JP7506217B2 - All secondary air-cooled industrial steam condensers - Google Patents
All secondary air-cooled industrial steam condensers Download PDFInfo
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- 239000007789 gas Substances 0.000 claims description 15
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28B—STEAM OR VAPOUR CONDENSERS
- F28B1/00—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser
- F28B1/06—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser using air or other gas as the cooling medium
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
- F28D1/0426—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with units having particular arrangement relative to the large body of fluid, e.g. with interleaved units or with adjacent heat exchange units in common air flow or with units extending at an angle to each other or with units arranged around a central element
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2339/00—Details of evaporators; Details of condensers
- F25B2339/04—Details of condensers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
- F25B39/04—Condensers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28B—STEAM OR VAPOUR CONDENSERS
- F28B1/00—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser
- F28B1/06—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser using air or other gas as the cooling medium
- F28B2001/065—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser using air or other gas as the cooling medium with secondary condenser, e.g. reflux condenser or dephlegmator
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F2009/0285—Other particular headers or end plates
- F28F2009/0287—Other particular headers or end plates having passages for different heat exchange media
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Description
本発明は、大規模現場組立型空冷式産業用蒸気復水器に関する。 The present invention relates to a large-scale, on-site assembled, air-cooled industrial steam condenser.
大部分の大規模現場組立型空冷式産業用蒸気復水器（「ＡＣＣ」）に使用される現在のフィン付き管は、長さ約１１メートル×幅２００ｍｍ（「空気移動長さ」とも称される）で、半円形の前縁および後縁を有し、また１８．８ｍｍの内部高さ（空気移動長さに垂直）を有する平坦な管を使用する。管壁の厚さは１．３５ｍｍである。フィンは、各管の両側の平らな側面にろう付けされる。フィンは、通常１８．５ｍｍの高さで、１インチ（２５．４ｍｍ）あたりフィンが１１枚の間隔である。フィン表面は、熱伝達を促進し、フィン剛性を支援するために波状のパターンを有する。管の中心間の標準間隔は５７．２ｍｍである。管自体は、断面面積（ｃｒｏｓｓ ｓｅｃｔｉｏｎａｌ ｆａｃｅ ａｒｅａ）（空気流れ方向に対して垂直な）の約３分の１を構成する一方、フィンは断面面積（ｃｒｏｓｓ ｓｅｃｔｉｏｎ ｆａｃｅ ａｒｅａ）のほぼ３分の２を占める。隣接するフィン先端の間に１．５ｍｍの小さなスペースが存在する。夏季の周囲条件では、管を通過する最大蒸気速度は、典型的には２８ｍｐｓほど高く、より典型的には２３～２５ｍｐｓである可能性がある。これらの管とフィンとを組み合わせた単一のＡ字型フレーム設計は、管の長さ、フィンの間隔、フィンの高さと形状、および空気移動長さに基づいて最適化されてきた。フィン付き管は、典型的には熱交換器管束あたり３９本の管の熱交換器管束へと組み立てられ、ファンあたり１０～１４個の管束が単一のＡ字型フレーム内に一緒に配列された２つの熱交換器へと配置される。ファンは、典型的にはＡ字型フレームの下部に存在し、管束を通して上向きに空気を強制通風する。管とフィンの全体的な設計と、管とフィンの組み合わせによる空気圧低下も、２００～２５０馬力で動作する大口径（３６フィート（１０．９メートル））のファンの空気移動能力に適合するように最適化されてきた。この最適化された配置は、２０年以上も前に単列楕円管の概念が導入されて以来、多くの異なる製造業者にわたってあまり変化していない。 Current finned tubes used in most large-scale field-assembled air-cooled industrial steam condensers ("ACC") use flat tubes approximately 11 meters long by 200 mm wide (also referred to as the "air travel length"), with semicircular leading and trailing edges, and with an internal height (perpendicular to the air travel length) of 18.8 mm. The tube wall thickness is 1.35 mm. The fins are brazed to the flat sides on both sides of each tube. The fins are typically 18.5 mm high and spaced 11 fins per inch (25.4 mm). The fin surface has a wavy pattern to promote heat transfer and aid fin stiffness. The standard spacing between tube centers is 57.2 mm. The tubes themselves make up approximately one third of the cross sectional face area (perpendicular to the air flow direction), while the fins take up nearly two thirds of the cross sectional face area. There is a small space of 1.5 mm between adjacent fin tips. At ambient summer conditions, the maximum steam velocity through the tubes can typically be as high as 28 mps, more typically 23-25 mps. These combined tube and fin single A-frame designs have been optimized based on tube length, fin spacing, fin height and shape, and air transfer length. The finned tubes are typically assembled into heat exchanger bundles of 39 tubes per bundle, with two heat exchangers arranged together in a single A-frame with 10-14 tube bundles per fan. The fan is typically located at the bottom of the A-frame and forces air upwards through the tube bundle. The overall tube and fin design and the air pressure drop through the tube/fin combination have also been optimized to match the air movement capabilities of large diameter (36 ft (10.9 m)) fans operating at 200-250 horsepower. This optimized arrangement has not changed significantly across many different manufacturers since the single row elliptical tube concept was introduced over 20 years ago.
