WO2010106699A1 - 熱交換器 - Google Patents
熱交換器 Download PDFInfo
- Publication number
- WO2010106699A1 WO2010106699A1 PCT/JP2009/063965 JP2009063965W WO2010106699A1 WO 2010106699 A1 WO2010106699 A1 WO 2010106699A1 JP 2009063965 W JP2009063965 W JP 2009063965W WO 2010106699 A1 WO2010106699 A1 WO 2010106699A1
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- WIPO (PCT)
- Prior art keywords
- heat exchanger
- heat transfer
- bare
- heat
- upstream
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
- F22B37/00—Component parts or details of steam boilers
- F22B37/02—Component parts or details of steam boilers applicable to more than one kind or type of steam boiler
- F22B37/40—Arrangements of partition walls in flues of steam boilers, e.g. built-up from baffles
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
- F22B1/00—Methods of steam generation characterised by form of heating method
- F22B1/02—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers
- F22B1/18—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23J—REMOVAL OR TREATMENT OF COMBUSTION PRODUCTS OR COMBUSTION RESIDUES; FLUES
- F23J13/00—Fittings for chimneys or flues
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23M—CASINGS, LININGS, WALLS OR DOORS SPECIALLY ADAPTED FOR COMBUSTION CHAMBERS, e.g. FIREBRIDGES; DEVICES FOR DEFLECTING AIR, FLAMES OR COMBUSTION PRODUCTS IN COMBUSTION CHAMBERS; SAFETY ARRANGEMENTS SPECIALLY ADAPTED FOR COMBUSTION APPARATUS; DETAILS OF COMBUSTION CHAMBERS, NOT OTHERWISE PROVIDED FOR
- F23M9/00—Baffles or deflectors for air or combustion products; Flame shields
- F23M9/003—Baffles or deflectors for air or combustion products; Flame shields in flue gas ducts
Definitions
- the present invention relates to a heat exchanger that makes a gas flow flowing in a heat exchanger uniform in a heat exchanger such as a heat recovery unit.
- a loop of a rear heat transfer section of a coal fired boiler provided with a rear heat transfer section connected to the rear side of the furnace via a sub-side wall and having a reheater and a superheater formed of a plurality of loop tubes inside.
- This is a pipe wear prevention device that flows in a substantially horizontal direction with a required width at the upper position of the bent end portion of the loop tube of the reheater and superheater on the heat transfer tube wall constituting the rear heat transfer unit.
- An erosion baffle projecting into a road is attached, and a coal ash circulation hole is formed on the entire surface of the erosion baffle (for example, Patent Document 2).
- drift prevention board in the upper part of the heat exchange tube of a boiler side wall is disclosed (for example, patent document 3).
- the horizontal elements are from the bare tube at the second stage from the top, and from the spiral fin tube at the second and lower stages to prevent wear and damage to the heat transfer tube from coal ash. Therefore, since a large amount of gas flows into the space between the end portion and the side wall tube and the tube in the vicinity thereof is damaged, a drift prevention plate is disclosed (for example, Patent Document 4).
- the present invention relates to an exhaust heat recovery device that recovers heat from exhaust gas etc. of a gas turbine, a front surface, a rear surface, and a side duct casing that form four surfaces, through which exhaust gas passes, and a flow direction of exhaust gas provided in the duct.
- the finned heat transfer tube group formed by a plurality of finned heat transfer tubes arranged in a direction orthogonal to the side duct casing and parallel to the longitudinal direction of the tube axis
- the finned heat transfer tube group What is provided with baffles that are fixed to the inner surfaces of the duct casings on both the exhaust gas upstream side and the wake side and that are formed so as to cover the ends of the finned heat transfer tube groups along the longitudinal direction of the tube axis is disclosed.
- Patent Document 5 proposes to cover the ends of the finned heat transfer tube groups along the longitudinal direction of the tube axis.
- Japanese Utility Model Publication No. 60-128017 Japanese Patent Laid-Open No. 11-110007 Japanese Patent Laid-Open No. 11-72202 JP 11-118101 A JP-A-9-137906
- the present invention has been made to solve the above-described problems, and an object of the present invention is to provide a heat exchanger that can greatly reduce drift.
