JPS5930885B2 - Internal combustion engine exhaust gas heat recovery device - Google Patents
Internal combustion engine exhaust gas heat recovery deviceInfo
- Publication number
- JPS5930885B2 JPS5930885B2 JP54170602A JP17060279A JPS5930885B2 JP S5930885 B2 JPS5930885 B2 JP S5930885B2 JP 54170602 A JP54170602 A JP 54170602A JP 17060279 A JP17060279 A JP 17060279A JP S5930885 B2 JPS5930885 B2 JP S5930885B2
- Authority
- JP
- Japan
- Prior art keywords
- exhaust gas
- steam
- piping system
- separation drum
- feed water
- 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.)
- Expired
Links
Classifications
-
- 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
- Y02E20/16—Combined cycle power plant [CCPP], or combined cycle gas turbine [CCGT]
-
- 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
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Landscapes
- Engine Equipment That Uses Special Cycles (AREA)
Description
【発明の詳細な説明】
本発明は内燃機関の排ガス回収装置に係り、特にディー
ゼル機関やガスタービン等の内燃機関の排ガスを利用し
て蒸気を発生させ、これを発動機タービンの駆動用蒸気
や雑用蒸気等に使用するための内燃機関の排ガス回収装
置に関するものである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an exhaust gas recovery device for an internal combustion engine, and in particular, generates steam by using exhaust gas from an internal combustion engine such as a diesel engine or a gas turbine, and uses the steam to drive a motor turbine or the like. This invention relates to an exhaust gas recovery device for an internal combustion engine used for miscellaneous steam, etc.
従来、船舶等におけるディーゼル機関の排ガス熱を回収
する装置として、第１図に示すような排ガスエコノマイ
ザによって蒸気を発生させるものが知られている。2. Description of the Related Art Conventionally, as a device for recovering exhaust gas heat from a diesel engine in a ship or the like, a device that generates steam using an exhaust gas economizer as shown in FIG. 1 has been known.
第１図における装置系統は、予熱部１１、蒸発部１２お
よび過熱部１３の各配管系を内蔵する排ガスエコノマイ
ザ１と、この排ガスエコノマイザの予熱部１１および蒸
発部１２へ供給される水を加熱するための給水加熱器４
と、蒸発部１２を出た気水混合流体から水蒸気を分離す
るための水蒸気分離ドラム２と、過熱部１３からの過熱
蒸気が供給されるタービン２１（これは発電機２２に連
結されている）とから主として構成されている。The equipment system in FIG. 1 includes an exhaust gas economizer 1 that includes piping systems for a preheating section 11, an evaporation section 12, and a superheating section 13, and heats water supplied to the preheating section 11 and the evaporation section 12 of this exhaust gas economizer. Water supply heater for 4
, a steam separation drum 2 for separating steam from the steam-water mixed fluid exiting the evaporation section 12, and a turbine 21 (which is connected to a generator 22) to which superheated steam from the superheating section 13 is supplied. It is mainly composed of.
上記構成において、ディーゼル機関より吐出される排ガ
スは、図中矢印喝で示すようにエコノマイザ１内に導入
され、蒸気を発生させてその熱量が回収される。In the above configuration, exhaust gas discharged from a diesel engine is introduced into the economizer 1 as shown by the arrow in the figure, and steam is generated and its heat quantity is recovered.
排ガスエコノマイザ１への給水は、主給水ポンプ７によ
り行なわれ、表面式給水加熱器４で加熱された後、補助
ボイラの蒸気ドラムと兼用されている主蒸気分離ドラム
２に吐出され、排ガスエコノマイザ１の蒸発部１２から
導かれた気水混合流体と混合され、ボイラ循環水として
給水循環ポンプ３により表面式給水加熱器４に戻され、
さらに配管４Ａを経て排ガスエコノマイザ１の予熱部１
１に導入され、次いで蒸発部１２にて蒸気を発生させた
後、気水混合流体として主蒸気分離ドラム２へ吐出され
る。Water is supplied to the exhaust gas economizer 1 by the main water supply pump 7, heated by the surface type feed water heater 4, and then discharged to the main steam separation drum 2 which also serves as the steam drum of the auxiliary boiler. It is mixed with the steam/water mixed fluid led from the evaporation section 12 and returned to the surface type feed water heater 4 by the feed water circulation pump 3 as boiler circulating water,
Furthermore, the preheating section 1 of the exhaust gas economizer 1 is passed through the pipe 4A.
