JPH09257202A - Waste heat recovery device - Google Patents
Waste heat recovery deviceInfo
- Publication number
- JPH09257202A JPH09257202A JP6981596A JP6981596A JPH09257202A JP H09257202 A JPH09257202 A JP H09257202A JP 6981596 A JP6981596 A JP 6981596A JP 6981596 A JP6981596 A JP 6981596A JP H09257202 A JPH09257202 A JP H09257202A
- Authority
- JP
- Japan
- Prior art keywords
- heat transfer
- exhaust gas
- heat
- transfer tube
- horizontal supports
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 238000011084 recovery Methods 0.000 title claims description 53
- 239000002918 waste heat Substances 0.000 title 1
- 230000002265 prevention Effects 0.000 claims description 52
- 238000002485 combustion reaction Methods 0.000 claims description 11
- 230000008602 contraction Effects 0.000 claims description 11
- 230000008878 coupling Effects 0.000 claims 2
- 238000010168 coupling process Methods 0.000 claims 2
- 238000005859 coupling reaction Methods 0.000 claims 2
- 238000003466 welding Methods 0.000 abstract description 2
- 239000002912 waste gas Substances 0.000 abstract 1
- 239000007789 gas Substances 0.000 description 93
- MWUXSHHQAYIFBG-UHFFFAOYSA-N nitrogen oxide Inorganic materials O=[N] MWUXSHHQAYIFBG-UHFFFAOYSA-N 0.000 description 11
- 238000010248 power generation Methods 0.000 description 9
- 239000011810 insulating material Substances 0.000 description 7
- 230000000694 effects Effects 0.000 description 4
- UGFAIRIUMAVXCW-UHFFFAOYSA-N Carbon monoxide Chemical compound [O+]#[C-] UGFAIRIUMAVXCW-UHFFFAOYSA-N 0.000 description 3
- 238000010586 diagram Methods 0.000 description 3
- 239000003546 flue gas Substances 0.000 description 3
- 238000011144 upstream manufacturing Methods 0.000 description 3
- 230000007423 decrease Effects 0.000 description 2
- 238000001556 precipitation Methods 0.000 description 2
- 238000009423 ventilation Methods 0.000 description 2
- TVZRAEYQIKYCPH-UHFFFAOYSA-N 3-(trimethylsilyl)propane-1-sulfonic acid Chemical compound C[Si](C)(C)CCCS(O)(=O)=O TVZRAEYQIKYCPH-UHFFFAOYSA-N 0.000 description 1
- QVGXLLKOCUKJST-UHFFFAOYSA-N atomic oxygen Chemical compound [O] QVGXLLKOCUKJST-UHFFFAOYSA-N 0.000 description 1
- 238000007796 conventional method Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 239000000428 dust Substances 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 239000003350 kerosene Substances 0.000 description 1
- 239000001301 oxygen Substances 0.000 description 1
- 229910052760 oxygen Inorganic materials 0.000 description 1
- 230000004043 responsiveness Effects 0.000 description 1
- 230000003442 weekly effect Effects 0.000 description 1
Landscapes
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は燃焼排ガスが通過す
る煙道中に設けられた排熱回収装置に係り、特に煙道内
で排ガスが偏流することなく熱交換効率が良好な構造の
排熱回収装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an exhaust heat recovery device provided in a flue passage through which combustion exhaust gas passes, and particularly to an exhaust heat recovery device having a structure with good heat exchange efficiency without uneven distribution of the exhaust gas in the flue gas passage. Regarding
【０００２】[0002]
【従来の技術】急増する電力需要に応えるために大容量
の火力発電所が建設されているが、これらのボイラは部
分負荷時においても高い発電効率を得るためにボイラの
変圧運転を行うことが要求されている。これは最近の電
力需要の特徴として、原子力発電の伸びと共に、負荷の
最大と最小の差も増大し、火力発電はベースロード用か
ら負荷調整用へと移行する傾向にある。つまり、火力発
電用ボイラは、ボイラ負荷を常に全負荷で運転されるケ
ースは少なく、ボイラ負荷を、７５％負荷、５０％負荷
あるいは２５％負荷へと、負荷を上げ、下げして運転し
たり、またボイラの運転を停止（休止）するなど、いわ
ゆる毎日起動停止（Daily Start Stop：以下単にＤＳＳ
と言う）運転や、週末起動停止（Weekly Start Stop：
以下単にＷＳＳという）運転を行って中間負荷を担い、
発電効率を向上させる運転が行われている。例えば、高
効率発電の一環として、最近は複合プラントが注目され
ている。この複合発電プラントは、まず、ガスタービン
による発電を行うと共に、ガスタービンから排出される
排ガス中の熱を排熱回収装置（排熱回収ボイラ）によっ
て回収し、この排熱回収ボイラで発生した蒸気により蒸
気タービンを駆動させて発電するものである。この複合
発電プラントは、ガスタービンによる発電と、蒸気ター
ビンによる発電とを同時に行うことができるため発電効
率が高い上に、ガスタービンは負荷応答性に優れ、この
ために急激な電力需要の上昇、下降にも十分対応し得る
負荷追従性に優れた利点もあり、特にＤＤＳ運転やＷＳ
Ｓ運転を行うプラントには有効である。ところが、この
複合発電プラントにおいては、ＬＮＧ、灯油などのクリ
ーンな燃料を使用するので、ＳＯｘ量やダスト量は少な
いが、ガスタービンの燃焼においては酸素量が多く、高
温燃焼を行うために排ガス中のＮＯｘ量が増加するの
で、脱硝装置を内蔵した排熱回収ボイラが開発されてい
る。図４から図８は、従来の排熱回収ボイラを示すもの
で、図４は、排熱回収ボイラの系統図を示し、図５は、
図４のＡ−Ａ矢視図で、排熱回収ボイラの保温構造を示
す断面図であり、図６は、図４のＢ部を拡大した側断面
図で、図７は、図６のＣ−Ｃ矢視図、図８は、図６のＤ
−Ｄ部位の詳細図、図９は、図８のＥ−Ｅ矢視図を示
す。図４において、ガスタービン（図示せず）からの排
ガスＧは、矢印で示すごとく、煙道１００内の上流側
（図４の左）から下流側（図４の右）へ向かって流れ、
この煙道１００内には、過熱器１、第１段高圧蒸発器
２、第２段高圧蒸発器４、高圧節炭器７、低圧蒸発器８
および低圧節炭器１１等の伝熱管群によって構成された
排熱回収ボイラが配置されている。排ガスＧは、過熱器
１、第１段高圧蒸発器２を経て脱硝装置３に至り、排ガ
ス中の窒素酸化物（ＮＯｘ）を除去する。続いて、排ガ
スＧは、第２段高圧蒸発器４、高圧節炭器７、低圧蒸発
器８、低圧節炭器１１を経て排出され、排ガス中の排熱
が回収される。この間に発生した高圧蒸気Ｓ1および低
圧蒸気Ｓ2は、蒸気タービンの動力源、所内の熱源とし
て利用される。図４の符号５および９は、各々高圧ドラ
ムおよび低圧ドラムを、符号６および１０は降水管を示
す。以上述べたように、排熱回収ボイラは、ガスタービ
ンからの排ガスＧを通過させる煙道１００内に配置され
ているが、この煙道１００は外部に対する熱の放散を防
止し、排熱回収ボイラの熱効率を高めるため、図５に示
すような保温構造となっている。図５の符号１７ａ、１
７ｂは側部外側ケーシング、１６は保温材、２０ａ、２
０ｂは側部内側ケーシングを示す。なお、排ガスＧは、
各伝熱管１２（図６参照）を通過するにしたがって排ガ
ス温度が低下するので、この排ガス温度に対応して、例
えば図５に示すように保温材１６の厚さを変化させてお
り、高温部（上流側）ほど保温材１６の厚みを大きくし
て断熱性を高め、低温部（下流側）では保温材１６の厚
さを薄くしている。図６は、図４に示す従来の排熱回収
ボイラのＢ部の拡大側断面図を示し、図７は、図６のＣ
