EP1876323A1 - Combustion engine with auto ignition of the air-fuel mix - Google Patents
Combustion engine with auto ignition of the air-fuel mix Download PDFInfo
- Publication number
- EP1876323A1 EP1876323A1 EP06466004A EP06466004A EP1876323A1 EP 1876323 A1 EP1876323 A1 EP 1876323A1 EP 06466004 A EP06466004 A EP 06466004A EP 06466004 A EP06466004 A EP 06466004A EP 1876323 A1 EP1876323 A1 EP 1876323A1
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- EP
- European Patent Office
- Prior art keywords
- combustion engine
- internal combustion
- pistons
- engine according
- piston
- 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.)
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Classifications
-
- 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
- F01B7/00—Machines or engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders
- F01B7/16—Machines or engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders with pistons synchronously moving in tandem arrangement
-
- 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
- F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
- F01B9/04—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft
- F01B9/047—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft with rack and pinion
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- 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
- F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
- F01B9/04—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft
- F01B9/08—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft with ratchet and pawl
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- 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
- F02B75/28—Engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders
-
- 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
- F02B75/32—Engines characterised by connections between pistons and main shafts and not specific to preceding main groups
-
- 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
-
- 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
- F02G2280/00—Output delivery
- F02G2280/10—Linear generators
Definitions
- the invention relates to the construction of the internal combustion engine with 4 combustion chambers for the four-stroke engine, in which successively auto-ignition of the sucked or transported by a compressor or turbocharger air, mixed with appropriate amount of fuel and thus drives the engine, wherein the time of self-ignition of Air-fuel mixture may vary depending on the load, frequency of auto-ignition, the temperature of the engine and the mixture, the power of the engine is thereby mechanically, electromagnetically or hydraulically dissipated and the efficiency of the engine is further increased by the fact that a part of the energy for Engine cooling and the amount of heat of the exhaust gases is used to generate the steam under pressure and with expansion of this steam in the middle cylinder the motor additional power is added and this steam is cooled again after the expansion by the air flow and liquefied and the circuit de s motor is returned.
- the internal combustion engines are today by a crankshaft, which converts the linear piston movements in individual cylinders in the rotating motion of the crankshaft with power reduction.
- the efficiency of the gasoline engine is limited, inter alia, by the auto-ignition limit, the so-called knocking.
- this auto-ignition limit does not apply, the amount of air compression is mainly limited by the size of the so-called "blow-by" quantity and the strength of the construction.
- the invention seeks to redesign the vorskizz faced disadvantages of today's engines so that the thermal losses are reduced, the efficiency of the engine is thereby increased, the need to increase the octane number of the fuel is partially avoided.
- the construction of the engine according to the invention is characterized in that the movement of the two pairs of pistons in the cylinders of the four-stroke engine is synchronized by two gears, that the inertial forces of these two pairs of pistons through equal mass one, in the middle between them in opposite Directed moving piston pair of the same mass are compensated.
- the engine has no spark plugs, thus no ignition distributor.
- the ignition of the air-fuel mixture is carried out by increasing the temperature after compression by the so-called auto-ignition.
- the engine In order to reduce the pressure increase in the engine by this auto-ignition, and to reduce the pollutants, especially NO x and NO, the engine is usually operated at lambda equal to 1.3 - 3.0, only at start and a short start-up phase, this engine is at 1.0 lambda operated.
- the performance of this engine is, as already mentioned, either mechanically, hydraulically or electrically dissipated.
- the mechanical type is that the reciprocating motion of the two pairs of pistons, as well as the opposite movement of the piston placed between them by two clutches, which alternately engage in one direction of the rotational movement, in the opposite direction but slide and vice versa.
- the power of the engine is dissipated by sucking the hydraulic fluid in the middle cylinder and adding it to the hydraulic motor or turbine during the power stroke, thus converting it into the engine's output.
