JP2008224173A - Two-tower type exhaust heat recovery system - Google Patents
Two-tower type exhaust heat recovery system Download PDFInfo
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- JP2008224173A JP2008224173A JP2007066148A JP2007066148A JP2008224173A JP 2008224173 A JP2008224173 A JP 2008224173A JP 2007066148 A JP2007066148 A JP 2007066148A JP 2007066148 A JP2007066148 A JP 2007066148A JP 2008224173 A JP2008224173 A JP 2008224173A
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E20/00—Combustion technologies with mitigation potential
- Y02E20/34—Indirect CO2mitigation, i.e. by acting on non CO2directly related matters of the process, e.g. pre-heating or heat recovery
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
- Y02P80/00—Climate change mitigation technologies for sector-wide applications
- Y02P80/10—Efficient use of energy, e.g. using compressed air or pressurized fluid as energy carrier
- Y02P80/15—On-site combined power, heat or cool generation or distribution, e.g. combined heat and power [CHP] supply
Abstract
Description
本発明は、輻射式熱交換器とシェルアンドチューブ式熱交換器の組合せによる2塔式排熱回収システムに関するものである。 The present invention relates to a two-column exhaust heat recovery system using a combination of a radiation heat exchanger and a shell and tube heat exchanger.
シェルアンドチューブ式熱交換器は、一般的に多くのプロセスで使用されている。図5に下水汚泥の流動焼却設備の例を示す。下水汚泥の流動焼却設備には、通常、流動焼却炉1の排熱回収及び流動用空気の予熱を目的とした熱交換器3が設置される。また炉内の燃焼温度が異常に高くなる事を防ぐため、一度昇温した流動空気を冷却するための熱交換器4及び冷却空気用送風機B2が必要となる。この熱交換器4は、炉内の燃焼温度が正常である場合、流動空気の冷却が必要でないため、通常は冷却用の空気を通風せず、650℃〜700℃流動空気のみが通過することとなる。したがって、熱交換器4に使用される金属材料は、高価な耐熱鋼を使用せざるを得ない。
一方、流動空気を予熱する熱交換器3は、850℃〜900℃の排ガスを利用し、流動空気送風機B1から導入される流動空気を650℃〜700℃に予熱する必要があるため、近年の排熱の高回収化、運転方法等により管板の熱疲労による割れ等が発生しやすく、流動焼却炉1の運転に支障を来たす場合もある。
On the other hand, since the heat exchanger 3 that preheats the fluid air needs to preheat the fluid air introduced from the fluid air blower B1 to 650 ° C. to 700 ° C. using exhaust gas at 850 ° C. to 900 ° C. Due to the high recovery of exhaust heat, the operation method, etc., cracks due to thermal fatigue of the tube sheet are likely to occur, which may hinder the operation of the fluidized incinerator 1.
本発明は、上記熱交換器4及び冷却空気用送風機B2を設置することなしに、上記熱交換器3から排出される流動空気P3の温度を制御可能とし、更に熱交換器3の損傷を低減する2塔式排熱回収システムを提供することを課題とする。 The present invention makes it possible to control the temperature of the flowing air P3 discharged from the heat exchanger 3 without installing the heat exchanger 4 and the cooling air blower B2, and further reduce damage to the heat exchanger 3. It is an object of the present invention to provide a two-column exhaust heat recovery system.