−Ｃ矢視図を示す。なお、図７において、Ｈ2、Ｗ2は煙
道１００内の伝熱空間を示し、Ｈ1、Ｈ3、Ｗ1、Ｗ3は非
伝熱空間を示す。排熱回収ボイラの伝熱管群は、図６に
示すように、伝熱管１２、上部および下部管寄せ１９お
よび１３、上部連絡管１８、下部連絡管２１によって構
成され、伝熱管１２は上部で管寄せサポート１４によっ
て支持され、その外周は図７に示すように、側部外側ケ
ーシング１７ａ、１７ｂ、下部外側ケーシング２４、上
部外側ケーシング２５、保温材１６、側部内側ケーシン
グ２０ａ、２０ｂ、上部内側ケーシング２２、下部内側
ケーシング２３によって囲われ、全体が管寄せサポート
ビーム１５に吊り下げ構造で支持されている。排熱回収
ボイラ伝熱管群は、タービンからの排ガスの熱回収率を
高めるために、伝熱管１２の配列は千鳥状に配置され、
伝熱空間Ｈ2、Ｗ2に位置する伝熱管１２には、フィンが
取付けられたフィン付伝熱管１２ａが使用されている。
このフィン付伝熱管１２ａは、排ガスＧがフィン付伝熱
管１２ａ間を流動することにより、個々のフィン付伝熱
管１２ａが揺れ、前後および左右のフィン付伝熱管１２
ａが接触することを避けるため、また振動等を防ぐため
に伝熱管の軸直角方向に設けられた水平サポート２８に
より結束し支持されている。一方、図７に示すように、
非伝熱空間Ｈ1、Ｈ3に位置する伝熱管１２の上部および
下部管寄せ１９、１３の近傍では、伝熱管１２が上部お
よび下部管寄せ１９、１３に集合させるために、あるい
は上部および下部管寄せ１９、１３と、伝熱管１２との
取合上、フィン付伝熱管１２ａに代えて裸伝熱管１２ｂ
が用いられている。このために、ガスタービンからの排
ガスＧが煙道１００内を通過する場合、煙道１００の
上、下方向においては伝熱空間Ｈ2に位置するフィン付
伝熱管１２ａの部分を通過する通気抵抗は、非伝熱空間
Ｈ1、Ｈ3に位置する裸伝熱管１２ｂの部分に比べて大き
くなる。したがって、図６に示す煙道１００において、
上部内側ケーシング２２、下部内側ケーシング２３の近
傍に、上下の熱交換に関与しない非伝熱空間Ｈ1、Ｈ3が
でき、排ガスＧは、通気抵抗の大きい伝熱空間Ｈ2には
流れにくくなる。これを防止するために、非伝熱空間Ｈ
1、Ｈ3には、排ガスＧが非伝熱空間Ｈ1、Ｈ3をバイパス
するのを防止するために、上部偏流防止部材２６ａ、下
部偏流防止部材２６ｂを、煙道１００を横切る方向に配
設されている。次に、図７に示すように、排熱回収ボイ
ラの幅方向においても、上部および下部管寄せ１９、１
３と、伝熱管１２と、側部内側ケーシング２０ａ、２０
ｂとの間には、やはり熱交換に直接関与しない非伝熱空
間Ｗ1、Ｗ3ができてしまう。この場合、図５に示すごと
く、煙道１００の下流に行くほど保温材１６の厚さが薄
く、かつ側部外側ケーシング１７ａ、１７ｂの外形寸法
は、上流から下流まで一定であるので、煙道の下流へ行
くほど非伝熱空間Ｗ1、Ｗ3は実質的に広くなる。この非
伝熱空間Ｗ1、Ｗ3は、排ガスＧが通過する際に抵抗とな
るべきものが伝熱空間Ｗ2に比較して少ないので、この
ために大量の排ガスＧがこの非伝熱空間Ｗ1、Ｗ3をバイ
パスしてしまい、ボイラ全体の熱回収効率が大幅に低下
してしまうことになる。この非伝熱空間Ｗ1、Ｗ3に、排
ガスＧがバイパスするのを防ぐために、図８、図９に示
すように、側部偏流防止部材２７が配設されている。こ
の側部偏流防止材２７が設けられている。なお、図８
は、図４のＣ−Ｃ矢視を拡大した側断面図で、図９は、
図８のＥ−Ｅ矢視である水平断面図である。図８に示す
ように、側面偏流防止部材２７は、 側部内側ケーシン
グ２０ａ、２０ｂに取り付けられ、排ガスＧとの熱交換
により上部および下部管寄せ１９、１３の熱伸びによ
り、伝熱管が移動（図８、図９に破線で示す）するのを
考慮し、ギャップを設けた構造としている。2. Description of the Related Art A large-capacity thermal power plant has been constructed to meet a rapidly increasing demand for electric power, and these boilers can perform a variable voltage operation of the boiler to obtain high power generation efficiency even under partial load. Is required. As a characteristic of recent power demand, the difference between the maximum and minimum loads increases with the increase in nuclear power generation, and thermal power generation tends to shift from base load use to load adjustment. In other words, there are few cases where the boiler load is always operated at full load, and the boiler load is operated by increasing or decreasing the load to 75% load, 50% load or 25% load. Also, the so-called daily start stop (hereinafter simply referred to as DSS) such as stopping (pausing) the boiler operation
Driving or Weekly Start Stop:
(Hereinafter simply referred to as WSS) and carry an intermediate load,
Operations are underway to improve power generation efficiency. For example, as a part of high-efficiency power generation, a combined plant has recently attracted attention. This combined cycle power generation plant first performs power generation by a gas turbine, recovers heat in exhaust gas discharged from the gas turbine by an exhaust heat recovery device (exhaust heat recovery boiler), and generates steam in the exhaust heat recovery boiler. It drives a steam turbine to generate electricity. This combined cycle power plant has high power generation efficiency because it can generate power by the gas turbine and power generation by the steam turbine at the same time, and the gas turbine has excellent load responsiveness. It also has the advantage of excellent load following capability that can sufficiently cope with descent, especially in DDS operation and WS.
This is effective for plants that perform S operation. However, in this combined cycle power plant, since clean fuel such as LNG and kerosene is used, the amount of SOx and the amount of dust are small, but the amount of oxygen is large in the combustion of the gas turbine, and the high temperature combustion results in the exhaust gas. Since the amount of NOx of NOx increases, an exhaust heat recovery boiler with a built-in NOx removal device has been developed. 4 to 8 show a conventional exhaust heat recovery boiler, FIG. 4 shows a system diagram of the exhaust heat recovery boiler, and FIG.
FIG. 7 is a cross-sectional view showing the heat retaining structure of the exhaust heat recovery boiler, taken along the line AA of FIG. 4, FIG. 6 is an enlarged side cross-sectional view of portion B of FIG. 4, and FIG. -C arrow view, FIG. 8 is D of FIG.
9 is a detailed view of the -D portion, and FIG. 9 shows a view taken along the line EE of FIG. In FIG. 4, the exhaust gas G from the gas turbine (not shown) flows from the upstream side (left in FIG. 4) to the downstream side (right in FIG. 4) in the flue 100, as indicated by an arrow.
Inside the flue 100, there are a superheater 1, a first-stage high-pressure evaporator 2, a second-stage high-pressure evaporator 4, a high-pressure economizer 7, and a low-pressure evaporator 8.
