JP2010540837A - Cascade type organic Rankine cycle (ORC) system using waste heat from reciprocating engine - Google Patents

Cascade type organic Rankine cycle (ORC) system using waste heat from reciprocating engine Download PDF

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JP2010540837A
JP2010540837A JP2010527922A JP2010527922A JP2010540837A JP 2010540837 A JP2010540837 A JP 2010540837A JP 2010527922 A JP2010527922 A JP 2010527922A JP 2010527922 A JP2010527922 A JP 2010527922A JP 2010540837 A JP2010540837 A JP 2010540837A
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working fluid
organic working
orc
temperature
heat
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ビダーマン，ブルース，ピー
ブラーズ，ジョスト
コグスウェル，フレデリック，ジェイ．
ムルゲタ，ジャルソー
ハング，リーリー
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Raytheon Technologies Corp
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United Technologies Corp
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G5/00—Profiting from waste heat of combustion engines, not otherwise provided for
    • F02G5/02—Profiting from waste heat of exhaust gases
    • F02G5/04—Profiting from waste heat of exhaust gases in combination with other waste heat from combustion engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • F01K23/065—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle the combustion taking place in an internal combustion piston engine, e.g. a diesel engine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
    • F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G2262/00—Recuperating heat from exhaust gases of combustion engines and heat from lubrication circuits
    • 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
    • Y02E20/14—Combined heat and power generation [CHP]
    • 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

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Abstract

容積形機関（１０６）からの２つの廃熱源を利用して、カスケード型有機ランキンサイクル（ＯＲＣ）システム（１００）を運転する方法およびシステムが使用され、機関（１０６）およびカスケード型ＯＲＣシステム（１００）の効率が上昇する。容積形機関（１０６）からの高温廃熱源は、第１のＯＲＣシステム（１０２）内で利用され、第１の作動流体（１１８）を蒸発させる。容積形機関（１０６）からの低温廃熱源は、第２のＯＲＣシステム（１０４）内で使用され、第２の作動流体（１３０）を蒸発温度よりは低い温度にまで加熱する。そして、第２の作動流体（１３０）は、第１の作動流体からの熱を使って蒸発される。一実施例においては、容積形機関（１０６）は、往復機関である。高温廃熱源は排気ガスとすることができ、低温排熱源はジャケット冷却水とすることができる。  A method and system for operating a cascaded organic Rankine cycle (ORC) system (100) utilizing two waste heat sources from a positive displacement engine (106) is used, the engine (106) and the cascaded ORC system (100 ) Efficiency increases. A high temperature waste heat source from the positive displacement engine (106) is utilized in the first ORC system (102) to evaporate the first working fluid (118). A low temperature waste heat source from the positive displacement engine (106) is used in the second ORC system (104) to heat the second working fluid (130) to a temperature below the evaporation temperature. Then, the second working fluid (130) is evaporated using heat from the first working fluid. In one embodiment, positive displacement engine (106) is a reciprocating engine. The high temperature waste heat source can be exhaust gas and the low temperature waste heat source can be jacket cooling water.

Description

本発明は、有機ランキンサイクル（ＯＲＣ）システムに関し、詳しくは、往復機関からの２つの廃熱源を利用してカスケード型ＯＲＣシステムを運転することに関する。   The present invention relates to an organic Rankine cycle (ORC) system, and more particularly to operating a cascaded ORC system utilizing two waste heat sources from a reciprocating engine.

ランキンサイクルシステムは、一般に、電力を発生させるために使用される。ランキンサイクルシステムは、作動流体を蒸発させる蒸発器ないしボイラと、蒸発器から蒸気を受けて発電機を駆動するタービンと、蒸気を凝縮する凝縮器と、凝縮された流体を蒸発器へ再循環させるポンプあるいは他の再循環手段と、を含む。ランキンサイクルシステムにおける作動流体は、たいていは水であり、その場合に、タービンは水蒸気によって駆動される。有機ランキンサイクル（ＯＲＣ）システムは、作動流体として水ではなく有機流体を使用すること以外は、従来のランキンサイクルと同様に運転する。   Rankine cycle systems are commonly used to generate electrical power. The Rankine cycle system is an evaporator or boiler that evaporates working fluid, a turbine that receives steam from the evaporator to drive a generator, a condenser that condenses the steam, and recirculates the condensed fluid to the evaporator. A pump or other recirculation means. The working fluid in the Rankine cycle system is usually water, in which case the turbine is driven by steam. The organic Rankine cycle (ORC) system operates in the same manner as a conventional Rankine cycle except that it uses an organic fluid rather than water as the working fluid.

ＯＲＣシステムは、蒸発器において有機流体を蒸発させるための熱を提供するために、廃熱を利用する。往復機関は、ＯＲＣシステムに利用される一般的な廃熱源の一つである。往復機関からの有用な廃熱としては、約５４０℃（約１０００°Ｆ）付近の温度の排気ガスと、約１０５℃（約２２０°Ｆ）の冷却水と、がある。往復機関からこれら両方の廃熱源を利用することは、特にこれら２つの間に温度差があるので、難しい問題が生じる。これに関して、排気ガスは、より大きな熱伝達のポテンシャルを有することを考慮すると、一般に、冷却水よりも好ましい。   The ORC system utilizes waste heat to provide heat to evaporate the organic fluid in the evaporator. A reciprocating engine is one of the common waste heat sources used for ORC systems. Useful waste heat from the reciprocating engine includes exhaust gas at a temperature around about 540 ° C. (about 1000 ° F.) and cooling water at about 105 ° C. (about 220 ° F.). Utilizing both these waste heat sources from a reciprocating engine presents a difficult problem, especially because of the temperature difference between the two. In this regard, exhaust gas is generally preferred over cooling water, considering that it has a greater potential for heat transfer.

