JPS6022185B2 - Exhaust gas heat recovery device for marine engines - Google Patents
Exhaust gas heat recovery device for marine enginesInfo
- Publication number
- JPS6022185B2 JPS6022185B2 JP54113207A JP11320779A JPS6022185B2 JP S6022185 B2 JPS6022185 B2 JP S6022185B2 JP 54113207 A JP54113207 A JP 54113207A JP 11320779 A JP11320779 A JP 11320779A JP S6022185 B2 JPS6022185 B2 JP S6022185B2
- Authority
- JP
- Japan
- Prior art keywords
- steam
- exhaust gas
- generation system
- miscellaneous
- steam generation
- 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
- 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】
この発明はディーゼル機関等の船舶用原動機の排ガス熱
を回収する装置に関するものである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a device for recovering exhaust gas heat from a marine engine such as a diesel engine.
この種の排ガス熱回収装置は排ガスェコノマィザを備え
、これにより原動機の排ガス熱を回収して船内電源を得
るためのターボ発電機駆動用蒸気と燃料油加熱用タンク
加熱用その他に用いる雑用蒸気を発生せしめる。第１図
に示すのはこのような回収装置の従来例を示すものであ
る。同図において、２１は排ガスェコノマィザで子熱部
２１ａ、蒸発部２１ｂ、過熱部２１ｃからなる。２２は
気水分離器、２３は給水加熱器、２４は蒸気タービン、
２５は復水器、２６はタンクや燃料加熱器等の雑用蒸気
を使用する機器、２７は給水タンク、２８は給水ポンプ
、２９は給水制御弁、３０は循環ポンプである。This type of exhaust gas heat recovery equipment is equipped with an exhaust gas economizer, which recovers the exhaust gas heat from the prime mover to generate steam for driving the turbo generator to obtain onboard power, and miscellaneous steam for heating tanks for fuel oil and other purposes. urge FIG. 1 shows a conventional example of such a collection device. In the figure, reference numeral 21 denotes an exhaust gas economizer, which consists of a child heating section 21a, an evaporation section 21b, and a superheating section 21c. 22 is a steam separator, 23 is a feed water heater, 24 is a steam turbine,
25 is a condenser, 26 is equipment using miscellaneous steam such as a tank or a fuel heater, 27 is a water supply tank, 28 is a water supply pump, 29 is a water supply control valve, and 30 is a circulation pump.
消費蒸気量に見合った給水は給水タンク２７から給水ポ
ンプ２８により給水加熱器２３、給水制御弁２９を経て
気水分離器２２に供給される。この気水分離器２２内の
飽和水は循環ポンプ３川こより、給水加熱器２３におい
て給水を加熱した後子熱部２１ａ、蒸発部２１ｂにおい
て原動機排ガスより熱回収して飽和水と飽和蒸気の混合
流となって気水分離器２２に循環される。ここで気水分
離された飽和蒸気は一部が雑用蒸気として雑用蒸気を使
用する機器２６に供給され、残りが過熱部２１ｃへ送ら
れる。この過熱部２１ｃにおいてさらに高温に加熱され
た過熱蒸気は蒸気タービン２４に送られこれを駆動する
。このタービン駆動用蒸気は復水器２５にて復水した後
給水タンク２７へ送られる。このような従来の回収装置
では蒸気発生系統は単一であり発生蒸気の一部を雑用蒸
気として使用し残りの蒸気を過熱した後蒸気タービン駆
動用蒸気として使用している。Feed water commensurate with the amount of steam consumed is supplied from the water supply tank 27 to the steam water separator 22 via the feed water heater 23 and the water supply control valve 29 by the water supply pump 28. The saturated water in the steam/water separator 22 is heated by the circulation pump 3 rivers, the feed water heater 23 heats the feed water, and then the heat is recovered from the motor exhaust gas in the subheating section 21a and the evaporator section 21b, and saturated water and saturated steam are mixed. The water is circulated as a stream to the steam separator 22. Part of the saturated steam separated into steam and water is supplied as miscellaneous steam to the equipment 26 that uses miscellaneous steam, and the rest is sent to the superheating section 21c. The superheated steam heated to a higher temperature in the superheating section 21c is sent to the steam turbine 24 to drive it. This turbine driving steam is condensed in a condenser 25 and then sent to a water supply tank 27. In such a conventional recovery device, there is a single steam generation system, and a part of the generated steam is used as miscellaneous steam, and the remaining steam is used as steam for driving the steam turbine after being superheated.