上述の典型的なＡ字型フレームＡＣＣは、第１段または「一次」復水器管束と第２段または「二次」管束との両方を含む。熱交換器管束の約８０％～９０％は第１段または一次復水器管束である。蒸気は一次復水器管束の頂部に入り、復水と一部の蒸気が底部から出される。第１段構成は熱効率が良好であるが、非凝縮性ガスを除去する手段が提供されない。第１段の管束を通る非凝縮性ガスを一掃するために、熱交換器管束の１０％～２０％は第２段または二次管束として構成され、典型的には一次管束の間に点在し、下部復水マニホールドからベイパーを吸引する。この配置では、蒸気および非凝縮性ガスは、それらが二次管束の底部に引き込まれるときに第１段の管束を通って進む。ガスの混合物が二次管束を通って上昇するにつれて、残りの蒸気は凝縮し、非凝縮性ガスを濃縮する。二次管束の頂部は、システムから非凝縮性ガスを除去する真空マニホールドに取り付けられる。 A typical A-frame ACC, as described above, includes both a first stage or "primary" condenser tube bundle and a second stage or "secondary" tube bundle. Approximately 80%-90% of the heat exchanger tube bundle is the first stage or primary condenser tube bundle. Steam enters the top of the primary condenser tube bundle, and condensate and some steam exit at the bottom. The first stage configuration is thermally efficient, but does not provide a means to remove non-condensable gases. To sweep the non-condensable gases through the first stage tube bundle, 10%-20% of the heat exchanger tube bundle is configured as a second stage or secondary tube bundle, typically interspersed between the primary tube bundles, and aspirates vapors from the lower condensate manifold. In this arrangement, steam and non-condensable gases travel through the first stage tube bundle as they are drawn into the bottom of the secondary tube bundle. As the gas mixture rises through the secondary tube bundle, the remaining steam condenses, concentrating the non-condensable gases. The top of the secondary bundle is attached to a vacuum manifold that removes non-condensable gases from the system.
標準的な先行技術のＡＣＣ配置に対する変形例は、例えば米国特許出願公開第２０１５／０２０４６１１号および同第２０１５／０３３０７０９号に開示されている。これらの明細書は、同一のフィン付き管を示すが、管の長さが大幅に短縮されたもので、一連の小さなＡ字型フレーム、典型的にはファンあたり５つのＡ字型フレームに配置されている。この論理の一部は、蒸気圧力降下を低減することであり、夏季における全容量に及ぼす影響は小さいが、冬季の条件ではより大きな影響を与える。この論理の別の一部は、工場において管束の各々に頂部蒸気マニホールドダクトを溶接してこれらを一緒に出荷し、高価な現場での溶接作業を省くことである。工場で取り付けられ、管束と共に出荷される蒸気マニホールドを用いたこの配置の正味の効果は、標準的なハイキューブ輸送コンテナ内のマニホールドに適合するように管の長さを短縮することである。管がより短く、従って表面積の総量が減少するため、夏季の条件においては、類似の全体的な寸法の標準単一Ａ字型フレーム設計に対する比較容量は約３％減少する。 Variations to the standard prior art ACC arrangement are disclosed, for example, in US Patent Application Publication Nos. 2015/0204611 and 2015/0330709. These specifications show the same finned tubes, but with a greatly reduced tube length, arranged in a series of small A-frames, typically five A-frames per fan. Part of the logic is to reduce steam pressure drop, which has a small effect on total capacity in summer but a larger effect in winter conditions. Another part of the logic is to weld a top steam manifold duct to each of the tube bundles at the factory and ship them together, eliminating expensive on-site welding operations. The net effect of this arrangement, with steam manifolds installed at the factory and shipped with the tube bundle, is to reduce the tube length to fit the manifolds in a standard high cube shipping container. Because the tubes are shorter and therefore the total amount of surface area is reduced, the comparative capacity is reduced by about 3% in summer conditions for a standard single A-frame design of similar overall dimensions.
