EP2002089B1 - Machine à vapeur à piston, à évaporation éclair interne du fluide de travail - Google Patents

Machine à vapeur à piston, à évaporation éclair interne du fluide de travail Download PDF

Info

Publication number
EP2002089B1
EP2002089B1 EP07723993.7A EP07723993A EP2002089B1 EP 2002089 B1 EP2002089 B1 EP 2002089B1 EP 07723993 A EP07723993 A EP 07723993A EP 2002089 B1 EP2002089 B1 EP 2002089B1
Authority
EP
European Patent Office
Prior art keywords
working medium
piston
steam engine
prechamber
working
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.)
Not-in-force
Application number
EP07723993.7A
Other languages
German (de)
English (en)
Other versions
EP2002089A2 (fr
Inventor
Michael Löffler
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.)
Electricite de France SA
Original Assignee
Electricite de France SA
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 Electricite de France SA filed Critical Electricite de France SA
Publication of EP2002089A2 publication Critical patent/EP2002089A2/fr
Application granted granted Critical
Publication of EP2002089B1 publication Critical patent/EP2002089B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • F02B75/00—Other engines
    • F02B75/26—Engines with cylinder axes coaxial with, or parallel or inclined to, main-shaft axis; Engines with cylinder axes arranged substantially tangentially to a circle centred on main-shaft axis
    • 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
    • F01K21/00—Steam engine plants not otherwise provided for
    • F01K21/02—Steam engine plants not otherwise provided for with steam-generation in engine-cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B5/00—Reciprocating-piston machines or engines with cylinder axes arranged substantially tangentially to a circle centred on main shaft axis
    • 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
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B27/00—Instantaneous or flash steam boilers
    • F22B27/16—Instantaneous or flash steam boilers involving spray nozzles for sprinkling or injecting water particles on to or into hot heat-exchange elements, e.g. into tubes