本発明の2塔式排熱回収システムは、流動焼却炉等の熱源装置から排ガス等の高温ガスを導入して熱を回収する輻射式熱交換器と、該輻射式熱交換器から温度が低下した上記高温ガスを導入して熱を更に回収すると共に該高温ガスを外部に排出するシェルアンドチューブ式熱交換器から成り、該シェルアンドチューブ式熱交換器に予熱流体を導入して上記回収熱により温度を高めると共に、該高温となった予熱流体を上記輻射式熱交換器に導入して上記回収熱により更に高温にし、該高温となった予熱流体を上記熱源装置に送り込むように構成したことを特徴とする。また、シェルアンドチューブ式熱交換器に導入する予熱流体を、上記高温ガスの上流側および下流側にそれぞれ分配するように構成したことを特徴とする。さらに、上記分配される予熱流体の流量を予熱流体流量調整弁によりコントロールすることを特徴とする。 The two-column exhaust heat recovery system of the present invention includes a radiant heat exchanger that recovers heat by introducing a high-temperature gas such as exhaust gas from a heat source device such as a fluidized incinerator, and a temperature drop from the radiant heat exchanger. A shell and tube heat exchanger that introduces the high temperature gas to further recover heat and discharges the high temperature gas to the outside, and introduces a preheating fluid into the shell and tube heat exchanger to The temperature of the preheating fluid is increased by the above, and the high temperature preheating fluid is introduced into the radiant heat exchanger to be further increased by the recovered heat, and the high temperature preheating fluid is sent to the heat source device. It is characterized by. Further, the present invention is characterized in that the preheating fluid introduced into the shell-and-tube heat exchanger is distributed to the upstream side and the downstream side of the high-temperature gas. Further, the flow rate of the preheated fluid to be distributed is controlled by a preheated fluid flow rate adjusting valve.
本発明の2塔式排熱回収システムを採用することにより、従来では予熱流体P3の温度を変化させるために設置されていた、予熱流体P3の温度冷却用熱交換器4と冷却空気用送風機B2の設置が不要となり、経済性が向上する。
また、シェルアンドチューブ式熱交換器3に導入される排ガスの温度を低下させる事が可能となり、排ガス導入部と予熱流体排出部に位置する管板の熱負荷を低減することができ、シェルアンドチューブ式熱交換器での予熱流体温度も低下できるので、従来のシェルアンドチューブ式熱交換器の熱疲労による管板割れを軽減することができる。
By adopting the two-column exhaust heat recovery system of the present invention, the heat exchanger 4 for cooling the temperature of the preheating fluid P3 and the blower B2 for cooling air, which are conventionally installed to change the temperature of the preheating fluid P3. Installation is unnecessary and the economy is improved.
Further, the temperature of the exhaust gas introduced into the shell-and-tube heat exchanger 3 can be lowered, and the heat load on the tube plates located at the exhaust gas introduction part and the preheating fluid discharge part can be reduced. Since the preheating fluid temperature in the tube heat exchanger can also be lowered, it is possible to reduce tube sheet cracking due to thermal fatigue of the conventional shell and tube heat exchanger.
以下、本発明を図示の実施例に基づき更に詳細に説明する。
図1において、1は流動焼却炉、2は輻射式熱交換器、3はシェルアンドチューブ式熱交換器である。
Hereinafter, the present invention will be described in more detail based on illustrated embodiments.
In FIG. 1, 1 is a fluidized incinerator, 2 is a radiant heat exchanger, and 3 is a shell and tube heat exchanger.
流動焼却炉1から排出される排ガスF1は、輻射式熱交換器2の上部から導入され予熱流体P2と熱交換した後、下部から排出される。続いて、上記輻射式熱交換器2から排出される排ガスは、シェルアンドチューブ式熱交換器3の下部に導入され、予熱流体P1と熱交換した後、温度が低下した排ガスF2として上部より排出される。 The exhaust gas F1 discharged from the fluidized incinerator 1 is introduced from the upper part of the radiant heat exchanger 2, exchanges heat with the preheating fluid P2, and is then discharged from the lower part. Subsequently, the exhaust gas discharged from the radiant heat exchanger 2 is introduced into the lower part of the shell-and-tube heat exchanger 3, and after exchanging heat with the preheating fluid P1, it is discharged from the upper part as exhaust gas F2 having a lowered temperature. Is done.
