality of through holes through which the plurality of heat transfer tubes 11 are inserted. The space between the through hole of the partition wall 20 and the plurality of heat transfer tubes 11 is sealed by welding or the like.

本体部１０と、複数の伝熱管１１と、上側の管板１２と、隔壁２０によって囲まれた上半分の空間は、後述する第１熱交換媒体３Ａが流通する第１熱交換流路４Ａとなる。また、本体部１０と、複数の伝熱管１１と、下側の管板１２と、隔壁２０によって囲まれた下半分の空間は、後述する第２熱交換媒体３Ｂが流通する第２熱交換流路４Ｂとなる。   The upper half space surrounded by the main body 10, the plurality of heat transfer tubes 11, the upper tube sheet 12, and the partition wall 20 is provided with a first heat exchange channel 4 </ b> A through which a first heat exchange medium 3 </ b> A described later flows. Become. The lower half space surrounded by the main body 10, the plurality of heat transfer tubes 11, the lower tube sheet 12, and the partition wall 20 is provided with a second heat exchange flow through which a second heat exchange medium 3 </ b> B described later flows. Road 4B.

第１熱交換媒体供給部３０は、第１熱交換流路４Ａに、第１凝固点を有する第１熱交換媒体３Ａを供給するものである。第１熱交換媒体３Ａには、第１熱交換流路４Ａにおいて相が変化しない液状媒体を用いる。本実施形態の第１熱交換媒体３Ａは、ＥＧＷであり、その第１凝固点は、３６％重量濃度で約−２２℃である。   The first heat exchange medium supply unit 30 supplies the first heat exchange medium 3A having the first freezing point to the first heat exchange channel 4A. As the first heat exchange medium 3A, a liquid medium whose phase does not change in the first heat exchange channel 4A is used. The first heat exchange medium 3A of the present embodiment is EGW, and has a first freezing point of about −22 ° C. at a 36% weight concentration.

第１熱交換媒体供給部３０は、第１熱交換媒体循環流路３１と、第１熱交換媒体加熱部３２と、バイパス流路３３と、を有する。また、第１熱交換媒体供給部３０は、第１熱交換媒体３Ａを循環させる図示しないポンプを有する。   The first heat exchange medium supply unit 30 has a first heat exchange medium circulation channel 31, a first heat exchange medium heating unit 32, and a bypass channel 33. The first heat exchange medium supply unit 30 has a pump (not shown) that circulates the first heat exchange medium 3A.

第１熱交換媒体循環流路３１は、第１熱交換流路４Ａにおいて熱交換した後の第１熱交換媒体３Ａを、再び第１熱交換流路４Ａに供給する流路である。本体部１０には、上部に第１熱交換媒体流入口１５が設けられ、また、隔壁２０より上側の中腹部に第１熱交換媒体流出口１６が設けられている。第１熱交換媒体循環流路３１は、第１熱交換媒体流出口１６を第１熱交換媒体流入口１５に接続し、第１熱交換媒体３Ａの閉ループを形成する。   The first heat exchange medium circulation flow path 31 is a flow path that supplies the first heat exchange medium 3A after heat exchange in the first heat exchange flow path 4A to the first heat exchange flow path 4A again. The main body 10 is provided with a first heat exchange medium inlet 15 at an upper part, and a first heat exchange medium outlet 16 at a middle part above the partition wall 20. The first heat exchange medium circulation flow path 31 connects the first heat exchange medium outlet 16 to the first heat exchange medium inlet 15, and forms a closed loop of the first heat exchange medium 3A.

第１熱交換媒体加熱部３２は、第１熱交換媒体循環路において第１熱交換媒体を加熱する加熱器である。第１熱交換媒体加熱部３２としては、例えば、エアファンヒーターを用いることができる。   The first heat exchange medium heating unit 32 is a heater that heats the first heat exchange medium in the first heat exchange medium circulation path. As the first heat exchange medium heating unit 32, for example, an air fan heater can be used.