Definitions

  • the invention relates to a piston steam engine and to a method for operating a piston steam engine.
  • the steam generators required for a piston steam engine usually consist of a heat exchanger in which the working medium, such as water, is vaporized at the desired working pressure.
  • the heat required for the evaporation process is provided by a heat transfer medium, such as flue gases.
  • the heat transfer medium in the steam generator is cooled to a temperature in the range of the evaporation temperature of the working medium.
  • a known steam engine has an external burner B, which heats the liquid working medium via a heat exchanger H.
  • the liquid working medium is injected directly into the working space.
  • the heat transfer medium of the heat source should be cooled down to ambient temperature in a process that is as reversible as possible.
  • the heat transfer medium of the heat source only cools down to a temperature close to the evaporation or condensation temperature.
  • the heat transfer medium is cooled, for example, only from 200 ° C to 140 ° C and not to the ambient temperature.
  • This object is achieved in a piston steam engine according to the preamble of claims 1 and 15 by the features of the characterizing parts of these claims.
  • This solution includes, among other things, that the working fluid is introduced in liquid form into the at least one antechamber of the piston steam engine when the piston is in the region of top dead center (TDC).
  • TDC top dead center
  • the cylinder volume increases and further working fluid can evaporate.
  • the liquid portion of the working medium cools down.
  • the vaporous portion of the working medium also cools down. Because of these processes, the efficiency, in particular the exergetic efficiency and the performance of the piston steam engine according to the invention are significantly increased compared to other heat engines.
  • At least one pre-chamber is provided, which is in communication with the working space, wherein the working medium is introduced into the pre-chamber and particularly preferably in a circle-like path in the prechamber.
  • the circular path of the liquid phase causes centrifugal forces which greatly accelerate the liquid phase radially outward due to the high density.
  • the resulting in the flash evaporation of the working medium vapor has a significantly lower density than the liquid phase and can flow into the cylinder chamber, since the connection between the antechamber and the working chamber in the center of the antechamber opens into this.
  • the radial acceleration causes the liquid phase can not escape from the antechamber. This achieves a very simple and at the same time effective phase separation.
  • the volume of the prechamber should be as small as possible.
  • a plurality of pre-chambers and / or a plurality of injectors per cylinder are provided, which are all connected to the working space.
  • This makes it possible to introduce the working fluid at different temperatures as a function of the pressure prevailing in the working space during the working cycle and / or the prevailing temperature in the working space and / or the position of the piston in the atria and / or the working space.
  • This allows working media with different Temperatures without Exergielope be coupled due to mixing operations in the piston steam engine according to the invention.
  • the working medium partially directly into the working space.
  • that liquid working medium can be atomized during the injection process and distributed in the form of small drops within the working space and the antechamber.
  • the friction between the droplets and the gaseous phase of the working medium avoids direct contact between the droplets and the surfaces of the piston steam engine.
  • injectors may serve injectors, as used in fuel injection systems of conventional gasoline or diesel internal combustion engines.
  • the heat transfer medium has a temperature of about 200 ° C to 350 ° C, water has proved to be particularly suitable.
  • heat or waste heat at a temperature of about 150 ° C to 200 ° C is available, methanol has proven to be particularly suitable.
  • R134a When heat or waste heat at a temperature of about 100 ° C is available, R134a has proven to be particularly suitable.
  • the internal thermal insulation is of particular importance to prevent the cooling liquid working fluid from receiving convective heat from the cyclone wall or other surfaces of the piston steam engine.
  • This arranged on the working space or cyclone inner wall heat-insulating coating may be for example of Teflon, enamel or ceramic.
  • the surfaces of the piston steam engine which come into contact with the working medium can be heated in order to effectively prevent the condensation of the working medium on these surfaces.
  • the gaseous phase accessible components of the machine must be at a temperature greater than the condensation temperature of the working fluid at the gas pressure being applied. If the surfaces of the components were colder, some of the resulting gaseous phase would suddenly condense on these surfaces and the condensed phase would no longer be available to drive the piston and the performance and efficiency of the machine would decrease.
  • FIG. 1 shows by way of example the construction of a first embodiment of a piston steam engine according to the invention with an antechamber 13, a piston 3, a cylinder 5, a connecting rod 7 and a crankshaft 9, which may be coupled to a generator, not shown.
  • the piston 3 and the cylinder 5 define a working space 11.
  • An antechamber 13 is connected to the working space 11.
  • In the antechamber 13 open a supply line 15 and a discharge line 17 for the working medium.
  • a switchable inlet valve 19 is arranged in the supply line 15 for the liquid working medium.
  • this inlet valve which can be designed as an injector, liquid working fluid can be injected into the pre-chamber 13 become. This injection is preferably carried out when the piston 3 is in the region of the top dead center OT.
  • a switchable outlet valve 21 located in the outlet 17 for the working medium is opened and the piston 3 pushes the remaining liquid phase and the working medium which has become vaporous during its subsequent movement in the direction TDC the work space 11 from.