本明細書に提示される発明は、１）大規模現場組立型産業用蒸気復水器を含むがこれに限定されない、熱交換器システムで使用するための新規な管設計と、２）発電所等のための大規模現場組立型産業用蒸気復水器の新規な設計とを含み、その両方とも、ＡＣＣの熱容量を著しく増大させる一方、いくつかの構成では材料を低減する。本発明の様々な態様および／または実施形態を以下に示す。 The inventions presented herein include 1) novel tube designs for use in heat exchanger systems, including but not limited to large-scale field-assembled industrial steam condensers, and 2) novel designs of large-scale field-assembled industrial steam condensers for power plants and the like, both of which significantly increase the thermal capacity of the ACC while reducing material in some configurations. Various aspects and/or embodiments of the invention are presented below.
管設計発明の様々な実施形態によれば、管は長さ２．０４４ｍであり、管の断面寸法は１００～２００ｍｍ幅、好ましくは１２５ｍｍ幅（空気移動長さ）であると共に、断面高さ（空気移動長さに垂直）は１０ｍｍ未満、好ましくは４～１０ｍｍ、より好ましくは５．０～９ｍｍ、さらにより好ましくは５．２～７ｍｍ、最も好ましくは６．０ｍｍの高さ（「外側管幅」とも呼ばれる）であり、１インチ（２５．４ｍｍ）あたりのフィンの数が９～１２枚、好ましくは９．８枚で配置されたフィンを有する。さらに好ましい実施形態によれば、実際のフィンは、高さが１７～２０ｍｍ、好ましくは高さが１８．５ｍｍであり、２本の隣接する管の間の空間にまたがり、効果的に９．２５ｍｍのフィンを各管に対してそれぞれの側で利用できるようにする。 According to various embodiments of the tube design invention, the tube is 2.044m long, the cross-sectional dimensions of the tube are 100-200mm wide, preferably 125mm wide (air travel length), and the cross-sectional height (perpendicular to the air travel length) is less than 10mm, preferably 4-10mm, more preferably 5.0-9mm, even more preferably 5.2-7mm, most preferably 6.0mm high (also called "outer tube width"), with fins arranged at 9-12 fins per inch (25.4mm), preferably 9.8 fins per inch. According to a further preferred embodiment, the actual fins are 17-20mm high, preferably 18.5mm high, spanning the space between two adjacent tubes, effectively allowing 9.25mm of fins to be available on each side for each tube.
より小さな断面の管（空気移動長さは同じであるが、高さが顕著により小さい）を製造することは、大規模な発電所によって出力される膨大な蒸気量に対応するために、できる限り大きな断面で管を製造する必要があり、管のサイズが大きくなるほどコストが下がるという当該技術分野における現行の支配的な見解に直接的に反している。この配置のコストは先行技術の管配置よりもはるかに大きいが、本発明者らは予期しないことに、より低い高さの管を用いることによる効率増加は（最も好ましい実施形態では、先行技術の管と比較して効率が３０％超より高い）、コストの増加を埋め合わせるに留まらないことを発見した。この新規な管設計は、先行技術の大規模現場組立型産業用蒸気復水器（例えば、背景技術の項で説明したような）に使用されてもよく、または本明細書で後述する新規なＡＣＣ設計と併せて使用されてもよい。 Producing smaller cross-section tubes (same air movement length but significantly smaller height) directly contradicts the current prevailing view in the art that tubes must be manufactured with as large a cross-section as possible to accommodate the enormous steam volumes output by large power plants, and that the larger the tube size, the lower the cost. Although the cost of this arrangement is much greater than prior art tube arrangements, the inventors unexpectedly discovered that the increased efficiency of using the lower height tubes (in the most preferred embodiment, over 30% higher efficiency compared to prior art tubes) more than offsets the increased cost. This novel tube design may be used in prior art large scale field assembled industrial steam condensers (e.g., as described in the Background section) or in conjunction with the novel ACC design described later in this specification.