- the linear electric motor is used in the middle cylinder / piston area.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Combustion Methods Of Internal-Combustion Engines (AREA)
- Hybrid Electric Vehicles (AREA)
- Engine Equipment That Uses Special Cycles (AREA)
Abstract
Description
Die Erfindung betrifft die Konstruktion des Verbrennungsmotors mit 4 Brennräumen für den Viertaktmotor, in welchem nacheinander Selbstzündung des angesaugten bzw. durch einen Kompressor bzw. Abgasturboladers beförderten Luft, vermischt mit entsprechender Menge des Treibstoffes erfolgt und so den Motor antreibt, wobei der Zeitpunkt der Selbstzündung des Luft-Brennstoffgemisches variieren kann, je nach Last, Frequenz der Selbstzündungen, der Temperatur des Motors und des Gemisches, die Leistung des Motors wird dabei mechanisch, elektromagnetisch oder hydraulisch abgeführt und der Wirkungsgrad des Motors wird weiter dadurch erhöht, dass ein Teil der Energie für Motorkühlung sowie der Wärmemenge der Auspuffgase zur Erzeugung des Dampfes unter Druck eingesetzt wird und mit Expansion diesen Dampfes im mittleren Zylinder dem Motor zusätzliche Leistung beigeführt wird und dieser Dampf nach der Expansion durch den Luftstrom wieder gekühlt und verflüssigt wird und dem Kreislauf des Motors zurückgeführt wird.The invention relates to the construction of the internal combustion engine with 4 combustion chambers for the four-stroke engine, in which successively auto-ignition of the sucked or transported by a compressor or turbocharger air, mixed with appropriate amount of fuel and thus drives the engine, wherein the time of self-ignition of Air-fuel mixture may vary depending on the load, frequency of auto-ignition, the temperature of the engine and the mixture, the power of the engine is thereby mechanically, electromagnetically or hydraulically dissipated and the efficiency of the engine is further increased by the fact that a part of the energy for Engine cooling and the amount of heat of the exhaust gases is used to generate the steam under pressure and with expansion of this steam in the middle cylinder the motor additional power is added and this steam is cooled again after the expansion by the air flow and liquefied and the circuit de s motor is returned.
Die Verbrennungsmotoren werden heute durch eine Kurbelwelle, welche die linearen Kolbenbewegungen in einzelnen Zylindern in die rotierende Bewegung der Kurbelwelle mit Leistungsabnahme umsetzt.
Der Wirkungsgrad des Ottomotors wird unter anderem durch die Selbstzündgrenze, dem so genannten Klopfen begrenzt.
Bei Dieselmotoren gilt diese Selbstzündgrenze nicht, die Höhe der Verdichtung der Luft wird hauptsächlich durch die Grösse der so genannten "blow-by" Menge und der Festigkeit der Konstruktion begrenzt.The internal combustion engines are today by a crankshaft, which converts the linear piston movements in individual cylinders in the rotating motion of the crankshaft with power reduction.
The efficiency of the gasoline engine is limited, inter alia, by the auto-ignition limit, the so-called knocking.
In diesel engines, this auto-ignition limit does not apply, the amount of air compression is mainly limited by the size of the so-called "blow-by" quantity and the strength of the construction.
Die Erfindung versucht die vorskizzierten Nachteile der heutigen Motoren neu so zu gestalten, dass die thermischen Verluste verringert werden, der Wirkungsgrad des Motors dadurch erhöht wird, die Notwendigkeit zur Erhöhung der Oktanzahl des Brennstoffes zum Teil vermieden wird.
Die Konstruktion des Motors nach Erfindung ist dadurch gekennzeichnet, dass die Bewegung der zwei Kolbenpaare in den Zylindern des Viertakt-Motors durch zwei Zahnräder synchronisiert wird, dass die Massenkräfte dieser zwei Paare von Kolben durch gleich grosse Masse eines, in der Mitte zwischen ihnen in entgegengesetzte Richtung bewegten Kolbenpaares von gleicher Masse ausgeglichen werden.
Der Motor besitzt keine Zündkerzen, dadurch auch keinen Zündverteiler. Die Zündung des Luft-Brennstoffgemisches erfolgt durch Erhöhung der Temperatur nach Kompression durch die so genannte Selbstzündung.
Um die Druckerhöhung im Motor durch diese Selbstzündung zu verkleinern, sowie die Schadstoffe, besonders NOx und NO zu senken, wird der Motor in der Regel bei Lambda gleich 1.3 - 3.0 betrieben, nur beim Start und kurzer Anlaufphase wird dieser Motor bei Lambda gleich 1.0 betrieben.
Die Leistung dieses Motors wird, wie schon erwähnt, entweder mechanisch, hydraulisch oder elektrisch abgeführt.