  • the discharge line 17 serves to discharge the liquid phase remaining in the pre-chamber 13. About the derivative 17 and the vaporized working medium can be removed. Alternatively, it is also possible in the working space 11 to provide an additional steam valve 22, which takes over the removal of the vaporized working medium.
  • the steam valve 22 may be formed as a poppet valve and (not shown) by a camshaft, similar to a gas exchange valve of an internal combustion engine and be actuated.
  • the discharge line 17.1 for the working medium opens into a condenser 23.
  • the working medium discharged through the steam valve 22 can be led into the condenser 23 through a discharge line 17.3.
  • FIG. 2 shows the structure of a piston steam engine according to the invention with two pre-chambers 13.1 and 13.2, two supply lines 15.1 and 15.2 for the working medium.
  • two switchable inlet valves 19.1 and 19.2 are arranged in the supply lines 15.1 and 15.2 in the supply lines 15.1 and 15.2 in the supply lines 15.1 and 15.2 in the supply lines 15.1 and 15.2 in the supply lines 15.1 and 15.2 in the supply lines 15.1 and 15.2 are arranged.
  • the working medium contained in the first supply line 15.1 has a higher temperature than the working medium contained in the second supply line 15.2. Therefore, first a certain amount of the working medium contained in the first supply line 15.1 is introduced into the first prechamber 13.1. There, this working fluid evaporates and gives off work on the piston 3. This reduces the pressure and temperature of the working medium 11 and pre-chambers 13.1 and 13.2 located working medium. As soon as the temperature of the working medium located in the working space 11 and prechambers 13.1 and 13.2 has approached the temperature of the working medium located in the second feed line 15.2, working medium from the second supply line 15.2 is still in the same working stroke of the piston 15 by brief opening of the second inlet valve 19.2 introduced into the second prechamber 13.2. Also, this working medium evaporates immediately after it has been introduced into the antechamber 15.2 and gives off work on the piston 3 from.
  • the two Temperature levels is available.
  • the waste heat of an internal combustion engine can be optimally utilized, since in an internal combustion engine, the exhaust gases at a temperature greater than 200 ° C incurred while the coolant heat and the oil have a temperature of about 120 ° C.
  • a first heat exchanger (not shown), which is operated with the waste heat of the exhaust gases, and a second heat exchanger (not shown), which is heated with the waste heat of the cooling water and the oil required ,
  • the warmer working fluid is injected at a temperature of 200 ° C. If this has cooled to 120 ° C, then some 120 ° C hot working medium is injected.
  • the related to the heat of combustion efficiency of an internal combustion engine can be increased by about 10% with the piston engine shown.
  • the piston steam engine according to the invention operates on the two-stroke principle. An intake stroke and a compression stroke eliminated.
  • the outlet valve or valves 21 are closed and then the working medium is injected through the inlet valve 19.
  • the outlet valve 21 is opened.
  • the remaining liquid phase and the resulting gaseous phase are discharged through the outlet valve 21. Liquid and gaseous phase can pass through the same outlet valve 21 or separate valves are provided.
  • hot liquid working fluid is injected under pressure into an antechamber of the piston steam engine.
  • the working fluid can be harmless water.
  • FIG. 3 shows the structure of an antechamber 13 for a piston steam engine according to the invention.
  • the prechamber 13 is constructed similar to a cyclone separator.
  • the supply line 15, the discharge line 17 and the valves 19 and 21 are indicated.
  • the liquid working fluid is introduced substantially tangentially into the antechamber 13 and moves on a radially outer circular path. Due to its lower density, the vapor produced during the flash evaporation is forced into the middle of the prechamber 13, so that a separation of liquid and vaporous working medium takes place in the prechamber 13.
  • a compound 29 is arranged, which opens into the working space 11. Via the connection 29, the vaporous working medium passes from the antechamber into the working space 11.
  • the gravity supports the separation of liquid and vapor phase in addition.
  • the affected surfaces of the piston 3, cylinder 5 and prechamber 13 must be heated and / or heat-insulated. So that no heat is released from the heated surfaces to the liquid phase of the working medium, two alternative measures can be taken.
  • the pre-chamber 13 is geometrically designed such that the injected liquid phase of the working medium can move stably on a circular path.
  • the pre-chamber 13 is referred to in this case as a cyclone.
  • the centrifugal forces occurring on the circular path ensure that the resulting vapor, on which act due to lower density low centrifugal forces, can escape into the cylinder chamber of the piston steam engine and the liquid Heat transfer medium, act on the large density due to the large centrifugal forces, remains in the circular path.
  • phase separation succeeds: the liquid phase remains in the flash vaporization in the cyclone, while the vapor phase escapes into the cylinder space.
  • FIG. 4 is a further embodiment of a piston steam engine according to the invention shown.
  • this embodiment eliminates the pre-chamber 13 and the liquid working medium is injected directly into the working space 11. This can be done with the aid of an injector known from the prior art.
  • the working fluid is atomized during the injection process into small drops, similar to the injection of diesel fuel into the combustion chamber of an internal combustion engine.
  • the drops are held in suspension by friction in the gas phase. In this way, the drops can touch the hot surfaces only to a small extent and the heat exchange between the liquid phase and the hot surfaces is kept low.

