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WO2008122429A1 - Utilisation de la chaleur produite par des moteurs à combustion interne pour générer de l'électricité - Google Patents

Utilisation de la chaleur produite par des moteurs à combustion interne pour générer de l'électricité Download PDF

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Publication number
WO2008122429A1
WO2008122429A1 PCT/EP2008/002737 EP2008002737W WO2008122429A1 WO 2008122429 A1 WO2008122429 A1 WO 2008122429A1 EP 2008002737 W EP2008002737 W EP 2008002737W WO 2008122429 A1 WO2008122429 A1 WO 2008122429A1
Authority
WO
WIPO (PCT)
Prior art keywords
medium
cycle
heat
heat exchanger
exhaust gas
Prior art date
Application number
PCT/EP2008/002737
Other languages
German (de)
English (en)
Inventor
Matthias Schuhknecht
Original Assignee
Matthias Schuhknecht
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Matthias Schuhknecht filed Critical Matthias Schuhknecht
Publication of WO2008122429A1 publication Critical patent/WO2008122429A1/fr

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Classifications

    • 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
    • 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

Definitions

  • the present invention relates to a method of utilizing waste heat from piston internal combustion engines to generate electric power using a cyclic process, the method comprising the steps of:
  • thermodynamic power plant in particular turbine, on which the cycle process medium performs work.
  • ORC ORC
  • the organic cycle medium such as a silicone oil
  • just when using biogas as fuel for the piston internal combustion engine operation of the internal combustion engine is often in a simple environment, such as farms.
  • the use of organic cyclic process media places increased demands on the system for utilizing the waste heat of piston internal combustion engines, which represents an undesirably high barrier against the use of waste heat from biogas-fueled internal combustion engines. It is therefore an object of the present invention to provide a generic method, which can be operated easily and safely and even in an environment with normal to low technological standard - so to speak, in a low-tech environment.
  • the water is used as a recycle medium in liquid and vapor states, it should only be expressed that the water is present in at least one point of the cycle in liquid form and at least one point of the cycle at least in vapor form.
  • the points of liquid and vapor state of aggregation may be the same, for instance if the water has a thermodynamic state which is in its two-phase state. Area in the temperature entropy diagram (Ts diagram).
  • the greatest possible efficiency can be obtained by transferring heat from the exhaust gas in at least one heat exchanger directly to the cycle medium.
  • the waste heat of the exhaust gas can be transmitted as lossless as possible to the cycle medium.
  • a basic functionality of the CRC process can be ensured if exhaust gas flows through at least one evaporator heat exchanger and then an economizer heat exchanger.
  • the exhaust gas flows through the evaporator heat exchanger in its flow direction and then through the economizer heat exchanger, whereas in its flow direction the circulating medium flows first through the economizer heat exchanger and then through the evaporator heat exchanger.
  • water can be effectively heated as a cycle process medium starting from the liquid state of aggregation and converted into the two-phase state up to the saturated steam state.
  • the circuit process medium only slightly overheat and the thermodynamic power plant (when viewed in Ts diagram) in the two-phase area in the vicinity of the saturated steam line to relax.
  • the method can be carried out in such a way that the intermediate medium heated by the absorption of heat from the exhaust gas successively flows through a plurality of heat exchangers, wherein heat is transferred from the intermediate medium to the circulating medium in each throughflowed heat exchanger. It is advantageously provided for the reasons already mentioned above, that the heated intermediate medium an evaporator heat exchanger and then an economizer Heat exchanger flows through.
  • a piston internal combustion engine develops operating heat during its operation, which is usually dissipated by a coolant, such as cooling water.
  • a coolant such as cooling water.
  • the efficiency of the system can be further increased if the heated by receiving operating heat of the piston internal combustion engine coolant emits heat to the cycle medium. It has been found that this is particularly advantageous when heat of the coolant is transferred at one point of the cycle to the cycle medium, which is located between two transfer points, at those derived from the exhaust heat, so either directly or indirectly via an intermediate medium to the cycle process medium is transmitted.
  • a particularly suitable point for the transmission of coolant heat to the cycle medium has thereby proven a point which is located in the flow direction of the cycle medium between the economizer heat exchanger and the evaporator heat exchanger.
  • the piston internal combustion engine in a stationary operating state, ie at a substantially constant speed.