次に、大規模現場組立型産業用蒸気復水器の新規な設計を検討してみるが、本発明の主な特徴は、本発明によるＡＣＣの全ての管束が二次管束として構築され、その中では蒸気は、底部から上向きに配向された管（管束の横断方向軸と平行に整列され、各管は概して２５°～３５°、好ましくは垂直から３０°に配向される）に供給され、復水は管束からは底部から回収され、好ましくは管への蒸気の送達と管からの復水の回収との両方を行う統合／ハイブリッドマニホールドを使用して回収される。一実施形態によれば、統合／ハイブリッドマニホールドは、復水が蒸気送達ライザー（複数可）を下降するのを阻止し、その代わりに統合／ハイブリッドマニホールドに接続された復水回収管に送達されるように構築されてもよい。代替的な実施形態によれば、復水は蒸気送達ライザーを下降することができ、地面により近い蒸気送達ダクトから除去されるように、統合／ハイブリッドマニホールドが構築されてもよい。管の頂部は、非凝縮性ガスを回収するための別個のマニホールドに接続されている。この新規な「全てが二次の」ＡＣＣ構成は、Ａ字型フレームで、管から非凝縮性ガスを集める単一のマニホールドを有する頂部で結合された２つの二次管束を有して、または各管束の頂部に１つずつの２つの非凝縮性マニホールドを有して構成されてもよい。 Considering now the novel design of a large scale field assembled industrial steam condenser, the main feature of the invention is that all tube bundles of the ACC according to the invention are constructed as secondary tube bundles in which steam is supplied to tubes oriented upwards from the bottom (aligned parallel to the transverse axis of the tube bundle, each tube generally oriented at 25°-35°, preferably 30° from vertical) and condensate is collected from the tube bundle from the bottom, preferably using an integrated/hybrid manifold that both delivers steam to the tubes and collects condensate from the tubes. According to one embodiment, the integrated/hybrid manifold may be constructed to prevent condensate from going down the steam delivery riser(s) and instead deliver it to a condensate collection pipe connected to the integrated/hybrid manifold. According to an alternative embodiment, the integrated/hybrid manifold may be constructed to allow condensate to go down the steam delivery riser and be removed from the steam delivery duct closer to the ground. The tops of the tubes are connected to a separate manifold for collecting non-condensable gases. This new "all secondary" ACC configuration may be configured with two secondary tube bundles joined at the top with a single manifold that collects non-condensable gases from the tubes in an A-frame, or with two non-condensable manifolds, one on top of each tube bundle.
本明細書で使用される場合、用語「全てが二次の」および「一次がない」は、全ての管束が底部から水蒸気を受け取り、底部において復水を回収し、非凝縮性ガスを上部から送達する大規模現場組立型空冷式産業用蒸気復水器を指す。比較すると、大規模現場組立型空冷式産業用蒸気復水器における一次管束は上部で蒸気を受け取り、底部で復水を送達し、また底部で別個の二次復水器に非凝縮ガスを送達する。 As used herein, the terms "all secondary" and "no primary" refer to a large-scale field-assembled, air-cooled industrial steam condenser in which all tube bundles receive steam from the bottom, collect condensate at the bottom, and deliver non-condensable gases from the top. In comparison, the primary tube bundles in a large-scale field-assembled, air-cooled industrial steam condenser receive steam at the top, deliver condensate at the bottom, and deliver non-condensable gases to a separate secondary condenser at the bottom.