Landscapes

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

Claims (18)

  1. Machine à vapeur à piston comprenant au moins un cylindre (5), un piston (3) oscillant dans le ou les cylindres (5), une chambre de travail (11), la chambre de travail (11) étant délimitée par le cylindre (5) et par le piston (3), au moins une soupape d'admission (19), le milieu actif pouvant être guidé dans la chambre de travail (11) en passant par la ou les soupapes d'admission (19), au moins une soupape d'évacuation (21), la machine à vapeur à piston étant conçue pour que le milieu actif soit introduit sous forme liquide au moins indirectement dans la chambre de travail (11), lorsque le piston (3) se situe dans la zone d'un point mort haut (OT) ou au cours du cycle de travail, la machine à vapeur à piston étant conçue pour que le milieu actif liquide soit transporté vers la soupape d'admission (19) en passant par une conduite d'amenée (15), caractérisée en ce qu'au moins une préchambre (13) est prévue, en ce que la chambre de travail (11) et la préchambre (13) sont en liaison (29) l'une avec l'autre, en ce que la machine à vapeur à piston est conçue en outre pour que le milieu actif soit introduit sous forme liquide dans la préchambre (13), en ce que la phase liquide du milieu actif reste en grande partie dans la préchambre (13), s'écoule dans la chambre de travail (11) pendant la phase vapeur du milieu actif, et en ce que le milieu actif peut être guidé à l'extérieur de la préchambre (13) en passant par la ou les soupapes d'évacuation (21).
  2. Machine à vapeur à piston selon la revendication 1, caractérisée en ce que le milieu actif est introduit de manière sensiblement tangentielle dans la préchambre (13) .
  3. Machine à vapeur à piston selon la revendication 1 ou 2, caractérisée en ce que la liaison (29) entre la chambre de travail (11) et la préchambre (13) débouche au centre de la préchambre (13) dans cette dernière.
  4. Machine à vapeur à piston selon l'une quelconque des revendications précédentes, caractérisée en ce que plusieurs préchambres (13.1, 13.2) sont disposées sur un cylindre (5), en ce que les préchambres (13.1, 13.2) sont reliées à la chambre de travail (11), et en ce que le milieu actif est introduit successivement dans les préchambres (13.1 ou 13.2) ou dans la chambre de travail (11) à une température différente en fonction de la pression régnant dans la chambre de travail (11) et/ou de la température régnant dans la chambre de travail (11).
  5. Machine à vapeur à piston selon l'une quelconque des revendications précédentes, caractérisée en ce que plusieurs soupapes d'admission (19.1, 19.2) sont prévues pour chaque cylindre (5).
  6. Machine à vapeur à piston selon l'une quelconque des revendications précédentes, caractérisée en ce que le milieu actif liquide injecté des différentes soupapes d'admission ou des différents injecteurs (19.1, 19.2) présente des températures différentes, et en ce que le milieu actif liquide injecté des différents injecteurs (19) est injecté dans l'ordre suivant, à savoir du milieu actif le plus chaud au milieu actif le plus froid, chaque milieu actif suivant étant injecté lorsque le milieu actif déjà situé dans la préchambre (13) ou la chambre de travail (11) a atteint la température du milieu actif plus froid suivant.
  7. Machine à vapeur à piston selon l'une quelconque des revendications précédentes, caractérisée en ce que le milieu actif liquide est injecté dans la chambre de travail (11) ou dans la ou les chambres de travail (13) à l'aide d'un injecteur (19).
  8. Machine à vapeur à piston selon l'une quelconque des revendications précédentes, caractérisée en ce que le milieu actif liquide, lors de la procédure d'injection, est pulvérisé en petites gouttes de liquide.
  9. Machine à vapeur à piston selon l'une quelconque des revendications précédentes, caractérisé en ce que de l'eau, du méthanol, du pentane et/ou du R134a est utilisé comme milieu actif.
  10. Machine à vapeur à piston selon l'une quelconque des revendications précédentes, caractérisé en ce que le cylindre (5), le piston (3) et/ou la ou les préchambres (13) sont thermo-isolés à l'intérieur et/ou à l'extérieur.