1, and then, after generating steam in the evaporator 12, it is discharged to the main steam separation drum 2 as a steam/water mixed fluid.
主蒸気分離ドラム２で分離された飽和蒸気は、一部燃料
油加熱等のため雑用蒸気として使用され、そのドレンは
ドレンタンク２６に導かれ、その他の主蒸気は排ガスエ
コノマイザ１の過熱部１３に導かれ、過熱蒸気としてタ
ーボ発電機用蒸気タービン２１を駆動し、排気を復水器
２３にて復水後、復水ポンプ２４によりドレンタンク２
６に吐出され、次いで主給水ポンプ７により吸引され、
給水加熱器４に戻される。Part of the saturated steam separated by the main steam separation drum 2 is used as miscellaneous steam for heating fuel oil, etc. The drain is led to the drain tank 26, and the other main steam is sent to the superheating section 13 of the exhaust gas economizer 1. The exhaust gas is guided as superheated steam to drive the turbo generator steam turbine 21, and after being condensed in the condenser 23, it is sent to the drain tank 2 by the condensate pump 24.
6, and then sucked in by the main water pump 7,
The water is returned to the feed water heater 4.
上記従来装置の排ガスエコノマイザ１における排ガス側
と循環給水側の温度変化を第２図の実線で示す。The temperature changes on the exhaust gas side and the circulating water supply side in the exhaust gas economizer 1 of the conventional device described above are shown by solid lines in FIG.
第２図において、Ｔｉは排ガスエコノマイザ１の排ガス
入口温度、Ｔｏはその排ガス出口温度、Ｔ１は排ガスエ
コノマイザ１の予熱部１１と蒸発部１２との間の排ガス
温度、Ｔ２は同じく蒸発部１２と過熱部１３との間の排
ガス温度、ｔｉは予熱部１１の循環水入口温度、ｔ８は
蒸発部１２の循環給水の飽和温度、ｔｏは過熱部１３の
過熱蒸気出口温度、Δｔｏは予熱部１１の循環給水入口
温度ｔｉと排ガス出口温度Ｔｏのターミナル温度差、Δ
ｔ□は蒸発部１２の循環給水出口温度ｔｓと排ガス入口
温度Ｔ１のターミナル温度差である。In Fig. 2, Ti is the exhaust gas inlet temperature of the exhaust gas economizer 1, To is the exhaust gas outlet temperature, T1 is the exhaust gas temperature between the preheating section 11 and the evaporation section 12 of the exhaust gas economizer 1, and T2 is the temperature between the evaporation section 12 and superheating. ti is the circulating water inlet temperature of the preheating section 11, t8 is the saturation temperature of the circulating water supply of the evaporation section 12, to is the superheated steam outlet temperature of the superheating section 13, and Δto is the circulating water temperature of the preheating section 11. Terminal temperature difference between water supply inlet temperature ti and exhaust gas outlet temperature To, Δ
t□ is the terminal temperature difference between the circulating water supply outlet temperature ts of the evaporator 12 and the exhaust gas inlet temperature T1.
ところでディーゼル機関の排ガス熱回収率を上げるため
には、排ガスエコノマイザ１の排ガス出口温度Ｔｏをで
きるだけ下げることが必要である。By the way, in order to increase the exhaust gas heat recovery rate of a diesel engine, it is necessary to lower the exhaust gas outlet temperature To of the exhaust gas economizer 1 as much as possible.