  • a fuel for cost reasons and for reasons of environmental protection is preferably intended to a biofuel, in particular to a biogas, as it is cost-effective in silos in agricultural holdings.
  • the piston internal combustion engine can be operated with any suitable fuel.
  • waste heat in a temperature range between 180 0 C and 500 0 C can be used for power generation.
  • the proposed method can increase the total electrical efficiency, for example of an internal combustion engine of 40%, by up to 55% by using the waste heat recovery described here.
  • FIG. 1 shows a first embodiment of a method according to the invention, in which heat is transferred from the exhaust gas of an internal combustion engine directly to the cycle medium,
  • FIG. 2 shows a second embodiment of the method according to the invention, in which heat is transferred from the exhaust gas of an internal combustion engine indirectly via an intermediate medium to the cycle medium;
  • FIG. 3 shows a T-s diagram of the cyclic process of the first embodiment
  • FIG. 1 is a Ts diagram of the cycle of the second embodiment.
  • a system for utilizing the waste heat of a stationarily operated internal combustion engine for generating electricity is generally designated 10. It comprises the stationarily operated internal combustion engine 12, in the example illustrated a gas Otto internal combustion engine. This is fed via a fuel line 14 biogas as fuel and 16 air via an air line. In the piston internal combustion engine 12, the biogas and the air in the piston combustion chambers are burned and the combustion products are discharged as exhaust gas via an exhaust pipe 18.
  • the exhaust gas in the exhaust pipe 18 is supplied in a very hot state, with a temperature of between 15O 0 C and 200 0 C, preferably of about 180 0 C, a superheater heat exchanger 20. There, the exhaust gas gives off heat to the water flowing in vapor form through the superheater heat exchanger 20 as the cycle process medium of the cycle process described below.
  • the water, in the considered here cycle process section more precisely the water vapor, as the cycle medium is thus overheated in the superheater heat exchanger 20 and exits from this in the steam line 22 as a slightly superheated steam.
  • the cycle system is generally indicated at 24 in FIG.
  • the superheated steam is fed to a turbine 26 and expanded therein. It emerges particularly preferably as wet steam with a steam content of about 85% from the turbine 26 again and is condensed in the condenser 28 in a conventional manner to substantially liquid water.
  • the thus condensed liquid cycle medium is fed via the feedwater line 30 of the feedwater pump system 32, where it is raised to a higher pressure level, on which it successively passes through a plurality of heat exchangers, until finally again as weakly superheated saturated steam in the steam line 22 again the turbine 26th is supplied.
  • the cyclic process medium starting from the feedwater pump system 32, passes through an economizer heat exchanger 34, an engine coolant heat exchanger 36 and an evaporator heat exchanger 38 and the superheater heat exchanger 20 already described above.
  • the exhaust gas of the internal combustion engine 12 exits from the superheater heat exchanger 20 due to the heat transfer to the gaseous cycle medium in the superheater heat exchanger 20 at a temperature about 10 K lower than at the heat exchanger inlet and enters the evaporator heat exchanger 38. There, it gives off heat to the circulating process medium entering the evaporator heat exchanger 38 in the liquid state of aggregation, as a result of which the cycle medium is at least partially vaporized.
  • the recycle medium exits the evaporator heat exchanger 38 as saturated steam.
  • the heat transfer from the exhaust gas to the cycle medium in the evaporator heat exchanger is considerably greater than in the superheater heat exchanger 20.
  • the exhaust gas occurs by about 80 to 110 K, preferably by 100 K colder from the Evaporator heat exchanger 38 from when it enters this.
  • the exhaust gas which is now approximately 60 to 80 ° C., is introduced into the economizer heat exchanger 34, where it preheats the cool cycle medium coming from the feedwater pump system 32.
  • the cyclic process fluid enters at a temperature of 30 to 35 ° C, preferably about 33 0 C, in the economizer heat exchanger 34 and leaves it at a temperature of about 6O 0 C.
  • the exhaust gas exits the economizer heat exchanger 34 with a temperature of about 40 0 C and is discharged via an exhaust fan into the environment.
  • the temperature increase of the circulating medium during the flow through the motor-coolant heat exchanger 36 is ideally also 20 K, but may be a few Kelvin lower due to usual losses.
  • energy can be obtained from the heat contained in the exhaust gas of the internal combustion engine 12 in addition to the energy which can be tapped off at the motor shaft of the internal combustion engine 12.
  • An overall electrical efficiency of approximately 52% is achieved.
  • FIG. 2 shows a second embodiment of a method according to the invention or a system with which a method according to the invention can be carried out.