  11. Machine à vapeur à piston selon la revendication 11, caractérisée en ce l'isolation thermique intérieure est constituée de préférence de téflon, d'émail et/ou de céramique.
  12. Machine à vapeur à piston selon l'une quelconque des revendications précédentes, caractérisée en ce que le cylindre (5), le piston (3) et/ou la ou les préchambres (13) peuvent être chauffés.
  13. Machine à vapeur à piston selon l'une quelconque des revendications précédentes, caractérisée en ce qu'une soupape de vapeur (22) est prévue, et en ce que le milieu actif sous forme de vapeur est évacué de la chambre de travail au moyen de la soupape de vapeur (22).
  14. Machine à vapeur à piston selon l'une quelconque des revendications précédentes, caractérisée en ce que la ou les soupapes d'évacuation (21) et la soupape de vapeur (22) sont fermées dans la zone du point mort haut (OT), en ce que le milieu actif liquide est ensuite introduit dans la préchambre (13) ou la chambre de travail (11), et en ce que la ou les soupapes d'évacuation (21) sont ouvertes dans la zone du point mort bas (UT).
  15. Procédé permettant de faire fonctionner une machine à vapeur à piston comprenant au moins un cylindre (5), au moins une soupape d'admission (19) et au moins une soupape d'évacuation (21), un piston (3) oscillant dans le ou les cylindres (5), une chambre de travail (11) et au moins une préchambre (13), la chambre de travail (11) étant délimitée par le cylindre (5) et par le piston (3), la chambre de travail (11) et la préchambre (13) étant en liaison (29) l'une avec l'autre, et au moins une soupape d'évacuation (21) étant disposée sur la préchambre (13), caractérisé en ce que la soupape d'évacuation (21) est fermée lorsque le piston (3) se situe dans la zone du point mort haut, en ce que le milieu actif liquide et chauffé est injecté dans la ou les préchambres (13), après la fermeture de la soupape d'évacuation (21) et lorsque le piston (3) se situe dans la zone du point mort haut ou au cours du cycle de travail, en ce que la phase liquide du milieu actif reste en majeure partie dans la préchambre (13), s'écoule dans la chambre de travail (11) pendant la phase vapeur du milieu actif, et en ce que le piston (3) évacue ensuite la phase liquide restante et le milieu actif se présentant désormais sous forme de vapeur par l'intermédiaire de la ou des soupapes d'évacuation (21) .
  16. Procédé selon la revendication 15, caractérisé en ce que la machine à vapeur à piston selon l'une quelconque des revendications précédentes est caractérisée en ce que plusieurs préchambres (13.1, 13.2) sont disposées sur un cylindre (5), en ce que les préchambres (13.1, 13.2) sont reliées à la chambre de travail (11), et en ce que le milieu actif est introduit successivement dans les préchambres (13.1 ou 13.2) ou dans la chambre de travail (11) à une température différente en fonction de la pression régnant dans la chambre de travail (11) et/ou de la température régnant dans la chambre de travail (11).
  17. Procédé selon la revendication 15 ou 16, caractérisé en ce que pendant le cycle de travail, un milieu actif liquide présentant différentes températures est injecté dans l'ordre suivant, du milieu actif le plus chaud au milieu actif le plus froid, et en ce que chaque milieu actif suivant est injecté lorsque le milieu actif déjà situé dans la préchambre (13) ou dans la chambre de travail (11) atteint la température du milieu actif plus froid suivant.
  18. Procédé selon l'une quelconque des revendications 15 à 17, caractérisé en ce qu'au moins une soupape d'évacuation (21) est ouverte lorsque le piston (3) se situe dans la zone du point mort bas.
EP07723993.7A 2006-04-04 2007-04-04 Machine à vapeur à piston, à évaporation éclair interne du fluide de travail Not-in-force EP2002089B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006015754 2006-04-04
PCT/EP2007/003052 WO2007115769A2 (fr) 2006-04-04 2007-04-04 Machine à vapeur à piston, à évaporation éclair interne du fluide de travail