ＯＲＣシステムは、往復機関からの高温の排気ガスの熱を有効利用するために、一般に、高温で沸騰する、高い臨界温度を有する有機流体を使用する。しかし、単一のタービンで大きな圧力比に亘って有機流体が膨張する場合、タービンから流出する蒸気がさらに過熱され、タービンから得られる動力の量が減少してしまう。また、タービンから流出する著しく過熱された流体に、特別な凝縮器が必要とされる。   The ORC system generally uses an organic fluid having a high critical temperature that boils at a high temperature in order to effectively utilize the heat of the hot exhaust gas from the reciprocating engine. However, when the organic fluid expands over a large pressure ratio in a single turbine, the steam flowing out of the turbine is further overheated, reducing the amount of power available from the turbine. Also, special condensers are required for the significantly superheated fluid exiting the turbine.

往復機関およびＯＲＣシステムの効率を向上させるために、往復機関からの廃熱を回収する、改善された方法およびシステムが必要とされている。   In order to improve the efficiency of reciprocating engines and ORC systems, there is a need for improved methods and systems that recover waste heat from reciprocating engines.

容積形機関からの２つの廃熱源を利用して、カスケード型有機ランキンサイクル（ＯＲＣ）システムを運転する方法およびシステムが提供され、これによって、機関およびカスケード型ＯＲＣシステムの効率が上昇する。容積形機関からの高温の廃熱源は、第１のＯＲＣシステム内で利用され、第１の作動流体を蒸発させる。容積形機関からの低温の廃熱源は、第２のＯＲＣシステム内で利用され、第２の作動流体を蒸発温度よりは低い温度にまで加熱する。そして、この第２の作動流体は、第１の作動流体からの熱を使って蒸気化される。一実施例においては、容積形機関は、往復機関であり、廃熱源は、排気ガスとジャケット冷却水である。   A method and system for operating a cascaded organic Rankine cycle (ORC) system utilizing two waste heat sources from a positive displacement engine is provided, which increases the efficiency of the engine and the cascaded ORC system. A hot waste heat source from the positive displacement engine is utilized in the first ORC system to evaporate the first working fluid. A cold waste heat source from the positive displacement engine is utilized in the second ORC system to heat the second working fluid to a temperature below the evaporation temperature. The second working fluid is vaporized using the heat from the first working fluid. In one embodiment, the positive displacement engine is a reciprocating engine and the waste heat sources are exhaust gas and jacket cooling water.

廃熱を利用して電力を発生させるように設計された有機ランキンサイクル（ＯＲＣ）システムの概略図。1 is a schematic diagram of an organic Rankine cycle (ORC) system designed to generate power using waste heat. 往復機関からの２つの廃熱源を利用するように設計された、第１のＯＲＣシステムおよび第２のＯＲＣシステムを含むカスケード型ＯＲＣシステムの概略図。1 is a schematic diagram of a cascaded ORC system including a first ORC system and a second ORC system designed to utilize two waste heat sources from a reciprocating engine. 図２に示したカスケード型ＯＲＣシステムについてのＴ−ｓ図。The Ts figure about the cascade type ORC system shown in FIG.

有機ランキンサイクル（ＯＲＣ）システムなどの廃熱回収システムは、往復機関などの原動機から熱を回収するために使用することができる。さらに、このＯＲＣシステムは、電力を発生させるために使用することができる。往復機関には、ＯＲＣシステムが回収し得る２つの廃熱源（排気ガス（高温）と冷却水（低温））がある。しかし、これらの廃熱源の間に大きな温度差がある場合、単一のＯＲＣシステム内でこれらの廃熱源の両方を有効に利用することは難しい。本明細書中に説明するように、カスケード型ＯＲＣシステムにおいて、第１のＯＲＣシステムが高温の作動流体を利用して発電機に動力を与え、第２のＯＲＣシステムが低温の作動流体を利用して第２の発電機に第２の動力を与える。第１のＯＲＣシステムは、往復機関の排気ガスから熱を回収する。第２のＯＲＣシステムは、往復機関の冷却水から熱を回収するとともに、第１のＯＲＣシステム内の高温の作動流体から凝縮熱を回収する。本明細書中で説明するカスケード型ＯＲＣシステムおよび方法は、往復機関からの廃熱をさらに多く利用し、これによって、往復機関からの廃熱の単位量当たりに発生する電力量が大きくなる。   Waste heat recovery systems such as organic Rankine cycle (ORC) systems can be used to recover heat from prime movers such as reciprocating engines. Furthermore, the ORC system can be used to generate power. The reciprocating engine has two waste heat sources (exhaust gas (high temperature) and cooling water (low temperature)) that can be recovered by the ORC system. However, if there is a large temperature difference between these waste heat sources, it is difficult to effectively utilize both of these waste heat sources within a single ORC system. As described herein, in a cascaded ORC system, a first ORC system utilizes a hot working fluid to power a generator and a second ORC system utilizes a cold working fluid. The second power is applied to the second generator. The first ORC system recovers heat from the exhaust gas of the reciprocating engine. The second ORC system recovers heat from the cooling water of the reciprocating engine and recovers condensation heat from the hot working fluid in the first ORC system. The cascaded ORC system and method described herein utilizes more waste heat from the reciprocating engine, thereby increasing the amount of power generated per unit amount of waste heat from the reciprocating engine.