Also, an exhaust heat recovery boiler configured by a heat transfer tube group such as the low pressure economizer 11 is arranged. The exhaust gas G reaches the denitration device 3 through the superheater 1 and the first-stage high-pressure evaporator 2 to remove nitrogen oxides (NOx) in the exhaust gas. Subsequently, the exhaust gas G is discharged through the second-stage high pressure evaporator 4, the high pressure economizer 7, the low pressure evaporator 8, and the low pressure economizer 11, and the exhaust heat in the exhaust gas is recovered. The high-pressure steam S 1 and the low-pressure steam S 2 generated during this period are used as a power source for the steam turbine and a heat source in the plant. Reference numerals 5 and 9 in FIG. 4 denote a high pressure drum and a low pressure drum, respectively, and reference numerals 6 and 10 denote downcomers. As described above, the exhaust heat recovery boiler is arranged in the flue 100 that allows the exhaust gas G from the gas turbine to pass through. The flue 100 prevents heat from being dissipated to the outside, and the exhaust heat recovery boiler is provided. In order to improve the thermal efficiency of the above, the heat retaining structure is as shown in FIG. Reference numerals 17a and 1 in FIG.
7b is a side outer casing, 16 is a heat insulating material, 20a, 2
0b indicates a side inner casing. The exhaust gas G is
Since the exhaust gas temperature decreases as it passes through each heat transfer tube 12 (see FIG. 6), the thickness of the heat insulating material 16 is changed in accordance with the exhaust gas temperature as shown in FIG. The thickness of the heat insulating material 16 is increased toward the upstream side to improve the heat insulating property, and the thickness of the heat insulating material 16 is reduced in the low temperature portion (downstream side). FIG. 6 is an enlarged side sectional view of a B part of the conventional exhaust heat recovery boiler shown in FIG. 4, and FIG.
-C shows an arrow view. In FIG. 7, H 2 and W 2 represent heat transfer spaces in the flue 100, and H 1 , H 3 , W 1 and W 3 represent non-heat transfer spaces. As shown in FIG. 6, the heat transfer tube group of the exhaust heat recovery boiler is composed of a heat transfer tube 12, upper and lower headers 19 and 13, an upper connecting tube 18, and a lower connecting tube 21, and the heat transfer tube 12 is an upper tube. As shown in FIG. 7, the outer periphery is supported by the shifting support 14, and the outer side casings 17a and 17b, the lower outer casing 24, the upper outer casing 25, the heat insulating material 16, the side inner casings 20a and 20b, and the upper inner casing. It is surrounded by the lower inner casing 22 and the lower inner casing 23, and is wholly supported by the pipe-heading support beam 15 in a hanging structure. In the exhaust heat recovery boiler heat transfer tube group, the arrangement of the heat transfer tubes 12 is arranged in a staggered manner in order to enhance the heat recovery rate of the exhaust gas from the turbine.
As the heat transfer tube 12 located in the heat transfer spaces H 2 and W 2 , a finned heat transfer tube 12a to which fins are attached is used.
In the finned heat transfer tube 12a, the exhaust gas G flows between the finned heat transfer tubes 12a, so that the individual finned heat transfer tubes 12a sway, and the front and rear and left and right finned heat transfer tubes 12a.
In order to prevent a from coming into contact with each other and to prevent vibration and the like, they are bound and supported by a horizontal support 28 provided in a direction perpendicular to the axis of the heat transfer tube. On the other hand, as shown in FIG.
In the vicinity of the upper and lower headers 19 and 13 of the heat transfer tubes 12 located in the non-heat transfer spaces H 1 and H 3 , the heat transfer tubes 12 are gathered in the upper and lower headers 19 and 13, or the upper and lower headers Due to the connection between the pipe headers 19 and 13 and the heat transfer pipe 12, the heat transfer pipe with fins 12a is replaced with a bare heat transfer pipe 12b.
Is used. For this reason, when the exhaust gas G from the gas turbine passes through the inside of the flue 100, the ventilation resistance passing through the portion of the finned heat transfer tube 12a located in the heat transfer space H 2 in the upper and lower directions of the flue 100. Is larger than the bare heat transfer tube 12b located in the non-heat transfer spaces H 1 and H 3 . Therefore, in the flue 100 shown in FIG.
In the vicinity of the upper inner casing 22 and the lower inner casing 23, non-heat transfer spaces H 1 and H 3 that do not participate in the upper and lower heat exchange are formed, and the exhaust gas G is less likely to flow into the heat transfer space H 2 having a large ventilation resistance. . To prevent this, the non-heat transfer space H
1, the H 3 is distribution to the exhaust gas G is prevented from bypassing the Hidden thermospatial H 1, H 3, upper drift preventing member 26a, a lower drift prevention member 26b, in a direction transverse to the flue 100 It is set up. Next, as shown in FIG. 7, also in the width direction of the exhaust heat recovery boiler, the upper and lower pipe drawers 19, 1
3, the heat transfer tube 12, and the side inner casings 20a, 20
Non-heat transfer spaces W 1 and W 3 which are not directly involved in heat exchange are formed between the two and b. In this case, as shown in FIG. 5, the heat insulating material 16 is thinner toward the downstream side of the flue 100, and the outer dimensions of the side outer casings 17a and 17b are constant from the upstream side to the downstream side. The non-heat transfer spaces W 1 and W 3 become substantially wider toward the downstream side of. Since the non-heat transfer spaces W 1 and W 3 have less resistance when the exhaust gas G passes therethrough as compared with the heat transfer space W 2 , for this reason, a large amount of the exhaust gas G is generated in the non-heat transfer space. Bypassing W 1 and W 3 , the heat recovery efficiency of the entire boiler is significantly reduced. In order to prevent the exhaust gas G from bypassing in the non-heat transfer spaces W 1 and W 3 , side drift preventing members 27 are arranged as shown in FIGS. 8 and 9. The side drift prevention member 27 is provided. FIG.
FIG. 9 is a side sectional view showing an enlarged view taken along the line CC of FIG. 4, and FIG.
FIG. 9 is a horizontal sectional view taken along the line EE of FIG. 8. As shown in FIG. 8, the side surface drift prevention member 27 is attached to the side inner casings 20a and 20b, and the heat transfer tubes move due to heat expansion of the upper and lower headers 19 and 13 due to heat exchange with the exhaust gas G ( 8 and 9 (indicated by broken lines), a gap is provided.
【０００３】[0003]
【発明が解決しようとする課題】上述したごとく従来技
術において、上部および下部管寄せと、側部偏流防止部
材との接触による損傷を避けるため、上部および下部管
寄せと伝熱管を一体化した、いわゆるパネル状の熱交換
器を設置した後に、側部偏流防止部材を取り付けねばな
らなかった。また、伝熱管や水平サポートと側部偏流防
止部材との接触を避けるために、排ガスによる熱交換器
の熱膨張による熱伸び量に相当するギャップを設ける
が、このギャップには排ガスのバイパス量を低減するた
めに、側部偏流防止部材の取り付け時に調整をする必要
があり、これは高所作業で、かつ伝熱管と側部内側ケー
シングとの狭い空間で作業をしなければならないという
問題があった。また、上記ギャップは、熱伸び量が最大
である排ガスの最高温度での熱伸び量にしなければ、伝
熱管の水平サポートと側部偏流防止部材とは接触しない
ため、排ガスが最高温度以下の場合には、熱伸び量が十
分でなく、そのため上記ギャップの幅は大きくなり排ガ
スのバイパス量は増加し、そのため排熱回収効率は低下
するという問題があった。As described above, in the prior art, in order to avoid damage due to the contact between the upper and lower headers and the side drift preventing member, the upper and lower headers are integrated with the heat transfer tube. After the so-called panel-shaped heat exchanger was installed, the side drift prevention member had to be installed. In addition, in order to avoid contact between the heat transfer tubes and horizontal support and the side drift prevention member, a gap corresponding to the amount of thermal expansion due to the thermal expansion of the heat exchanger due to the exhaust gas is provided. In order to reduce it, it is necessary to make adjustments when installing the side drift prevention member, which has the problem that work must be performed in high places and in a narrow space between the heat transfer tube and the side inner casing. It was In addition, the above-mentioned gap does not come into contact with the horizontal support of the heat transfer tube and the side drift prevention member unless the thermal expansion amount at the maximum temperature of the exhaust gas having the maximum thermal expansion amount is made. However, there is a problem in that the amount of thermal expansion is not sufficient, the width of the gap is increased, and the amount of bypass of exhaust gas is increased, resulting in a decrease in exhaust heat recovery efficiency.