また排ガスエコノマイザ１の予熱部１１人口の循環給水
温度ｔｉおよび排ガス出口温度Ｔｏをある一定温度以上
に保持して排ガスエコノマイザチューブの表面温度を上
げ、排ガス中に含まれる硫黄分による硫酸腐食を防止す
ると、および排ガスエコノマイザ１の蒸発部１２におけ
る気水混合蒸気の飽和温度ｔ８と排ガス温度Ｔ１のター
ミナル温度差Δｔ１を排ガスエコノマイザ１の寸法上適
度なものとするため、通常１５〜２０℃に抑えることが
重要である。In addition, the circulating water supply temperature ti of the preheating section 11 of the exhaust gas economizer 1 and the exhaust gas outlet temperature To are maintained above a certain temperature to raise the surface temperature of the exhaust gas economizer tube to prevent sulfuric acid corrosion due to sulfur contained in the exhaust gas. , and the terminal temperature difference Δt1 between the saturation temperature t8 of the steam/water mixture vapor in the evaporation section 12 of the exhaust gas economizer 1 and the exhaust gas temperature T1 can be kept to an appropriate value in terms of the dimensions of the exhaust gas economizer 1, so it is usually possible to suppress it to 15 to 20°C. is important.
しかし、排ガスエコノマイザ１の予熱部１１人口の循環
給水温度ｔｉを一定温度（通常１３０℃〜１４０℃）と
した場合、排ガスエコノマイザ１の蒸発部１２における
ターミナル温度差Δｔ１を一定値（１５〜２０℃）に設
定すれば、排ガスエコノマイザ１出口の排ガス出口温度
を充分下げることができなくなり、従って排ガスの熱回
収率を高くすることができず、また排ガス出口温度Ｔｏ
を許容値まで下げて排ガス熱回収率を高めた場合、排ガ
スエコノマイザ１の予熱部１１人口の給水温度ｔｉが硫
酸腐食の可能性がある範囲まで低下せざるを得ないとい
う欠点があった。However, if the circulating water supply temperature ti of the preheating section 11 of the exhaust gas economizer 1 is set to a constant temperature (usually 130 to 140 degrees Celsius), the terminal temperature difference Δt1 in the evaporation section 12 of the exhaust gas economizer 1 is set to a constant value (15 to 20 degrees Celsius). ), the exhaust gas outlet temperature of the exhaust gas economizer 1 outlet cannot be lowered sufficiently, and therefore the heat recovery rate of the exhaust gas cannot be increased, and the exhaust gas outlet temperature To
If the exhaust gas heat recovery rate is increased by lowering the temperature to an allowable value, there is a drawback that the feed water temperature ti of the preheating section 11 of the exhaust gas economizer 1 must fall to a range where sulfuric acid corrosion may occur.
本発明の目的は、上記した従来技術の欠点を除去し、排
ガスエコノマイザの伝熱管の硫酸腐食を防止しつつ、熱
回収率を高めることができる内燃機関の排ガス熱回収装
置を提供することにある。SUMMARY OF THE INVENTION An object of the present invention is to provide an exhaust gas heat recovery device for an internal combustion engine that can improve the heat recovery rate while eliminating the drawbacks of the prior art described above and preventing sulfuric acid corrosion of the heat exchanger tubes of an exhaust gas economizer. .