バイパス流路３３は、第１熱交換媒体加熱部３２によって加熱された第１熱交換媒体３Ａの一部を、後述する気化器５０に供給する流路である。バイパス流路３３は、第１熱交換媒体加熱部３２と第１熱交換媒体流入口１５との間の第１熱交換媒体循環流路３１から分岐して、第１熱交換媒体３Ａを気化器５０に供給すると共に、気化器５０を通過した後の第１熱交換媒体３Ａを、第１熱交換媒体流出口１６と第１熱交換媒体加熱部３２との間の第１熱交換媒体循環流路３１に合流させる。   The bypass passage 33 is a passage that supplies a part of the first heat exchange medium 3 </ b> A heated by the first heat exchange medium heating unit 32 to a vaporizer 50 described below. The bypass flow path 33 branches off from the first heat exchange medium circulation flow path 31 between the first heat exchange medium heating unit 32 and the first heat exchange medium inflow port 15 to convert the first heat exchange medium 3A into a vaporizer. The first heat exchange medium 3A that has been supplied to the first heat exchange medium and passed through the vaporizer 50 is supplied to the first heat exchange medium circulation flow between the first heat exchange medium outlet 16 and the first heat exchange medium heating unit 32. Merge into road 31.

第２熱交換媒体供給部４０は、第２熱交換流路４Ｂに、第２凝固点を有する第２熱交換媒体３Ｂを供給するものである。第２熱交換媒体３Ｂには、第２熱交換流路４Ｂにおいて気体から液体に相が変化する凝縮性媒体を用いる。本実施形態の第２熱交換媒体３Ｂは、プロパンであり、その第２凝固点は、上述した第１凝固点（約−２２℃）よりも低い約−１８７℃である。   The second heat exchange medium supply unit 40 supplies the second heat exchange medium 3B having the second freezing point to the second heat exchange channel 4B. As the second heat exchange medium 3B, a condensable medium whose phase changes from gas to liquid in the second heat exchange channel 4B is used. The second heat exchange medium 3B of the present embodiment is propane, and its second freezing point is about -187 ° C, which is lower than the above-mentioned first freezing point (about -22 ° C).

本体部１０には、第２熱交換流路４Ｂにおける熱交換によって凝縮した第２熱交換媒体３Ｂを気化させる気化器５０が付設されている。第２熱交換媒体供給部４０は、第２熱交換媒体循環流路４１を有する。また、第２熱交換媒体供給部４０は、第２熱交換媒体３Ｂを循環させる図示しないブロワーを有する。   The main body 10 is provided with a vaporizer 50 for vaporizing the second heat exchange medium 3B condensed by heat exchange in the second heat exchange channel 4B. The second heat exchange medium supply unit 40 has a second heat exchange medium circulation channel 41. In addition, the second heat exchange medium supply unit 40 has a blower (not shown) that circulates the second heat exchange medium 3B.

第２熱交換媒体循環流路４１は、気化器５０によって気化した第２熱交換媒体３Ｂを、再び第２熱交換流路４Ｂに供給する流路である。本体部１０には、隔壁２０より下側の中腹部に第２熱交換媒体流入口１７が設けられ、付設された気化器５０に第２熱交換媒体流出口１８が設けられている。第２熱交換媒体循環流路４１は、第２熱交換媒体流出口１８を第２熱交換媒体流入口１７に接続し、第２熱交換媒体３Ｂの閉ループを形成する。   The second heat exchange medium circulation flow path 41 is a flow path that supplies the second heat exchange medium 3B vaporized by the vaporizer 50 to the second heat exchange flow path 4B again. The main body 10 is provided with a second heat exchange medium inlet 17 at a middle portion below the partition wall 20, and an attached vaporizer 50 is provided with a second heat exchange medium outlet 18. The second heat exchange medium circulation flow path 41 connects the second heat exchange medium outlet 18 to the second heat exchange medium inlet 17, and forms a closed loop of the second heat exchange medium 3B.

気化器５０は、貯溜部５１と、水封板５２と、を有する。
貯溜部５１は、凝縮した第２熱交換媒体３Ｂを貯溜するものであり、第２熱交換流路４Ｂの底部４Ｂ１に接続されている。第２熱交換流路４Ｂの底部４Ｂ１の下面は、下側の管板１２によって形成されており、貯溜部５１は、下側の管板１２から垂れ落ちた第２熱交換媒体３Ｂを貯溜する構成となっている。 The vaporizer 50 has a storage part 51 and a water sealing plate 52.
The storage section 51 stores the condensed second heat exchange medium 3B, and is connected to the bottom 4B1 of the second heat exchange flow path 4B. The lower surface of the bottom portion 4B1 of the second heat exchange channel 4B is formed by the lower tube sheet 12, and the storage portion 51 stores the second heat exchange medium 3B that has dropped from the lower tube sheet 12. It has a configuration.