【０００４】本発明の目的は、上記従来技術における問
題点を解消するものであって、高所作業や狭い空間での
取り付け作業を少なくし、かつ排ガスのバイパス量を大
幅に低減することが可能な構造の熱交換効率の良好な排
熱回収装置を提供することにある。An object of the present invention is to solve the above-mentioned problems in the prior art, and it is possible to reduce work in high places and installation work in a narrow space, and to greatly reduce the amount of exhaust gas bypass. An object of the present invention is to provide an exhaust heat recovery device having a simple structure and good heat exchange efficiency.
【０００５】[0005]
【課題を解決するための手段】上記本発明の目的を達成
するために、本発明は特許請求の範囲に記載のような構
成とするものである。すなわち、本発明は請求項１に記
載のように、燃焼排ガスが通過する煙道中に、複数の伝
熱管を、上、下に設けられた管寄せに接続して配置し、
上記排ガス中の熱を回収する排熱回収装置であって、上
記伝熱管は、該伝熱管の軸直角方向に設けられた複数列
の水平サポートと、該伝熱管の長手方向に複数段配設さ
れた上記水平サポートによって結束支持され、上記複数
列の水平サポートの端部に、該複数列の水平サポートを
結束する水平サポート結束部材を設け、該水平サポート
結束部材を、伝熱管の長手方向に配列された複数の垂直
連結部材により支持固定して一体構造のパネル型熱交換
器を構成し、該熱交換器を少なくとも１基以上、上記煙
道の内部に配設した排熱回収装置とするものである。ま
た、本発明は請求項２に記載のように、燃焼排ガスが通
過する煙道中に、複数の伝熱管を、上、下に設けられた
管寄せに接続して配置し、上記排ガス中の熱を回収する
排熱回収装置であって、上記伝熱管は、該伝熱管の軸直
角方向に設けられた複数列の水平サポートと、該伝熱管
の長手方向に複数段配設された上記水平サポートによっ
て結束支持され、上記複数列の水平サポートの端部に、
該複数列の水平サポートを結束する水平サポート結束部
材を設け、該水平サポート結束部材を、伝熱管の長手方
向に配列された複数の垂直連結部材により支持固定して
一体構造のパネル型熱交換器を構成し、該一体構造の熱
交換器と、上記煙道の内壁との間の排ガスの偏流が生じ
易い隙間部に、上記熱交換器側に設ける排ガス偏流防止
部材と、煙道の内壁に設ける排ガス偏流防止部材とが互
いに嵌挿でき、かつ熱膨張および収縮によってスライド
可能な構造に配設した排熱回収装置とするものである。
また、本発明は請求項３に記載のように、燃焼排ガスが
通過する煙道中に、複数の伝熱管を、上、下に設けられ
た管寄せに接続して配置し、上記排ガス中の熱を回収す
る排熱回収装置であって、上記伝熱管は、該伝熱管の軸
直角方向に設けられた複数列の水平サポートと、該伝熱
管の長手方向に複数段配設された上記水平サポートによ
って結束支持され、上記複数列の水平サポートの端部
に、該複数列の水平サポートを結束する水平サポート結
束部材を設け、該水平サポート結束部材を、伝熱管の長
手方向に配列された複数の垂直連結部材により支持固定
して一体構造のパネル型熱交換器を構成し、該一体構造
の熱交換器と、上記煙道の側壁との間の排ガスの偏流が
生じ易い部位に、上記熱交換器側に設ける排ガス偏流防
止部材と、煙道の側壁に設ける排ガス偏流防止部材とが
互いに嵌挿でき、かつ熱膨張および収縮によってスライ
ド可能な構造に配設した排熱回収装置とするものであ
る。また、本発明は請求項４に記載のように、燃焼排ガ
スが通過する煙道中に、複数の伝熱管を、上、下に設け
られた管寄せに接続して配置し、上記排ガス中の熱を回
収する排熱回収装置であって、上記伝熱管は、該伝熱管
の軸直角方向に設けられた複数列の水平サポートと、該
伝熱管の長手方向に複数段配設された上記水平サポート
によって結束支持され、上記複数列の水平サポートの端
部に、該複数列の水平サポートを結束する水平サポート
結束部材を設け、該水平サポート結束部材を、伝熱管の
長手方向に配列された複数の垂直連結部材により支持固
定して一体構造のパネル型熱交換器を構成し、上記煙道
の側壁に、伝熱管の長手方向に凹型の断面形状をしたメ
ス形の排ガス偏流防止部材を配設し、該排ガス偏流防止
部材の凹部に、上記熱交換器の水平サポート結束部材と
垂直連結部材とにより構成される断面が凸型形状のオス
型の排ガス偏流防止部材を嵌挿し、かつ熱膨張および収
縮によってスライド可能な構造に配設した排熱回収装置
とするものである。本発明の排熱回収装置において、請
求項１に記載のように、伝熱管を水平サポートを結束す
る水平サポート結束部材と垂直連結部材により支持固定
して一体構造のパネル型熱交換器を構成しているので、
上部および下部管寄せと伝熱管を一体化することがで
き、地上において組立てられるため、煙道内の高所およ
び狭い空間での作業量が少なくなると同時に、熱交換器
の組立てが容易であり、能率良く安全に作業が行える効
果がある。また、本発明の排熱回収装置は、請求項２に
記載のように、一体構造の熱交換器と、上記煙道の内壁
との間の排ガスの偏流が生じ易い隙間部に、上記熱交換
器側に設ける排ガス偏流防止部材と、煙道の内壁に設け
る排ガス偏流防止部材とが互いに嵌挿でき、かつ熱膨張
および収縮によってスライド可能な構造に配設している
ので、上記排ガス偏流防止部材間に生じる隙間部を最小
限に小さくしているので、排ガスのバイパス量を著しく
少なくすることができ、排熱回収効率を向上できる効果
がある。また、本発明の排熱回収装置は、請求項３に記
載のように、煙道の側壁との間の排ガスの偏流が生じ易
い部位に、上記熱交換器側に設ける排ガス偏流防止部材
と、煙道の側壁に設ける排ガス偏流防止部材とが互いに
嵌挿でき、かつ熱膨張および収縮によってスライド可能
な構造に設けているので、最も排ガスが偏流しやすい煙
道の側壁部に、互いに嵌挿できる構造の排ガス偏流防止
部材を設けているので、排ガスのバイパス量を効果的に
抑制することが可能となり、排熱回収効率を向上させる
ことができる効果がある。また、本発明の排熱回収装置
は、請求項４に記載のように、煙道の側壁に伝熱管の長
手方向に凹型の断面形状をしたメス形の排ガス偏流防止
部材を配設し、該排ガス偏流防止部材の凹部に、上記熱
交換器の水平サポート結束部材と垂直連結部材とにより
構成される断面が凸型形状のオス型の排ガス偏流防止部
材を嵌挿し、かつ熱膨張および収縮によってスライド可
能な構造に設けているので、煙道の側壁の最も排ガスが
バイパスしやすい部分に、一体構造のパネル型熱交換器
の水平サポート結束部材と垂直連結部材とにより構成さ
れたオス型の排ガス偏流防止部材を配設しているので、
極めて簡易な構成で排ガスの偏流を有効に抑制すること
ができ、排ガスのバイパス量を効果的に抑制することが
可能となり、排熱回収効率が向上できる効果がある。In order to achieve the above-mentioned object of the present invention, the present invention has a constitution as set forth in the claims. That is, according to the present invention, as described in claim 1, in the flue passage through which the combustion exhaust gas passes, a plurality of heat transfer tubes are arranged so as to be connected to the headers provided above and below,
In the exhaust heat recovery device for recovering heat in the exhaust gas, the heat transfer tube comprises a plurality of rows of horizontal supports provided in a direction perpendicular to the axis of the heat transfer tube, and a plurality of stages arranged in the longitudinal direction of the heat transfer tube. A horizontal support binding member for binding the horizontal supports of the plurality of rows is provided at the end of the horizontal supports of the plurality of rows, and the horizontal support binding member is provided in the longitudinal direction of the heat transfer tube. A panel-type heat exchanger having an integral structure is constructed by being supported and fixed by a plurality of arranged vertical connecting members, and at least one heat exchanger is provided in the flue gas exhaust heat recovery device. It is a thing. Further, according to the present invention, as described in claim 2, in the flue passage through which the combustion exhaust gas passes, a plurality of heat transfer tubes are arranged so as to be connected to the headers provided above and below, and the heat in the exhaust gas is removed. In the exhaust heat recovery apparatus for recovering heat, the heat transfer tube comprises a plurality of rows of horizontal supports provided in a direction perpendicular to the axis of the heat transfer tube, and the horizontal supports arranged in a plurality of stages in the longitudinal direction of the heat transfer tube. Supported by bundling by the ends of the horizontal support of multiple rows,
A panel type heat exchanger having an integral structure is provided, which is provided with a horizontal support binding member for binding the plurality of rows of horizontal supports, and the horizontal support binding member is supported and fixed by a plurality of vertical connection members arranged in the longitudinal direction of the heat transfer tube. The heat exchanger of the integral structure, in the gap portion between the inner wall of the flue and the flue gas is likely to cause uneven flow of exhaust gas, the exhaust gas non-uniform flow prevention member provided on the heat exchanger side, and the inner wall of the flue The exhaust heat recovery device is provided in such a structure that the provided exhaust gas non-uniform flow prevention member can be fitted into each other and can slide by thermal expansion and contraction.