- the present invention aims to solve the problems by using the following means.
- the heat exchanger of the first means is a heat exchange having a duct extension portion, a heat transfer tube bundle storage duct, and heat transfer tube bundles provided in a plurality of stages at intervals in the flow direction of the exhaust gas in the heat transfer tube bundle storage duct.
- a plurality of introduction portion rectifying plates provided in the heat transfer tube bundle housing duct on the upstream side of the heat tube bundle.
- the heat exchanger of the second means is characterized in that, in the first means, each of the bare tube portion upstream flow rectifying plates or each bare tube portion downstream flow rectifying plate is a flat plate.
- the heat exchanger of the third means is characterized in that, in the first means, each of the bare tube portion upstream rectifying plates has a plurality of holes.
- the heat exchanger of the fourth means is characterized in that, in the third means, an opening ratio of a large number of holes in the upstream straightening plate of each bare tube part is 20 to 50%.
- the distance between the upstream straightening plate of each bare tube part and the heat medium tube on the most upstream side of each heat transfer tube bundle is the hole. It is characterized by being at least 10 times the diameter D of
- each introduction portion rectifying plate is formed with a plurality of openings so that the pressure loss coefficient is in the range of 1 to 3. To do.
- the heat exchanger of the seventh means is characterized in that, in the first means, the plurality of stages of introducing-portion rectifying plates are a combination of strip-like flat plates in a cross-beam shape.
- the plurality of openings formed in each of the introduction-portion rectifying plates on the downstream side have the total area of the introduction portion on the upstream side. It is formed so as to be equal to or larger than the total area of the plurality of openings formed in the current plate.
- the invention according to each claim described in the claims employs each of the above-described means, and the exhaust gas flowing into the heat exchanger is in the duct extension and / or upstream of the heat transfer tube bundle.
- the flow is rectified by the multi-stage inlet rectifier plates provided in the bundle storage duct, and the rectified exhaust gas flows into each heat transfer tube bundle, so that the upstream side and the wake flow of the bare tube portion of each heat transfer tube bundle
- the drift can be greatly suppressed by the bare tube portion upstream flow rectifying plate and the bare tube portion downstream flow rectifying plate respectively provided on the side.
- FIG. 1 is an overall configuration diagram of a thermal power plant that employs a heat exchanger according to an embodiment of the present invention.
- FIG. 2 is an enlarged plan view of the heat exchanger in FIG.
- FIGS. 3A and 3B are configuration diagrams of the introduction-portion rectifying plate in FIG. 2, in which FIG. FIG. 4 is an enlarged view of the vicinity of the bare tube portion of the fin tube portion in FIG. 2.
- the combustion exhaust gas discharged from the boiler 1 is introduced into a denitration device 2 filled with a catalyst.
- NOx in the exhaust gas is reduced to water and nitrogen by ammonia (NH 3) injected as a reducing agent and rendered harmless.
- NH 3 ammonia
- the temperature of the hot exhaust gas discharged from the denitration apparatus 2 is generally 120 to 150 ° C. via an air heater (A / H).
- This high-temperature exhaust gas is introduced into a heat recovery device 3 as a heat exchanger, and heat is recovered by exchanging heat with a heat medium (water or the like).
- the exhaust gas temperature discharged from the heat recovery device 3 is 80 to 110 ° C.
- the heat medium heated in the heat recovery device 3 is sent to the reheating device 6 described later via the heat medium circulation pipe 8.
- a suit blower device 9 is provided on the side of the heat recovery device 3.
- the low-temperature exhaust gas discharged from the heat recovery device 3 joins and is introduced into the electrostatic precipitator 4 to remove dust from the low-temperature exhaust gas.
- the exhaust gas from which the dust has been removed is pressurized by a blower (ID fan) 10 driven by an electric motor. Note that the blower 10 may not be provided.