Die mechanische Art beruht darin, dass die Hin- und Herbewegung der zwei Kolbenpaare, sowie die gegenläufige Bewegung der zwischen ihnen platzierten Kolben durch zwei Kupplungen, welche abwechslungsweise in einer Richtung der Drehbewegung greifen, in die entgegen gesetzte Richtung aber gleiten und umgekehrt.
Hydraulisch wird die Leistung des Motors abgeführt, indem die hydraulische Flüssigkeit im mittleren Zylinder angesaugt und beim Arbeitstakt dem hydraulischen Motor oder der Turbine beigeführt wird und so in die Leistung des Motors umgesetzt wird.
Für den Start dieses Motors, sowie für die Stromerzeugung im ganzen Leistungsbereich wird der lineare Elektromotor im Bereich der mittleren Zylinder/Kolben eingesetzt.The invention seeks to redesign the vorskizzierten disadvantages of today's engines so that the thermal losses are reduced, the efficiency of the engine is thereby increased, the need to increase the octane number of the fuel is partially avoided.
The construction of the engine according to the invention is characterized in that the movement of the two pairs of pistons in the cylinders of the four-stroke engine is synchronized by two gears, that the inertial forces of these two pairs of pistons through equal mass one, in the middle between them in opposite Directed moving piston pair of the same mass are compensated.
The engine has no spark plugs, thus no ignition distributor. The ignition of the air-fuel mixture is carried out by increasing the temperature after compression by the so-called auto-ignition.
In order to reduce the pressure increase in the engine by this auto-ignition, and to reduce the pollutants, especially NO x and NO, the engine is usually operated at lambda equal to 1.3 - 3.0, only at start and a short start-up phase, this engine is at 1.0 lambda operated.
The performance of this engine is, as already mentioned, either mechanically, hydraulically or electrically dissipated.
The mechanical type is that the reciprocating motion of the two pairs of pistons, as well as the opposite movement of the piston placed between them by two clutches, which alternately engage in one direction of the rotational movement, in the opposite direction but slide and vice versa.
Hydraulically, the power of the engine is dissipated by sucking the hydraulic fluid in the middle cylinder and adding it to the hydraulic motor or turbine during the power stroke, thus converting it into the engine's output.
For the start of this engine, as well as for the power generation in the entire power range, the linear electric motor is used in the middle cylinder / piston area.
Die Erfindung wird im Folgenden an Hand der in den Zeichnungen dargestellten Ausführungsbeispiele näher beschrieben.
In den Zeichnungen stellen dar:
- Fig. 1
- schematisch einen Längsschnitt des Verbrennungsmotors, bestehend aus zwei in der Mitte verschraubten Zylinderhälften, zwei verbundenen Kolbenpaaren mit üblichen Dichtringen, vier Brennräumen, vier oder fünf Ventilen pro Kopf, sowie je einer Einspritzdüse pro Zylinderkopf sowie in der Mitte zwischen diesen Zylindern angeordnete zwei verbundene Ausgleichskolben, welche durch die zwei Zahnräder die gegenläufige Bewegung zu den Kolben des Verbrennungsmotors haben. Alle Kolben laufen berührungslos in den Zylindern, sie werden durch geschmierte Zahnstangen, welche durch zwei Zahnräder genau und ohne Spiel positioniert sind, die Kolben im mittleren Zylinderpaar sind durch gleiche zwei Zahräder, welche in die beidseitig verzahnte Verbindungsstange zwischen den Kolben des mittleren Zylinderpaares greifen, positioniert.
Die vier bzw. fünf Ventile pro Zylinderkopf, zwei Ansaugventile und zwei Auspuffventile oder drei Ansaugventile und zwei Auspuffventile sind pneumatisch, piezoelektrisch oder elektromagnetisch betätigt, genau so wie die vier oder fünf Ventile pro Kopf des Massenausgleich- Kolbenpaares zwischen ihnen, und auf diese Art wird die, in gewissen Grenzen variierende Bewegung der Kolbenpaare gemeistert. - Fig. 2
- zeigt schematisch den Längsschnitt des Verbrennungsmotors nach Fig. 1 mit folgenden Änderungen: Die Kolben sind nicht mit Kolbenringen bestückt und die Stirnflächen der Kolben haben eine sphärische Form. Das hat den Grund, dass diese Form des Motors für höhere Temperaturen der Kolben sowie der Zylinder und der Zylinderköpfe bestimmt ist, für welche kein Schmierstoff geeignet wäre. Der Motor läuft "trocken", die blow-by Menge wird durch geeignete Labyrinthstrukturen an den Kolben begrenzt, alle Kolben sind in den Zylindern durch Wasser oder Wasserdampf gekühlt.