  • Figure 2 will be described in the following only in so far as they differs from Figure 1.
  • the heat of the exhaust gas from the exhaust pipe 118 is not directly transferred in heat exchangers to the cycle medium, but is transferred in an intermediate medium heat exchanger 150 to a thermal oil as an intermediate medium.
  • the thermal oil is pumped through a thermal oil pump 152 in a thermal oil circulation line 154. After the passage of the exhaust gas through the intermediate medium heat exchanger 150, it is blown off by the exhaust fan 140 into the ambient air.
  • the exhaust gas from the exhaust pipe 118 at a temperature of about 170 to 190 0 C, preferably 180 0 C enters the intermediate medium heat exchanger 150 and leaves it at a temperature of about 40 to 60 ° C, preferably from 45 to 50 0 C.
  • the thermal oil is heated during passage through the intermediate medium heat exchanger 150 from a temperature of about 35 to 45 ° C, preferably 40 0 C, to a temperature of about 160 to 180 0 C, preferably 17O 0 C. At this temperature, the thermal oil enters the evaporator heat exchanger 138. Due to the indirect heat transfer of heat from the exhaust gas to the cycle medium, the cycle process plant 124 shown in FIG. 2 does not have a superheater heat exchanger.
  • the cycle medium is introduced into the turbine 126 only as saturated steam in the second embodiment.
  • the thermal oil After the thermal oil has left the evaporator heat exchanger 138 with the release of heat to the cycle medium, it enters the economizer heat exchanger 134, where it preheats the circular process medium flowing towards the evaporator heat exchanger 138.
  • the thermal oil After passing through the economizer heat exchanger 134, the thermal oil is passed through the intermediate medium heat exchanger 150 for re-absorption of heat, etc.
  • FIG. 3 shows a T-s diagram of the cycle medium (water) of the Clausius-Rankine cycle of the first embodiment of FIG.
  • the entropy s is rising to the right plotted, in the ordinate direction, the temperature T is applied upward. Furthermore, in the Ts diagram, a region 60 is shown in which water is liquid only, a two-phase region 62 is shown in which water is both liquid and vapor, the vapor content being left to right in FIG 0% to 100% (at the saturated steam line 64) and a region 66 is shown in which water is exclusively vapor, more specifically superheated steam.
  • KP refers to the critical point of water, which is known to be at an absolute pressure of 220.55 bar and a temperature of 373.98 ° C.
  • the consideration of the cycle of the first embodiment of the method according to the invention begins after the feedwater pump system 32 at point A in the region 60 of the liquid phase of the water. Through the heat exchangers 34 and 36, the water is heated as a cycle medium to the point B, which is located at the edge of the two-phase region 62 to the liquid phase region 60.
  • the water in the evaporator heat exchanger 38 is isobarically and isothermally vaporized to the state of saturated steam (point C). Subsequently, the vaporous water in the superheater heat exchanger 20 is ideally isobarically overheated to point D, at about 170 ° C. Starting from point D, the water is released into the wet steam area, that is, into the two-phase area 62 up to a steam content of about 85% in the turbine, thereby performing work.
  • the point E After relaxation in the turbine, the point E is reached, which is at a temperature of about 33 ° C and an absolute pressure of 50 mbar.
  • the stated values of the water in point E are predetermined by the capacitor 28.
  • the water In the condenser 28, the water is isobaric and isothermal condensed starting from point E until at point F, the entire water is liquid again.
  • the feedwater pump system 32 then ideally raises the pressure of the liquid circulating medium to isentropically increasing the temperature T to the point A, whereupon the cycle medium passes through the cycle again.
  • FIG. 4 shows the Ts diagram of the cycle medium (water) of the Rankine cycle process of the second embodiment of FIG.
  • the representation of the cyclic process in the Ts diagram is substantially the same as that of Figure 3.
  • Analogous points in the cyclic process of Figure 4 are denoted by the same capital letters as those of Figure 3 but provided with an apostrophe.
  • Identical regions or lines as in FIG. 3 are given the same reference symbols in FIG. 4, but increased by the number 100.
  • the points E 1 and F 1 which are predetermined by the capacitor used, are identified by the points E and F of FIG identical.
  • the point B 1 is at a lower temperature level than the corresponding point B of Figure 3, namely at about 160 0 C. and an absolute pressure of just over 6 bar. At these values, the water is isobarically and isothermally evaporated by the evaporator heat exchanger 138. Because in the second
  • the cycle medium is relaxed as saturated steam from point C in the turbine 126 in the two-phase region 162 to point E '.
  • the relaxation preferably ends again at a steam content of about 85%. It can easily be seen from a comparison of the two diagrams of FIGS. 3 and 4 that the
  • Circular process medium in the cycle of the first embodiment performs more work than in the cycle of the second embodiment.