- the desulfurization apparatus 5 the SOX in the exhaust gas is absorbed and removed by limestone, and gypsum is generated as a byproduct.
- the exhaust gas discharged from the desulfurizer 5 is generally lowered to 45 to 55 ° C. If this exhaust gas is released into the atmosphere as it is, problems such as white smoke becoming difficult to diffuse due to low temperature. Therefore, the exhaust gas is introduced into the reheating device 6, heated to a predetermined temperature or higher by the heat medium sent from the heat recovery device 3 through the heat medium circulation pipe 8, and discharged from the chimney 7.
- FIG. 1 Although the example of the boiler 1 is shown by FIG. 1, it is not limited to this, Various exhaust gas generation sources, such as an internal combustion engine, a gas turbine, and an incinerator, are employable. Moreover, as a thermal power plant, a thermal power plant or a garbage incineration plant can be employed.
- the heat exchanger includes a heat transfer tube, a reheater, a superheater, a heat exchange tube, a heat transfer tube, and the like.
- a duct-shaped heat recovery device 3 having a square cross section is connected to the exhaust gas duct 20 on the downstream side of the denitration device 2. The exhaust gas discharged from the denitration device 2 shown in FIG. 1 is introduced into the heat recovery device 3.
- the heat recovery device 3 includes a duct expansion part 21 connected to the downstream side of the exhaust gas duct 20 and a heat transfer tube bundle storage duct 22 connected to the downstream side of the duct expansion part 21.
- a plurality of rectifying plates 23 to 27 are attached as follows.
- each introduction portion rectifying plate 23, 24, 25 has a plurality of strip-like horizontal flat plates Px and a plurality of strip-like vertical plates.
- the flat plate Py is combined in the form of a cross in the vertical and horizontal directions.
- the opening of each introducing portion rectifying plate 23, 24, 25 has a total pressure loss coefficient of three sheets (or two total pressure loss coefficients if there are only two introducing portion rectifying plates 23). Within the range, preferably 2.
- the cross-sectional area of the exhaust gas duct 20 is set to So, and the total cross-sectional area of the multiple (plural) openings of the first-stage introduction portion rectifying plate 23 is set to S1, the multiple (plural) openings of the first-stage introduction portion rectifying plate 24.
- S2 is the total cross-sectional area of a large number (a plurality of) openings of the third-stage introduction portion rectifying plate 25
- S3 is the cross-sectional area Sd of the heat transfer tube bundle storage duct 22.
- S1 ⁇ S2 ⁇ S3 ⁇ Sd A large number (a plurality of) openings are formed in each introduction portion rectifying plate 23, 24, 25.
- the total cross-sectional area S3 of the opening of the introduction portion rectifying plate 25 at least in the third stage (most downstream side) is set to be larger than the cross-sectional area So of the exhaust gas duct 20.
- the inlet rectifying plates 23, 24, 25 are configured such that the total cross-sectional area of a large number (plurality) of openings gradually increases toward the wake, thereby allowing the inlets of the heat recovery devices 3a, 3b to enter. Nearby ash erosion can be prevented.
- the cross-sectional area So ⁇ total cross-sectional area S1 ⁇ total cross-sectional area S2 ⁇ total cross-sectional area S3 ⁇ cross-sectional area Sd Alternatively, the total sectional area S1 ⁇ the sectional area So ⁇ the total sectional area S2 ⁇ the total sectional area S3 ⁇ the sectional area Sd, Or, the total cross-sectional area S1 ⁇ total cross-sectional area S2 ⁇ cross-sectional area So ⁇ total cross-sectional area S3 ⁇ cross-sectional area Sd, To be.
- the number of the horizontal plates Px and the vertical plates Py is the same, and the mounting interval between the horizontal plates Px and / or the vertical plates Py is set to rectify the introduction part on the downstream side. It may be configured such that the total cross-sectional areas S1, S2, and S3 of a large number (plurality) of openings gradually increase toward the downstream by making them equal or wider as going to the plates 23, 24, and 25. Alternatively, the size of the large number (a plurality of) openings may be the same, and the number of the horizontal flat plate Px and the vertical flat plate Py may be increased as going to the downstream side introduction portion rectifying plates 23, 24, 25. good.