本発明は、予熱部、蒸発部および過熱部の各配管系を有
する排ガスエコノマイザと、排ガスエコノマイザの前記
配管系へ供給する水を加熱する給水加熱器と、排ガスエ
コノマイザを出た気水混合流体から蒸気を分離する主蒸
気分離ドラムと、この主蒸気分離ドラムで分離された蒸
気の少なくとも一部を排ガスエコノマイザの前記過熱部
に供給し、さらにこれを蒸気タービンに送る配管系と、
この蒸気タービンからの蒸気を復水器で凝縮させた後、
これを前記給水加熱器に循環させる配管系と、前記主蒸
気分離ドラムで分離された凝縮水を前記給水加熱器およ
び排ガスエコノマイザの蒸発部とにそれぞれ戻す配管系
と、前記主蒸気分離ドラムで分離された凝縮水を前記給
水加熱器に戻す配管系の途中に設けられた熱交換手段お
よび凝縮水の流量調整手段とを備えたことを特徴とし、
とれによって前記目的を達成せしめたものである。The present invention provides an exhaust gas economizer that has piping systems for a preheating section, an evaporation section, and a superheating section, a feed water heater that heats water supplied to the piping system of the exhaust gas economizer, and an air-water mixed fluid that exits the exhaust gas economizer. a main steam separation drum that separates steam; a piping system that supplies at least a portion of the steam separated by the main steam separation drum to the superheating section of the exhaust gas economizer and further sends it to the steam turbine;
After condensing the steam from this steam turbine in a condenser,
A piping system that circulates the condensed water to the feed water heater, a piping system that returns the condensed water separated by the main steam separation drum to the feed water heater and the evaporation section of the exhaust gas economizer, and separates the condensed water by the main steam separation drum. It is characterized by comprising a heat exchange means and a condensed water flow rate adjustment means provided in the middle of a piping system that returns the condensed water to the feed water heater,
By doing so, the above objective was achieved.
以下、本発明の一実施例を図面によって説明する 第３図は本発明の一実施例を示す装置系統図である。Hereinafter, one embodiment of the present invention will be explained with reference to the drawings. FIG. 3 is an apparatus system diagram showing one embodiment of the present invention.
この装置系統図において、第１図に示す従来装置と意な
る点は、表面式給水加熱器４の代りに混合式加熱器６を
用い、主蒸気分離ドラム２への給水配管を除き、また主
蒸気分離ドラム２から給水加熱器６への循環水の配管系
に熱交換手段としての低圧蒸気発生装置５、温水発生装
置５４および雑用機器５２を設けるとともに給水循環ポ
ンプ３から導かれる循環水を低圧蒸気発生装置５などの
熱交換手段と排ガスエコノマイザの蒸発部１２とに供給
するための分岐した配管系を設け、この配管系の分岐点
に凝縮水の流量を調整する制御弁５５を設けたことであ
る。This system diagram is different from the conventional system shown in FIG. A low-pressure steam generator 5 as a heat exchange means, a hot water generator 54, and miscellaneous equipment 52 are installed in the circulating water piping system from the steam separation drum 2 to the feed water heater 6, and the circulating water led from the feed water circulation pump 3 is kept under low pressure. A branched piping system is provided for supplying heat exchange means such as the steam generator 5 and the evaporation section 12 of the exhaust gas economizer, and a control valve 55 for adjusting the flow rate of condensed water is provided at the branch point of this piping system. It is.
したがって第３図に示す装置系統図において、第１図に
示す装置系統図と同一または相当部分は同一符号で示し
ている。Therefore, in the device system diagram shown in FIG. 3, the same or equivalent parts as in the device system diagram shown in FIG. 1 are indicated by the same symbols.
第３図において、主給水ポンプ７によって送水される給
水ｑｆと、給水循環ポンプ３によって主蒸気分離ドラム
（またはボイラ蒸気ドラム）２から制御弁５５を介して
吸引された循環水ｑｒは、低圧蒸気発生装置５に送られ
、ここで低圧蒸気ｑ、を発生させ、次いで温水発生装置
５４にて温水（ｌｈを発生させた後、混合式給水加熱器
６に供給される。In FIG. 3, feed water qf fed by the main feed water pump 7 and circulating water qr sucked from the main steam separation drum (or boiler steam drum) 2 by the feed water circulation pump 3 via the control valve 55 are converted into low pressure steam. The water is sent to the generator 5, where it generates low-pressure steam q, and then the hot water generator 54 generates hot water (lh), which is then supplied to the mixed feed water heater 6.
温水発生装置５４にて発生した温水（ｌｈは温水供給ポ
ンプ５１を介して雑用機器５３の温熱に利用される。Hot water (lh) generated by the hot water generator 54 is used to heat the miscellaneous equipment 53 via the hot water supply pump 51.