しかし、好ましくは、本発明のＡＣＣはＶ字構成で配置されてもよく、その中で２つの二次専用コンデンサ束が底部で単一の統合蒸気分配マニホールド／復水回収マニホールドと接続され、別個の非凝縮物回収マニホールドを各管束の頂部に有している。 However, preferably, the ACC of the present invention may be arranged in a V-configuration in which two secondary-only condenser bundles are connected at the bottom with a single integrated steam distribution manifold/condensate return manifold and have separate non-condensable return manifolds at the top of each tube bundle.
好ましいＶ字構成の実施形態によれば、蒸気マニホールドは管束の底部に存在するため、２つ以上の位置でマニホールドに入ることでマニホールドのサイズが小さくなり、フィン付き管を少し長くすることができる。本明細書に記載のより小さい断面の管（２００ｍｍ×高さ１０ｍｍ未満、好ましくは４～１０ｍｍ、より好ましくは５．０～９ｍｍ、さらにより好ましくは５．２～７ｍｍ、最も好ましくは６．０ｍｍ）と組み合わせると、システムは、上述した標準的なＡＣＣ配置および構成に対して、少なくとも２５％～３０％の改善された性能を示し、ユニットは、床面積の点でも同様な量だけ小さくできる場合がある。 According to the preferred V-configuration embodiment, the steam manifold is at the bottom of the tube bundle, so entering the manifold at two or more locations reduces the size of the manifold and allows for a slightly longer finned tube. When combined with the smaller cross-section tubes described herein (less than 200mm x 10mm height, preferably 4-10mm, more preferably 5.0-9mm, even more preferably 5.2-7mm, most preferably 6.0mm), the system shows at least 25%-30% improved performance over the standard ACC arrangement and configuration described above, and the unit may be smaller in floor space by a similar amount.
さらなる代替的な実施形態によれば、本発明の新規なＡＣＣ設計は、１００ｍｍ×、好ましくは４～１０ｍｍ、より好ましくは５．０～９ｍｍ、さらにより好ましくは５．２～７ｍｍの寸法を有し、最も好ましくは６．０ｍｍの高さの管と共に、オフセットフィンを有して、使用されてもよい。 According to a further alternative embodiment, the novel ACC design of the present invention may be used with a tube having dimensions of 100 mm x, preferably 4-10 mm, more preferably 5.0-9 mm, even more preferably 5.2-7 mm, and most preferably 6.0 mm high, with offset fins.
さらなる実施形態によれば、本発明の新規なＡＣＣ設計は、１インチ（２５．４ｍｍ）あたりフィンが９．８枚配置された「アローヘッド」タイプのフィンを有する１２０ｍｍまたは最大２００ｍｍ×５ｍｍ～７ｍｍの管で使用されてもよい。 According to further embodiments, the novel ACC design of the present invention may be used with 120mm or up to 200mm x 5mm-7mm tubes with "arrowhead" type fins arranged at 9.8 fins per inch (25.4mm).
さらに別の実施形態によれば、本発明の新規なＡＣＣ設計は、オフセットフィンとほぼ同様に機能する「ルーバー」フィンを有する管と共に使用されてもよく、より容易に入手可能で製造が容易となる。 According to yet another embodiment, the novel ACC design of the present invention may be used with tubes having "louver" fins that function much like offset fins, but are more readily available and easier to manufacture.