Further, according to the present invention, as described in claim 3, a plurality of heat transfer tubes are arranged in the flue passage through which the combustion exhaust gas passes, by connecting them to headers provided above and below, and the heat in the exhaust gas is removed. In the exhaust heat recovery apparatus for recovering heat, the heat transfer tube comprises a plurality of rows of horizontal supports provided in a direction perpendicular to the axis of the heat transfer tube, and the horizontal supports arranged in a plurality of stages in the longitudinal direction of the heat transfer tube. A horizontal support bundling member for bundling and supporting the plurality of rows of horizontal supports is provided at an end portion of the plurality of rows of horizontal supports, and the plurality of horizontal support bundling members are arranged in the longitudinal direction of the heat transfer tubes. A panel-type heat exchanger having an integral structure is supported and fixed by a vertical connecting member, and the heat exchange is performed at a portion where a drift of exhaust gas is likely to occur between the integral heat exchanger and the side wall of the flue. Exhaust gas drift prevention member to be installed on the side of the flue and the side of the flue Can fitted each other and the exhaust gas drift prevention member provided in, and it is an exhaust heat recovery apparatus disposed in slidable structure by thermal expansion and contraction. Further, according to the present invention, as described in claim 4, in the flue passage through which the combustion exhaust gas passes, a plurality of heat transfer tubes are arranged so as to be connected to the headers provided above and below, and the heat in the exhaust gas is removed. In the exhaust heat recovery apparatus for recovering heat, the heat transfer tube comprises a plurality of rows of horizontal supports provided in a direction perpendicular to the axis of the heat transfer tube, and the horizontal supports arranged in a plurality of stages in the longitudinal direction of the heat transfer tube. A horizontal support bundling member for bundling and supporting the plurality of rows of horizontal supports is provided at an end portion of the plurality of rows of horizontal supports, and the plurality of horizontal support bundling members are arranged in the longitudinal direction of the heat transfer tubes. A panel-type heat exchanger having an integral structure is supported and fixed by a vertical connecting member, and a female-shaped exhaust gas drift prevention member having a concave cross-section in the longitudinal direction of the heat transfer tube is arranged on the side wall of the flue. , The above-mentioned heat in the concave portion of the exhaust gas drift prevention member. Exhaust heat recovery in which a male exhaust gas drift prevention member with a convex cross section composed of a horizontal support bundling member and a vertical connection member of the exchanger is inserted and arranged in a slidable structure by thermal expansion and contraction It is a device. In the exhaust heat recovery apparatus of the present invention, as described in claim 1, a panel type heat exchanger having an integral structure is constructed by supporting and fixing the heat transfer tubes by a horizontal support binding member for binding the horizontal supports and a vertical connection member. Because
Since the heat transfer tubes can be integrated with the upper and lower headers, and they are assembled on the ground, the amount of work in the high places and narrow spaces in the flue is reduced, and at the same time, the heat exchanger can be easily assembled for efficiency. There is an effect that work can be done well and safely. Further, in the exhaust heat recovery apparatus of the present invention, as described in claim 2, the heat exchange is performed in the gap portion between the heat exchanger having the integral structure and the inner wall of the flue, in which a drift of exhaust gas is likely to occur. Since the exhaust gas non-uniform flow prevention member provided on the device side and the exhaust gas non-uniform flow prevention member provided on the inner wall of the flue are arranged so as to be slidable by thermal expansion and contraction, the exhaust gas non-uniform flow prevention member is provided. Since the gap between them is made as small as possible, the bypass amount of exhaust gas can be significantly reduced, and there is an effect that the exhaust heat recovery efficiency can be improved. Further, according to the exhaust heat recovery apparatus of the present invention, as described in claim 3, an exhaust gas non-uniform flow prevention member provided on the heat exchanger side at a portion where the non-uniform flow of the exhaust gas between the side wall of the flue is likely to occur, Since the exhaust gas non-uniform flow prevention member provided on the side wall of the flue can be fitted into each other and is provided in a structure that can slide by thermal expansion and contraction, it can be inserted into the side wall of the flue where the exhaust gas is most likely to flow non-uniformly. Since the exhaust gas non-uniform flow prevention member having the structure is provided, it is possible to effectively suppress the bypass amount of the exhaust gas, and it is possible to improve the exhaust heat recovery efficiency. Further, in the exhaust heat recovery system of the present invention, as described in claim 4, a female-shaped exhaust gas non-uniform flow prevention member having a concave cross-section in the longitudinal direction of the heat transfer tube is disposed on the side wall of the flue, Into the recess of the exhaust gas drift prevention member, a male exhaust gas drift prevention member having a convex cross section constituted by the horizontal support binding member and the vertical connection member of the heat exchanger is fitted and slid by thermal expansion and contraction. Since it is installed in a possible structure, the male type exhaust gas drift formed by the horizontal support bundling member and the vertical connecting member of the panel type heat exchanger of the integral structure in the part of the side wall of the flue where the exhaust gas is most likely to bypass. Since the prevention member is arranged,
With an extremely simple configuration, the uneven flow of exhaust gas can be effectively suppressed, the bypass amount of exhaust gas can be effectively suppressed, and the exhaust heat recovery efficiency can be improved.