主給水ポンプ７より配管７Ａを経て低圧蒸気発生装置５
に導入され、ここで発生した低圧蒸気ｑ、は雑用機器類
５２に導入された後、ドレンはドレンタンク２６に返送
される。Low pressure steam generator 5 from main water supply pump 7 via piping 7A
The low-pressure steam q, generated here is introduced into the miscellaneous equipment 52, and then the drain is returned to the drain tank 26.
混合式給水加熱器６に供給された水は、ここで熱交換さ
れた後排ガスエコノマイザ１の予熱部１１を通り、内燃
機関の排ガスＱｉ熱交換され、気水混合流体として主蒸
気ドラム２に導入される。The water supplied to the mixed feed water heater 6 undergoes heat exchange there, passes through the preheating section 11 of the exhaust gas economizer 1, undergoes heat exchange with the exhaust gas Qi of the internal combustion engine, and is introduced into the main steam drum 2 as a steam-water mixed fluid. be done.
一方、給水循環ポンプ３によって主蒸気分離ドラム（ま
たはボイラの蒸気ドラム）２から吸引された循環水の一
部は制御弁５５を介して排ガスエコノマイザ１の蒸発部
１２に導入され、気水混合流体として主蒸気ドラム２に
導入される。On the other hand, a part of the circulating water sucked from the main steam separation drum (or steam drum of the boiler) 2 by the feed water circulation pump 3 is introduced into the evaporation section 12 of the exhaust gas economizer 1 via the control valve 55, and the water-water mixture is The steam is introduced into the main steam drum 2 as a
主蒸気分離ドラム２によって分離された飽和蒸気の一部
は比較的圧力の高い蒸気を必要とする雑用蒸気ｑｍとし
て機関用燃料油加熱器等の雑用機器２５へ導かれ、他の
飽和蒸気は排ガスエコノマイザ１の過熱部１３で過熱さ
れ、発電機用蒸気タービン２１を１駆動した後、復水器
２３で復水し、復水ポンプ２４によってドレンタンク２
６へ導入される。A part of the saturated steam separated by the main steam separation drum 2 is led to miscellaneous equipment 25 such as an engine fuel oil heater as miscellaneous steam qm that requires relatively high pressure steam, and the other saturated steam is used as exhaust gas. After being superheated in the superheating part 13 of the economizer 1 and driving the generator steam turbine 21, the water is condensed in the condenser 23 and sent to the drain tank 2 by the condensate pump 24.
6 will be introduced.
ここで、第５図に本願明細書記載の従来例と本発明との
排ガスエコノマイザの温度変化の差を示す。Here, FIG. 5 shows the difference in temperature change of the exhaust gas economizer between the conventional example described in this specification and the present invention.
本発明によれば、排ガスエコノマイザ１の予熱部１１に
おける循環給水側の温度勾配（ｔ８−ｔｉ）が排ガス側
の温度勾配（ＴＩ ＴＯつとほぼ等しくなるように給水
循環ポンプによる流量ｑｒを決定することにより、第５
図に示す如く排ガスエコノマイザ１の予熱部１１出入口
における排ガスと循環給水の各ターミナル温度差をほぼ
同じにすることができる。According to the present invention, the flow rate qr by the water supply circulation pump is determined so that the temperature gradient (t8-ti) on the circulating water supply side in the preheating section 11 of the exhaust gas economizer 1 is approximately equal to the temperature gradient (TITO) on the exhaust gas side. According to the fifth
As shown in the figure, the temperature difference between the terminals of the exhaust gas and the circulating supply water at the inlet and outlet of the preheating section 11 of the exhaust gas economizer 1 can be made almost the same.
