GB2033017A - Internal combustion engine plant - Google Patents

Internal combustion engine plant Download PDF

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Publication number
GB2033017A
GB2033017A GB7937090A GB7937090A GB2033017A GB 2033017 A GB2033017 A GB 2033017A GB 7937090 A GB7937090 A GB 7937090A GB 7937090 A GB7937090 A GB 7937090A GB 2033017 A GB2033017 A GB 2033017A
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GB
United Kingdom
Prior art keywords
vapour
circuit
cooling water
working medium
engine
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.)
Granted
Application number
GB7937090A
Other versions
GB2033017B (en
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Sulzer AG
Original Assignee
Sulzer AG
Gebrueder Sulzer AG
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 Sulzer AG, Gebrueder Sulzer AG filed Critical Sulzer AG
Publication of GB2033017A publication Critical patent/GB2033017A/en
Application granted granted Critical
Publication of GB2033017B publication Critical patent/GB2033017B/en
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B33/00—Engines characterised by provision of pumps for charging or scavenging
    • F02B33/44—Passages conducting the charge from the pump to the engine inlet, e.g. reservoirs
    • F02B33/446—Passages conducting the charge from the pump to the engine inlet, e.g. reservoirs having valves for admission of atmospheric air to engine, e.g. at starting
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
    • F02B29/04—Cooling of air intake supply
    • F02B29/0406—Layout of the intake air cooling or coolant circuit
    • F02B29/0412—Multiple heat exchangers arranged in parallel or in series
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
    • F02B29/04—Cooling of air intake supply
    • F02B29/0406—Layout of the intake air cooling or coolant circuit
    • F02B29/0437—Liquid cooled heat exchangers
    • F02B29/0443—Layout of the coolant or refrigerant circuit
    • 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
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
    • F02B29/04—Cooling of air intake supply
    • F02B29/0493—Controlling the air charge temperature
    • 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
    • F02G2260/00—Recuperating heat from exhaust gases of combustion engines and heat from cooling 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
    • 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
    • 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
    • Y02T70/00—Maritime or waterways transport
    • Y02T70/50—Measures to reduce greenhouse gas emissions related to the propulsion system

Landscapes

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

Abstract

An internal combustion engine plant comprises a water-cooled internal combustion engine (1), at least one supercharging unit (3,8) the air charge conduit (6) of which includes an air cooler heat exchanger (7), a first vapour circuit (13) arranged to operate at a higher pressure and temperature level and to extract, in a heat exchanger 12, waste heat from the exhaust gases of the engine, and a second vapour circuit (25) arranged to operate at a lower pressure and temperature level and to extract, in heat exchanger 7, heat from the air charge and to extract waste heat from the cooling water of the engine, in heat exchanger 22. Working medium from the two vapour circuits is fed to a vapour turbine (32) for expansion to perform work, the cooling water circuit of the internal combustion engine being arranged as a hot-water circuit (21, 22, 23, 24) at positive pressure e.g. 5 atmospheres and with cooling water temperatures in excess of 100 DEG C, e.g. 130 DEG C, in which the second vapour circuit for the evaporation of the working medium in that circuit includes a heat exchanger (28) disposed in the heat exchanger 7 for heating the working medium in a liquid state, an expansion device (31) for vapour generation, and a chamber (34) in which vapour and liquid are separated. <IMAGE>