一方、予熱流体P1は、予熱流体送風機B1から送り出され、予熱流体流量調整弁V1およびV2により分配され、シェルアンドチューブ式熱交換器3の上下に設置された導入口に導入される。導入された予熱流体P1は、シェルアンドチューブ式熱交換器3で排ガスとの熱交換により、温度が上昇し予熱流体P2となって下部の排出口より排出される。昇温された予熱流体P2は、輻射型熱交換器2に設置された上部の導入口に送り込まれ、排ガスF1との熱交換により更に温度が上昇した後、予熱流体P3として輻射型熱交換器2の下部排出口より排出され、流動焼却炉1に送り込まれる。 On the other hand, the preheating fluid P <b> 1 is sent out from the preheating fluid blower B <b> 1, distributed by the preheating fluid flow rate adjusting valves V <b> 1 and V <b> 2, and introduced into the inlets installed above and below the shell and tube heat exchanger 3. The introduced preheating fluid P1 rises in temperature by heat exchange with the exhaust gas in the shell-and-tube heat exchanger 3 and becomes a preheating fluid P2 and is discharged from the lower discharge port. The heated preheating fluid P2 is sent to the upper inlet installed in the radiant heat exchanger 2, and after the temperature is further increased by heat exchange with the exhaust gas F1, the radiant heat exchanger is used as the preheating fluid P3. 2 is discharged from the lower discharge port 2 and fed into the fluidized incinerator 1.
上記熱交換プロセスにおいて、予熱流体P3の温度は、予熱流体調整弁V1およびV2による予熱流体P1の分配量を変化させる事によって可能となる。
すなわち、流体流量調整弁V1側の流量を増加させると共に、流体流量調整弁V2側の流量を減少させることにより、予熱流体P3の温度は高温とすることができ、これとは逆に流体流量調整弁V2側の流体流量を増加させることにより、予熱流体P3の温度を低下させることができる。
In the heat exchange process, the temperature of the preheating fluid P3 can be changed by changing the distribution amount of the preheating fluid P1 by the preheating fluid regulating valves V1 and V2.
That is, by increasing the flow rate on the fluid flow rate adjustment valve V1 side and decreasing the flow rate on the fluid flow rate adjustment valve V2 side, the temperature of the preheating fluid P3 can be increased, and conversely, the fluid flow rate adjustment By increasing the fluid flow rate on the valve V2 side, the temperature of the preheating fluid P3 can be lowered.
図2は、上記輻射式熱交換器2およびシェルアンドチューブ式熱交換器3の縦断面を示し、図3および4は、それぞれ輻射式熱交換器2およびシェルアンドチューブ式熱交換器3の横断面を示す。
本実施例において、排ガスF1は輻射型熱交換器2の排ガス導入口23から熱交換器内に導入され、排ガスの持つガス輻射(ガス放射)熱により伝熱管5を加熱しながら降下し、排ガス排出室11から排出される。
FIG. 2 shows a longitudinal section of the radiant heat exchanger 2 and the shell-and-tube heat exchanger 3, and FIGS. 3 and 4 show crossings of the radiant heat exchanger 2 and the shell-and-tube heat exchanger 3, respectively. Show the surface.
In the present embodiment, the exhaust gas F1 is introduced into the heat exchanger from the exhaust gas inlet 23 of the radiant heat exchanger 2, and falls while heating the heat transfer tube 5 by the gas radiation (gas radiation) heat of the exhaust gas. It is discharged from the discharge chamber 11.
一方、予熱流体P2は、予熱流体導入口6より導入され、予熱流体導入側環状ヘッダー7に導かれ、図3に示されるように円周上に配置された伝熱管5の内部を降下しながら、加熱された伝熱管5の熱を吸収して所定の温度に昇温され、予熱流体排出側環状ヘッダー8を経て、予熱流体排出口9より予熱流体P3として排出される。 On the other hand, the preheating fluid P2 is introduced from the preheating fluid introduction port 6, guided to the preheating fluid introduction side annular header 7, and descends inside the heat transfer tube 5 arranged on the circumference as shown in FIG. Then, the heat of the heated heat transfer tube 5 is absorbed and the temperature is raised to a predetermined temperature, and is discharged as a preheated fluid P3 from the preheated fluid discharge port 9 through the preheated fluid discharge side annular header 8.