- the introduction part rectifying plate may be two sheets or four sheets or more (a plurality of sheets).
- the shape of each introduction portion rectifying plate 23, 24, 25 is not limited to that shown in FIG. 3, and may be a shape in which a large number of circular holes are formed in a flat plate.
- the most downstream side introduction portion rectifying plate 25 may be attached in the heat transfer tube bundle housing duct 22.
- the position of the opening of the first-stage introduction portion rectifying plate 23 in the vertical and horizontal directions and the position of the opening of the second-stage introduction portion rectifying plate 24 in the vertical and horizontal directions or By configuring each inlet rectifying plate 23, 24, 25 so that the position of the opening in the upper / lower / left / right direction does not match the position of the opening of the third stage inlet rectifying plate 25 in the vertical / left / right direction, The flow can be made more uniform.
- the vertical and horizontal positions of the portion where the wake side horizontal plate Px and the vertical plate Py intersect are positioned in the vertical and horizontal positions of the upstream opening Si. To do.
- ⁇ Rectifying plate in heat transfer tube bundle storage duct> As shown in FIG. 2, in the heat transfer tube bundle housing duct 22 of the heat recovery device 3, a three-stage structure including a high temperature heat transfer tube bundle 11, an intermediate temperature heat transfer tube bundle 12, and a low temperature heat transfer tube bundle 13 in the exhaust gas flow direction. (Multi-stage) heat transfer tube bundles are attached at intervals.
- Each of the heat transfer tube bundles 11 to 13 includes a plurality of rows and stages of fin tube portions (heat transfer portions) 15 and a bare tube portion (U-shaped) that connects the end portions of the adjacent fin tube portions (heat transfer portions) 15. Tube portion) 18.
- the upstream end and the rear end of each heat transfer tube bundle 11 to 13 are connected to a header 14 attached to the wall surface of the heat recovery apparatus 3.
- Each header 14 is connected to the heat medium circulation pipe 8 shown in FIG. And, on the upstream side and the downstream side of the bare tube portion 18 at both ends of each fin tube portion 15, the bare tube portion upstream side rectifying plate 26 and the bare tube portion downstream side rectifying plate are covered so as to cover the bare tube portion 18. 27 is attached.
- the fin tube portion 15 includes a plurality of straight heat medium tubes 16, spiral heat transfer fins 17 attached to the outer peripheral surface of each heat medium tube 16, and ends of adjacent heat medium tubes 16. It is comprised from the bare tube part 18 to connect.
- a gas short path is provided in the bare tube portion 18. It can happen. Therefore, in order to prevent a gas short path, a bare tube portion upstream flow straightening plate 26 and a bare tube portion downstream flow straightening plate are provided on the side walls in the heat transfer tube bundle housing duct 22 on the upstream side and the rear flow side of the bare tube portion 18. 27 is attached.
- a number of holes having a diameter D are formed in the upstream straightening plate 26 on the bare tube portion.
- the aperture ratio due to the large number of holes is 20 to 50%.
- the heat medium tube 16 is disposed at a position where the distance L between the heat medium tube 16 (upstream end of the bare tube portion 18) and the bare tube portion upstream rectifying plate 26 is 10 times or more the diameter D of the hole. .
- the upper limit of the ratio of the distance L / the diameter D of the hole is inevitably determined by the distance between the adjacent fin tube portions 15 and 15, the size of the heat transfer tube bundle housing duct 22, and the like.
- the bare tube portion posterior flow side rectifying plate 27 is a solid one.
- the pressure loss of the exhaust gas flow in the portion of the heat medium tube 16 and the pressure loss of the exhaust gas flow in the portion of the bare tube portion 18 can be made substantially the same. Can be reduced).
- Both the bare tube portion upstream flow rectifying plate 26 and the bare tube portion downstream flow rectifying plate 27 may be solid, or both may have a large number of holes.