【０００６】[0006]
【発明の実施の形態】以下に、本発明の実施の形態につ
いて図面を用いて説明する。図１、図２および図３は、
本発明の排熱回収装置の伝熱管の取付け構造の一例を示
す。なお、従来技術と同様の構成部分については説明を
省略する。図１は、図６に示すＤ−Ｄ部位に配設されて
いる熱交換器の構成を示し、図２は、図１のＥ−Ｅ矢視
図、図３は、図１のＦ−Ｆ矢視図である。図１におい
て、フィン付伝熱管１２ａ同士の接触および振動等を防
ぐために、伝熱管の軸直角方向に複数段設けられた水平
サポート２８の各端部に、複数列の水平サポート２８を
結束する水平サポートの結束部材２９が溶接により取り
付けられており、複数段の水平サポートの結束部材２９
を連結するために、垂直連結部材３０が設けられてい
る。水平サポートの結束部材２９は、図３に示すよう
に、上側の垂直連結部材３０とはボルトにて固定され、
下側の垂直連結部材３０とはボルトによりスライド構造
で支持し、フィン付伝熱管１２ａと垂直連結部材３０
が、排ガスＧの熱による伸び量により垂直連結部材３０
の損傷を防ぐ構造となっている。水平サポートの結束部
材２９と、垂直連結部材３０は、上部および下部管寄せ
と、伝熱管を一体化する時に取り付けられるため、煙道
内での高所作業および狭い空間での取付け作業を行う必
要がなく、地上で製作することができるので組立が容易
となり作業の安全性が確保される。また、図２に示すよ
うに、断面が凹型形状（メス型）の偏流防止部材３１
は、側面内側ケーシング２０ａ、ｂに、水平サポートの
結束部材２９と垂直連結部材３０からなる凸型形状（オ
ス型）の偏流防止部材をスライド可能に挾み込むように
取付けられている。このような構造とすることにより、
排ガスＧによる熱膨張（図１、２に破線で示す）は、オ
ス型偏流防止部材とメス型偏流防止部材とが互いにスラ
イドすることにより吸収されることになる。また、上記
構造とすることにより、 フィン付伝熱管１２ａや、
水平サポート２８と側部内側ケーシング２０ａ、ｂに設
けられた凹型の偏流防止部材との接触が無くなるため
に、従来の排ガスのバイパス量を減らすためのギャップ
を設ける必要が無くなり、また熱膨張により凸型の偏流
防止部材と凹型の偏流防止部材との間の隙間を低減する
ことができるので、排ガスの偏流によるバイパス量を減
らすことができ、排ガスの熱交換効率が向上する。BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to the drawings. 1, 2 and 3
An example of the attachment structure of the heat transfer tube of the exhaust heat recovery apparatus of the present invention is shown. Note that the description of the same components as those of the conventional technique will be omitted. 1 shows the structure of the heat exchanger arranged in the DD section shown in FIG. 6, FIG. 2 is a view taken along the line EE of FIG. 1, and FIG. 3 is FF of FIG. FIG. In FIG. 1, in order to prevent contact between the finned heat transfer tubes 12a, vibration, and the like, a horizontal support 28 that binds a plurality of rows of horizontal supports 28 to each end of a horizontal support 28 that is provided in a plurality of stages in a direction perpendicular to the axis of the heat transfer tubes. The bundling member 29 of the support is attached by welding, and the bundling member 29 of the horizontal support of a plurality of stages
A vertical connecting member 30 is provided to connect the. As shown in FIG. 3, the bundling member 29 of the horizontal support is fixed to the upper vertical connecting member 30 with a bolt,
The lower vertical connecting member 30 is supported by a bolt with a sliding structure, and the finned heat transfer tube 12a and the vertical connecting member 30 are supported.
However, due to the amount of expansion of the exhaust gas G due to heat, the vertical connecting member 30
It has a structure that prevents damage to. The bundling member 29 of the horizontal support and the vertical connecting member 30 are attached when the upper and lower pipe headers and the heat transfer pipe are integrated, so that it is necessary to perform work at a high place in the flue and work in a narrow space. Instead, it can be manufactured on the ground, which facilitates assembly and ensures work safety. Further, as shown in FIG. 2, the drift prevention member 31 having a concave cross section (female type)
Is attached to the side inner casings 20a and 20b so as to slidably insert a convex (male) drift prevention member including a bundling member 29 of a horizontal support and a vertical connecting member 30. By adopting such a structure,
The thermal expansion due to the exhaust gas G (indicated by the broken line in FIGS. 1 and 2) is absorbed by the male type drift prevention member and the female type drift prevention member sliding on each other. Further, by adopting the above structure, the finned heat transfer tube 12a,
Since there is no contact between the horizontal support 28 and the concave drift prevention members provided on the side inner casings 20a and 20b, it is not necessary to provide a gap for reducing the bypass amount of exhaust gas, which is required in the related art. Since the gap between the mold drift prevention member and the concave drift prevention member can be reduced, the amount of bypass due to drift of exhaust gas can be reduced, and the heat exchange efficiency of exhaust gas is improved.
【０００７】[0007]
【発明の効果】本発明の排熱回収装置は、請求項１に記
載のように、伝熱管を水平サポートを結束する水平サポ
ート結束部材と垂直連結部材により支持固定して一体構
造のパネル型熱交換器を構成しているので、上部および
下部管寄せと伝熱管を一体化することができ、地上にお
いて組立てられるため、煙道内の高所および狭い空間で
の作業量が少なくなると同時に、熱交換器の組立てが容
易であり、能率良く安全に作業が行える効果がある。ま
た、本発明の排熱回収装置は、請求項２に記載のよう
に、一体構造の熱交換器と、上記煙道の内壁との間の排
ガスの偏流が生じ易い隙間部に、上記熱交換器側に設け
る排ガス偏流防止部材と、煙道の内壁に設ける排ガス偏
流防止部材とが互いに嵌挿でき、かつ熱膨張および収縮
によってスライド可能な構造に配設しているので、上記
排ガス偏流防止部材間に生じる隙間部を最小限に小さく
しているので、排ガスのバイパス量を著しく少なくする
ことができ、排熱回収効率を向上できる効果がある。ま
た、本発明の排熱回収装置は、請求項３に記載のよう
に、煙道の側壁との間の排ガスの偏流が生じ易い部位
に、上記熱交換器側に設ける排ガス偏流防止部材と、煙
道の側壁に設ける排ガス偏流防止部材とが互いに嵌挿で
き、かつ熱膨張および収縮によってスライド可能な構造
に設けているので、最も排ガスが偏流しやすい煙道の側
壁部に、互いに嵌挿できる構造の排ガス偏流防止部材を
設けているので、排ガスのバイパス量を効果的に抑制す
ることが可能となり、排熱回収効率を向上させることが
できる効果がある。また、本発明の排熱回収装置は、請
求項４に記載のように、煙道の側壁に伝熱管の長手方向
に凹型の断面形状をしたメス形の排ガス偏流防止部材を
配設し、該排ガス偏流防止部材の凹部に、上記熱交換器
の水平サポート結束部材と垂直連結部材とにより構成さ
れる断面が凸型形状のオス型の排ガス偏流防止部材を嵌
挿し、かつ熱膨張および収縮によってスライド可能な構
造に設けているので、煙道の側壁の最も排ガスがバイパ
スしやすい部分に、一体構造のパネル型熱交換器の水平
サポート結束部材と垂直連結部材とにより構成されたオ
ス型の排ガス偏流防止部材を配設しているので、極めて
簡易な構成で排ガスの偏流を有効に抑制することがで
き、排ガスのバイパス量を効果的に抑制することが可能
となり、排熱回収効率が向上できる効果がある。According to the exhaust heat recovery apparatus of the present invention, as described in claim 1, the heat transfer tube is integrally supported by the horizontal support binding member for binding the horizontal support and the vertical connection member to fix the heat transfer tube in a unitary structure. Since the exchanger is configured, the upper and lower headers and the heat transfer tubes can be integrated, and because they are assembled on the ground, the amount of work in high places and narrow spaces in the flue is reduced, and at the same time heat exchange is performed. It is easy to assemble the container, and it has the effect of enabling efficient and safe work. Further, in the exhaust heat recovery apparatus of the present invention, as described in claim 2, the heat exchange is performed in the gap portion between the heat exchanger having the integral structure and the inner wall of the flue, in which a drift of exhaust gas is likely to occur. Since the exhaust gas non-uniform flow prevention member provided on the device side and the exhaust gas non-uniform flow prevention member provided on the inner wall of the flue are arranged so as to be slidable by thermal expansion and contraction, the exhaust gas non-uniform flow prevention member is provided. Since the gap between them is made as small as possible, the bypass amount of exhaust gas can be significantly reduced, and there is an effect that the exhaust heat recovery efficiency can be improved. Further, according to the exhaust heat recovery apparatus of the present invention, as described in claim 3, an exhaust gas non-uniform flow prevention member provided on the heat exchanger side at a portion where the non-uniform flow of the exhaust gas between the side wall of the flue is likely to occur, Since the exhaust gas non-uniform flow prevention member provided on the side wall of the flue can be fitted into each other and is provided in a structure that can slide by thermal expansion and contraction, it can be inserted into the side wall of the flue where the exhaust gas is most likely to flow non-uniformly. Since the exhaust gas non-uniform flow prevention member having the structure is provided, it is possible to effectively suppress the bypass amount of the exhaust gas, and it is possible to improve the exhaust heat recovery efficiency. Further, in the exhaust heat recovery system of the present invention, as described in claim 4, a female-shaped exhaust gas non-uniform flow prevention member having a concave cross-section in the longitudinal direction of the heat transfer tube is disposed on the side wall of the flue, Into the recess of the exhaust gas drift prevention member, a male exhaust gas drift prevention member having a convex cross section constituted by the horizontal support binding member and the vertical connection member of the heat exchanger is fitted and slid by thermal expansion and contraction. Since it is installed in a possible structure, the male type exhaust gas drift formed by the horizontal support bundling member and the vertical connecting member of the panel type heat exchanger of the integral structure in the part of the side wall of the flue where the exhaust gas is most likely to bypass. Since the prevention member is provided, the uneven flow of the exhaust gas can be effectively suppressed with an extremely simple configuration, the bypass amount of the exhaust gas can be effectively suppressed, and the exhaust heat recovery efficiency can be improved. A.