- Fig. 3
- zeigt schematisch einen der zwei linearen Elektromotoren, platziert im mittleren Zylinder zwischen den zwei Motorzylindern mit ihren Kolben, welche der Stromerzeugung dienen.
- Fig. 4
- zeigt schematisch einerseits die Lage der Ventile und der Einspritzdüsen im Motor, anderseits die Verschraubung der zwei Zylinderhälften.
- Fig.5
- zeigt schematisch die zwei Lamellenkupplungen, wobei die eine in eine Richtung des Kolbens greift, die andere gleitet, bei nächstem entgegengesetzten Hub umgekehrt, diese gleitet und die zweite Kupplung greift und so die Leistung des Motors abführt.
- Fig.6
- zeigt eine der insgesamt zwei in die Gegenrichtung greifende Lamellenkupplungen mit Einsatz um je 1°.
- Fig. 7
- zeigt eine, für höhere Leistungen gebaute Kupplung, welche in gleichgesetzter Richtung gleitet, die zweite Kupplung gleicher Art umgekehrt konzipiert, in die entgegengesetzte Richtung greift und in die gleichgesetzte Richtung gleitet.
In the drawings:
- Fig. 1
- schematically a longitudinal section of the internal combustion engine, consisting of two screwed in the middle cylinder halves, two connected piston pairs with conventional sealing rings, four combustion chambers, four or five valves per head, and one injector per cylinder head and in the middle between these cylinders arranged two connected balance piston, which by the two gears have the opposite movement to the pistons of the engine. All pistons run contact-free in the cylinders, they are lubricated by racks, which are accurately and without play positioned by two gears, the pistons in the middle pair of cylinders are by the same two Zahräder which engage in the double-toothed connecting rod between the pistons of the middle pair of cylinders positioned.
The four or five valves per cylinder head, two intake valves and two exhaust valves or three intake valves and two exhaust valves are pneumatically, piezoelectrically or electromagnetically actuated, as are the four or five valves per head of the mass balance piston pair between them, and thus the, within certain limits varying movement of the piston pairs mastered. - Fig. 2
- shows schematically the longitudinal section of the internal combustion engine according to Fig. 1 with the following changes: The pistons are not equipped with piston rings and the end faces of the pistons have a spherical shape. This is because this form of engine is designed for higher temperatures of the pistons, as well as the cylinders and cylinder heads, for which no lubricant would be suitable. The engine runs "dry", the blow-by amount is limited by suitable labyrinth structures on the piston, all pistons are cooled in the cylinders by water or steam.
- Fig. 3
- shows schematically one of the two linear electric motors, placed in the middle cylinder between the two engine cylinders with their pistons, which are used to generate electricity.
- Fig. 4
- shows schematically on the one hand the position of the valves and the injection nozzles in the engine, on the other hand the screw connection of the two cylinder halves.
- Figure 5
- shows schematically the two multi-plate clutches, the one engages in one direction of the piston, the other slides, reversed at the next opposite stroke, this slides and the second clutch engages and so dissipates the power of the engine.
- Figure 6
- shows one of the two in the opposite direction cross-plate multi-plate clutches with use by 1 °.
- Fig. 7
- shows a built for higher performance clutch, which slides in the same direction, the second clutch of the same kind designed in reverse, engages in the opposite direction and slides in the same direction.
- 1.1.
- Zwei der insgesamt 24 VentilsitzeTwo of the total of 24 valve seats
- 2.Second
- Zwei der insgesamt 8 Kanälen des DampfmotorsTwo of the total of 8 channels of the steam engine
- 3.Third
- Zwei der insgesamt 16 Ein- und AuspuffkanäleTwo of the total of 16 intake and exhaust ports
- 4.4th
- Ein der insgesamt 4 Kompressionsräumen des MotorsOne of the four compression chambers of the engine
- 5.5th
- Zwei der insgesamt 8 Ventilen des DampfmotorsTwo of the total of 8 valves of the steam engine
- 6.6th
- Einer der insgesamt 2 mittleren Zylinderräumen des MotorsOne of the two middle cylinder chambers of the engine
- 7.7th
- Eine de Verbindungsschrauben der zwei ZylinderhälftenOne de connecting screws of the two cylinder halves
- 8.8th.