貯溜部５１には、伝熱管５３が収容されている。伝熱管５３は、コイル状に形成されている。伝熱管５３には、バイパス流路３３を介して第１熱交換媒体３Ａが供給される。伝熱管５３に供給された第１熱交換媒体３Ａは、凝縮した第２熱交換媒体３Ｂを気化させる熱交換媒体として用いられる。   The heat transfer tube 53 is accommodated in the storage section 51. The heat transfer tube 53 is formed in a coil shape. The first heat exchange medium 3 </ b> A is supplied to the heat transfer tube 53 via the bypass passage 33. The first heat exchange medium 3A supplied to the heat transfer tube 53 is used as a heat exchange medium for vaporizing the condensed second heat exchange medium 3B.

水封板５２は、貯溜部５１に貯溜された第２熱交換媒体３Ｂの液面３Ｂ１に挿し込まれ、気化した第２熱交換媒体３Ｂの第２熱交換流路４Ｂへの逆流を阻止するものである。水封板５２は、伝熱管５３の上方を囲い、伝熱管５３の上方空間と第２熱交換媒体流出口１８とを連通させると共に、伝熱管５３の上方空間と第２熱交換流路４Ｂとの間を縁切りする。   The water sealing plate 52 is inserted into the liquid surface 3B1 of the second heat exchange medium 3B stored in the storage section 51, and prevents the vaporized second heat exchange medium 3B from flowing back to the second heat exchange flow path 4B. Things. The water sealing plate 52 surrounds the upper part of the heat transfer tube 53, communicates the space above the heat transfer tube 53 with the second heat exchange medium outlet 18, and connects the space above the heat transfer tube 53 with the second heat exchange flow path 4B. Cut off between.

熱交換流路４は、熱交換媒体３を回流させる複数のバッフルプレート５を有する。バッフルプレート５には、切欠き部５ａが形成されている。複数のバッフルプレート５は、本体部１０の内部において鉛直方向に間をあけて設けられており、切欠き部５ａが交互に左右となるように配置されている。このため、熱交換媒体３は、バッフルプレート５を迂回しながら本体部１０の中を回流することができる。   The heat exchange channel 4 has a plurality of baffle plates 5 for circulating the heat exchange medium 3. The baffle plate 5 has a notch 5a. The plurality of baffle plates 5 are provided at intervals in the vertical direction inside the main body 10, and are arranged such that the cutouts 5 a are alternately left and right. Therefore, the heat exchange medium 3 can circulate in the main body 10 while bypassing the baffle plate 5.

第２熱交換流路４Ｂのバッフルプレート５Ｂは、水平面から傾いて配置されている。バッフルプレート５Ｂは、凝縮した第２熱交換媒体３Ｂを第２熱交換流路４Ｂの底部４Ｂ１に導く傾斜を備える。バッフルプレート５Ｂの傾斜が大きすぎると、第２熱交換流路４Ｂの途中の流路面積が狭くなるため、圧力損失の関係から、傾斜をあまり大きくしないことが好ましい。バッフルプレート５Ｂの傾斜は、水平面を０°としたときに、例えば５°〜１５°程度とすることが好ましい。   The baffle plate 5B of the second heat exchange channel 4B is arranged to be inclined from the horizontal plane. The baffle plate 5B has an inclination for guiding the condensed second heat exchange medium 3B to the bottom 4B1 of the second heat exchange channel 4B. If the inclination of the baffle plate 5B is too large, the flow passage area in the middle of the second heat exchange flow path 4B becomes small. Therefore, it is preferable that the inclination is not too large in view of the pressure loss. The inclination of the baffle plate 5B is preferably, for example, about 5 ° to 15 ° when the horizontal plane is 0 °.

続いて、上記構成の熱交換器１の動作及び作用について説明する。   Subsequently, an operation and an operation of the heat exchanger 1 having the above configuration will be described.