Publications (2)

Publication Number Publication Date
EP2002089A2 EP2002089A2 (fr) 2008-12-17
EP2002089B1 true EP2002089B1 (fr) 2016-03-23

Family

ID=38581444

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07723993.7A Not-in-force EP2002089B1 (fr) 2006-04-04 2007-04-04 Machine à vapeur à piston, à évaporation éclair interne du fluide de travail

Country Status (8)

Country Link
US (1) US8061133B2 (fr)
EP (1) EP2002089B1 (fr)
JP (1) JP5145326B2 (fr)
KR (1) KR101417143B1 (fr)
CN (1) CN101454542A (fr)
CA (1) CA2650541C (fr)
IL (1) IL194523A (fr)
WO (1) WO2007115769A2 (fr)

Families Citing this family (29)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8065876B2 (en) * 2005-09-21 2011-11-29 Solartrec Inc. Heat engine improvements
DE102008013673B3 (de) * 2008-03-11 2009-09-17 Richard Engelmann Kolbendampfmaschine für einen solar betriebenen Rankine-Kreislauf
DE102008041939A1 (de) * 2008-09-10 2010-03-11 Ago Ag Energie + Anlagen Verfahren zum Betreiben einer Wärmepumpe oder Kältemaschine bzw. einer Kraftmaschine sowie Wärmepumpe oder Kältemaschine und Kraftmaschine
JP5169984B2 (ja) * 2009-05-11 2013-03-27 株式会社デンソー 熱機関
WO2010132924A1 (fr) * 2009-05-18 2010-11-25 Martin De Silva Système, procédé et composants pour puissance thermique
DE102010027347B4 (de) * 2010-07-16 2021-08-12 Josef Birner Vorrichtung zur Durchführung eines thermodynamischen Kreisprozesses
WO2012097215A1 (fr) 2011-01-13 2012-07-19 General Compression, Inc. Systèmes, procédés et dispositifs permettant la gestion de l'élimination de chaleur dans un dispositif ou un système de compression et/ou de dilatation
CN102230404B (zh) * 2011-07-06 2013-10-16 浙江大学 智能热能回收转换系统及其使用方法
JP5804555B2 (ja) * 2011-09-14 2015-11-04 定見 ▲吉▼山 蒸気機関
EP2751391A4 (fr) * 2011-10-18 2015-04-22 Lightsail Energy Inc Système de stockage d'énergie à gaz comprimé
CN102434257B (zh) * 2011-11-17 2013-08-14 徐明奇 车、船发动机废热发电装置
US9574765B2 (en) * 2011-12-13 2017-02-21 Richard E. Aho Generation of steam by impact heating
DE102013007337A1 (de) * 2013-04-27 2014-10-30 Manfred Carlguth Wärmekraftmaschine mit hohem thermischen Wirkungsgrad
DE112014006400A5 (de) 2014-02-25 2016-12-22 Manfred Carlguth Wärmekraftmaschine mit hohem thermischen Wirkungsgrad
CN104806297A (zh) * 2015-03-11 2015-07-29 郭富强 一种余热利用的方法
CN107614832B (zh) * 2015-05-18 2020-04-14 理查德·E·阿霍 空化引擎
JP5826962B1 (ja) * 2015-05-25 2015-12-02 ライトブレインラボ合同会社 凝縮室付き熱機関
DE102015109174B3 (de) * 2015-06-10 2016-03-31 En3 Gmbh Verfahren zur Energieanreicherung eines Arbeitsmediums bei einer Entspannungsverdampfung und Vorrichtung zur Durchführung des Verfahrens
WO2017025700A1 (fr) * 2015-08-13 2017-02-16 Gas Expansion Motors Limited Moteur thermodynamique
DE102015013896B3 (de) * 2015-10-27 2017-01-12 JuB-Creative Product GmbH Niedertemperaturwärmekraftanlage
DE102015013895B4 (de) * 2015-10-27 2020-06-18 JuB-Creative Product GmbH Gebäudetechnische Hybridanlage
CN108533328A (zh) * 2018-04-28 2018-09-14 曹连国 一种基于空调原理逆向应用的新型低温蒸汽机
CN113803114A (zh) * 2020-06-16 2021-12-17 机械科学研究院浙江分院有限公司 活塞式甲醇蒸汽机及其系统，以及蒸汽机循环做功方法
CN112343662A (zh) * 2020-12-14 2021-02-09 王新跃 一种以水为能源的发动机
DE102021102803B4 (de) 2021-02-07 2024-06-13 Kristian Roßberg Vorrichtung und Verfahren zur Umwandlung von Niedertemperaturwärme in technisch nutzbare Energie
DE102021108558B4 (de) 2021-04-06 2023-04-27 Kristian Roßberg Verfahren und Vorrichtung zur Umwandlung von Niedertemperaturwärme in technisch nutzbare Energie
WO2023232672A1 (fr) * 2022-05-31 2023-12-07 Manfred Rapp Moteur à air/vapeur et son utilisation
EP4306775B1 (fr) 2022-07-11 2024-08-14 Kristian Roßberg Procédé et dispositif de conversion de chaleur à basse température en énergie mécanique techniquement utilisable
WO2024016076A1 (fr) * 2022-07-20 2024-01-25 Hydrograph Clean Power Inc. Actionneur comprenant un matériau poreux électroconducteur