- the bare tube portion upstream flow straightening plate 26 and the bare tube portion downstream flow straightening plate 27 are detachable in consideration of maintenance.
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Abstract
Description
しかしながら、特許文献1~5に記載のものは、いずれも熱交換器の近傍にしか整流板が設けられておらず、十分な整流(偏流の軽減)効果が得られないという問題がある。
先ず、図1に基づき、本発明の実施の形態に係る熱交換器を採用した火力プラントの全体の構成につき説明する。
なお、ボイラ1の燃料としては石炭、石油等が使用されており、ボイラ1からの排ガス中には、窒素酸化物(NOX)、硫黄酸化物(SOX)、ダスト等の大気汚染物質が含まれている。
脱硝装置2において、還元剤として注入されるアンモニア(NH3)により、排ガス中のNOXが水と窒素とに還元され無害化される。
脱硝装置2から排出された高温の排ガスの温度は、エアヒータ(A/H)を経由し、一般的に120~150℃となっている。
熱回収装置3から排出された排ガス温度は、80~110℃となる。
なお、熱回収装置3において加熱された熱媒体は、熱媒体循環配管8を介して、後述する再加熱装置6に送付される。
この熱回収装置3の側部には、スーツブロア装置9が設けられている。
ダストが除去された排ガスは、電動機により駆動される送風機(IDファン)10により加圧される。
なお、送風機10は設けられないこともある。
脱硫装置5において、石灰石により、排ガス中のSOXが吸収除去され、副生物として石膏が生成される。
このとき、脱硫装置5から排出される排ガスは、一般的に45~55℃に低下している。
この排ガスをこのまま大気に放出すると、低温のため拡散しにくく、白煙になるなどの問題が生じる。
そこで、この排ガスを、再加熱装置6に導入し、熱回収装置3から熱媒体循環配管8を介して送られてきた熱媒体により所定温度以上に加熱して、煙突7から排出している。
また、火力プラントとしては、火力発電プラント、ゴミ等焼却プラントが採用可能である。
次に、図2に基づき、熱交換器としての熱回収装置3の詳細につき説明する。
なお、熱交換器としては、図2に図示の熱回収装置3以外に、伝熱管、再熱器、過熱器、熱交換チューブ、伝熱管チューブ等がある。
図2に図示のように、脱硝装置2の後流側の排ガスダクト20には、断面が四角のダクト状の熱回収装置3が接続されている、
図1に図示の脱硝装置2から排出された排ガスは、熱回収装置3に導入されるようになっている。
図2に図示のように、ダクト拡張部21内には、3枚の導入部整流板(多孔板)23、24、25が取り付けられている。
なお、3枚の導入部整流板(多孔板)23、24、25の内の一枚或いは全部を、伝熱管バンドル収納ダクト22内(フィンチューブ部15より上流側)に取り付けても良い。
各導入部整流板23、24、25は、図3(a)の側面図、図3(b)の正面図に図示のように、複数本の帯状の横平板Pxと複数本の帯状の縦平板Pyとを縦横に井桁状に組み合わせて構成されている。
この場合、各導入部整流板23、24、25の開口は、3枚の合計圧損係数(導入部整流板23・・・が2枚しかない場合は2枚の合計圧損係数)が1~3の範囲内、好ましくは2となるようにする。
S1<S2<S3<Sd、
となるように、各導入部整流板23、24、25に、多数(複数)の開口が形成されている。
このように、各導入部整流板23、24、25を、多数(複数)の開口の総断面積が後流に行くに従って次第に大きくなるように構成することにより、熱回収装置3a、3bの入口付近のアッシュエロージョンを防止することができる。
或いは、総断面積S1<断面積So<総断面積S2<総断面積S3<断面積Sd、
又は、総断面積S1<総断面積S2<断面積So<総断面積S3<断面積Sd、
となるようにする。
或いは、多数(複数)の開口の大きさは同じにして、横平板Px及び縦平板Pyの本数を後流側の導入部整流板23、24、25に行くに従って増加さるように構成しても良い。
また、各導入部整流板23、24、25の形状としては、図3に図示のものに限定されるものではなく、平板に多数の円状の孔を開けた形状のものでも良い。
また、最も後流側の導入部整流板25は、伝熱管バンドル収納ダクト22内に取り付けても良い。