【図１】本発明の実施の形態で例示した排熱回収装置の
構成を示す模式図。FIG. 1 is a schematic diagram showing a configuration of an exhaust heat recovery device exemplified in an embodiment of the present invention.
【図２】図１のＥ−Ｅ矢視図。FIG. 2 is an EE arrow view of FIG.
【図３】図１のＦ−Ｆ矢視図。FIG. 3 is a view on arrow FF in FIG.
【図４】従来の排熱回収ボイラの構成を示す模式図。FIG. 4 is a schematic diagram showing a configuration of a conventional exhaust heat recovery boiler.
【図５】図４のＡ−Ａ矢視図で、従来の排熱回収ボイラ
の保温構造を示す断面図。5 is a sectional view taken along the line AA in FIG. 4, showing a heat retaining structure of a conventional exhaust heat recovery boiler.
【図６】図４のＢ部の拡大図。FIG. 6 is an enlarged view of part B of FIG.
【図７】図６のＣ−Ｃ矢視図。FIG. 7 is a view taken in the direction of the arrows CC in FIG. 6;
【図８】図７のＤ−Ｄ部位の詳細図。FIG. 8 is a detailed view of the DD section in FIG.
【図９】図８のＥ−Ｅ矢視図。FIG. 9 is a view on arrow EE in FIG.
１…過熱器 ２…第１段高圧蒸発器 ３…脱硝装置 ４…第２段高圧蒸発器 ５…高圧ドラム ６…降水管 ７…高圧節炭器 ８…低圧蒸発器 ９…低圧ドラム １０…降水管 １１…低圧節炭器 １２…伝熱管 １２ａ…フィン付伝熱管 １２ｂ…裸伝熱管 １３…下部管寄せ １４…管寄せサポート １５…管寄せサポートビーム １６…保温材 １７ａ…側部外側ケーシング １７ｂ…側部外側ケーシング １８…上部連絡管 １９…上部管寄せ ２０ａ…側部内側ケーシング ２０ｂ…側部内側ケーシング ２１…下部連絡管 ２２…上部内側ケーシング ２３…下部内側ケーシング ２４…下部外側ケーシング ２５…上部外側ケーシング ２６ａ…上部偏流防止部材 ２６ｂ…下部偏流防止部材 ２７…側部偏流防止部材 ２８…水平サポート ２９…水平サポートの結束部材 ３０…垂直連結部材 ３１…凹型形状（メス型）の偏流防止部材 １００…煙道 Ｇ…排ガス Ｓ1…高圧蒸気 Ｓ2…低圧蒸気 Ｈ1…非伝熱空間 Ｈ2…伝熱空間 Ｈ3…非伝熱空間 Ｗ1…非伝熱空間 Ｗ2…伝熱空間 Ｗ3…非伝熱空間1 ... Superheater 2 ... First-stage high-pressure evaporator 3 ... Denitrification device 4 ... Second-stage high-pressure evaporator 5 ... High-pressure drum 6 ... Precipitation pipe 7 ... High-pressure economizer 8 ... Low-pressure evaporator 9 ... Low-pressure drum 10 ... Precipitation Tube 11 ... Low pressure economizer 12 ... Heat transfer tube 12a ... Heat transfer tube with fins 12b ... Bare heat transfer tube 13 ... Bottom guide 14 ... Guide support 15 ... Support support beam 16 ... Heat insulating material 17a ... Side outer casing 17b ... Side outer casing 18 ... Upper connecting pipe 19 ... Upper pipe shifting 20a ... Side inner casing 20b ... Side inner casing 21 ... Lower connecting pipe 22 ... Upper inner casing 23 ... Lower inner casing 24 ... Lower outer casing 25 ... Upper outside Casing 26a ... Upper drift prevention member 26b ... Lower drift prevention member 27 ... Side drift prevention member 28 ... Horizontal support 29 ... Horizontal support binding member 30 ... vertical connecting member 31 ... concave shape drift prevention member 100 ... flue G ... exhaust gas (female) S 1 ... high pressure steam S 2 ... low-pressure steam H 1 ... Hidden thermospatial H 2 ... heat transfer space H 3 ... Non-heat transfer space W 1 … Non-heat transfer space W 2 … Heat transfer space W 3 … Non heat transfer space
Claims (4)
熱管を、上、下に設けられた管寄せに接続して配置し、
上記排ガス中の熱を回収する排熱回収装置であって、上
記伝熱管は、該伝熱管の軸直角方向に設けられた複数列
の水平サポートと、該伝熱管の長手方向に複数段配設さ
れた上記水平サポートによって結束支持され、上記複数
列の水平サポートの端部に、該複数列の水平サポートを
結束する水平サポート結束部材を設け、該水平サポート
結束部材を、伝熱管の長手方向に配列された複数の垂直
連結部材により支持固定して一体構造のパネル型熱交換
器を構成し、該熱交換器を少なくとも１基以上、上記煙
道の内部に配設したことを特徴とする排熱回収装置。1. A plurality of heat transfer tubes are arranged in a flue passage through which combustion exhaust gas passes, connected to upper and lower heat transfer tubes.
In the exhaust heat recovery device for recovering heat in the exhaust gas, the heat transfer tube comprises a plurality of rows of horizontal supports provided in a direction perpendicular to the axis of the heat transfer tube, and a plurality of stages arranged in the longitudinal direction of the heat transfer tube. A horizontal support binding member for binding the horizontal supports of the plurality of rows is provided at the end of the horizontal supports of the plurality of rows, and the horizontal support binding member is provided in the longitudinal direction of the heat transfer tube. An exhaust system characterized in that a panel-type heat exchanger having an integral structure is constituted by being supported and fixed by a plurality of arranged vertical connecting members, and at least one heat exchanger is arranged inside the flue. Heat recovery device.