Description

SPECIFICATION Internal combustion engine plant This invention relates to an internal combustion engine plant comprising a water-cooled internal combustion engine, at least one supercharging unit for the engine, the air charge conduit of which includes an air cooler, and a first vapour circuit arranged to operate at a higher pressure and temperature level for the utilization of the waste heat from the exhaust gases of the engine, and a second vapour circuit arranged to operate at a lower pressure and temperature level for the utilization of the compression heat of the air charge and the waste heat in the cooling water of the engine, and working medium from the two vapour circuits is fed to a vapour turbine for expansion to perform work, the cooling water circuit of the internal combustion engine being arranged as a hot-water circuit at positive pressure and with cooling water temperatures in excess of 100"C.
A plant of the kind to which the invention is particularly applicable has already been disclosed in British Patent Application No.
3402/78. In the plant according to that proposal, a charge air cooler acts as an evaporator for at least some of the working medium of the second vapour circuit, which operates at a lower pressure and temperature level than the first circuit. In this plant, the vapour generated is fed as saturated vapour, without superheating, from the charge air cooler to a turbine or an intermediate stage of a turbine for expansion to perform work.
One of the disadvantages of the above plane is that the charge air cooler is relatively expensive to construct, for example because the tube coil for the heater in which the working medium of the second vapour circuit is evaporated is relative extensive.
The object of this invention, therefore, is to retain the good waste-heat utilization achieved in the above plant but reduce the cost of construction of the charge air cooler.
Accordingly the present invention provides an internal combustion engine plant comprising a water-cooled internal combustion engine, at least one supercharging unit for the engine, the air charge conduit of which includes an air cooler, and a first vapour circuit arranged to operate at a higher pressure and temperature level for the utilization of the waste heat from the exhaust gases of the engine, and the second vapour circuit arranged ta operate at a lower pressure and temperature level for the utilization of the compression heat of the air charge and the waste heat in the cooling water of the engine, and working medium from the two vapour circuits is fed to a vapour turbine for expansion to perform work, the cooling water circuit of the internal combustion engine being arranged as a hot-water circuit at positive pressure and with cooling water temperatures in excess of 1 00 C, in which the second vapour circuit for the evaporation of the working medium in that circuit includes a heater disposed in the charge air cooler for heating the working medium in a liquid state, an expansion device for vapour generation, and a means for separation of vapour and liquid.
In the heater of the new plant, the liquid working medium of the second vapour circuit is heated to such an extent that the amount of vapour required is generated by expansion evaporation after the charge air cooler (as considered in the direction of flow), no additional external heat source being provided.
Thus it is possible to design the secondary side of the charge air cooler only for liquid heat media (as known per so see "Schiff- 8 Hafen/Kommandobriicke" 29(1977), No, 5.
pages 488/489) without losing the overall advantages of the type of plant.
The approach to total utilization of all the heat sources of the internal combustion engine (and particularly of the part which performs mechanical work) can be improved if a superheater, which is heated by engine cooling water, is provided for the vapour of the second vapour circuit at the vapour space of the separator means, and in some cases it may be advantageous if the cooling water of the internal combustion engine is heated up by the exhaust gases of the engine before the heat of the cooling water is yielded up to the working medium of the second vapour circuit.
The liquid in the separator is advantageously conveyed to the heater from the separator via a condensate return conduit provided with a pressure-increasing pump and/or by means of a condensate pre-heater upstream of the heater in the charge air cooler. Another possible use of the preheated condensate in the separator is in a vapour producing circuit which includes a circulating pump which draws liquid from the separator to be heated by the engine cooling water.
Finally, it may be advantageous if the heater is designed for the quantity of working medium of the two vapour circuits, and the flow of working medium between the heater and the expansion device is divided between the two vapour circuits, since the heat utilized by the charge air cooler as a result is increased only insignificantly.
In order to promote a fuller understanding of the above and other aspects of the present invention, an embodiment will now be described, by way of example only, with reference to the accompanying drawing, the single Figure of which diagrammatically illustrates a plant embodying the invention.
A supercharging unit is associated with the engine 1 (the latter is shown only diagrammatically) and the blower 3 for the charge air draws air from atmosphere via a filter 2 and through a conduit 4 and delivers it to the engine 1 via a conduit 6. The latter includes an air charge cooler 7 for the compressed charge air.
The blower 3 is driven by an exhaust-gas turbine 8 via a shaft 10, the hot exhaust gases of the engine 1 being fed to the turbine 8 via a conduit 9 and, after expansion in turbine 8, being discharged via conduit 11, which includes a heat-exchanger or waste-heat duct 12.
The heat-exchanger 1 2 acts as an evaporator and superheater for the working medium of a steam or vapour circuit 1 3 which operates at a relatively high pressure and serves for utilization of the exhaust-gas waste heat.