図１に示すように、熱交換器１の本体部１０の内部に形成された熱交換流路４は、隔壁２０によって、第１熱交換流路４Ａと第２熱交換流路４Ｂに分割されている。第１熱交換媒体供給部３０は、第１熱交換流路４Ａに、第１凝固点を有する第１熱交換媒体３Ａを供給し、複数の伝熱管１１の下流側を流れる流体２と熱交換させる。また、第２熱交換媒体供給部４０は、第２熱交換流路４Ｂに、第２凝固点を有する第２熱交換媒体３Ｂを供給し、複数の伝熱管１１の上流側を流れる流体２と熱交換させる。   As shown in FIG. 1, the heat exchange channel 4 formed inside the main body 10 of the heat exchanger 1 is divided by a partition wall 20 into a first heat exchange channel 4A and a second heat exchange channel 4B. ing. The first heat exchange medium supply unit 30 supplies the first heat exchange medium 3A having a first freezing point to the first heat exchange channel 4A, and causes heat exchange with the fluid 2 flowing downstream of the plurality of heat transfer tubes 11. . Further, the second heat exchange medium supply unit 40 supplies the second heat exchange medium 3B having the second freezing point to the second heat exchange flow path 4B, and heats the fluid 2 flowing on the upstream side of the plurality of heat transfer tubes 11 with the heat. Let me exchange.

複数の伝熱管１１の上流側を流れる流体２は、複数の伝熱管１１の下流側を流れる流体２よりも低温であるが、第２熱交換媒体３Ｂの第２凝固点は、第１熱交換媒体３Ａの第１凝固点よりも低い。本実施形態では、第２熱交換媒体３Ｂとして凝固点が約−１８７℃のプロパンを使用しているため、流体２として約−１６２℃のＬＮＧを使用しても凍結することはない。このように、流体２が低温である複数の伝熱管１１の上流側において、凝固点の低い第２熱交換媒体３Ｂを使用することにより、第２熱交換媒体３Ｂの凍結を防止することができる。   The fluid 2 flowing on the upstream side of the plurality of heat transfer tubes 11 is lower in temperature than the fluid 2 flowing on the downstream side of the plurality of heat transfer tubes 11, but the second freezing point of the second heat exchange medium 3B is different from that of the first heat exchange medium. It is lower than the first freezing point of 3A. In the present embodiment, since propane having a freezing point of about −187 ° C. is used as the second heat exchange medium 3 </ b> B, it does not freeze even if LNG of about −162 ° C. is used as the fluid 2. As described above, by using the second heat exchange medium 3B having a low freezing point on the upstream side of the plurality of heat transfer tubes 11 where the fluid 2 is at a low temperature, it is possible to prevent the second heat exchange medium 3B from freezing.

そして、複数の伝熱管１１の上流側における熱交換媒体３（第２熱交換媒体３Ｂ）の凍結の懸念が解消されることで、本体部１０の内部の熱交換媒体３の流れを全て対向流とすることができる。すなわち、図１に示すように、第１熱交換流路４Ａにおいて複数の伝熱管１１の下流側から上流側に向かって第１熱交換媒体３Ａを流通させると共に、第２熱交換流路４Ｂにおいても複数の伝熱管１１の下流側から上流側に向かって第２熱交換媒体３Ｂを流通させることができる。対向流は、並行流よりも熱交換効率が高いため、熱交換効率の改善を図ることが可能となる。   Then, since the concern of freezing of the heat exchange medium 3 (the second heat exchange medium 3B) on the upstream side of the plurality of heat transfer tubes 11 is eliminated, the flow of the heat exchange medium 3 inside the main body 10 is all counter-current. It can be. That is, as shown in FIG. 1, the first heat exchange medium 3A flows from the downstream side to the upstream side of the plurality of heat transfer tubes 11 in the first heat exchange channel 4A, and the second heat exchange channel 4B Also, the second heat exchange medium 3B can flow from the downstream side of the plurality of heat transfer tubes 11 to the upstream side. Since the counter flow has higher heat exchange efficiency than the parallel flow, it is possible to improve the heat exchange efficiency.