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB171291A (en) * 1920-10-18 1921-11-17 Walter Irving Hoover Improvements in combined steam generators and engines
DE689961C (de) * 1937-08-06 1940-04-10 Kloeckner Humboldt Deutz Akt G Dampfkraftmaschine mit Dampfbildung im Zylinder
US3720188A (en) * 1971-01-11 1973-03-13 G Mead Compact steam generator and system
US3720186A (en) * 1971-10-14 1973-03-13 Rourke W O Dispensing apparatus
DE2419688A1 (de) * 1974-01-21 1975-08-07 Boehler & Co Ag Geb Dampfturbinenprozess mit organischen medien
US4149383A (en) * 1977-07-29 1979-04-17 Spalding Wesley H Internal vaporization engine
JPS5638507A (en) * 1979-09-03 1981-04-13 Toshimi Negishi Prime mover
US4301655A (en) * 1979-12-14 1981-11-24 Thomas Luther B Combination internal combustion and steam engine
GB2082683B (en) * 1980-08-18 1984-03-07 Thermal Systems Ltd External combustion reciprocating heat engine
US4416113A (en) * 1980-12-15 1983-11-22 Francisco Portillo Internal expansion engine
JPS58140410A (ja) * 1981-07-23 1983-08-20 ジアンニ・アブラモ・ドツト 往復機関
US4599859A (en) * 1985-02-01 1986-07-15 Urso Charles L Combined steam generator and engine
JPH06117256A (ja) * 1992-09-30 1994-04-26 Isuzu Motors Ltd 直接噴射式ディーゼル機関の燃焼室
FI101738B (fi) * 1996-01-30 1998-08-14 Waertsilae Nsd Oy Ab Ruiskutusventtiilijärjestely
DE10000082A1 (de) * 1999-11-12 2001-05-17 Guenter Frank Dampfmotor und Verfahren zum Betreiben von Dampfmotoren
DE10062835A1 (de) * 2000-12-17 2002-06-20 Erich Schneider Kolbenverbrennungsmotor mit sequentieller Dampfeinspritzung

Also Published As

Publication number Publication date
US20090100832A1 (en) 2009-04-23
JP5145326B2 (ja) 2013-02-13
US8061133B2 (en) 2011-11-22
WO2007115769A2 (fr) 2007-10-18
WO2007115769A3 (fr) 2008-07-10
IL194523A0 (en) 2009-08-03
KR101417143B1 (ko) 2014-07-08
IL194523A (en) 2013-02-28
KR20080112362A (ko) 2008-12-24
CN101454542A (zh) 2009-06-10
CA2650541C (fr) 2014-12-09
CA2650541A1 (fr) 2007-10-18
JP2009532619A (ja) 2009-09-10
EP2002089A2 (fr) 2008-12-17