最も好ましいＡＣＣ構成と最も好ましい管寸法とを組み合わせた本発明の好ましい実施形態および最も好ましい実施形態によれば、本発明のＡＣＣは、以下の特徴及び寸法を有する：
一次管束はなく、全てが二次の管束（全ての管は底部から蒸気を受け、復水を底部を通して分配し、非凝縮性ガスを頂部から外へ分配する）、
セル／ファンあたり４つ、５つ（最も好ましい）または６つのＶ字型の管束の対
管の外径４～１０ｍｍ（好ましくは５～７ｍｍ、最も好ましくは６．０ｍｍ）×１００～２００ｍｍ（最も好ましくは１２５ｍｍ）の断面、
管中心間の間隔が２０～２９ｍｍ（最も好ましくは２４．５ｍｍ）、
管壁の厚さ０．７～０．９ｍｍ（最も好ましくは０．８ｍｍ）、
管束あたりの管数＝４０～６０（最も好ましくは５０）、
管の長さ１，７００～２，４００ｍｍ（最も好ましくは２，０４４ｍｍ）、
隣接する管の間にまたがり両方の管に熱的に接続されているアローヘッドフィン（好ましいが、要件ではない）、
フィン高さ１７～１９（最も好ましくは１８．５ｍｍ（有効高さは管の片側あたり９．２５ｍｍ））、
空気移動長さのフィン９５ｍｍ～１９５ｍｍ、最も好ましくは１２０ｍｍ。
According to the preferred and most preferred embodiment of the present invention, which combines the most preferred ACC configuration with the most preferred tube dimensions, the ACC of the present invention has the following characteristics and dimensions:
There are no primary tube bundles, all are secondary (all tubes receive steam from the bottom, distribute condensate through the bottom, and distribute non-condensable gases out the top),
4, 5 (most preferred) or 6 V-shaped tube bundle pairs per cell/fan Tube outer diameter 4-10mm (preferably 5-7mm, most preferred 6.0mm) x 100-200mm (most preferred 125mm) cross section;
Tube center-to-center spacing of 20-29 mm (most preferably 24.5 mm);
Tube wall thickness: 0.7-0.9 mm (most preferably 0.8 mm);
Number of tubes per bundle = 40-60 (most preferably 50);
Tube length 1,700-2,400 mm (most preferably 2,044 mm),
Arrowhead fins spanning adjacent tubes and thermally connected to both tubes (preferred, but not required);
Fin height 17-19 (most preferably 18.5 mm (effective height 9.25 mm per side of tube));
Air movement length of fins 95mm to 195mm, most preferably 120mm.
この最も好ましい実施形態によれば、総ファン出力、蒸気量、および熱条件が同一である先行技術のＡＣＣに対する管束面の総面積は７９％であり、同様に、この最も好ましい実施形態の総床面積は、総ファン出力、蒸気量、および熱条件が同一である先行技術のＡＣＣの面積の７９％である。 According to this most preferred embodiment, the total tube bundle surface area is 79% of that of a prior art ACC with the same total fan power, steam volume, and thermal conditions, and similarly, the total floor area of this most preferred embodiment is 79% of that of a prior art ACC with the same total fan power, steam volume, and thermal conditions.
さらに、本発明のＡＣＣ設計は、より容易に設置することができ、発電所内の必要とされる全体のスペースをより小さくすることができる。 Additionally, the ACC design of the present invention is easier to install and requires less overall space within the power plant.
（全てが二次の管束を有するＡフレームＡＣＣ） (All A-frame ACC with secondary tube bundles)
図２を参照すると、管２は二次管束４に配置されている。管２の長手方向軸は、管束の横断方向軸と平行に整列され、各管は概して垂直から２５°～３５°、好ましくは３０°に配向されている。統合蒸気分配／凝縮回収マニホールド６は、Ａフレーム構成でその頂部で結合されている２つの二次管束４の各々の底部に取り付けられている。蒸気は、統合蒸気分配／復水回収マニホールド６を介して管２に分配され、蒸気が凝縮すると管２内に復水を形成し、管２を下降して統合蒸気分配／復水回収マニホールド６に流入する。単一の非凝縮物回収マニホールド８が、管２の頂部に移動する非凝縮性ガスを集めるために、両方の管束６の頂部に取り付けられている。蒸気は、ライザー１２を介して蒸気ダクト１０から統合蒸気分配／復水回収マニホールド６に供給される。統合蒸気分配／復水回収マニホールド６に集まる凝縮水は、復水回収管１４内でＡＣＣから運び去られる。
Referring to FIG. 2, the