The vapour circuit 1 3 branches from a condensate feed pipe 1 6 at a point 1 5 which, up to this point, is common to the vapour circuit 1 3 and a second vapour circuit 25 at a lower-level pressure. The arrangement of the vapour circuit 25 is described in greater detail later.
In the vapour circuit system 1 3 a condensate-carrying conduit 14 connects point 1 5 to an exhaust-gas-heated evaporator coil 1 7 in the heat exchanger 1 2 which is connected to a liquid separator 1 8. The liquid separated in the latter is discharged via a conduit 49 and, after its residual heat has been partially utilized, it is returned to the common flow of working medium of the two circuits 1 3 and 25.The vapour space of the separator 1 8 is connected to an exhaust-gas-heated superheater coil 19 in the heat exchanger 12, from which a vapour line 20 leads to the high pressure side of a turbine 32 which is common to the two circuits 1 3 and 25 and which drives an electrical generator 33.
In the drawing, the engine 1 also includes a hot-water cooling circuit 21 which includes exhaust-gas heated coil 24 in the heat exchanger 12 which supplies heat to the cooling water heat exchange coil in a cooler 22, and a pump 23 by which the cooling water is circulated. The hot-water cooling system, which is known per se, differs from the generally conventional cooling systems in that it operates at temperatures above 100"C, the cooling water leaving the engine 1 at a temperature of about 130"C for example, being heated up to about 133"C in the heat exchanger coil 24 of this plant, unlike conventional plants, entering the cooler 22, where it is cooled by about 1 3, to 120"C, and returning to the engine at such temperature.
Since evaporation must be prevented in this cooling water circuit, the circulating system is at a positive pressure, which is kept at about 5 atmospheres absolute, for example, by means of compressed air and an artificial head tank.
The heat-absorbing medium in the engine cooling water cooler 22 is the working medium of the second vapour circuit 25 which flows through a superheater coil 36 and an evaporator coil 40. This second vapour circuit 25, which operates at a lower pressure and temperature level in relation to the first circuit, is combined with the first vapour circuit 1 3 from the outlet of turbine 32 as far as the branch point 1 5. A feed pump 26 is provided in this common zone and feeds the working medium generally water-from a condenser 27 to a condensate preheater coil 28 in the charge air cooler 7.
In this preheater coil 28, which is situated in the charge air cooler 7, the cold condensate is preheated by the compressed charge air before being heated to a higher temperature in a heater coil 29, without any vaporization taking place. The heat-yielding medium for the heater 29 is also the compressed charge air.
A condensate return circuit 30, which returns preheated condensate upstream of the heater 29, is connected between the preheater coil 28 and the heater coil 29. The above mentioned condensate pipe 1 6 is connected to the downstream end of the heater 29.
Via point 15, where the conduit 14 for the pre-heated liquid working medium of the first vapour circuit 1 3 branches off, the conduit 1 6 leads to an expansion device 31, e.g. a throttle device. Some of the working medium circulating in the second vapour circuit 25 is evaporated in this by expansion, with simultaneous cooling. The vapour and remaining condensate flow together in the conduit 1 6 to a separator 34 for separating vapour and liquid.
From the vapour space of this separator 34 a pipe 35 leads to the cooling-water-heated superheater coil 36, from which superheated vapour flows via conduit 37 to an intermediate stage of the common turbine 32 for expansion to perform work.
From the condensate sump of the separator 34 a pump 38 which simultaneously makes up the pressure loss produced by expansion feeds the preheated condensate back via the condensate return line 30 to the point 39 which is situated between the preheater coil 28 and the heater coil 29 and in the common zone of the two circuits 1 3 and 25. This recycled preheated condensate can be heated afresh and then be fed to the expansion device 31.
The above mentioned cooling water-heated evaporator coil 40 is used for additional vapour generation in the second vapour circuit 25 and is connected via a condensate-carrying conduit 41 to the conduit 30 and thus to the condensate sump of the separator 34, and via a conduit 42 to the vapour space of the separator 34. The flow through the evaporator coil 40 is produced by a circulating pump 43 disposed in conduit 41.
If the heat withdrawal produced by the working medium flowing through the preheater coil 28 and the heater coil 29 is not sufficient to cool the charge air adequately, a heat exchanger 43 is provided for the charge air at the end of the charge air cooler 7, this heat exchanger being cooled by an external coolant by means of a pump 44, such external coolant also serving as a heat-dissipating medium in the condenser 27. A heat exchange coil is provided for the coolant for this purpose in the condenser 27, connected in parallel with the heat exchanger coil 45. The flow of coolant is divided up over the two units 45 and 46 by adjustable throttle members 47 and 48, which are shown diagrammatically.
Of course the invention is not restricted to the exemplified embodiment illustrated. More particularly, depending upon the quantity and temperature distribution of the waste heat between the cooling water and charge air waste-heat sources, either or both of the evaporator coil 40 or the condensate return conduit 30 may be dispensed with.
In some cases the two vapour circuits 1 3 and 25 may be further separated from one another in stages, e.g. separate condensate preheaters and heaters or even separate feed pumps, condensers and/or turbines being provided for the two.
The temperatures and quantities of heat derived from the two waste-heat sources in each individual case must govern which of the various possibilities is most favourable for optimum heat recovery with a new plant. To give an idea of applicable temperature conditions, temperatuie values in "C are shown at various points in the Figure in respect of a prototype plant.