図１は、凝縮器１２、ポンプ１４、蒸発器１６およびタービン１８を含む、単一のＯＲＣシステム１０を概略的に示す。作動流体２２がシステム１０内を循環し、電力を発生させるために使用される。凝縮器１２から流出する液体の作動流体２２ａは、ポンプ１４を通り、圧力が上昇する。高圧となった液体流体２２ａは、蒸発器１６内へ流れ、この蒸発器１６が、熱源２４を利用して、流体２２を蒸発させる。熱源２４としては、往復機関、燃料電池、マイクロタービンなどの種々の形式の廃熱や、太陽、地熱、廃ガスなどの他の形式の熱源があるが、これらに限らない。作動流体２２は、蒸発器１６から蒸気（２２ｂ）として流出し、ここからタービン１８内へ流れる。蒸気化した作動流体２２ｂは、タービン１８を駆動するために使用され、このタービン１８は発電機２８に動力を与え、この発電機２８は電力を発生させる。タービン１から流出する作動流体２２ｂは、凝縮器１２へ戻り、この凝縮器１２で凝縮されて液体２２ａとなる。ヒートシンク３０を使用して、この凝縮器１２を冷却する。   FIG. 1 schematically illustrates a single ORC system 10 that includes a condenser 12, a pump 14, an evaporator 16, and a turbine 18. A working fluid 22 is circulated through the system 10 and used to generate electrical power. The liquid working fluid 22a flowing out of the condenser 12 passes through the pump 14 and increases in pressure. The high-pressure liquid fluid 22 a flows into the evaporator 16, and the evaporator 16 uses the heat source 24 to evaporate the fluid 22. The heat source 24 includes, but is not limited to, various types of waste heat such as a reciprocating engine, a fuel cell, and a micro turbine, and other types of heat sources such as the sun, geothermal heat, and waste gas. The working fluid 22 flows out of the evaporator 16 as steam (22 b) and flows from here into the turbine 18. The vaporized working fluid 22b is used to drive a turbine 18, which powers a generator 28 that generates electrical power. The working fluid 22b flowing out of the turbine 1 returns to the condenser 12, and is condensed in the condenser 12 to become a liquid 22a. A heat sink 30 is used to cool the condenser 12.

熱源２４が高温の熱源である場合、作動流体２２は、高い臨界温度を有する高温の流体であることが好ましい。その場合、熱源２４は、蒸発器１６において作動流体を臨界温度よりも低い温度に維持しつつ、この作動流体に十分な熱を伝達することができる。しかし、そのような高温の作動流体の欠点は、タービン１８から流出するときに、著しく過熱されているということである。過熱された蒸気からの熱の少なくとも一部は、電力に変換されないので、タービン１８の効率が低下する。さらには、高温の作動流体を使用する場合、凝縮器１２において追加の冷却が必要とされ、その結果、高価な装置が必要になるとともに、一般に、大量の廃熱を作動流体から回収することができない。   When the heat source 24 is a high temperature heat source, the working fluid 22 is preferably a high temperature fluid having a high critical temperature. In that case, the heat source 24 can transfer sufficient heat to the working fluid while maintaining the working fluid at a temperature lower than the critical temperature in the evaporator 16. However, a disadvantage of such hot working fluid is that it is significantly overheated as it exits the turbine 18. Since at least a portion of the heat from the superheated steam is not converted to electrical power, the efficiency of the turbine 18 is reduced. Furthermore, when using hot working fluids, additional cooling is required in the condenser 12, which results in the need for expensive equipment and generally recovering large amounts of waste heat from the working fluid. Can not.

これに対して、熱源２４が低温の熱源である場合、システム１０内で、低温の作動流体を使用することができる。しかし、システム１０が高温の熱源から熱を回収するときと比較して、出力電力の効率が低下する。   On the other hand, when the heat source 24 is a low-temperature heat source, a low-temperature working fluid can be used in the system 10. However, the efficiency of the output power is reduced compared to when the system 10 recovers heat from a high temperature heat source.

熱源２４が往復機関からの廃熱である場合、ＯＲＣシステムは、一般に、排気ガス（すなわち、高温廃熱）あるいはジャケット冷却水（すなわち、低温廃熱）のいずれかを利用するが、その理由は、これらの両方を使うことは難しいからである。従って、往復機関からの廃熱の一部は、ＯＣＲシステム１０で回収することができない。   If the heat source 24 is waste heat from a reciprocating engine, the ORC system typically utilizes either exhaust gas (ie, high temperature waste heat) or jacket cooling water (ie, low temperature waste heat) for the reason. Because it is difficult to use both of these. Therefore, part of the waste heat from the reciprocating engine cannot be recovered by the OCR system 10.

図２は、第１のＯＲＣシステム１０２および第２のＯＲＣシステム１０４を含み、これらの双方が往復機関１０６からの廃熱を回収する、カスケード型ＯＲＣシステム１００の概略を示す。第１のＯＲＣシステム１０２は、図１のＯＲＣシステムと類似したものであり、蒸発器１１０、タービン１１２、凝縮器１１４およびポンプ１１６を備えている。第１の作動流体１１８は、システム１０２内を循環して、タービン１１２を駆動するために使用され、これによって、発電機１２０が電力を発生させることができる。第２のＯＲＣシステム１０４は、タービン１１２、凝縮器１２４、ポンプ１２６、熱交換器１２８および蒸発器１１４を含む。第２の作動流体１３０は、第２のＯＲＣシステム１０４内で、タービン１２２を駆動するために使用され、このタービン１２２は、発電機１３２を駆動する。また、第２のＯＲＣシステム１０４の凝縮器１２４は、ヒートシンク１３４を使って冷却を行い、タービン１２２からの作動流体蒸気１３０を凝縮する。ヒートシンク１３４は、水あるいは空気とすることができ、また、いくつかの例では、以下にさらに説明するように、外部ソースへ有用な熱を提供するように使用することができる。第１の作動流体１１８および第２の作動流体１３０は、有機作動流体であり、以下にいくつかの例を挙げる。   FIG. 2 shows a schematic of a cascaded ORC system 100 that includes a first ORC system 102 and a second ORC system 104, both of which recover waste heat from the reciprocating engine 106. The first ORC system 102 is similar to the ORC system of FIG. 1 and includes an evaporator 110, a turbine 112, a condenser 114 and a pump 116. The first working fluid 118 circulates in the system 102 and is used to drive the turbine 112, which allows the generator 120 to generate power. The second ORC system 104 includes a turbine 112, a condenser 124, a pump 126, a heat exchanger 128 and an evaporator 114. The second working fluid 130 is used within the second ORC system 104 to drive a turbine 122 that drives a generator 132. The condenser 124 of the second ORC system 104 also uses a heat sink 134 to cool and condense the working fluid vapor 130 from the turbine 122. The heat sink 134 can be water or air and, in some examples, can be used to provide useful heat to an external source, as further described below. The first working fluid 118 and the second working fluid 130 are organic working fluids, and some examples are given below.