図３は、図２の実施形態と非常に類似した実施形態を示しているが、ただし各管束４はその頂部で専用の非凝縮物回収マニホールドに取り付けられている。
Figure 3 shows an embodiment very similar to that of Figure 2, except that each
（全てが二次の管束を有するＶ字型ＡＣＣ） (V-shaped ACC with all secondary tube bundles)
図４Ａおよび図４Ｂを参照すると、管２は二次管束４に配置されている。管２の長手方向軸は、管束の横断方向軸と平行に、各管は概して垂直から２５°～３５°、好ましくは３０°に配向されている。２つの二次管束４の底部には、Ｖ字構成で５５°～６５°、好ましくは６０°の角度で結合された統合蒸気分配／復水回収マニホールド６が取り付けられている。蒸気は、統合蒸気分配／復水回収マニホールド６を介して管２に分配され、蒸気が凝縮して管２内に復水を形成し、管２を下降して統合蒸気分配／復水集合マニホールド６の中へと入る。非凝縮物回収マニホールド８が両方の管束６の頂部に取り付けられて、管２の頂部に移動する非凝縮性ガスを回収する。蒸気は、ライザー１２を介して蒸気ダクト１０から統合蒸気分配／復水回収マニホールド６に供給される。統合蒸気分配／復水回収マニホールド６に回収された凝縮水は、復水回収管１４内でＡＣＣから運び去られる。
Referring to Figures 4A and 4B, the
上述の新規なＡＣＣ設計は、長さ約１１メートル、幅２００ｍｍ（または「空気移動長さ」）で半円形の先端と後端を有し、且つ内部高さ（空気移動長さに垂直）が１８．８ｍｍで管壁の厚さが１．３５ｍｍであり、各管の両方の平らな側面にろう付けされたフィンであって、通常、１８．５ｍｍの高さで、１インチ（２５．４ｍｍ）あたりフィンが１１枚の間隔であるフィンを有する図５に示された管を含む任意の先行技術の管にも使用されてもよい。しかし、より好ましい実施形態によれば、本発明の新規なＡＣＣ設計は、以下の特徴および寸法を有する：
一次管束はなく、全てが二次の管束（全ての管は底部から蒸気を受け、復水を底部から分配し、非凝縮性ガスを頂部から外へ分配する）、
セル／ファンあたり４つ、５つ（最も好ましい）または６つのＶ字型の管束の対、
管の外径４～１０ｍｍ（好ましくは５～７ｍｍ、最も好ましくは６．０ｍｍ）×１００～２００ｍｍ（最も好ましくは１２５ｍｍ）の断面、
管中心間隔が２０～２９ｍｍ（最も好ましくは２４．５ｍｍ）、
管壁の厚さ０．７～０．９ｍｍ（最も好ましくは０．８ｍｍ）
管束あたりの管数＝４０～６０（最も好ましくは５０）
管の長さ１，７００～２，４００ｍｍ（最も好ましくは２，０４４ｍｍ）
隣接する管の間にまたがり両方の管に熱的に接続されているアローヘッドフィン（好ましいが、要件ではない）
フィン高さ１８．５ｍｍ（有効高さは管の片側あたり９．２５ｍｍ）、
空気移動長さフィン９５ｍｍ～１９５ｍｍ、最も好ましくは１２０ｍｍ。
この好ましい実施形態によれば、２５～３０％の容量増加が、一定のファン出力で単一のセルに対して、標準的な管を用いた先行技術のＡ字形フレーム設計を上回って提供される。
The novel ACC design described above may also be used with any prior art tube including the tube shown in Figure 5 which is approximately 11 meters long, 200 mm wide (or "air travel length"), with semi-circular leading and trailing ends, and has an internal height (perpendicular to the air travel length) of 18.8 mm and a tube wall thickness of 1.35 mm, with fins brazed to both flat sides of each tube, typically 18.5 mm high and spaced 11 fins per inch (25.4 mm). However, according to a more preferred embodiment, the novel ACC design of the present invention has the following features and dimensions:
There are no primary tube bundles, all are secondary tube bundles (all tubes receive steam from the bottom, distribute condensate from the bottom, and distribute non-condensable gases out the top),
4, 5 (most preferred) or 6 V-shaped tube bundle pairs per cell/fan;
Tube outer diameter 4-10 mm (preferably 5-7 mm, most preferably 6.0 mm) x cross section 100-200 mm (most preferably 125 mm);
Tube center spacing is 20 to 29 mm (most preferably 24.5 mm);
Tube wall thickness: 0.7-0.9 mm (most preferably 0.8 mm)
Number of tubes per bundle = 40-60 (most preferably 50)
Pipe length: 1,700-2,400 mm (most preferably 2,044 mm)
Arrowhead fins spanning adjacent tubes and thermally connected to both tubes (preferred, but not required)
Fin height 18.5 mm (effective height 9.25 mm per side of tube),
Air movement length fin 95mm to 195mm, most preferably 120mm.