例えば、図3に図示の構造のものでは、後流側の横平板Pxと縦平板Pyとが交差する箇所の上下左右方向の位置が、その上流側の開口Siの上下左右方向の位置に位置するようにする。
図2に図示のように、熱回収装置3の伝熱管バンドル収納ダクト22内には、排ガスの流れ方向に高温伝熱管バンドル11、中温伝熱管バンドル12、及び低温伝熱管バンドル13からなる3段(複数段)の伝熱管バンドルが、間隔を明けて取り付けられている。
伝熱管バンドル11~13は、各々、複数列、多数段のフィンチューブ部(伝熱部)15と、隣接するフィンチューブ部(伝熱部)15の端部を接続するベアチューブ部(U字管部)18とにより構成されている。
各伝熱管バンドル11~13の上流端及び後流端は、熱回収装置3の壁面に取り付けられたヘッダ14に接続されている。
そして、各フィンチューブ部15の両端のベアチューブ部18の上流側及び後流側には、ベアチューブ部18を覆うように、ベアチューブ部上流側整流板26及びベアチューブ部後流側整流板27が取り付けられている。
フィンチューブ部15は、複数条の直管の熱媒体チューブ16と、各熱媒体チューブ16の外周面に取り付けられた螺旋状の伝熱フィン17と、隣接する熱媒体チューブ16の端部同士を接続するベアチューブ部18とから構成されている。
そこで、ガスショートパスを防止すべく、ベアチューブ部18の上流側及び後流側の伝熱管バンドル収納ダクト22内の側壁に、ベアチューブ部上流側整流板26及びベアチューブ部後流側整流板27が取り付けられている。
この多数の孔による開口率は、20~50%とする。
また、熱媒体チューブ16(ベアチューブ部18の上流端)とベアチューブ部上流側整流板26との距離Lが、孔の直径Dの10倍以上となる位置に、熱媒体チューブ16を配置する。
なお、距離L/孔の直径Dの比の上限は、隣接するフィンチューブ部15、15間の距離、伝熱管バンドル収納ダクト22の大きさ等により必然的に決定される。
一方、ベアチューブ部後流側整流板27は、ソリッドのものを配置する。
また、ベアチューブ部上流側整流板26及びベアチューブ部後流側整流板27は、メインテナンスを考慮して、着脱可能なものとする。
以上、本発明の各実施の形態について説明したが、本発明は上記の各実施の形態に限定されず、本発明の範囲内で種々の変更を加えてよいことは言うまでもない。
2 脱硝装置
3 熱回収装置(熱交換器)
4 電気集塵装置
5 脱硫装置
6 再加熱装置
7 煙突
8 熱媒体循環配管
9 スーツブロア装置
10 送風機
11 高温伝熱管バンドル
12 中温伝熱管バンドル
13 低温伝熱管バンドル
14 ヘッダ
15 フィンチューブ部(伝熱部)
16 熱媒体チューブ
17 伝熱フィン
18 ベアチューブ部(U字管部)
20 排ガスダクト
21 ダクト拡張部
22 伝熱管バンドル収納ダクト
23 1段目の導入部整流板
24 2段目の導入部整流板
25 3段目の導入部整流板
26 ベアチューブ部上流側整流板
27 ベアチューブ部後流側整流板
So 排ガスダクト断面積
S1 1段目の導入部整流板の開口の総断面積
S2 2段目の導入部整流板の開口の総断面積
S3 3段目の導入部整流板の開口の総断面積
Sd 伝熱管バンドル収納ダクト断面積
Si 導入部整流板の各開口
D 孔の直径
L 距離
Px 横平板
Py 縦平板
Claims (8)
- ダクト拡張部と伝熱管バンドル収納ダクトと前記伝熱管バンドル収納ダクト内に排ガスに流れ方向に間隔を明けて複数段設けられた伝熱管バンドルとを有する熱交換器において、
前記各伝熱管バンドルのベアチューブ部の上流側及び後流側に各々設けられたベアチューブ部上流側整流板及びベアチューブ部後流側整流板と、
前記ダクト拡張部内及び又は前記伝熱管バンドルより上流側の前記伝熱管バンドル収納ダクト内に設けられた複数段の導入部整流板と、
を備えたことを特徴とする熱交換器。 - 前記各ベアチューブ部上流側整流板又は前記各ベアチューブ部後流側整流板は、平板であることを特徴とする請求項1に記載の熱交換器。
- 前記各ベアチューブ部上流側整流板は、多数の孔を有するものであることを特徴とする請求項1に記載の熱交換器。
- 前記各ベアチューブ部上流側整流板の多数の孔の開口率は、20~50%であることを特徴とする請求項3に記載の熱交換器。
- 前記各ベアチューブ部上流側整流板と前記各伝熱管バンドルの最も上流側の熱媒体チューブとの間の距離は、前記孔の直径Dの10倍以上であることを特徴とする請求項3又は4に記載の熱交換器。
- 前記各導入部整流板には、圧損係数が1~3の範囲内となるように複数の開口が形成されていることを特徴とする請求項1に記載の熱交換器。