第１のＯＲＣシステム１０２の凝縮器１１４は、第２のＯＲＣシステム１０４の蒸発器としても機能する。さらに以下に説明するように、第１の作動流体１１８は、高温の作動流体であり、第２の作動流体１３０は、低温の作動流体である。従って、蒸発器／凝縮器１１４は、タービン１１２からの作動流体蒸気１１８を凝縮させ、このときの熱を伝達して、第２の作動流体１３０を蒸発させるように構成されている。   The condenser 114 of the first ORC system 102 also functions as the evaporator of the second ORC system 104. As will be described further below, the first working fluid 118 is a hot working fluid and the second working fluid 130 is a cold working fluid. Accordingly, the evaporator / condenser 114 is configured to condense the working fluid vapor 118 from the turbine 112 and transmit heat at this time to evaporate the second working fluid 130.

往復機関１０６は、システム１００が回収可能な２つの廃熱源を有する。第１の源は、約４７５℃〜約５４０℃（約８８５°Ｆ〜約１００５°Ｆ）の範囲で温度変化する。第２の源は、約１００℃〜約１１０℃（約２１２°Ｆ〜約２３０°Ｆ）の範囲で温度変化する。排気ガスからの熱は、第１のＯＲＣシステム１０２によって使用される。詳しくは、排気ガスは、作動流体１１８を蒸発させるように、蒸発器１１０で使用される。   The reciprocating engine 106 has two waste heat sources that the system 100 can recover. The first source varies in temperature in the range of about 475 ° C to about 540 ° C (about 885 ° F to about 1005 ° F). The second source varies in temperature in the range of about 100 ° C to about 110 ° C (about 212 ° F to about 230 ° F). Heat from the exhaust gas is used by the first ORC system 102. Specifically, the exhaust gas is used in the evaporator 110 to evaporate the working fluid 118.

第２のＯＲＣシステム１０４は、ジャケット冷却水から熱を受ける。システム１０４の熱交換器１２８は、ポンプ１２６と蒸発器１１４との間に配置され、ジャケット冷却水から液体の作動流体１３０へ熱を伝達するように設計されている。ジャケット冷却水は、排気ガスと比較して、低温の廃熱源であるので、作動流体１３０を蒸発温度よりも低い温度にまで加熱するために使用される。従って、作動流体１３０は、熱交換器１２８の入口よりも出口において温度が高い。このジャケット冷却水は、熱交換器１２８から流出した後、往復機関１０６へ戻るように再循環される。   The second ORC system 104 receives heat from the jacket cooling water. The heat exchanger 128 of the system 104 is positioned between the pump 126 and the evaporator 114 and is designed to transfer heat from the jacket cooling water to the liquid working fluid 130. Since the jacket cooling water is a low-temperature waste heat source compared to the exhaust gas, it is used to heat the working fluid 130 to a temperature lower than the evaporation temperature. Accordingly, the working fluid 130 has a higher temperature at the outlet than at the inlet of the heat exchanger 128. The jacket cooling water is recirculated so as to return to the reciprocating engine 106 after flowing out of the heat exchanger 128.

第２の作動流体１３０は、熱交換器１２８を通流した後、凝縮器／蒸発器１１４を流れる。この凝縮器／蒸発器１１４は、第１の作動流体１１８を液体に凝縮させるとともに、第２の作動流体１３０を蒸発させるように、第１の作動流体１１８と第２の作動流体１３０との間で熱を伝達させるように設計されている。第１の作動流体１１８は、第２の作動流体１３０を沸騰させるのに適した凝縮温度を有することが好ましい。   The second working fluid 130 flows through the condenser / evaporator 114 after flowing through the heat exchanger 128. The condenser / evaporator 114 condenses the first working fluid 118 to a liquid and evaporates the second working fluid 130 between the first working fluid 118 and the second working fluid 130. Designed to transfer heat at. The first working fluid 118 preferably has a condensing temperature suitable for boiling the second working fluid 130.

第２の作動流体１３０は、蒸発器１１４からタービン１２２へ流れ、さらに、水冷式凝縮器あるいは空冷式凝縮器（すなわち、ヒートシンク１３４は、水または空気）とし得る凝縮器１２４へ流れる。いくつかの実施例においては、ヒートシンク１３４内の水が凝縮器１２４から流出した後、この高温の水は、カスケード型ＯＲＣシステム１００の外部ソースを加熱するために使用することができる。ヒートシンク１３４は、例えば、地域暖房用水を加熱するか、および／または、周囲環境（例えば、農作物あるいは温室）を加熱するために利用することができる。   The second working fluid 130 flows from the evaporator 114 to the turbine 122 and further to the condenser 124, which may be a water cooled condenser or an air cooled condenser (ie, the heat sink 134 is water or air). In some embodiments, after the water in the heat sink 134 has flowed out of the condenser 124, this hot water can be used to heat the external source of the cascaded ORC system 100. The heat sink 134 can be utilized, for example, to heat district heating water and / or to heat the surrounding environment (eg, crops or greenhouses).

カスケード型ＯＲＣシステムを用いることにより、往復機関１０６からの廃熱のほぼすべてを利用することができる。高温廃熱源（排気ガス）は、高温の作動流体を利用するＯＲＣシステム１０２によって回収される。低温廃熱源（ジャケット冷却水）は、低温の作動流体を利用するＯＲＣシステム１０４によって回収される。さらには、カスケード型ＯＲＣシステム１００の設計とすることにより、タービン１１２から流出する第１の作動流体１１８からの熱を第２の作動流体へ伝達することができるので、全体の効率が高くなる。また、熱交換器１２８内で第２の作動流体１３０を予熱することによって、第２のＯＲＣシステム１０４の効率が高くなる。さらに、カスケード型ＯＲＣシステム１００の外部ソースを加熱するようにヒートシンク１３４を利用することによって、ＯＲＣシステム１００の熱利用効率がさらに高まる。   By using a cascaded ORC system, almost all of the waste heat from the reciprocating engine 106 can be utilized. The high-temperature waste heat source (exhaust gas) is recovered by the ORC system 102 that uses a high-temperature working fluid. The low-temperature waste heat source (jacket cooling water) is recovered by the ORC system 104 that uses a low-temperature working fluid. Furthermore, the design of the cascaded ORC system 100 allows the heat from the first working fluid 118 flowing out of the turbine 112 to be transferred to the second working fluid, thereby increasing the overall efficiency. Also, preheating the second working fluid 130 in the heat exchanger 128 increases the efficiency of the second ORC system 104. Furthermore, the heat utilization efficiency of the ORC system 100 is further enhanced by utilizing the heat sink 134 to heat the external source of the cascaded ORC system 100.