Claims (8)

1. An internal combustion engine plant comprising a water-cooled internal combustion engine, at least one supercharging unit for the engine, the air charge conduit of which includes an air cooler, and a first vapour circuit arranged to operate at a higher pressure and temperature level for the utilization of the waste heat from the exhaust gases of the engine, and a second vapour circuit arranged to operate at a lower pressure and temperature level for the utilization of the compression heat of the air charge and the waste heat in the cooling water of the engine, and working medium from the two vapour circuits is fed to a vapour turbine for expansion to perform work, the cooling water circuit of the internal combustion engine being arranged as a hotwater circuit at positive pressure and with cooling water temperatures in excess of 100"C, in which the second vapour circuit for the evaporation of the working medium in that circuit includes a heater disposed in the charge air cooler for heating the working medium in a liquid state, an expansion device for vapour generation, and a means for separation of vapour and liquid.
2. A plant as claimed in Claim 1, in which a condensate return pipe provided with a pressure-increasing pump leads from the separator means to a point upstream of the heater.
3. A plant as claimed in Claim 1 or 2, in which a condensate preheater is provided in the charge air cooler connected upstream of the heater.
4. A plant as claimed in Claim 3, in which an evaporating circuit provided with a circulating pump is connected to draw liquid from the separator means and heat is supplied to that liquid from the cooling water of the internal combustion engine.
5. A plant as claimed in any one of Claims 1 to 4, in which a superheater, which is heated by the engine cooling water, is provided for the vapour of the second vapour circuit connected to the vapour space of the separator means.
6. A plant as claimed in any preceding Claim, in which the heater is designed for the quantity of the working medium of the two vapour circuits and the flow of working medium between the heater and the expansion device is divided between the two vapour circuits.
7. A plant as claimed in any preceding Claim, in which the cooling water of the internal combustion engine is heated by the exhaust gas of the engine before cooling water heat is yielded up to the working medium of the second vapour circuit.
8. A plant substantially as herein described with reference to the accompanying drawing.
GB7937090A 1978-10-25 1979-10-25 Internal combustion engine plant Expired GB2033017B (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CH1102978A CH632051A5 (en) 1978-10-25 1978-10-25 INTERNAL COMBUSTION ENGINE.

Publications (2)

Publication Number Publication Date
GB2033017A true GB2033017A (en) 1980-05-14
GB2033017B GB2033017B (en) 1982-12-08

Family

ID=4369325

Family Applications (1)

Application Number Title Priority Date Filing Date
GB7937090A Expired GB2033017B (en) 1978-10-25 1979-10-25 Internal combustion engine plant

Country Status (9)

Country Link
JP (1) JPS5557609A (en)
CH (1) CH632051A5 (en)
DE (1) DE2847028C2 (en)
DK (1) DK145242C (en)
FR (1) FR2439871A1 (en)
GB (1) GB2033017B (en)
IT (1) IT1123877B (en)
NL (1) NL7907785A (en)
SE (1) SE7908812L (en)