また低圧蒸気発生装置５および温水発生装置５４により
排ガスエコノマイザ１への循環給水の入口温度ｔｉを排
ガスエコノマイザチューブの硫酸腐食を防止し得る許容
最低温度（約１３０〜１４０℃）となるように設定でき
る。Furthermore, the inlet temperature ti of the circulating water supply to the exhaust gas economizer 1 can be set by the low-pressure steam generator 5 and the hot water generator 54 to be the lowest allowable temperature (approximately 130 to 140°C) that can prevent sulfuric acid corrosion of the exhaust gas economizer tube. .
したがって硫酸腐食防止を考慮した上で、排ガスの熱回
収率を向上させることができる。Therefore, the heat recovery rate of exhaust gas can be improved while taking prevention of sulfuric acid corrosion into consideration.
すなわち、第５図に示すように従来例では低温腐食防止
のため排ガスエコノマイザの予熱部１１においては給水
加熱量Ｈｆのみしか排熱を回収できなかったが、本発明
では循環給水入口温度ｔｉを一定に保持しつつ排ガス出
口温度をＴｏ→Ｔｏ′と低下させ、給水加熱量Ｈｆのみ
ならず低圧蒸気（及び温水）の発生必要熱量Ｈｅも排熱
から回収することができる。That is, as shown in FIG. 5, in the conventional example, only the feed water heating amount Hf could be recovered in the preheating section 11 of the exhaust gas economizer to prevent low-temperature corrosion, but in the present invention, the circulating feed water inlet temperature ti is kept constant. By lowering the exhaust gas outlet temperature from To to To' while maintaining the same temperature, not only the feed water heating amount Hf but also the required heat amount He for generating low pressure steam (and hot water) can be recovered from the exhaust heat.
一例として、常用出力１２，３００ＰＳの２サイクルデ
イ一ゼル機関に上記の本発明システムを採用した場合、
第１図に示す従来のシステムと比較して回収熱量で約１
５係、ターボ発電機の出力で１００〜１２０ｋＷの増加
が期待できる。As an example, when the above-mentioned system of the present invention is adopted in a two-stroke diesel engine with a normal output of 12,300 PS,
Compared to the conventional system shown in Figure 1, the amount of recovered heat is approximately 1
In Section 5, the output of the turbo generator can be expected to increase by 100 to 120 kW.
第２に制御弁５５を設けているため、給水循環ポンプ３
によって主蒸気分離ドラム２から吸引された循環水を雑
用機器５２などを設けた熱交換手段と、排ガスエコノマ
イザ１の蒸発部１２とに適量ずつ供給できることから、
排ガスのみならず、主蒸気分離ドラム２の圧力Ｐ３、雑
用機器５２．５３の負荷変動に対しても対処でき、また
給水循環ポンプの必要動力を小さくすることができる。Secondly, since the control valve 55 is provided, the water supply circulation pump 3
Since the circulating water sucked from the main steam separation drum 2 can be supplied in appropriate amounts to the heat exchange means provided with the miscellaneous equipment 52 and the like, and to the evaporation section 12 of the exhaust gas economizer 1,
It is possible to deal with not only the exhaust gas but also the pressure P3 of the main steam separation drum 2 and load fluctuations of the miscellaneous equipment 52, 53, and the power required for the feed water circulation pump can be reduced.
第３に排ガスエコノマイザ１の予熱部１１において発生
する気水混合流体は直接主蒸気分離ドラム２に導入され
るようになっているため、予熱部１１で蒸発が起っても
これは直ちに主蒸気分離ドラム２に導入される結果、ベ
ーパロックによる排ガスエコノマイザ１の損傷を最小限
に抑えることができる。Thirdly, the steam/water mixed fluid generated in the preheating section 11 of the exhaust gas economizer 1 is directly introduced into the main steam separation drum 2, so even if evaporation occurs in the preheating section 11, it is immediately removed from the main steam. As a result of being introduced into the separation drum 2, damage to the exhaust gas economizer 1 due to vapor lock can be minimized.