排ガスからの回収熱量は、排ガスの熱量・温度が高いほ
どまた発生蒸気の圧力が低く飽和温度が低くなるほど熱
交換が容易となり交換熱量が増加するが、このような従
来の装置では運転時の蒸気圧力は排ガスからの回収熱量
と消費蒸気量とのバランスから決定されト次のような問
題点が生じることになる。■ 冬季のように大気温度が
低い場合、排ガスの熱量。The amount of heat recovered from exhaust gas increases as the amount of heat and temperature of the exhaust gas increases, and as the pressure and saturation temperature of the generated steam decreases, heat exchange becomes easier and the amount of heat exchange increases. The pressure is determined based on the balance between the amount of heat recovered from the exhaust gas and the amount of steam consumed, resulting in the following problems. ■ When the atmospheric temperature is low, such as in winter, the amount of heat in the exhaust gas.
温度が低下するとともにタンク加熱蒸気の増加等に起因
し雑用蒸気量が増えるため蒸気圧力は低いところで運転
され、さらに蒸気圧力が低下した場合には蒸気タービン
が失速してしまう。■ 夏季のように大気温度が高い場
合、排ガスの熱量・温度が高くなるとともに冷房装置を
使用するので冬季に比べ発電機負荷は増加するが雑用蒸
気量が少なくなるため蒸気圧力は高いところで運転され
る。As the temperature decreases, the amount of miscellaneous steam increases due to an increase in tank heating steam, etc., so the steam turbine is operated at a low steam pressure, and if the steam pressure further decreases, the steam turbine will stall. ■ When the atmospheric temperature is high, such as in the summer, the calorific value and temperature of the exhaust gas increases, and the air conditioner is used, so the generator load increases compared to the winter, but the amount of miscellaneous steam is reduced, so the generator is operated at a high steam pressure. Ru.
そして「冬季に蒸気タービンが失速しないように排ガス
ェコノマイザの熱交換能力に十分余裕をもつて計画して
いる場合には、夏季には排ガスからの回収可能熱量が多
くなり、運転時の蒸気圧力が高くなり過ぎることを防ぐ
ために発生蒸気の一部を直接復水器に送り熱量を捨てる
ことになる。この発明は前記従来の問題点を解消すべく
提案されたもので、次の二点を目的とするものである。``If the heat exchange capacity of the exhaust gas economizer is planned with sufficient margin to prevent the steam turbine from stalling in the winter, the amount of heat that can be recovered from the exhaust gas will increase in the summer, and the steam during operation will increase. In order to prevent the pressure from becoming too high, a part of the generated steam is sent directly to the condenser and the heat is discarded.This invention was proposed to solve the above-mentioned conventional problems, and has the following two points. The purpose is to
■ 排ガスェコノマィザの従来のような無駄な余裕を省
き経済的で小型な装置を製作する。■ Eliminate the wasteful margins of conventional exhaust gas economizers and manufacture an economical and compact device.
■ 従来の装置よりも最適状態で運転されるようにする
。■ Ensuring that the equipment operates more optimally than conventional equipment.
この発明は上記目的を達成するために「蒸気発生系統を
ターボ発電機駆動用蒸気を発生せしめる主蒸気発生系統
と雑用蒸気を発生せしめる補助蒸気発生系統とに分割し
、両系統の出口側蒸気配管を逆止弁を介して接続し、雑
用蒸気消費量が多い場合には両系統がそれぞれ独立に運
転されるようにし、雑用蒸気消費量が少なく発電機負荷
が大きい場合には補助蒸気発生系統から主蒸気発生系統
に蒸気が流入して主蒸気発生系統の補助を行なうように
したものである。In order to achieve the above object, this invention divides the steam generation system into a main steam generation system that generates steam for driving a turbo generator and an auxiliary steam generation system that generates miscellaneous steam, and steam piping on the outlet side of both systems. are connected via a check valve, so that when the amount of miscellaneous steam consumption is high, both systems are operated independently, and when the amount of miscellaneous steam consumption is low and the generator load is large, the auxiliary steam generation system is connected. Steam flows into the main steam generation system to assist the main steam generation system.
以下この発明を図示する一実施例に基づいて説明する。The present invention will be described below based on an illustrated embodiment.