- Eine der Muttern zur Befestigung der zwei ZylinderhälftenOne of the nuts for fixing the two cylinder halves
- 9.9th
- Zwei gleiche, verbundene Zylinderhälften mit ZylinderköpfenTwo identical, connected cylinder halves with cylinder heads
- 10.10th
- Die Lagerung der zwei ZahnräderThe storage of the two gears
- 11.11th
- Die beidseitig verzahnte Verbindungsstange zwischen den zwei Kolben des mittleren DampfzylindersThe double-toothed connecting rod between the two pistons of the middle steam cylinder
- 12.12th
- Zwei der insgesamt vier Zylinderräumen, dargestellt bei annähernd maximalem VolumenTwo of the four cylinder chambers, shown at approximately maximum volume
- 13.13th
- Zwei der insgesamt vier Einspritzdüsen, bzw. deren SitzeTwo of the four injectors, or their seats
- 14.14th
- Zwei der insgesamt 16 Ein- und Auslassventile des MotorsTwo of the 16 intake and exhaust valves of the engine
- 15.15th
- Ein der insgesamt zwei Kühlräume des Motors, Fig. 1One of the two cooling chambers of the engine, Fig. 1
- 16.16th
- Einführung des Kühlmittels in den Motor, Fig. 2, Fig. 3 und Fig. 8Introduction of the coolant into the engine, FIGS. 2, 3 and 8
- 17.17th
-
Kolbenringe an allen Kolben des Motors nach Einspruch 1, Fig. 1Piston rings on all pistons of the engine according to
claim 1, Fig. 1 - 18.18th
- Eine der insgesamt 6 geschmierten Laufflächen des Motors, Fig. 1One of the total of 6 lubricated running surfaces of the engine, Fig. 1
- 19.19th
- Die zwei verzahnten und geschmierten Verbindungsstücke zwischen den KolbenThe two toothed and lubricated connectors between the pistons
- 20.20th
- Ein der beiden mittleren Kolben des Dampfmotors, Fig. 1 und Fig. 2One of the two central pistons of the steam engine, Fig. 1 and Fig. 2
- 21.21st
- Die zwei geschmierten Stützen, welche die Kräfte an die Verbindungsstücke ausgleichenThe two lubricated supports, which balance the forces on the connectors
- 22.22nd
- Die zwei Zahnräder, welche in die Verbindungsstücke greifen und so die Bewegung der Kolben angleichen und abführenThe two gears, which engage in the connectors and so adjust the movement of the piston and dissipate
- 23.23rd
- Die zwei und zwei verbundene Kolben des MotorsThe two and two connected pistons of the engine
- 24.24th
- Die Kolbenringe des mittleren Dampfmotors, Fig. 1The piston rings of the middle steam engine, Fig. 1
- 25.25th
- Die Labyrinthstruktur an allen Kolben des Motors, Fig. 2, Fig. 3 und Fig. 8The labyrinth structure on all pistons of the engine, FIGS. 2, 3 and 8
- 26.26th
- Die Kolbenstirnseiten mit Spiegelschutzschicht, Fig. 2, Fig. 3 und Fig. 8The piston end faces with mirror protection layer, FIGS. 2, 3 and 8
- 27.27th
- Die Befestigung der beiden verzahnten Verbindungsstücke (19) in den KolbenThe attachment of the two toothed connecting pieces (19) in the piston
- 28.28th
- Abfluss des Kühlwasserstromes, bzw. -dampfes, Fig. 2, Fig. 3 und Fig. 8Outflow of the cooling water flow, or steam, Fig. 2, Fig. 3 and Fig. 8
- 29.29th
- Die vergrösserte Länge des mittleren linearen Elektromotors, Fig. 3The enlarged length of the middle linear electric motor, Fig. 3rd
- 30.30th
- Die eiserne Hülse des linearen Elektromotors/Generators Fig. 3The iron sleeve of the linear electric motor / generator Fig. 3
- 31.31st
- Die Statorwicklung des linearen Elektromotors/Generators Fig. 3The stator winding of the linear electric motor / generator FIG. 3
- 32.32nd
- Ein der beiden magnetischen Kerne des linearen Elektromotors/Generators Fig. 3One of the two magnetic cores of the linear electric motor / generator FIG. 3
- 33.33rd