Similar Documents

Publication Publication Date Title
EP2002089B1 (fr) Machine à vapeur à piston, à évaporation éclair interne du fluide de travail
EP1330592B1 (fr) Procede de fonctionnement d'un moteur thermique a vapeur, en particulier comme mecanisme d'entrainement de vehicule
DD156097A5 (de) Drehkolbenmotor mit aeusserer verbrennung,verfahren zum betrieb dieses motors und bausatz aus teilen des motors
DD156096A5 (de) Verbrennungsmotor mit hin-und hergehenden kolben und mit aeusserer verbrennung
DE3049124A1 (de) "kolbenmotor, verfahren zu seinem betrieb und bausatz aus teilen des motors"
EP2299097A2 (fr) Moteur thermique
EP0773349A1 (fr) Refroidisseur d'air de refroidissement pour centrales
DE3049182A1 (de) Drehkolbenmotor, verfahren zum betrieb des drehkolbenmotors und bausatz mit teilen des drehkolbenmotors
EP3320189B1 (fr) Procédé à cycle fermé supercritique à détente isotherme et machine thermique à piston libre à découplage énergétique hydraulique pour ce procédé à cycle fermé
DE102007038073A1 (de) Effiziente Energiewandlungsmaschine durch kombinierte Brennkraftmaschine mit Dampfprozess
DE4303692A1 (de) Freikolben-Exergie-Verbrennungsmotor mit verringertem Brennstoffbedarf
DE102010027347B4 (de) Vorrichtung zur Durchführung eines thermodynamischen Kreisprozesses
DE19533249C1 (de) Strömungsmaschine zur Erzeugung mechanischer Arbeit aus Wärmeenergie und ein Verfahren zur Erzeugung mechanischer Arbeit aus Wärmeenergie mit einer solchen Strömungsmaschine
CH699696A2 (de) Verfahren zur Erhöhung des Wirkungsgrades eines Hubkolben-Verbrennungsmotors sowie Hubkolben-Verbrennungsmotor.
DE2743584A1 (de) Waermekraftmaschine
DE2240426A1 (de) Verbrennungsmotor mit abwaermeverwertung
EP1700023A2 (fr) Moteur a gaz chaud
WO2010045925A2 (fr) Moteur à piston avec un cylindre torique partiel et un piston torique partiel
DE102013013807A1 (de) Verdampfungs-Hubkolbenmotor
DE19506186B4 (de) Verfahren zum Betreiben einer Dampfkraftmaschinenanlage und Vorrichtung zur Durchführung des Verfahrens
DE531532C (de) Vereinigte Brennkraft- und Dampfkraftanlage
DE332227C (de) Vereinigte Viertaktexplosionskraft- und Dampfmaschine
DE202007018776U1 (de) Dampf-Motor mit rotierenden Dampfeinlass- und auslassrohren
DE102008002903A1 (de) Verfahren zum Abbremsen einer Brennkraftmaschine
DE102011052502B4 (de) Verbrennungsmotor

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20081021

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC MT NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR MK RS

17Q First examination report despatched

Effective date: 20090323

DAX Request for extension of the european patent (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20150929

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC MT NL PL PT RO SE SI SK TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 783369

Country of ref document: AT

Kind code of ref document: T

Effective date: 20160415

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502007014653

Country of ref document: DE

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20160323

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160323

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160624

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160323

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160323

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160323

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160430

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160323

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160323

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160323

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160723

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502007014653

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160323

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160725

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160323

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160323

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160323

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160323

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20161230

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160523

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160430

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160323

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160430

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161101

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160623

26N No opposition filed

Effective date: 20170102

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20160623

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160323

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160623

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160404

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 783369

Country of ref document: AT

Kind code of ref document: T

Effective date: 20160404

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160404

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160323

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20070404

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160323

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160323

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160323

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160404