また、輻射式熱交換器2から排出された排ガスは、図2におけるシェルアンドチューブ式熱交換器3の排ガス導入室20から導入され、図4に示されるように、外筒19内に配置された伝熱管12の中を上昇しながら熱交換した後、排ガス排出室21を経由して、排出口22から排ガスF2として排出される。 Further, the exhaust gas discharged from the radiant heat exchanger 2 is introduced from the exhaust gas introduction chamber 20 of the shell and tube heat exchanger 3 in FIG. 2, and is arranged in the outer cylinder 19 as shown in FIG. After exchanging heat while moving up in the heat transfer pipe 12, it is discharged as exhaust gas F <b> 2 from the exhaust port 22 via the exhaust gas discharge chamber 21.
一方、予熱流体P1は、予熱流体流量調整弁V1、V2により分配され、予熱流体導入口13および16からそれぞれ導入される。予熱流体導入口13から導入される予熱流体は、予熱流体導入側ヘッダー14にて、最も熱交換率が高くなる方向より、多数本の伝熱管12と直交するよう外筒19内に導かれる。外筒19内に導かれた予熱流体P1は、外筒19内に多数設置されているバッフルプレート(邪魔板)15により伝熱管12に対し直交および並行の流れに整流されながら、伝熱管12との間で熱交換される。熱交換により温度が上昇した予熱流体P1は、予熱流体排出ヘッダー17に於いて予熱流体流量調整弁V2から分配される予熱流体P1と合流し、予熱流体排出口18から予熱流体P2として排出される。 On the other hand, the preheating fluid P1 is distributed by the preheating fluid flow rate adjusting valves V1 and V2 and introduced from the preheating fluid introduction ports 13 and 16, respectively. The preheated fluid introduced from the preheated fluid introduction port 13 is guided into the outer cylinder 19 in the preheated fluid introduction side header 14 so as to be orthogonal to the multiple heat transfer tubes 12 from the direction in which the heat exchange rate is highest. The preheating fluid P1 guided into the outer cylinder 19 is rectified into a flow perpendicular to and parallel to the heat transfer pipe 12 by baffle plates (baffle plates) 15 installed in the outer cylinder 19, while Heat exchange between. The preheating fluid P1 whose temperature has been raised by heat exchange joins with the preheating fluid P1 distributed from the preheating fluid flow rate adjusting valve V2 in the preheating fluid discharge header 17, and is discharged as the preheating fluid P2 from the preheating fluid discharge port 18. .
本実施例のシステムは、流動焼却炉1に送る予熱流体P3の温度幅により、必要温度に調節可能なように、輻射式熱交換器2およびシェルアンドチューブ式熱交換器3がそれぞれ設計される。 In the system of the present embodiment, the radiant heat exchanger 2 and the shell and tube heat exchanger 3 are respectively designed so as to be adjustable to the required temperature depending on the temperature range of the preheating fluid P3 sent to the fluidized incinerator 1. .