第１の作動流体１１８は、第２の作動流体１３０よりも高い臨界温度を有する。蒸発器１１０において第１の作動流体１１８を蒸発させるために、往復機関１０６からの排気ガスが利用されるので、作動流体１１８は、蒸発器１１０内において高温で沸騰するように、高い臨界点を有することが好ましい。超臨界相の作動流体を取り扱うことは、技術的に難しい問題を提起するので、臨界温度よりも低い温度に維持することによって、これらの問題を回避することが好ましい。   The first working fluid 118 has a higher critical temperature than the second working fluid 130. Since the exhaust gas from the reciprocating engine 106 is utilized to evaporate the first working fluid 118 in the evaporator 110, the working fluid 118 has a high critical point so that it boils at a high temperature in the evaporator 110. It is preferable to have. Handling supercritical fluids presents technically difficult problems, and it is preferable to avoid these problems by maintaining a temperature below the critical temperature.

他方で、第２のＯＲＣシステム１０４においては、低温の熱源（すなわち、冷却水と、作動流体１１８の低温の凝縮熱）を利用して第２の作動流体１３０を蒸発させるので、作動流体１３０の臨界温度は、作動流体１１８の臨界温度よりも低いことが好ましい。仮に、第２のＯＲＣシステム１０４で、高い臨界温度を有する作動流体が使用されるとすれば、システム１０４内の圧力が低下し過ぎ、その結果、流体の密度が小さくなり、さらに大きな装置が必要とされる。   On the other hand, in the second ORC system 104, the second working fluid 130 is evaporated using a low-temperature heat source (that is, cooling water and the low-temperature condensation heat of the working fluid 118). The critical temperature is preferably lower than the critical temperature of the working fluid 118. If a working fluid having a high critical temperature is used in the second ORC system 104, the pressure in the system 104 will drop too much, resulting in a lower fluid density and a need for larger equipment. It is said.

第１の作動流体１１８としては、シロキサン、トルエン、イソブテン、イソペンタン、ｎ−ペンタン、および４−トリフルオロメチル−１，１，１，３，５，５，５−ヘプタフルオロ−２−ペンテン（（ＣＦ3）2ＣＨＣＦ＝ＣＨＣＦ3）があるが、これらに限定しない。第１の作動流体１１８に適用なシロキサンの例としては、ＭＭ ヘキサメチルジシロキサン（Ｃ6Ｈ18ＯＳｉ2）、ＭＤＭ オクタメチルトリシロキサン（Ｃ8Ｈ24Ｏ2Ｓｉ3）、およびＭＤ２Ｄ デカメチルテトラシロキサン（Ｃ10Ｈ30Ｏ3Ｓｉ4）があるが、これらに限定しない。いくつかの実施例においては、シロキサンは、可燃性の、トルエン、イソブテン、イソペンタンおよびｎ−ペンタンよりも好ましい。 Examples of the first working fluid 118 include siloxane, toluene, isobutene, isopentane, n-pentane, and 4-trifluoromethyl-1,1,1,3,5,5,5-heptafluoro-2-pentene (( CF 3) 2 CHCF = CHCF 3 ) there are, without limitation. Examples of siloxanes applicable to the first working fluid 118 include MM hexamethyldisiloxane (C 6 H 18 OSi 2 ), MDM octamethyltrisiloxane (C 8 H 24 O 2 Si 3 ), and MD2D decamethyltetra Although there is siloxane (C 10 H 30 O 3 Si 4 ), it is not limited to these. In some embodiments, siloxane is preferred over flammable toluene, isobutene, isopentane and n-pentane.

第２の作動流体１３０としては、Ｒ１２３、Ｒ１３４ａ、Ｒ２３６ｆａおよびＲ２４５ｆａがあるが、これらに限定しない。好ましい実施例においては、ＯＲＣシステム１０４内で、Ｒ１３４ａまたはＲ２４５ｆａが使用される。環境空気温度が低い場合、ヒートシンク３４の温度が低下するので、Ｒ１３４を使用することが好ましい。環境空気温度が高い場合、Ｒ２４５ｆａを使用することが好ましい。   Examples of the second working fluid 130 include, but are not limited to, R123, R134a, R236fa, and R245fa. In the preferred embodiment, R134a or R245fa is used within the ORC system 104. Since the temperature of the heat sink 34 decreases when the ambient air temperature is low, it is preferable to use R134. When the ambient air temperature is high, R245fa is preferably used.

第１の作動流体１１８および第２の作動流体１３０としては、上記に挙げていない有機作動流体を含み得ることを理解されたい。また、第１の作動流体１１８および第２の作動流体１３０の多くの組み合わせを用いることができる。上記のように、カスケード型ＯＲＣシステム１００は、第２の作動流体１３０よりも高い臨界温度を有する第１の作動流体１１８を用いて運転されることが好ましい。   It should be understood that the first working fluid 118 and the second working fluid 130 may include organic working fluids not listed above. Also, many combinations of the first working fluid 118 and the second working fluid 130 can be used. As described above, the cascaded ORC system 100 is preferably operated with the first working fluid 118 having a higher critical temperature than the second working fluid 130.