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4394813A (en) * 1980-12-25 1983-07-26 Mitsui Engineering And Shipbuilding Company Limited Exhaust gas heat recovery system in internal combustion engine
WO1986002977A1 (en) * 1984-11-14 1986-05-22 Caterpillar Tractor Co. Heat recovery system including a dual pressure turbine
EP0259545A1 (en) * 1986-09-06 1988-03-16 Dr.Ing.h.c. F. Porsche Aktiengesellschaft Propulsion device
EP0453007A2 (en) * 1990-03-23 1991-10-23 Adviesbureau Amerconsult B.V. Gas heating system
US5351487A (en) * 1992-05-26 1994-10-04 Abdelmalek Fawzy T High efficiency natural gas engine driven cooling system
EP0645272A1 (en) * 1993-09-27 1995-03-29 Gianluigi Reis Recovery system for dissipated energy of an engine motor vehicle during its runnig conditions
EP0750106A1 (en) * 1995-06-12 1996-12-27 Wartsila Diesel International Ltd. OY Utilization of low-value heat in a supercharged thermal engine
US6484501B1 (en) * 1998-02-03 2002-11-26 Miturbo Umwelttechnik Gmbh & Co. Kg Method of heat transformation for generating heating media with operationally necessary temperature from partly cold and partly hot heat loss of liquid-cooled internal combustion piston engines and device for executing the method
FR2891050A1 (en) * 2005-09-20 2007-03-23 Renault Sas Air supercharging plant for Diesel type single cylinder test bench, has cooler and reheater provided in downstream connection with temperature control valves connected by channel and mounted in opposition for forming mixer
WO2008035108A1 (en) * 2006-09-21 2008-03-27 Ray Mason Engine assemblies
WO2008125827A2 (en) * 2007-04-13 2008-10-23 City University Organic rankine cycle apparatus and method
CN103758658A (en) * 2013-12-27 2014-04-30 天津大学 Heat recovery system for gradient utilization of two-stage double-circuit internal-combustion engine waste heat
EP2562380A3 (en) * 2011-08-01 2014-07-09 Behr GmbH & Co. KG Heat exchanger system and method for operating a heat exchanger system for a vehicle
RU2630284C1 (en) * 2016-06-08 2017-09-06 Федеральное государственное бюджетное образовательное учреждение высшего образования "Ярославский государственный технический университет" (ФГБОУВО "ЯГТУ") Cogeneration unit with deep waste energy disposal of thermal engine
EP1925806B1 (en) * 2006-11-24 2017-10-04 MAHLE Behr GmbH & Co. KG System with an organic Rankine cycle for operating at least one expansion machine, heat exchanger for operating one expansion machine, method for operating at least one expansion machine
EP2577016A4 (en) * 2010-05-25 2018-01-24 Scania CV AB Cooler arrangement for a vehicle powered by a supercharged combustion engine
EP3258094A4 (en) * 2015-02-13 2018-10-03 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) Heat exchanger, energy recovery device, and ship

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FR2489418A1 (en) * 1980-08-26 1982-03-05 Bertin & Cie Heat recovery for IC engine - has fluid for rankine cycle vapour motor heated by exhaust gases
JPS5865917A (en) * 1981-10-15 1983-04-19 Takuma Sogo Kenkyusho:Kk Power generating device of exhaust heat recovery in diesel engine
JP4923639B2 (en) * 2005-11-11 2012-04-25 ダイキン工業株式会社 Indoor panel of air conditioner and air conditioner
DE202005021603U1 (en) 2005-12-29 2008-11-27 Deutsche Energie Holding Gmbh ORC engine
ITMI20062046A1 (en) * 2006-10-24 2008-04-25 Iveco Motorenforschung Ag MOTOR SYSTEM WITH HEAT RECOVERY SYSTEM AND RELATIVE HEAT RECOVERY METHOD
DE102008029729A1 (en) * 2008-06-20 2009-12-24 Müller, Robert Thermally-combined combustion engine, particularly internal combustion engine, has body for burning in circulating heat transfer medium with high boiling point, where additional heat exchanger is provided
DE102010000487B4 (en) 2010-02-21 2023-06-29 von Görtz & Finger Techn. Entwicklungs GmbH Process and device for internal combustion engines
JP2011231636A (en) * 2010-04-26 2011-11-17 Mitsubishi Heavy Ind Ltd Exhaust heat recovery power generator and ship provided with exhaust heat recovery power generator
CN104929805A (en) * 2015-06-22 2015-09-23 沈阳航空航天大学 Vehicle engine waste heat recycling device using reheat type organic Rankine cycle technology