- Zwei geschmierte Wellen, welche die hin- und her- Bewegung der Kolben zur Gleichrichtung führen Fig. 4 und Fig. 5Two lubricated shafts guiding the reciprocating motion of the pistons for rectification FIG. 4 and FIG. 5
- 34.34th
- Zwei ineinander greifende Zahnräder, welche mit Hilfe der 2 Lamellenkupplungen Fig. 6 oder 2 Wälzlagerkupplungen Fig. 7, die hin- und her- Bewegung der Wellen gleichrichten und abführenTwo intermeshing gears which, with the aid of the two multi-plate clutches Fig. 6 or 2 roller bearing clutches Fig. 7, rectify the back and forth motion of the waves and dissipate
- 35.35th
- Die Abführung der Leistung des Motors, Fig. 5The dissipation of the power of the motor, Fig. 5
- 36.36th
- Der durch Zahnräder verbundene Elektromotor/Dynamo, Fig. 5The electric motor / dynamo connected by gears, FIG. 5
- 37.37th
- Eine der insgesamt zwei Lamellenkupplungen, welche je 1° der Wellenbewegung greift, in die entgegengesetzte Richtung gleitet, Fig. 6One of the two multi-disc clutches, each of which grips 1 ° of the shaft movement, slides in the opposite direction, FIG. 6
- 38.38th
- Eine der insgesamt zwei Wälzlagerkupplungen, welche in einer Drehrichtung greift, in die entgegengesetzte Richtung gleitet, die zweite umgekehrt, Fig. 7One of the total of two rolling bearing clutches, which engages in one direction of rotation, slides in the opposite direction, the second vice versa, Fig. 7
- 39.39th
- Hydraulische Leistungsabführung, Fig. 8Hydraulic power dissipation, Fig. 8
- 40.40th
- Zwei Kolben des hydraulischen MotorsTwo pistons of the hydraulic motor
- 41.41st
- Abfluss des Leckmengenstromes aus den mittleren Zylindern, Fig. 8Outflow of the leakage flow from the middle cylinders, Fig. 8
Claims (15)
Priority Applications (6)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP06466004A EP1876323A1 (en) | 2006-06-01 | 2006-06-01 | Combustion engine with auto ignition of the air-fuel mix |
CNA2007800278138A CN101495714A (en) | 2006-06-01 | 2007-05-23 | Combustion engine with self-ignition of air-and-fuel mixture |
JP2009512394A JP2010506072A (en) | 2006-06-01 | 2007-05-23 | Combustion engine with self-ignition of air-fuel mixture |
PCT/CZ2007/000036 WO2007137525A2 (en) | 2006-06-01 | 2007-05-23 | Combustion engine with self-ignition of air-and-fuel mixture |
US12/302,620 US20090314252A1 (en) | 2006-06-01 | 2007-05-23 | Combustion engine with self-ignition of air-and-fuel mixture |
RU2008148123/06A RU2008148123A (en) | 2006-06-01 | 2007-05-23 | AIR-FUEL MIXTURE INTERNAL COMBUSTION ENGINE |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP06466004A EP1876323A1 (en) | 2006-06-01 | 2006-06-01 | Combustion engine with auto ignition of the air-fuel mix |
Publications (1)
Publication Number | Publication Date |
---|---|
EP1876323A1 true EP1876323A1 (en) | 2008-01-09 |
Family
ID=38544356
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP06466004A Withdrawn EP1876323A1 (en) | 2006-06-01 | 2006-06-01 | Combustion engine with auto ignition of the air-fuel mix |
Country Status (6)
Country | Link |
---|---|
US (1) | US20090314252A1 (en) |
EP (1) | EP1876323A1 (en) |
JP (1) | JP2010506072A (en) |
CN (1) | CN101495714A (en) |
RU (1) | RU2008148123A (en) |
WO (1) | WO2007137525A2 (en) |
Cited By (2)
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CN104564336A (en) * | 2014-11-17 | 2015-04-29 | 李冠伟 | Gasoline vapor hybrid power multi-port gas supply and exhaust engine |
CN105927280A (en) * | 2016-04-06 | 2016-09-07 | 夏建国 | Steam engine |
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GR1006188B (en) * | 2007-08-10 | 2008-12-08 | Φωτιος Τσολπακης | Internal combustion engine without crankshaft. |