1 流動焼却炉
2 輻射型熱交換器
3 シェルアンドチューブ式熱交換器
4 空気冷却用熱交換器
5 伝熱管
6 予熱流体導入口
7 導入側環状ヘッダー
8 予熱流体排出側環状ヘッダー
9 予熱流体排出口
10 外筒
11 排ガス排出室
12 伝熱管
13 予熱流体導入口
14 予熱流体導入側ヘッダー
15 バッフルプレート(邪魔板)
16 予熱流体導入口
17 予熱流体排出側ヘッダー
18 予熱流体排出口
19 外筒
20 排ガス導入室
21 排ガス排出室
22 排ガス排出口
23 排ガス導入口
B1 流動空気送風機
B2 冷却空気用送風機
P1 予熱流体
P2 予熱流体
P3 予熱流体
V1 予熱流体流量調整弁
V2 予熱流体流量調整弁
DESCRIPTION OF SYMBOLS 1 Fluidized incinerator 2 Radiation type heat exchanger 3 Shell-and-tube heat exchanger 4 Air cooling heat exchanger 5 Heat transfer tube 6 Preheating fluid introduction port 7 Introduction side annular header 8 Preheating fluid discharge side annular header 9 Preheating fluid discharge port 10 Outer cylinder 11 Exhaust gas discharge chamber 12 Heat transfer tube 13 Preheating fluid introduction port 14 Preheating fluid introduction side header 15 Baffle plate (baffle plate)
16 Preheating fluid introduction port 17 Preheating fluid discharge side header 18 Preheating fluid discharge port 19 Outer cylinder 20 Exhaust gas introduction chamber 21 Exhaust gas discharge chamber 22 Exhaust gas discharge port 23 Exhaust gas introduction port B1 Fluid air blower B2 Cooling air blower P1 Preheating fluid P2 Preheating fluid P3 Preheating fluid V1 Preheating fluid flow rate adjustment valve V2 Preheating fluid flow rate adjustment valve
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JP2010144999A (en) * | 2008-12-18 | 2010-07-01 | Alstom Technology Ltd | Multitubular heat exchanger |
JP2010169326A (en) * | 2009-01-23 | 2010-08-05 | Alstom Technology Ltd | Shell-and-tube exchanger |
CN101943529A (en) * | 2010-09-29 | 2011-01-12 | 西安航天华威化工生物工程有限公司 | Dry cooling device and method for high-temperature gas |
JP2013083384A (en) * | 2011-10-07 | 2013-05-09 | Alstom Technology Ltd | Operation method and device of multitubular heat exchanger in fluidized incinerator system |
CN103672933A (en) * | 2012-09-17 | 2014-03-26 | 邹岳明 | Smoke flue, and vehicle, burning furnace, gas water heater all applying smoke flue |
JP2017096532A (en) * | 2015-11-20 | 2017-06-01 | 株式会社マツダ | Regenerative combustion furnace |
JP2020176728A (en) * | 2019-04-15 | 2020-10-29 | 株式会社タクボ精機製作所 | Heat exchanger |
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DE102015220742A1 (en) * | 2015-10-23 | 2017-04-27 | Arvos Gmbh | Industrierußherstellungsanlage |
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JP2005114218A (en) * | 2003-10-06 | 2005-04-28 | Sanki Eng Co Ltd | Operation method for fluidized incinerator system |
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JPH01234713A (en) * | 1988-03-16 | 1989-09-20 | Ngk Insulators Ltd | Temperature control of incinerator |
JP2002372219A (en) * | 2001-06-14 | 2002-12-26 | Tsukishima Kikai Co Ltd | Processing apparatus for waste gas, and its method |
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Cited By (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2010144999A (en) * | 2008-12-18 | 2010-07-01 | Alstom Technology Ltd | Multitubular heat exchanger |
JP2010169326A (en) * | 2009-01-23 | 2010-08-05 | Alstom Technology Ltd | Shell-and-tube exchanger |
CN101943529A (en) * | 2010-09-29 | 2011-01-12 | 西安航天华威化工生物工程有限公司 | Dry cooling device and method for high-temperature gas |
JP2013083384A (en) * | 2011-10-07 | 2013-05-09 | Alstom Technology Ltd | Operation method and device of multitubular heat exchanger in fluidized incinerator system |
CN103672933A (en) * | 2012-09-17 | 2014-03-26 | 邹岳明 | Smoke flue, and vehicle, burning furnace, gas water heater all applying smoke flue |
CN103672933B (en) * | 2012-09-17 | 2016-05-18 | 邹岳明 | A kind of flue and apply motor vehicle, combustion furnace and the gas heater of this flue |
JP2017096532A (en) * | 2015-11-20 | 2017-06-01 | 株式会社マツダ | Regenerative combustion furnace |
JP2020176728A (en) * | 2019-04-15 | 2020-10-29 | 株式会社タクボ精機製作所 | Heat exchanger |
JP7253237B2 (en) | 2019-04-15 | 2023-04-06 | 株式会社タクボ精機製作所 | Heat exchanger |
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