第２図において１は排ガスェコノマィザであり予熱部亀
Ａ、補助蒸発部ＩＢ、主蒸発部ｌｃ、過熱部ＩＤから構
成される。２Ａおよび２Ｂはそれぞれ補助および主気水
分離器、３は給水加熱器、４は蒸気タービン、５は復水
器、６はタンクや燃料加熱器等の雑用蒸気を使用する機
器、７は給水タンク、８は給水ポンプ、９Ａ，９８は給
水制御弁、１０Ａ，１０８は循環ポンプ、１１は逆止弁
である。In FIG. 2, reference numeral 1 denotes an exhaust gas economizer, which is composed of a preheating section A, an auxiliary evaporation section IB, a main evaporation section lc, and a superheating section ID. 2A and 2B are auxiliary and main steam separators, respectively, 3 is a feedwater heater, 4 is a steam turbine, 5 is a condenser, 6 is equipment that uses miscellaneous steam such as a tank or fuel heater, and 7 is a water supply tank. , 8 is a water supply pump, 9A and 98 are water supply control valves, 10A and 108 are circulation pumps, and 11 is a check valve.
給水タンク７から給水ポンプ８により圧送された給水は
給水加熱器３を経て予熱部ＩＡに送られ加熱された後、
消費蒸気量に見合って給水を制御する給水制御弁９Ａお
よび９Ｂを経て補助気水分離器２Ａおよび主気水分離器
２８に送られる。After the water pumped from the water tank 7 by the water pump 8 is sent to the preheating section IA via the water heater 3 and heated,
The water is sent to the auxiliary steam/water separator 2A and the main steam/water separator 28 via water supply control valves 9A and 9B that control water supply according to the amount of steam consumed.
ここで第３図に示すように必要があれば主気水分磁器２
８への給水は補助気水分鱗器２Ａの循環水により補助給
水加熱器１２において加熱されるようにしてもよい。こ
の高温給水の一部は給水加熱器３に送られここで熱交換
を行ない給水タンク？に循環される。気水分離器２Ａ，
２Ｂ内の飽和水は循環ポンプ１０Ａ，１０Ｂによりそれ
ぞれ蒸発部ＩＢ，ＩＣに送られここで排ガス熱を回収し
て一部蒸気となって気水分雛器２Ａ，２Ｂへ戻される。
補助気水分離器２Ａにおいて気水分離された補助蒸気は
雑用蒸気として雑用蒸気を使用する機器６に供給され、
主気水分離器２Ｂにおいて気水分離された主蒸気は過熱
部３Ｄを経て高温に加熱された後蒸気タービンＷこ供給
される。補助気水分機器２Ａと主気水分雛器２Ｂとは逆
止弁１１を備えた蒸気配管で接続されており、冬季のよ
うに雑用蒸気量が多いときは補助蒸気系統は低圧となり
逆止弁１１によって高圧の主蒸気系統と独立して運転さ
れる。夏季のように雑用蒸気量が少なく発電機負荷の大
きい場合は補助気水分雛器２Ａの圧力が上昇しこの発生
蒸気の一部は逆止弁１１を通り主蒸気発生系統に送られ
蒸気タービン駆動用蒸気となって主蒸気発生系統の役割
を補助する。この場合二つの蒸気発生系統は同一圧力で
運転されることになる。ここにおいて主蒸気圧力は４．
５ｋ９／塊以上、補助蒸気圧力は２．５ｋｇ／の以上に
計画するのが適当である。次に本発明と従来例との排ガ
ス熱回収状況の比較を第４図、第５図に示す。Here, as shown in Figure 3, if necessary, the main air moisture porcelain 2
8 may be heated in the auxiliary water heater 12 by circulating water of the auxiliary steam/moisture scaler 2A. A part of this high-temperature feed water is sent to the feed water heater 3, where heat exchange is performed and the water is transferred to the water tank. is circulated. Steam water separator 2A,
The saturated water in 2B is sent to evaporation sections IB and IC by circulation pumps 10A and 10B, respectively, where exhaust gas heat is recovered and a portion of the water is turned into steam and returned to steam and moisture hatchers 2A and 2B.
The auxiliary steam separated into steam and water in the auxiliary steam and water separator 2A is supplied as miscellaneous steam to the equipment 6 that uses miscellaneous steam,
The main steam separated into steam and water in the main steam and water separator 2B is heated to a high temperature through a superheating section 3D, and then supplied to the steam turbine W. The auxiliary steam and moisture device 2A and the main steam and moisture device 2B are connected by steam piping equipped with a check valve 11. When the amount of miscellaneous steam is large, such as in winter, the auxiliary steam system is at low pressure and the check valve 11 is connected. operated independently from the high-pressure main steam system. When the amount of miscellaneous steam is small and the generator load is large, such as in the summer, the pressure in the auxiliary steam generator 2A increases, and a portion of this generated steam is sent to the main steam generation system through the check valve 11 to drive the steam turbine. It serves as commercial steam and assists the role of the main steam generation system. In this case, the two steam generation systems will be operated at the same pressure. Here, the main steam pressure is 4.