流体２は、複数の伝熱管１１の上流側において第２熱交換媒体３Ｂ（プロパン）の凝縮熱により気化（天然ガス化）し、複数の伝熱管１１の下流側において第１熱交換媒体３Ａ（ＥＧＷ）の顕熱により必要温度まで昇温する。本実施形態では、第２熱交換流路４Ｂにおける熱交換によって凝縮した第２熱交換媒体３Ｂを気化させる気化器５０を有し、第２熱交換媒体供給部４０は、気化器５０によって気化した第２熱交換媒体３Ｂを、再び第２熱交換流路４Ｂに供給する第２熱交換媒体循環流路４１を有する。これにより、第２熱交換媒体３Ｂの閉ループを形成しつつ、第２熱交換媒体３Ｂの凝縮熱を利用することができるため、熱交換効率の向上を図ることが可能となる。   The fluid 2 is vaporized (naturalized gas) by the heat of condensation of the second heat exchange medium 3B (propane) on the upstream side of the plurality of heat transfer tubes 11, and the first heat exchange medium 3A ( The temperature is raised to a required temperature by the sensible heat of EGW). In the present embodiment, the second heat exchange medium has a vaporizer 50 for vaporizing the second heat exchange medium 3B condensed by heat exchange in the second heat exchange flow path 4B, and the second heat exchange medium supply unit 40 is vaporized by the vaporizer 50. There is a second heat exchange medium circulation channel 41 that supplies the second heat exchange medium 3B to the second heat exchange channel 4B again. Thereby, since the heat of condensation of the second heat exchange medium 3B can be utilized while forming a closed loop of the second heat exchange medium 3B, the heat exchange efficiency can be improved.

気化器５０は、凝縮した第２熱交換媒体３Ｂを貯溜する貯溜部５１と、貯溜部５１に貯溜された第２熱交換媒体３Ｂの液面３Ｂ１に挿し込まれた水封板５２と、を有する。この構成によれば、貯溜部５１において気化した第２熱交換媒体３Ｂの第２熱交換流路４Ｂへの逆流を阻止することができる。   The vaporizer 50 includes a storage unit 51 that stores the condensed second heat exchange medium 3B, and a water seal plate 52 that is inserted into the liquid surface 3B1 of the second heat exchange medium 3B stored in the storage unit 51. Have. According to this configuration, the backflow of the second heat exchange medium 3B vaporized in the storage section 51 to the second heat exchange flow path 4B can be prevented.

また、貯溜部５１は、第２熱交換流路４Ｂの底部４Ｂ１に接続されており、第２熱交換流路４Ｂの複数のバッフルプレート５Ｂは、凝縮した第２熱交換媒体３Ｂを底部４Ｂ１に導く傾斜を備えるため、凝縮した第２熱交換媒体３Ｂは貯溜部５１に垂れ落ち、貯溜部５１において気化し、閉ループ内を自動的に循環するようになる。このように、第２熱交換媒体３Ｂが閉ループ内を自動的に循環することで、第２熱交換媒体循環路４１に設けられた不図示のブロワーは、第２熱交換媒体３Ｂの循環を補助する低出力のものとすることができる。   Further, the storage unit 51 is connected to the bottom 4B1 of the second heat exchange channel 4B, and the plurality of baffle plates 5B of the second heat exchange channel 4B transfer the condensed second heat exchange medium 3B to the bottom 4B1. Because of the guiding inclination, the condensed second heat exchange medium 3B drips down into the storage part 51, evaporates in the storage part 51, and automatically circulates in the closed loop. In this manner, the second heat exchange medium 3B automatically circulates in the closed loop, so that the blower (not shown) provided in the second heat exchange medium circulation path 41 assists the circulation of the second heat exchange medium 3B. Low output.

また、第１熱交換媒体供給部３０は、第１熱交換媒体加熱部３２によって加熱された第１熱交換媒体３Ａの一部を、第２熱交換媒体３Ｂを気化させる熱交換媒体として気化器５０に供給するバイパス流路３３を有する。この構成によれば、気化器５０の熱源を別途用意する必要がなくなり、熱交換器１の簡略化、小型化及び低コスト化を図ることができる。   Further, the first heat exchange medium supply unit 30 uses a part of the first heat exchange medium 3A heated by the first heat exchange medium heating unit 32 as a heat exchange medium for vaporizing the second heat exchange medium 3B as a vaporizer. It has a bypass flow path 33 for supplying to 50. According to this configuration, it is not necessary to separately prepare a heat source for the vaporizer 50, and the heat exchanger 1 can be simplified, downsized, and reduced in cost.