- 前記複数段の導入部整流板は、帯状の平板を井桁状に組み合わせたものであることを特徴とする請求項1に記載の熱交換器。
- 後流側の前記各導入部整流板に形成された複数の開口は、その総面積が上流側の前記導入部整流板に明けられた複数の開口の総面積と同等もしくはより大きくなるように形成されていることを特徴とする請求項1乃至7のいずれかに記載の熱交換器。
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US13/059,884 US9400102B2 (en) | 2009-03-18 | 2009-08-06 | Heat exchanger including flow regulating plates |
EP09841901.3A EP2410241A4 (en) | 2009-03-18 | 2009-08-06 | Heat exchanger |
KR1020117003860A KR101277001B1 (ko) | 2009-03-18 | 2009-08-06 | 열교환기 |
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JP2009065610A JP5010635B2 (ja) | 2009-03-18 | 2009-03-18 | 熱交換器 |
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US (1) | US9400102B2 (ja) |
EP (1) | EP2410241A4 (ja) |
JP (1) | JP5010635B2 (ja) |
KR (1) | KR101277001B1 (ja) |
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WO2018123209A1 (ja) * | 2016-12-28 | 2018-07-05 | 三菱重工業株式会社 | 熱交換器及び船舶 |
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JP5721472B2 (ja) * | 2011-02-28 | 2015-05-20 | 三菱重工業株式会社 | 熱交換器 |
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WO2017053499A1 (en) * | 2015-09-25 | 2017-03-30 | Fuel Tech, Inc. | Process and apparatus for reducing plume |
CN108700392A (zh) * | 2016-02-17 | 2018-10-23 | 株式会社Ihi | 热处理装置 |
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WO2018139669A1 (ja) * | 2017-01-30 | 2018-08-02 | 三菱日立パワーシステムズ株式会社 | ガスガス熱交換器 |
KR101983969B1 (ko) * | 2017-11-17 | 2019-09-03 | 한국전력공사 | 순환유동층 보일러 |
JP7130569B2 (ja) * | 2019-02-01 | 2022-09-05 | 三菱重工業株式会社 | 熱交換器及びボイラ並びに熱交換器の吸熱量調整方法 |
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EP2410241A4 (en) | 2017-08-23 |
KR101277001B1 (ko) | 2013-06-24 |
KR20110043698A (ko) | 2011-04-27 |
TWI372843B (ja) | 2012-09-21 |
US20110139426A1 (en) | 2011-06-16 |
TW201035494A (en) | 2010-10-01 |
EP2410241A1 (en) | 2012-01-25 |
US9400102B2 (en) | 2016-07-26 |
JP2010216749A (ja) | 2010-09-30 |
JP5010635B2 (ja) | 2012-08-29 |
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