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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

L'invention concerne un procédé pour utiliser la chaleur produite par des moteurs à combustion interne à pistons pour générer du courant électrique au moyen d'un processus cyclique, comprenant les étapes qui consistent : à entraîner la substance de circulation pour créer un flux de circulation; à faire fonctionner un moteur à combustion interne à pistons (12) alimenté en carburant et en air dont la combustion produit des gaz d'échappement lors dudit fonctionnement; à transférer la chaleur provenant des gaz d'échappement du moteur à combustion interne (12) à la substance de circulation; à faire fonctionner une centrale électrique thermodynamique, en particulier une turbine (26) dans laquelle la substance de circulation est en activité. Selon l'invention, le processus cyclique est un processus cyclique Clausius-Rankine au cours duquel la substance de circulation se présente sous la forme d'eau dans des états d'agrégation liquide et gazeux.
PCT/EP2008/002737 2007-04-05 2008-04-07 Utilisation de la chaleur produite par des moteurs à combustion interne pour générer de l'électricité WO2008122429A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007016557A DE102007016557A1 (de) 2007-04-05 2007-04-05 Nutzung von Abwärme aus Verbrennungsmotoren zur Stromerzeugung
DE102007016557.0 2007-04-05

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WO2008122429A1 true WO2008122429A1 (fr) 2008-10-16

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104061030A (zh) * 2014-06-27 2014-09-24 上海泰欣环保工程有限公司 垃圾焚烧发电厂低温烟气余热发电系统
CN105351019A (zh) * 2014-08-20 2016-02-24 福建正仁环保有限公司 一种生活垃圾制备rdf热解气化燃气焚烧发电工艺

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013226742A1 (de) 2013-12-19 2015-06-25 Mahle International Gmbh Strömungsmaschine
CN104075328B (zh) * 2014-06-27 2017-02-15 上海泰欣环境工程股份有限公司 垃圾焚烧低温发电装置

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2459886A1 (fr) * 1979-06-27 1981-01-16 Sev Marchal Dispositif de recuperation d'energie pour moteur a combustion interne
EP1243758A1 (fr) * 1999-12-08 2002-09-25 Honda Giken Kogyo Kabushiki Kaisha Dispositif d'entrainement
EP1326009A1 (fr) * 2000-10-10 2003-07-09 Honda Giken Kogyo Kabushiki Kaisha Dispositif a cycle de rankine de moteur a combustion interne
WO2006138459A2 (fr) * 2005-06-16 2006-12-28 Utc Power Corporation Cycle organique de rankine couple mecaniquement et thermiquement a un moteur entrainant une charge commune

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2005248809A (ja) * 2004-03-03 2005-09-15 Denso Corp 流体機械
DE102004041108C5 (de) * 2004-08-24 2008-03-13 Adoratec Gmbh Vorrichtung und Verfahren zum Ausführen eines verbesserten ORC-Prozesses
FR2884556A1 (fr) * 2005-04-13 2006-10-20 Peugeot Citroen Automobiles Sa Dispositif de recuperation d'energie d'un moteur a combustion interne

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2459886A1 (fr) * 1979-06-27 1981-01-16 Sev Marchal Dispositif de recuperation d'energie pour moteur a combustion interne
EP1243758A1 (fr) * 1999-12-08 2002-09-25 Honda Giken Kogyo Kabushiki Kaisha Dispositif d'entrainement
EP1326009A1 (fr) * 2000-10-10 2003-07-09 Honda Giken Kogyo Kabushiki Kaisha Dispositif a cycle de rankine de moteur a combustion interne
WO2006138459A2 (fr) * 2005-06-16 2006-12-28 Utc Power Corporation Cycle organique de rankine couple mecaniquement et thermiquement a un moteur entrainant une charge commune

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104061030A (zh) * 2014-06-27 2014-09-24 上海泰欣环保工程有限公司 垃圾焚烧发电厂低温烟气余热发电系统
CN105351019A (zh) * 2014-08-20 2016-02-24 福建正仁环保有限公司 一种生活垃圾制备rdf热解气化燃气焚烧发电工艺

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