このように、上述の本実施形態によれば、流体２が流通する複数の伝熱管１１を収容する本体部１０と、本体部１０の内部に形成された、複数の伝熱管１１の間を熱交換媒体３が流通する熱交換流路４を分割する隔壁２０と、隔壁２０によって分割された熱交換流路４のうち、複数の伝熱管１１の下流側の第１熱交換流路４Ａに、第１凝固点を有する第１熱交換媒体３Ａを供給する第１熱交換媒体供給部３０と、隔壁２０によって分割された熱交換流路４のうち、複数の伝熱管１１の上流側の第２熱交換流路４Ｂに、第１凝固点よりも低い第２凝固点を有する第２熱交換媒体３Ｂを供給する第２熱交換媒体供給部４０と、有する、という構成を採用することによって、熱交換媒体４の凍結を防止し、熱交換効率の改善を図ることができる。   As described above, according to the above-described embodiment, heat is applied between the main body 10 that houses the plurality of heat transfer tubes 11 through which the fluid 2 flows and the plurality of heat transfer tubes 11 that are formed inside the main body 10. A partition wall 20 that divides the heat exchange flow path 4 through which the exchange medium 3 flows, and a first heat exchange flow path 4A downstream of the plurality of heat transfer tubes 11 among the heat exchange flow paths 4 divided by the partition wall 20, A first heat exchange medium supply unit 30 for supplying a first heat exchange medium 3A having a first freezing point; and a second heat upstream of the plurality of heat transfer tubes 11 in the heat exchange flow path 4 divided by the partition wall 20. The second heat exchange medium supply unit 40 that supplies the second heat exchange medium 3B having the second freezing point lower than the first freezing point to the exchange flow path 4B is provided. Can be prevented from freezing, and the heat exchange efficiency can be improved.

以上、図面を参照しながら本発明の好適な実施形態について説明したが、本発明は上記実施形態に限定されるものではない。上述した実施形態において示した各構成部材の諸形状や組み合わせ等は一例であって、本発明の主旨から逸脱しない範囲において設計要求等に基づき種々変更可能である。   The preferred embodiment of the present invention has been described with reference to the drawings, but the present invention is not limited to the above embodiment. The shapes, combinations, and the like of the respective constituent members shown in the above-described embodiments are merely examples, and can be variously changed based on design requirements and the like without departing from the gist of the present invention.

図２は、本発明の別実施形態における熱交換器１Ａの構成図である。
図２に示すように、熱交換器１Ａの隔壁２０Ａは、第１熱交換流路４Ａ及び第２熱交換流路４Ｂの少なくともいずれか一方（図２においては両方）に突出し、第２熱交換媒体３Ｂの熱を第１熱交換媒体３Ａに伝熱させる複数の突起部２１を有する。第１熱交換流路４Ａの下流側（隔壁２０Ａの上面）を流れる第１熱交換媒体３Ａは低温であるが、第２熱交換流路４Ｂの上流側（隔壁２０Ａの下面）を流れる第２熱交換媒体３Ｂは高温であるため、第２熱交換媒体３Ｂの熱を第１熱交換媒体３Ａに積極的に伝熱させることで、第１熱交換媒体３Ａの凍結を確実に防止することができる。複数の突起部２１は、隔壁２０Ａの表面積を増加させ、第１熱交換媒体３Ａと第２熱交換媒体３Ｂとの間の熱交換を促進させる。なお、複数の突出部２１が高いと、圧力損失が生じるため、例えば、１０〜２０ｍｍ程度の高さとして密集して配置することが好ましい。 FIG. 2 is a configuration diagram of a heat exchanger 1A according to another embodiment of the present invention.
As shown in FIG. 2, the partition wall 20A of the heat exchanger 1A protrudes into at least one of the first heat exchange channel 4A and the second heat exchange channel 4B (both in FIG. 2), and the second heat exchange. It has a plurality of protrusions 21 for transferring the heat of the medium 3B to the first heat exchange medium 3A. The first heat exchange medium 3A flowing on the downstream side of the first heat exchange flow path 4A (the upper surface of the partition wall 20A) has a low temperature, but the second heat exchange medium 3A flowing on the upstream side of the second heat exchange flow path 4B (the lower surface of the partition wall 20A). Since the heat exchange medium 3B has a high temperature, it is possible to reliably prevent the first heat exchange medium 3A from freezing by positively transferring the heat of the second heat exchange medium 3B to the first heat exchange medium 3A. it can. The plurality of protrusions 21 increase the surface area of the partition wall 20A and promote heat exchange between the first heat exchange medium 3A and the second heat exchange medium 3B. If the plurality of protrusions 21 are high, a pressure loss occurs. For example, it is preferable that the protrusions 21 are densely arranged at a height of, for example, about 10 to 20 mm.

また、例えば、上記実施形態では、第１熱交換媒体３ＡとしてＥＧＷを例示したが、例えば海水を使用してもよい。   Further, for example, in the above embodiment, the EGW is illustrated as the first heat exchange medium 3A, but for example, seawater may be used.