図３は、図２に示したカスケード型ＯＲＣシステム１００についてのＴ−ｓ図である。第１の作動流体１１８と第２の作動流体１３０の両方について、温度Ｔが、エントロピＳの関数としてプロットされている。以下にさらに詳しく説明するように、図３は、往復機関１０６の排気ガスから第１の作動流体１１８への熱エネルギの移動と、エンジン１０６のジャケット冷却水から第２の作動流体１３０への熱エネルギの移動と、を示す。さらに図３に示すように、第１の作動流体１１８は、第２の作動流体１３０へ熱を伝達し、この第２の作動流体１３０は、ヒートシンク１３４へ熱を伝達する。   FIG. 3 is a Ts diagram for the cascaded ORC system 100 shown in FIG. The temperature T is plotted as a function of entropy S for both the first working fluid 118 and the second working fluid 130. As will be described in more detail below, FIG. 3 illustrates the transfer of thermal energy from the exhaust gas of the reciprocating engine 106 to the first working fluid 118 and the heat from the jacket cooling water of the engine 106 to the second working fluid 130. Energy transfer. As further shown in FIG. 3, the first working fluid 118 transfers heat to the second working fluid 130, which transfers heat to the heat sink 134.

往復機関１０６の排気ガスからの熱は、第１の作動流体１１８へ伝達され、図３に示すように、作動流体１１８が蒸発温度に達するまで、作動流体１１８の温度を上昇させる。しかし、流体１１８は、臨界温度Ｔ1criticalよりも低い温度に保たれている。この蒸気化した流体１１８は、タービン１１２内で膨張するとともに、温度が低下するが、蒸気相であることに変わりはない。第２のＯＲＣシステム１０４に対して蒸発器としても機能する凝縮器１１４において、流体１１８は、凝縮温度に達するまで過熱が低減される。流体１１８からの熱は、凝縮器／蒸発器１１４において第２の作動流体１３０へ伝達される。流体１３０の温度は、臨界温度Ｔ2criticalよりも低い温度に保たれている。 Heat from the exhaust gas of the reciprocating engine 106 is transferred to the first working fluid 118, which raises the temperature of the working fluid 118 until the working fluid 118 reaches the evaporation temperature, as shown in FIG. However, the fluid 118 is kept at a temperature lower than the critical temperature T1critical . The vaporized fluid 118 expands in the turbine 112 and decreases in temperature, but remains in the vapor phase. In the condenser 114, which also functions as an evaporator for the second ORC system 104, the fluid 118 is reduced in superheat until the condensation temperature is reached. Heat from the fluid 118 is transferred to the second working fluid 130 in the condenser / evaporator 114. The temperature of the fluid 130 is maintained at a temperature lower than the critical temperature T2critical .

第１の作動流体１１８からの熱は、凝縮器／蒸発器１１４内で、第２の作動流体１３０を蒸発させるのに十分である。これは、一部は、凝縮器／蒸発器１１４の上流における第２の作動流体の予熱による。図３に示すように、往復機関１０６からのジャケット冷却水が作動流体１３０の温度を蒸発温度よりは低い温度にまで上昇させるために使用される。   Heat from the first working fluid 118 is sufficient to evaporate the second working fluid 130 in the condenser / evaporator 114. This is due in part to the preheating of the second working fluid upstream of the condenser / evaporator 114. As shown in FIG. 3, jacket cooling water from the reciprocating engine 106 is used to raise the temperature of the working fluid 130 to a temperature lower than the evaporation temperature.

流体１１８について説明したのと同様に、第２の作動流体１３０は、タービン１２２を通過した後、温度が低下する。ここで、過熱状態の流体１３０は、周囲空気あるいはヒートシンク１３４からの冷却水を使って、凝縮器／ヒータ１２４内で凝縮される。換言すると、図３に示すように、作動流体１３０からの熱は、ヒートシンク３４へ伝達される。上記に説明したように、いくつかの実施例においては、ヒートシンク３４は、例えば温室などの外部ソースを加熱するために利用することができる。   Similar to that described for fluid 118, second working fluid 130 decreases in temperature after passing through turbine 122. Here, the overheated fluid 130 is condensed in the condenser / heater 124 using ambient air or cooling water from the heat sink 134. In other words, as shown in FIG. 3, the heat from the working fluid 130 is transferred to the heat sink 34. As explained above, in some embodiments, the heat sink 34 can be utilized to heat an external source, such as a greenhouse.

図２の実施例において、カスケード型ＯＲＣシステム１００は、往復機関からの２つの廃熱源を利用する。このうち低温の熱源は、ジャケット冷却水である。また、システム１００に廃熱を供給するために、往復機関に加え、機関の運転に冷却水を必要とする他の型式の容積形機関をさらに利用できることが理解されよう。この例としては、ヴァンケルエンジンなどがあるが、これに限定しない。   In the embodiment of FIG. 2, the cascaded ORC system 100 utilizes two waste heat sources from the reciprocating engine. Of these, the low-temperature heat source is jacket cooling water. It will also be appreciated that other types of positive displacement engines that require cooling water to operate the engine may be further utilized in addition to the reciprocating engine to supply the system 100 with waste heat. Examples of this include, but are not limited to, a Wankel engine.

本明細書中で説明するカスケード型ＯＲＣシステムは、往復機関からの２つの別個の廃熱源を使用する。２つのＯＲＣシステムが使用されるので、カスケード型ＯＲＣシステムにおいては、発生する電力が増える。往復機関の排出物レベルは変化しないので、発生する電力の単位量当たりの往復機関からの排出物は減少する。さらには、本明細書中に説明したカスケード型ＯＲＣシステムは、第１のＯＲＣシステムおよび第２のＯＲＣシステムからの廃熱を少なくする。従って、本明細書中に説明したシステムおよび方法を使用することによって、往復機関の効率および各ＯＲＣシステムの効率が向上する。   The cascaded ORC system described herein uses two separate waste heat sources from the reciprocating engine. Since two ORC systems are used, more power is generated in a cascaded ORC system. Since the emission level of the reciprocating engine does not change, the emissions from the reciprocating engine per unit amount of power generated are reduced. Further, the cascaded ORC system described herein reduces waste heat from the first ORC system and the second ORC system. Thus, the use of the systems and methods described herein improves the efficiency of the reciprocating engine and the efficiency of each ORC system.