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US2637684A (en) * 1945-05-08 1953-05-05 Badger Mfg Company Engine-driven vapor compression distillation
CH457038A (en) * 1966-04-28 1968-05-31 Sulzer Ag Plant for the utilization of waste heat from a reciprocating internal combustion engine to drive ships
JPS52149514A (en) * 1976-06-07 1977-12-12 Kawasaki Heavy Ind Ltd Effective use of heat generated from supercharged air of diesel engine
CH626426A5 (en) * 1977-11-21 1981-11-13 Sulzer Ag Internal combustion engine system with a pressure-charged, water-cooled engine
CH627524A5 (en) * 1978-03-01 1982-01-15 Sulzer Ag METHOD AND SYSTEM FOR THE USE OF HEAT THROUGH THE EXTRACTION OF HEAT FROM AT LEAST ONE FLOWING HEAT CARRIER.

Cited By (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4394813A (en) * 1980-12-25 1983-07-26 Mitsui Engineering And Shipbuilding Company Limited Exhaust gas heat recovery system in internal combustion engine
WO1986002977A1 (en) * 1984-11-14 1986-05-22 Caterpillar Tractor Co. Heat recovery system including a dual pressure turbine
EP0259545A1 (en) * 1986-09-06 1988-03-16 Dr.Ing.h.c. F. Porsche Aktiengesellschaft Propulsion device
EP0453007A2 (en) * 1990-03-23 1991-10-23 Adviesbureau Amerconsult B.V. Gas heating system
EP0453007A3 (en) * 1990-03-23 1991-10-30 Adviesbureau Amerconsult B.V. Gas heating system
US5351487A (en) * 1992-05-26 1994-10-04 Abdelmalek Fawzy T High efficiency natural gas engine driven cooling system
EP0645272A1 (en) * 1993-09-27 1995-03-29 Gianluigi Reis Recovery system for dissipated energy of an engine motor vehicle during its runnig conditions
US5549174A (en) * 1993-09-27 1996-08-27 Reis; Gianluigi Recovery system for dissipated energy of an engine motor vehicle during its running conditions
AU684302B2 (en) * 1993-09-27 1997-12-11 Gianluigi Reis Recovery system for dissipated energy of an engine motor vehicle during its running conditions
EP0750106A1 (en) * 1995-06-12 1996-12-27 Wartsila Diesel International Ltd. OY Utilization of low-value heat in a supercharged thermal engine
US5797265A (en) * 1995-06-12 1998-08-25 Waertsilae Nsd Oy Ab Utilization of low-value heat in a supercharged thermal engine
US6484501B1 (en) * 1998-02-03 2002-11-26 Miturbo Umwelttechnik Gmbh & Co. Kg Method of heat transformation for generating heating media with operationally necessary temperature from partly cold and partly hot heat loss of liquid-cooled internal combustion piston engines and device for executing the method
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DK437279A (en) 1980-04-26
DK145242B (en) 1982-10-11
DK145242C (en) 1983-02-28
JPS5557609A (en) 1980-04-28
IT1123877B (en) 1986-04-30
FR2439871A1 (en) 1980-05-23
IT7926548A0 (en) 1979-10-17
FR2439871B1 (en) 1983-07-08
SE7908812L (en) 1980-04-26
CH632051A5 (en) 1982-09-15
NL7907785A (en) 1980-04-29
DE2847028B1 (en) 1980-04-24
GB2033017B (en) 1982-12-08
DE2847028C2 (en) 1980-12-18

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