It is appropriate to plan for 5k9/lump or more and the auxiliary steam pressure to be 2.5kg/or more. Next, a comparison of exhaust gas heat recovery status between the present invention and the conventional example is shown in FIGS. 4 and 5.
同図においてＡは本発明に係る装置の場合、ａは従来装
置の場合の温水および蒸気の温度条件と回収熱量を示し
たものである。第４図に示すのは回収装置を排ガス温度
が低く雑用蒸気量の多い冬季において運転した場合であ
り、この図から本発明のものＡは排ガスェコノマィザ蒸
気発生部において排ガス側と蒸気側との温度差を大きく
とれるので排ガスェコノマイザの伝熱面積を従釆に比べ
て小さくすることができる。また、蒸気タービン駆動用
蒸気は従来よりも高い圧力で使用することができる。第
５図は排ガス温度の高い夏季の運転状態を示すものであ
る。In the figure, A shows the temperature conditions of hot water and steam and the amount of recovered heat in the case of the device according to the present invention, and a shows the temperature conditions of hot water and steam in the case of the conventional device. Figure 4 shows the case where the recovery device is operated in winter when the exhaust gas temperature is low and the amount of miscellaneous steam is large. Since the difference can be made large, the heat transfer area of the exhaust gas economizer can be made smaller than that of the slave. Furthermore, the steam for driving the steam turbine can be used at a higher pressure than before. FIG. 5 shows operating conditions in summer when exhaust gas temperature is high.
夏季は冷房機を使用するため冬季よりも５０ないし８０
ＫＷ程度ターボ発電機の負荷が増えるが、雑用蒸気消費
量が約半分に減るため、従来のものａでは蒸気圧力が高
くなりすぎて一部の蒸気を復水器に捨てるなどして圧力
調整をしていたが、本発明のものＡでは排ガスェコノマ
ィザの伝熱面積を従来よりも小さくすることができるこ
とと補助蒸気発生系統の昇圧による主蒸気発生系統の補
助が行なわれることから従来のものより過度な蒸気圧力
上昇を防止することができる。前述のとおりこの発明に
よれば蒸気発生系統を二つに分け、逆止弁によって両系
統を接続したため、雑用蒸気消費量が多い場合には両系
統がそれぞれ独立に運転され、雑用蒸気消費量が少ない
場合には補助蒸気発生系統が本蒸気発生系統を補助する
ことになり、常に最適状態で運転される。また、排ガス
ェコノマィザに従来のような無駄な余裕を計画しなくて
もよいため経済的で小型の装置が得られる。In the summer, the air conditioner is used, so the price is 50 to 80% lower than in the winter.
Although the load on the turbo generator increases by about kW, the amount of miscellaneous steam consumed is reduced by about half, so with conventional type a, the steam pressure becomes too high, so some steam is dumped into the condenser to adjust the pressure. However, in the method A of the present invention, the heat transfer area of the exhaust gas seconomizer can be made smaller than before, and the main steam generation system is assisted by boosting the pressure of the auxiliary steam generation system. It is possible to prevent a significant rise in steam pressure. As mentioned above, according to this invention, the steam generation system is divided into two and the two systems are connected by a check valve, so when the amount of miscellaneous steam consumption is large, both systems are operated independently, and the amount of miscellaneous steam consumption is reduced. If the amount is low, the auxiliary steam generation system will assist the main steam generation system, and it will always be operated in an optimal state. Furthermore, since there is no need to provide an unnecessary margin for the exhaust gas economizer as in the conventional case, an economical and compact device can be obtained.