本発明において、第３図の１点鎖線のブロックで示す熱
交換手段の代りに第４図に示す雑用機器５２ａを設け、
給水循環ポンプ３から制御弁５５を介して導入される循
環水を温水加熱として使用後、混合式給水加熱器６へ返
すシステムとすることもできる。In the present invention, a miscellaneous equipment 52a shown in FIG. 4 is provided in place of the heat exchange means shown in the block indicated by the dashed dotted line in FIG.
It is also possible to adopt a system in which circulating water introduced from the water supply circulation pump 3 via the control valve 55 is used for hot water heating and then returned to the mixed water supply heater 6.
本実施例によっても、上記同様の効果を有する。This embodiment also has the same effects as described above.
以上、本発明によれば、排ガスエコノマイザの循環給水
入口温度を一定値以上に保持して排ガスエコノマイザの
硫酸腐食を防止することができ、かつ排ガス出口温度を
給水入口温度とのターミナル温度差の許容最小値まで下
げることができるので、従来の排ガス熱回収システムよ
りも熱回収率を高めることができる。As described above, according to the present invention, it is possible to prevent sulfuric acid corrosion of the exhaust gas economizer by maintaining the circulating water inlet temperature of the exhaust gas economizer above a certain value, and to allow for a terminal temperature difference between the exhaust gas outlet temperature and the water supply inlet temperature. Since the heat recovery rate can be lowered to the minimum value, the heat recovery rate can be higher than that of conventional exhaust gas heat recovery systems.
第１図は従来の排ガス熱回収の装置系統を示す図、第２
図は排ガスエコノマイザの各部の温度変化を示す図、第
３図は本発明の一例を示す装置系統図、第４図は第３図
における熱交換手段の変形例を示す図、第５図は従来例
と本発明との排ガスエコノマイザの温度変化の差を示す
グラフである。
１・・・排ガスエコノマイザ、２主蒸気分離ドラム、３
・・・給水循環ポンプ、４・・・表面式給水加熱器、５
・・・低圧蒸気発生器、６・・・混合式給水加熱器、７
・・・主給水ポンプ、１１・・・予熱部、１２・・・蒸
発部、１３・・・過熱部、２１・・・蒸気タービン、２
３・・・復水器、２５．５２．５２ａ、５３・・・雑用
機器、２６・・・ドレンタンク、５４・・・温水発生装
置。Figure 1 shows the conventional exhaust gas heat recovery equipment system, Figure 2
The figure shows the temperature changes in each part of the exhaust gas economizer, Figure 3 is a system diagram of the device showing an example of the present invention, Figure 4 is a diagram showing a modification of the heat exchange means in Figure 3, and Figure 5 is the conventional one. It is a graph showing the difference in temperature change of the exhaust gas economizer of the example and the present invention. 1...Exhaust gas economizer, 2 main steam separation drum, 3
...Water circulation pump, 4...Surface water heater, 5
...Low pressure steam generator, 6...Mixed feed water heater, 7
... Main water pump, 11 ... Preheating section, 12 ... Evaporation section, 13 ... Superheating section, 21 ... Steam turbine, 2
3... Condenser, 25.52.52a, 53... Miscellaneous equipment, 26... Drain tank, 54... Hot water generator.