好ましい実施例を参照して本発明を説明したが、当業者であれば、本発明の趣旨および範囲を逸脱することなく、形態や詳細にいくつかの変更がなされ得ることを理解されるであろう。   Although the present invention has been described with reference to preferred embodiments, those skilled in the art will recognize that several changes can be made in form and detail without departing from the spirit and scope of the invention. Let's go.

Claims (22)

カスケード型ランキンサイクル（ＯＲＣ）システムを運転する方法であって、
容積形機関からの高温熱源を利用して、第１のＯＲＣシステム内の第１の有機作動流体を蒸発させ、
容積形機関からの低温熱源を利用して、第２のＯＲＣシステム内の第２の有機作動流体を加熱し、
第１の有機作動流体からの熱を利用して、第２の有機作動流体を蒸発させること、
を含み、
第１の有機作動流体の臨界温度は、第２の有機作動流体の臨界温度よりも高いことを特徴とする方法。 A method of operating a cascaded Rankine cycle (ORC) system comprising:
Utilizing a high temperature heat source from the positive displacement engine to evaporate the first organic working fluid in the first ORC system;
Utilizing a low temperature heat source from the positive displacement engine to heat the second organic working fluid in the second ORC system;
Evaporating the second organic working fluid utilizing heat from the first organic working fluid;
Including
A method wherein the critical temperature of the first organic working fluid is higher than the critical temperature of the second organic working fluid. 上記容積形機関は、往復機関であることを特徴とする請求項１に記載の方法。   The method of claim 1, wherein the positive displacement engine is a reciprocating engine. 上記高温熱源は排気ガスであり、上記低温熱源はジャケット冷却水であることを特徴とする請求項１に記載の方法。   2. The method of claim 1, wherein the high temperature heat source is exhaust gas and the low temperature heat source is jacket cooling water. 上記高温熱源の温度は、約４７５℃〜約５４０℃であり、上記低温熱源の温度は、約１００℃〜約１１０℃であることを特徴とする請求項１に記載の方法。   The method of claim 1, wherein the temperature of the high temperature heat source is from about 475 ° C to about 540 ° C, and the temperature of the low temperature heat source is from about 100 ° C to about 110 ° C. 上記第２の有機作動流体の蒸発が、第１の有機作動流体を凝縮するとともに第２の有機作動流体を蒸発させるように構成された熱交換器によって行われることを特徴とする請求項１に記載の方法。   The evaporation of the second organic working fluid is performed by a heat exchanger configured to condense the first organic working fluid and evaporate the second organic working fluid. The method described. 上記第２のＯＲＣシステム内の第２の有機作動流体の加熱が、上記低温熱源から熱を引き出して第２の有機作動流体を予熱するように構成された熱交換器によって行われることを特徴とする請求項１に記載の方法。   Heating the second organic working fluid in the second ORC system is performed by a heat exchanger configured to draw heat from the low temperature heat source to preheat the second organic working fluid. The method of claim 1. 第１の有機作動流体は、シロキサン、トルエン、イソブテン、イソペンタン、ｎ−ペンタン、および４−トリフルオロメチル−１，１，１，３，５，５，５−ヘプタフルオロ−２−ペンテン（（ＣＦ3）2ＣＨＣＦ＝ＣＨＣＦ3）からなる群から選択されることを特徴とする請求項１に記載の方法。 The first organic working fluid was siloxane, toluene, isobutene, isopentane, n-pentane, and 4-trifluoromethyl-1,1,1,3,5,5,5-heptafluoro-2-pentene ((CF the method according to claim 1, characterized in that it is selected from the group consisting of 3) 2 CHCF = CHCF 3) . 第２の有機作動流体は、Ｒ１２３、Ｒ１３４ａ、Ｒ２３６ｆａおよびＲ２４５ｆａからなる群から選択されることを特徴とする請求項１に記載の方法。   The method of claim 1, wherein the second organic working fluid is selected from the group consisting of R123, R134a, R236fa, and R245fa. 第２の有機作動流体を利用して外部ソースを加熱することを含む請求項１に記載の方法。   The method of claim 1, comprising heating the external source utilizing a second organic working fluid. 上記外部ソースは、地域暖房用水、温室および農作物のうちの少なくとも１つを含むことを特徴とする請求項９に記載の方法。   The method of claim 9, wherein the external source comprises at least one of district heating water, a greenhouse, and a crop. 往復機関からの高温廃熱源を利用して第１の有機作動流体を蒸発させるとともに、この第１の有機作動流体を使用して電力を発生させるように構成された第１の有機ランキンサイクル（ＯＲＣ）システムと、
第１の有機作動流体から熱を受けて第２の有機作動流体を蒸発させるとともに、この第２の有機作動流体を使用して電力を発生させるように構成された第２の有機ランキンサイクル（ＯＲＣ）システムと、
第２の作動流体を蒸発させる前に、上記往復機関からの低温廃熱源を利用して第２の有機作動流体の温度を上昇させるように構成された熱交換器と、
を備え、
第１の有機作動流体の臨界温度は、第２の有機作動流体の臨界温度よりも高いことを特徴とする廃熱回収システム。 A first organic Rankine cycle (ORC) configured to evaporate a first organic working fluid utilizing a high-temperature waste heat source from a reciprocating engine and generate electric power using the first organic working fluid. ) System,
A second organic Rankine cycle (ORC) configured to receive heat from the first organic working fluid to evaporate the second organic working fluid and generate electric power using the second organic working fluid. ) System,
A heat exchanger configured to increase the temperature of the second organic working fluid using a low-temperature waste heat source from the reciprocating engine before evaporating the second working fluid;
With