第１図は従来の排ガス熱回収装置を示す系統図、第２図
はこの発明に係る排ガス熱回収装置の第一実施例を示す
系統図、第３図は同様の第二実施例を示す系統図、第４
図、第５図は従来と本発明の装置の熱回収状況を比較し
た線図である。
１，２１・・・・・・排ガスェコノマィザ、ＩＡ，２１
ａ・・・・・・子熱部、ＩＢ・・・…補助蒸発部、ＩＣ
…・・・主蒸発部、２１ｂ・・・・・・蒸発部、ＩＤ，
２１ｃ・・・・・・過熱部、２Ａ・・・・・・補助気水
分雛器、２Ｂ・・・・・・主気水分離器、２２・・…・
気水分離器、３，２３・・・・・・給水加熱器、４，２
４…・・・蒸気タービン、５，２５・・・…復水器、６
，２６……雑用蒸気を使用する機器、７，２７・・・・
・・給水タンク、８，２８…・・・給水ポンプ、９Ａ，
９Ｂ，２９……給水制御弁、１０Ａ，１０Ｂ，３０・・
・・・・循環ポンプ、１１・・・・・・逆止弁、１２・
・・・・・補助給水加熱器。
※Ｔ図
繁ム図
滋５図
※２図
※３図Fig. 1 is a system diagram showing a conventional exhaust gas heat recovery device, Fig. 2 is a system diagram showing a first embodiment of the exhaust gas heat recovery device according to the present invention, and Fig. 3 is a system diagram showing a similar second embodiment. Figure, 4th
FIG. 5 is a diagram comparing the heat recovery status of the conventional apparatus and the apparatus of the present invention. 1,21・・・Exhaust gas seconomizer, IA, 21
a...Child heating section, IB...Auxiliary evaporation section, IC
...Main evaporation section, 21b...Evaporation section, ID,
21c...Superheating section, 2A...Auxiliary steam/water container, 2B...Main steam/water separator, 22...
Steam/water separator, 3, 23... Feed water heater, 4, 2
4... Steam turbine, 5, 25... Condenser, 6
, 26... Equipment that uses miscellaneous steam, 7, 27...
...Water tank, 8,28...Water pump, 9A,
9B, 29... Water supply control valve, 10A, 10B, 30...
...Circulation pump, 11...Check valve, 12.
...Auxiliary water heater. *Figure T, Shigeru Musu, Figure 5 *Figure 2, Figure 3
Claims (1)
発電機の蒸気タービンを駆動する蒸気および前記蒸気タ
ービン以外に使用する雑用蒸気を発生せしめる排ガスエ
コノマイザを備えた排ガス熱回収装置において、気水分
離器、排ガスエコノマイザ蒸発部および強制循環管路か
ら構成される蒸気発生系統を蒸気タービン駆動用蒸気を
発生せしめる主蒸気発生系統と雑用蒸気を発生せしめる
補助蒸気発生系統とに分割し、前記両蒸気発生系統にエ
コノマイザ予熱部にて加熱した温水を同一圧力で並列に
給水をおこない雑用蒸気消費量が多い場合に両蒸気発生
系統がそれぞれ独立に運転されかつ雑用蒸気消費量が少
なく発電機負荷が大きい場合に補助蒸気発生系統から主
蒸気発生系統に蒸気が流入して主蒸気発生系統を補助し
得るように、補助蒸気発生系統と主蒸気発生系統の出口
側蒸気配管を逆止弁を介して接続したことを特徴とする
船舶用原動機の排ガス熱回収装置。1 In an exhaust gas heat recovery device equipped with an exhaust gas economizer that recovers heat from exhaust gas discharged from a prime mover and generates steam for driving a steam turbine of a turbo generator and miscellaneous steam for use other than the steam turbine, a steam separator is used. , the steam generation system consisting of the exhaust gas economizer evaporation section and the forced circulation pipe is divided into a main steam generation system that generates steam for driving the steam turbine and an auxiliary steam generation system that generates miscellaneous steam, and both of the steam generation systems are separated. When hot water heated in the economizer preheating section is supplied in parallel at the same pressure and the amount of miscellaneous steam consumed is large, both steam generation systems are operated independently, and when the amount of miscellaneous steam consumed is small and the generator load is large. The outlet side steam piping of the auxiliary steam generation system and the main steam generation system are connected via a check valve so that steam can flow into the main steam generation system from the auxiliary steam generation system and assist the main steam generation system. An exhaust gas heat recovery device for a marine engine, characterized by:
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP54113207A JPS6022185B2 (en) | 1979-09-04 | 1979-09-04 | Exhaust gas heat recovery device for marine engines |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP54113207A JPS6022185B2 (en) | 1979-09-04 | 1979-09-04 | Exhaust gas heat recovery device for marine engines |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5638544A JPS5638544A (en) | 1981-04-13 |
| JPS6022185B2 true JPS6022185B2 (en) | 1985-05-31 |
Family
ID=14606261
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP54113207A Expired JPS6022185B2 (en) | 1979-09-04 | 1979-09-04 | Exhaust gas heat recovery device for marine engines |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6022185B2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6333788U (en) * | 1986-04-19 | 1988-03-04 |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS58204865A (en) * | 1982-05-21 | 1983-11-29 | レメツト・コ−ポレ−シヨン | Refractories |
-
1979
- 1979-09-04 JP JP54113207A patent/JPS6022185B2/en not_active Expired
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6333788U (en) * | 1986-04-19 | 1988-03-04 |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5638544A (en) | 1981-04-13 |
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