Claims (1)
ガスエコノマイザと、排ガスエコノマイザの前記配管系
へ供給する水を加熱する給水加熱器と、排ガスエコノマ
イザを出た気水混合流体から蒸気を分離する主蒸気分離
ドラムと、この主蒸気分離ドラムで分離された蒸気の少
なくとも一部を排ガスエコノマイザの前記過熱部に供給
し、さらにこれを蒸気タービンに送る配管系と、この蒸
気タービンからの蒸気を復水器で凝縮させた後、これを
前記給水加熱器に循環させる配管系と、前記主蒸気分離
ドラムで分離された凝縮水を前記給水加熱器および排ガ
スエコノマイザの前記蒸発部とにそれぞれ戻す配管系と
、前記主蒸気分離ドラムで分離された凝縮水を前記給水
加熱器に戻す配管系に設けられた熱交換手段および凝縮
水の流量調整手段とを備えたことを特徴とする内燃機関
の排ガス熱回収装置。 ２、特許請求の範囲第１項において、前記凝縮水の流量
調整手段は、前記主蒸気分離ドラムで分離された凝縮水
を前記給水加熱器に戻す配管系と排ガスエコノマイザの
前記蒸発部に戻す配管系との分岐点に設けられた流量制
御弁であることを特徴とする内燃機関の排ガス熱回収装
置。 ３ 特許請求の範囲第１項において、前記熱交換手段は
、前記主蒸気ドラムで分離された凝縮水を順次導入する
低圧蒸気発生装置および温水発生装置と、前記低圧蒸気
発生装置より発生した低圧蒸気を導入する加熱機器とか
らなることを特徴とする内燃機関の排ガス熱回収装置。 ４ 特許請求の範囲第３項において、前記蒸気タービン
からの蒸気を復水器で凝縮させた後、これを前記給水加
熱器に循環させる配管を分岐させ、前記低圧蒸気発生装
置と連結したことを特徴とする内燃機関の排ガス熱回収
装置。[Scope of Claims] 1. An exhaust gas economizer that has piping systems for a preheating section, an evaporation section, and a superheating section, a feed water heater that heats water supplied to the piping system of the exhaust gas economizer, and air water that exits the exhaust gas economizer. a main steam separation drum that separates steam from a mixed fluid; a piping system that supplies at least a portion of the steam separated by the main steam separation drum to the superheating section of the exhaust gas economizer and further sends it to the steam turbine; A piping system that condenses steam from a steam turbine in a condenser and then circulates it to the feed water heater; and a piping system that circulates the condensed water separated in the main steam separation drum to the feed water heater and the exhaust gas economizer. and a piping system for returning the condensed water separated by the main steam separation drum to the feed water heater, respectively, and a heat exchange means and a condensed water flow rate adjustment means provided in the piping system for returning the condensed water separated by the main steam separation drum to the feed water heater. Exhaust gas heat recovery equipment for internal combustion engines. 2. In claim 1, the condensed water flow rate adjustment means includes a piping system that returns the condensed water separated by the main steam separation drum to the feed water heater, and a piping system that returns the condensed water separated by the main steam separation drum to the evaporation section of the exhaust gas economizer. An exhaust gas heat recovery device for an internal combustion engine, characterized in that it is a flow control valve provided at a branch point with a system. 3. In claim 1, the heat exchange means includes a low-pressure steam generator and a hot water generator that sequentially introduce condensed water separated by the main steam drum, and low-pressure steam generated from the low-pressure steam generator. An exhaust gas heat recovery device for an internal combustion engine, comprising a heating device that introduces. 4. Claim 3 provides that after condensing steam from the steam turbine in a condenser, piping for circulating the steam to the feed water heater is branched and connected to the low-pressure steam generator. Features of exhaust gas heat recovery equipment for internal combustion engines.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP54170602A JPS5930885B2 (en) | 1979-12-28 | 1979-12-28 | Internal combustion engine exhaust gas heat recovery device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP54170602A JPS5930885B2 (en) | 1979-12-28 | 1979-12-28 | Internal combustion engine exhaust gas heat recovery device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5696105A JPS5696105A (en) | 1981-08-04 |
| JPS5930885B2 true JPS5930885B2 (en) | 1984-07-30 |
Family
ID=15907885
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP54170602A Expired JPS5930885B2 (en) | 1979-12-28 | 1979-12-28 | Internal combustion engine exhaust gas heat recovery device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5930885B2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS61166912U (en) * | 1985-04-05 | 1986-10-16 |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102006010247B4 (en) * | 2006-03-02 | 2019-12-19 | Man Truck & Bus Se | Drive unit with heat recovery |
-
1979
- 1979-12-28 JP JP54170602A patent/JPS5930885B2/en not_active Expired
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS61166912U (en) * | 1985-04-05 | 1986-10-16 |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5696105A (en) | 1981-08-04 |
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