熱管を、上、下に設けられた管寄せに接続して配置し、
上記排ガス中の熱を回収する排熱回収装置であって、上
記伝熱管は、該伝熱管の軸直角方向に設けられた複数列
の水平サポートと、該伝熱管の長手方向に複数段配設さ
れた上記水平サポートによって結束支持され、上記複数
列の水平サポートの端部に、該複数列の水平サポートを
結束する水平サポート結束部材を設け、該水平サポート
結束部材を、伝熱管の長手方向に配列された複数の垂直
連結部材により支持固定して一体構造のパネル型熱交換
器を構成し、該一体構造の熱交換器と、上記煙道の内壁
との間の排ガスの偏流が生じ易い隙間部に、上記熱交換
器側に設ける排ガス偏流防止部材と、煙道の内壁に設け
る排ガス偏流防止部材とが互いに嵌挿でき、かつ熱膨張
および収縮によってスライド可能な構造に配設したこと
を特徴とする排熱回収装置。2. A plurality of heat transfer tubes are arranged in a flue passage through which combustion exhaust gas passes, connected to upper and lower heat transfer tubes.
In the exhaust heat recovery device for recovering heat in the exhaust gas, the heat transfer tube comprises a plurality of rows of horizontal supports provided in a direction perpendicular to the axis of the heat transfer tube, and a plurality of stages arranged in the longitudinal direction of the heat transfer tube. A horizontal support binding member for binding the horizontal supports of the plurality of rows is provided at the end of the horizontal supports of the plurality of rows, and the horizontal support binding member is provided in the longitudinal direction of the heat transfer tube. A panel-type heat exchanger having an integral structure is supported and fixed by a plurality of arranged vertical coupling members, and a gap between the heat exchanger having the integral structure and the inner wall of the flue is likely to cause a drift of exhaust gas. In the portion, the exhaust gas non-uniform flow prevention member provided on the heat exchanger side and the exhaust gas non-uniform flow prevention member provided on the inner wall of the flue can be fitted into each other and arranged in a structure that can slide by thermal expansion and contraction. Exhaust heat to Osamu apparatus.
熱管を、上、下に設けられた管寄せに接続して配置し、
上記排ガス中の熱を回収する排熱回収装置であって、上
記伝熱管は、該伝熱管の軸直角方向に設けられた複数列
の水平サポートと、該伝熱管の長手方向に複数段配設さ
れた上記水平サポートによって結束支持され、上記複数
列の水平サポートの端部に、該複数列の水平サポートを
結束する水平サポート結束部材を設け、該水平サポート
結束部材を、伝熱管の長手方向に配列された複数の垂直
連結部材により支持固定して一体構造のパネル型熱交換
器を構成し、該一体構造の熱交換器と、上記煙道の側壁
との間の排ガスの偏流が生じ易い部位に、上記熱交換器
側に設ける排ガス偏流防止部材と、煙道の側壁に設ける
排ガス偏流防止部材とが互いに嵌挿でき、かつ熱膨張お
よび収縮によってスライド可能な構造に配設したことを
特徴とする排熱回収装置。3. A plurality of heat transfer tubes are arranged in a flue passage through which combustion exhaust gas passes, connected to upper and lower heat transfer tubes.
In the exhaust heat recovery device for recovering heat in the exhaust gas, the heat transfer tube comprises a plurality of rows of horizontal supports provided in a direction perpendicular to the axis of the heat transfer tube, and a plurality of stages arranged in the longitudinal direction of the heat transfer tube. A horizontal support binding member for binding the horizontal supports of the plurality of rows is provided at the end of the horizontal supports of the plurality of rows, and the horizontal support binding member is provided in the longitudinal direction of the heat transfer tube. A portion of a panel-type heat exchanger having an integral structure that is supported and fixed by a plurality of arranged vertical coupling members, and a portion where exhaust gas is liable to flow unevenly between the integral heat exchanger and the side wall of the flue In addition, the exhaust gas non-uniform flow prevention member provided on the heat exchanger side, and the exhaust gas non-uniform flow prevention member provided on the side wall of the flue can be inserted into each other, and arranged in a structure slidable by thermal expansion and contraction, Exhaust heat times Apparatus.
熱管を、上、下に設けられた管寄せに接続して配置し、
上記排ガス中の熱を回収する排熱回収装置であって、上
記伝熱管は、該伝熱管の軸直角方向に設けられた複数列
の水平サポートと、該伝熱管の長手方向に複数段配設さ
れた上記水平サポートによって結束支持され、上記複数
列の水平サポートの端部に、該複数列の水平サポートを
結束する水平サポート結束部材を設け、該水平サポート
結束部材を、伝熱管の長手方向に配列された複数の垂直
連結部材により支持固定して一体構造のパネル型熱交換
器を構成し、上記煙道の側壁に、伝熱管の長手方向に凹
型の断面形状をしたメス形の排ガス偏流防止部材を配設
し、該排ガス偏流防止部材の凹部に、上記熱交換器の水
平サポート結束部材と垂直連結部材とにより構成される
断面が凸型形状のオス型の排ガス偏流防止部材を嵌挿
し、かつ熱膨張および収縮によってスライド可能な構造
に配設したことを特徴とする排熱回収装置。4. A plurality of heat transfer tubes are arranged in a flue passage through which combustion exhaust gas passes, connected to upper and lower heat transfer tubes.
In the exhaust heat recovery device for recovering heat in the exhaust gas, the heat transfer tube comprises a plurality of rows of horizontal supports provided in a direction perpendicular to the axis of the heat transfer tube, and a plurality of stages arranged in the longitudinal direction of the heat transfer tube. A horizontal support binding member for binding the horizontal supports of the plurality of rows is provided at the end of the horizontal supports of the plurality of rows, and the horizontal support binding member is provided in the longitudinal direction of the heat transfer tube. A panel-type heat exchanger with an integral structure is supported and fixed by a plurality of arranged vertical connecting members, and a female-shaped exhaust gas drift prevention with a concave cross-sectional shape in the longitudinal direction of the heat transfer tube is formed on the side wall of the flue. A member is provided, and a concave portion of the exhaust gas non-uniform flow prevention member is fitted with a male-shaped exhaust gas non-uniform flow prevention member having a convex cross-section formed by a horizontal support binding member and a vertical connection member of the heat exchanger, And thermal expansion and Shrinkage exhaust heat recovery apparatus being characterized in that disposed in slidable structure by.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP06981596A JP3737186B2 (en) | 1996-03-26 | 1996-03-26 | Waste heat recovery device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP06981596A JP3737186B2 (en) | 1996-03-26 | 1996-03-26 | Waste heat recovery device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH09257202A true JPH09257202A (en) | 1997-09-30 |
| JP3737186B2 JP3737186B2 (en) | 2006-01-18 |
Family
ID=13413643
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP06981596A Expired - Lifetime JP3737186B2 (en) | 1996-03-26 | 1996-03-26 | Waste heat recovery device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3737186B2 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002106805A (en) * | 2000-09-28 | 2002-04-10 | Ishikawajima Harima Heavy Ind Co Ltd | Horizontal load transfer structure of heat transfer tube in heat recovery steam generator |
| JP2002107092A (en) * | 2000-09-27 | 2002-04-10 | Sumitomo Chem Co Ltd | Multi-tubular heat exchanger and its repair method |
| JP2012229908A (en) * | 2011-03-22 | 2012-11-22 | Nuovo Pignone Spa | Vessel of heat storage and release apparatus, heat storage and release assembly and energy production plant |
-
1996
- 1996-03-26 JP JP06981596A patent/JP3737186B2/en not_active Expired - Lifetime
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002107092A (en) * | 2000-09-27 | 2002-04-10 | Sumitomo Chem Co Ltd | Multi-tubular heat exchanger and its repair method |
| JP2002106805A (en) * | 2000-09-28 | 2002-04-10 | Ishikawajima Harima Heavy Ind Co Ltd | Horizontal load transfer structure of heat transfer tube in heat recovery steam generator |
| JP2012229908A (en) * | 2011-03-22 | 2012-11-22 | Nuovo Pignone Spa | Vessel of heat storage and release apparatus, heat storage and release assembly and energy production plant |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3737186B2 (en) | 2006-01-18 |
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