This preferred embodiment provides a 25-30% increase in capacity for a single cell at a given fan power over prior art A-frame designs using standard tubes.
図８～図１０は、図４Ａに示されたＶ字型の二次熱交換管束の対のみを有する、本発明の実施形態による代表的な大規模現場組立型空冷式産業用蒸気復水器を示す。図８～図１０に示す装置は、３６セル（６ストリート×６セル）のＡＣＣであり、セルあたり５つの管束対の最も好ましい実施形態であるが、本発明は、任意のサイズのＡＣＣで使用されてもよく、また１セルあたり任意の数の管束対を用いてもよい。 FIGS. 8-10 show a representative large-scale field-assembled, air-cooled industrial steam condenser according to an embodiment of the present invention having only the V-shaped secondary heat exchange tube bundle pairs shown in FIG. 4A. The apparatus shown in FIGS. 8-10 is a 36-cell (6 streets by 6 cells) ACC with a most preferred embodiment of 5 tube bundle pairs per cell, but the present invention may be used with any size ACC and with any number of tube bundle pairs per cell.
Claims (11)
Ａ字型またはＶ字型の構成に配置された複数の復水器管束の対を備え、各復水器管束は、互いに隣接して適合されたフィン付き扁平単一チャネル管の単一列を含み、
各復水器管束の対が底端部で取り付けられており、前記フィン付き扁平単一チャネル管の底部に蒸気を送給すること、および前記フィン付き扁平単一チャネル管内で冷却されると前記蒸気から形成される復水を回収することの両方のために構成された前記復水器管束の対の長さに沿って延在する、統合蒸気分配－復水回収マニホールドを備え、
各復水器管束がその頂端部で取り付けられており、前記統合蒸気分配－復水回収マニホールドの各々に対して平行な前記復水器管束の長さに沿って延在し、前記蒸気から非凝縮性ガスを回収するように構成される、非復水回収マニホールドを備え、
前記空冷式産業用蒸気復水器は、前記復水器管束の下方に延在する蒸気ダクトを含み、前記蒸気ダクトは、前記復水器管束の長手方向軸に対して垂直な長手方向軸を有し、前記統合蒸気分配－復水回収マニホールドの底面に接続され、
前記復水器管束に送給される蒸気の全てが前記統合蒸気分配－復水回収マニホールドを経由して送給される、空冷式産業用蒸気復水器。 1. An air-cooled industrial steam condenser comprising:
a plurality of condenser tube bundle pairs arranged in an A -shaped or V-shaped configuration, each condenser tube bundle including a single row of finned flattened single channel tubes fitted adjacent one another ;
each condenser tube bundle pair is attached at a bottom end thereof and includes an integrated steam distribution-condensate return manifold extending along the length of the condenser tube bundle pair configured for both delivering steam to the bottom of the finned flattened single-channel tubes and for recovering condensate formed from the steam as it is cooled within the finned flattened single-channel tubes;
a non-condensing recovery manifold attached to each condenser tube bundle at a top end thereof and extending along a length of the condenser tube bundle parallel to each of the integrated steam distribution-condensing recovery manifolds and configured to recover non-condensable gases from the steam;
the air-cooled industrial steam condenser includes a steam duct extending below the condenser tube bundle, the steam duct having a longitudinal axis perpendicular to a longitudinal axis of the condenser tube bundle and connected to a bottom side of the integrated steam distribution and condensate return manifold;
An air- cooled industrial steam condenser, wherein all of the steam delivered to said condenser tube bundle is delivered through said integrated steam distribution and condensate return manifold.
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| US15/629,205 US20170363358A1 (en) | 2016-06-21 | 2017-06-21 | All-secondary air cooled industrial steam condenser |
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| RU2018144943A (en) | 2020-07-23 |
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| PL3472545T3 (en) | 2022-02-21 |
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