また、例えば、上記実施形態では、第２熱交換媒体３Ｂとしてプロパンを例示したが、例えばブタンを使用してもよい。   Further, for example, in the above embodiment, propane is exemplified as the second heat exchange medium 3B, but for example, butane may be used.

また、例えば、上記実施形態では、流体２としてＬＮＧを例示したが、例えば液化石油ガス（ＬＰＧ）や液体窒素等を使用してもよい。   Further, for example, in the above embodiment, LNG is exemplified as the fluid 2, but for example, liquefied petroleum gas (LPG), liquid nitrogen, or the like may be used.

１ 熱交換器
２ 流体
３ 熱交換媒体
３Ａ 第１熱交換媒体
３Ｂ 第２熱交換媒体
３Ｂ１ 液面
４ 熱交換流路
４Ａ 第１熱交換流路
４Ｂ 第２熱交換流路
４Ｂ１ 底部
５ バッフルプレート
５Ｂ バッフルプレート
１０ 本体部
１１ 伝熱管
２０ 隔壁
３０ 第１熱交換媒体供給部
３１ 第１熱交換媒体循環流路
３２ 第１熱交換媒体加熱部
３３ バイパス流路
４０ 第２熱交換媒体供給部
４１ 第２熱交換媒体循環流路
５０ 気化器
５１ 貯溜部
５２ 水封板 REFERENCE SIGNS LIST 1 heat exchanger 2 fluid 3 heat exchange medium 3A first heat exchange medium 3B second heat exchange medium 3B1 liquid level 4 heat exchange flow path 4A first heat exchange flow path 4B second heat exchange flow path 4B1 bottom 5 baffle plate 5B Baffle plate 10 Main body 11 Heat transfer tube 20 Partition wall 30 First heat exchange medium supply section 31 First heat exchange medium circulation path 32 First heat exchange medium heating section 33 Bypass path 40 Second heat exchange medium supply section 41 Second Heat exchange medium circulation channel 50 Vaporizer 51 Storage unit 52 Water seal plate

Claims (6)