The waste heat recovery system, wherein the critical temperature of the first organic working fluid is higher than the critical temperature of the second organic working fluid. 上記高温廃熱源は、第１の有機作動流体を蒸発させるように、第１のＯＲＣシステム内の蒸発器を通流することを特徴とする請求項１１に記載の廃熱回収システム。   The waste heat recovery system according to claim 11, wherein the high-temperature waste heat source flows an evaporator in the first ORC system so as to evaporate the first organic working fluid. 第１の有機作動流体は、該第１の有機作動流体が凝縮されるとともに第２の有機作動流体を蒸発させるように、第１のＯＲＣシステムの蒸発器の下流に配置された凝縮器を通流することを特徴とする請求項１２に記載の廃熱回収システム。   The first organic working fluid passes through a condenser disposed downstream of the evaporator of the first ORC system so that the first organic working fluid is condensed and the second organic working fluid is evaporated. The waste heat recovery system according to claim 12, wherein the waste heat recovery system is flowed. 上記熱交換器は、第２のＯＲＣシステムの凝縮器の下流かつ第２のＯＲＣシステムの蒸発器の上流に配置されることを特徴とする請求項１１に記載の廃熱回収システム。   The waste heat recovery system according to claim 11, wherein the heat exchanger is disposed downstream of a condenser of the second ORC system and upstream of an evaporator of the second ORC system. 上記高温廃熱源は上記往復機関からの排気ガスであり、上記低温排熱源は上記往復機関からのジャケット冷却水であることを特徴とする請求項１１に記載の廃熱回収システム。   The waste heat recovery system according to claim 11, wherein the high temperature waste heat source is exhaust gas from the reciprocating engine, and the low temperature exhaust heat source is jacket cooling water from the reciprocating engine. 第１の有機作動流体は、シロキサン、トルエン、イソブテン、イソペンタン、ｎ−ペンタン、および４−トリフルオロメチル−１，１，１，３，５，５，５−ヘプタフルオロ−２−ペンテン（（ＣＦ3）2ＣＨＣＦ＝ＣＨＣＦ3）からなる群から選択され、上記第２の有機作動流体は、Ｒ１２３、Ｒ１３４ａ、Ｒ２３６ｆａおよびＲ２４５ｆａからなる群から選択されることを特徴とする請求項１１に記載の廃熱回収システム。 The first organic working fluid was siloxane, toluene, isobutene, isopentane, n-pentane, and 4-trifluoromethyl-1,1,1,3,5,5,5-heptafluoro-2-pentene ((CF 3) is selected from 2 CHCF = group consisting CHCF 3), the second organic working fluid, R123, R134a, waste according to claim 11, characterized in that it is selected from the group consisting of R236fa and R245fa Heat recovery system. 第２の有機作動流体から熱を受けて外部ソースを加熱するように構成されたヒートシンクを備えることを特徴とする請求項１１に記載の廃熱回収システム。   The waste heat recovery system of claim 11, comprising a heat sink configured to receive heat from the second organic working fluid to heat an external source. 第１の作動流体を循環させるように構成された第１のＯＲＣシステムと、第２の作動流体を循環させるように構成された第２のＯＲＣシステムと、を含むカスケード型有機ランキンサイクル（ＯＲＣ）システムを運転する方法であって、
往復機関からの排気ガスを利用して、第１のＯＲＣシステムの蒸発器内の第１の作動流体を蒸発させ、
上記往復機関からの冷却水を利用して、第２のＯＲＣシステムの蒸発器の上流を流れている第２の作動流体を加熱し、
第１のＯＲＣシステムの第１の作動流体からの熱を利用して第２のＯＲＣシステムの蒸発器内の第２の作動流体を蒸発させること、
を含み、
第１の作動流体の臨界温度は、第２の作動流体の臨界温度よりも高いことを特徴とする方法。 A cascaded organic Rankine cycle (ORC) comprising: a first ORC system configured to circulate a first working fluid; and a second ORC system configured to circulate a second working fluid. A method of operating a system,
Utilizing the exhaust gas from the reciprocating engine to evaporate the first working fluid in the evaporator of the first ORC system;
Using the cooling water from the reciprocating engine to heat the second working fluid flowing upstream of the evaporator of the second ORC system;
Evaporating a second working fluid in an evaporator of the second ORC system utilizing heat from the first working fluid of the first ORC system;
Including
A method wherein the critical temperature of the first working fluid is higher than the critical temperature of the second working fluid. 第２のＯＲＣシステムの蒸発器は、第１のＯＲＣシステムの凝縮器として構成されていることを特徴とする請求項１８に記載の方法。   The method of claim 18, wherein the evaporator of the second ORC system is configured as a condenser of the first ORC system. 第１の作動流体は、シロキサン、トルエン、イソブテン、イソペンタン、ｎ−ペンタン、および４−トリフルオロメチル−１，１，１，３，５，５，５−ヘプタフルオロ−２−ペンテン（（ＣＦ3）2ＣＨＣＦ＝ＣＨＣＦ3）からなる群から選択され、第２の作動流体は、Ｒ１２３、Ｒ１３４ａ、Ｒ２３６ｆａおよびＲ２４５ｆａからなる群から選択されることを特徴とする請求項１８に記載の方法。 The first working fluid was siloxane, toluene, isobutene, isopentane, n-pentane, and 4-trifluoromethyl-1,1,1,3,5,5,5-heptafluoro-2-pentene ((CF 3 ) 2 CHCF = CHCF 3) is selected from the group consisting of, a second working fluid, R123, R134a, the method according to claim 18, characterized in that it is selected from the group consisting of R236fa and R245fa. 上記往復機関から流出する排気ガスの温度は、約４７５℃〜約５４０℃であり、上記往復機関から流出する冷却水の温度は、約１００℃〜約１１０℃であることを特徴とする請求項１８に記載の方法。   The temperature of exhaust gas flowing out from the reciprocating engine is about 475 ° C to about 540 ° C, and the temperature of cooling water flowing out from the reciprocating engine is about 100 ° C to about 110 ° C. 18. The method according to 18. 第２のＯＲＣシステム内の第２の作動流体からの熱を利用して外部ソースを加熱することを含む請求項１８に記載の方法。   The method of claim 18, comprising heating an external source utilizing heat from a second working fluid in the second ORC system.
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