流体が流通する複数の伝熱管を収容する本体部と、
前記本体部の内部に形成された、前記複数の伝熱管の間を熱交換媒体が流通する熱交換流路を分割する隔壁と、
前記隔壁によって分割された前記熱交換流路のうち、前記複数の伝熱管の下流側の第１熱交換流路に、第１凝固点を有する第１熱交換媒体を供給する第１熱交換媒体供給部と、
前記隔壁によって分割された前記熱交換流路のうち、前記複数の伝熱管の上流側の第２熱交換流路に、前記第１凝固点よりも低い第２凝固点を有する第２熱交換媒体を供給する第２熱交換媒体供給部と、
前記第２熱交換流路における熱交換によって凝縮した前記第２熱交換媒体を気化させる気化器と、を有し、
前記第２熱交換媒体供給部は、前記気化器によって気化した前記第２熱交換媒体を、再び前記第２熱交換流路に供給する第２熱交換媒体循環流路を有する、ことを特徴とする熱交換器。 A body that houses a plurality of heat transfer tubes through which the fluid flows,
A partition formed inside the main body, dividing a heat exchange channel through which a heat exchange medium flows between the plurality of heat transfer tubes,
A first heat exchange medium supply for supplying a first heat exchange medium having a first freezing point to a first heat exchange path downstream of the plurality of heat transfer tubes among the heat exchange paths divided by the partition. Department and
A second heat exchange medium having a second freezing point lower than the first freezing point is supplied to a second heat exchange passage upstream of the plurality of heat transfer tubes among the heat exchange passages divided by the partition. A second heat exchange medium supply unit,
A vaporizer for vaporizing the second heat exchange medium condensed by heat exchange in the second heat exchange flow path,
The second heat exchange medium supply unit has a second heat exchange medium circulation channel that supplies the second heat exchange medium vaporized by the vaporizer to the second heat exchange channel again. Heat exchanger. 前記気化器は、
前記凝縮した前記第２熱交換媒体を貯溜する貯溜部と、
前記貯溜部に貯溜された前記第２熱交換媒体の液面に挿し込まれ、前記気化した前記第２熱交換媒体の前記第２熱交換流路への逆流を阻止する水封板と、を有する、ことを特徴とする請求項１に記載の熱交換器。 The vaporizer comprises:
A storage unit for storing the condensed second heat exchange medium,
A water sealing plate that is inserted into the liquid surface of the second heat exchange medium stored in the storage unit and that prevents the vaporized second heat exchange medium from flowing back into the second heat exchange channel. The heat exchanger according to claim 1 , comprising: 前記気化器は、前記第２熱交換流路の底部に接続されており、
前記第２熱交換流路は、前記第２熱交換媒体を回流させると共に、前記凝縮した前記第２熱交換媒体を前記底部に導く傾斜を備える複数のバッフルプレートを有する、ことを特徴とする請求項１または２に記載の熱交換器。 The vaporizer is connected to a bottom of the second heat exchange channel,
Wherein said second heat exchange passage is that causes flow round the second heat exchange medium, having a plurality of baffle plates with a slope for guiding the condensed second heat exchange medium to the bottom, it is characterized by Item 3. The heat exchanger according to item 1 or 2 . 前記第１熱交換媒体供給部は、
前記第１熱交換流路において熱交換した後の前記第１熱交換媒体を、再び前記第１熱交換流路に供給する第１熱交換媒体循環流路と、
前記第１熱交換媒体循環路において前記第１熱交換媒体を加熱する第１熱交換媒体加熱部と、
前記第１熱交換媒体加熱部によって加熱された前記第１熱交換媒体の一部を、前記第２熱交換媒体を気化させる熱交換媒体として前記気化器に供給するバイパス流路と、を有する、ことを特徴とする請求項１〜３のいずれか一項に記載の熱交換器。 The first heat exchange medium supply unit includes:
A first heat exchange medium circulation flow path that supplies the first heat exchange medium after heat exchange in the first heat exchange flow path to the first heat exchange flow path again;
A first heat exchange medium heating unit that heats the first heat exchange medium in the first heat exchange medium circulation path;
A bypass flow path that supplies a part of the first heat exchange medium heated by the first heat exchange medium heating unit to the vaporizer as a heat exchange medium that vaporizes the second heat exchange medium, The heat exchanger according to claim 1 , wherein: 前記隔壁は、前記第１熱交換流路及び前記第２熱交換流路の少なくともいずれか一方に突出し、前記第１熱交換媒体と前記第２熱交換媒体との伝熱を促進させる突起部を有する、ことを特徴とする請求項１〜４のいずれか一項に記載の熱交換器。 The partition wall projects to at least one of the first heat exchange flow path and the second heat exchange flow path, and includes a protrusion that promotes heat transfer between the first heat exchange medium and the second heat exchange medium. The heat exchanger according to any one of claims 1 to 4 , comprising: 流体が流通する複数の伝熱管を収容する本体部と、A body that houses a plurality of heat transfer tubes through which the fluid flows,
前記本体部の内部に形成された、前記複数の伝熱管の間を熱交換媒体が流通する熱交換流路を分割する隔壁と、A partition formed inside the main body, dividing a heat exchange channel through which a heat exchange medium flows between the plurality of heat transfer tubes,
前記隔壁によって分割された前記熱交換流路のうち、前記複数の伝熱管の下流側の第１熱交換流路に、第１凝固点を有する第１熱交換媒体を供給する第１熱交換媒体供給部と、A first heat exchange medium supply for supplying a first heat exchange medium having a first freezing point to a first heat exchange path downstream of the plurality of heat transfer tubes among the heat exchange paths divided by the partition. Department and
前記隔壁によって分割された前記熱交換流路のうち、前記複数の伝熱管の上流側の第２熱交換流路に、前記第１凝固点よりも低い第２凝固点を有する第２熱交換媒体を供給する第２熱交換媒体供給部と、を有し、A second heat exchange medium having a second freezing point lower than the first freezing point is supplied to a second heat exchange passage upstream of the plurality of heat transfer tubes among the heat exchange passages divided by the partition. A second heat exchange medium supply unit,
前記隔壁は、前記第１熱交換流路及び前記第２熱交換流路の少なくともいずれか一方に突出し、前記第１熱交換媒体と前記第２熱交換媒体との伝熱を促進させる突起部を有する、ことを特徴とする熱交換器。The partition wall projects to at least one of the first heat exchange flow path and the second heat exchange flow path, and includes a protrusion that promotes heat transfer between the first heat exchange medium and the second heat exchange medium. A heat exchanger comprising:
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