NO328416B1 (en) * | 2008-03-14 | 2010-02-15 | Odd Bernhard Torkildsen | Combined internal combustion engine and steam engine |
FR2963805A1 (en) * | 2010-08-12 | 2012-02-17 | Const Metalliques Et Mecaniques E C M M Et | EFFORT TRANSMISSION DEVICE FOR A PISTON ENGINE AND PISTON MOTOR COMPRISING SUCH A DEVICE |
US9080498B2 (en) * | 2012-04-11 | 2015-07-14 | Mustafa Rez | Combustion engine with a pair of one-way clutches used as a rotary shaft |
CN103573407A (en) * | 2013-10-28 | 2014-02-12 | 北京理工大学 | Self-balancing free-piston internal-combustion generator |
CN103573406A (en) * | 2013-10-28 | 2014-02-12 | 北京理工大学 | Double-cylinder opposed free-piston internal combustion engine generator |
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KR20160068044A (en) * | 2014-12-04 | 2016-06-15 | 현대자동차주식회사 | Engine for vihicles |
PL234850B1 (en) * | 2015-08-31 | 2020-04-30 | Gaj Jablonski Wojciech | Hydrogen engine and method for producing the hydrogen fuel to supply it |
FR3046629B1 (en) * | 2016-01-08 | 2018-01-12 | Peugeot Citroen Automobiles Sa | METHODS AND SYSTEMS FOR POWER SUPPLY IN A MOTOR VEHICLE |
US9926871B2 (en) * | 2016-01-25 | 2018-03-27 | Ford Global Technologies, Llc | Methods and systems for estimating an air-fuel ratio with a variable voltage oxygen sensor |
CN114251184A (en) * | 2017-03-22 | 2022-03-29 | 阿凯提兹动力公司 | Cylinder bore surface structure for opposed-piston engines |
CN213298114U (en) * | 2020-01-14 | 2021-05-28 | 熵零技术逻辑工程院集团股份有限公司 | Engine |
US20230349319A1 (en) * | 2022-05-02 | 2023-11-02 | Enginuity Power Systems, Inc. | Multi-fuel engines and related methods |
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FR2295234A1 (en) * | 1974-12-18 | 1976-07-16 | Energiagazdalkodasi Intezet | Twin cylinder free piston engine - has output shaft driven through worm and wheel from piston rods |
DE3531862A1 (en) * | 1985-09-06 | 1987-03-19 | Zott Kg | Reciprocating piston internal combustion engine |
DE3709790A1 (en) * | 1987-03-25 | 1988-10-13 | Sangchin Lee | GEAR DRIVE FOR CONVERTING THE ROTATION OF THE PISTONS IN THE CYLINDERS OF AN INTERNAL COMBUSTION ENGINE IN THE ROTATIONAL MOVEMENT OF A SHAFT |
DE4201569A1 (en) * | 1992-01-22 | 1993-07-29 | Kurt Dr Ing Werner | Two=stroke opposed-:piston engine without crank drive. - is started by moving magnet or linear motor, and drives rotary shaft via controlled slip coupling. |
DE4223490A1 (en) * | 1992-01-22 | 1994-01-20 | Kurt Dr Ing Werner | Two=stroke reciprocating piston engine - has neighbouring pistons with toothed racks, which are connected by shaft with gear, to form working unit |
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WO2003016701A1 (en) * | 2001-08-20 | 2003-02-27 | Stoyan Stoimenov Kokudev | Combined piston engine |
WO2003087556A1 (en) * | 2002-04-09 | 2003-10-23 | Rodrigues Casimiro Moises | Internal-combustion engine |
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US6574743B1 (en) * | 1999-03-30 | 2003-06-03 | Siemens Energy & Automation | Programmable logic controller method, system and apparatus |
-
2006
- 2006-06-01 EP EP06466004A patent/EP1876323A1/en not_active Withdrawn
-
2007
- 2007-05-23 RU RU2008148123/06A patent/RU2008148123A/en not_active Application Discontinuation
- 2007-05-23 WO PCT/CZ2007/000036 patent/WO2007137525A2/en active Application Filing
- 2007-05-23 US US12/302,620 patent/US20090314252A1/en not_active Abandoned
- 2007-05-23 CN CNA2007800278138A patent/CN101495714A/en active Pending
- 2007-05-23 JP JP2009512394A patent/JP2010506072A/en active Pending
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US2482136A (en) * | 1945-05-12 | 1949-09-20 | William N Wright | Engine |
FR2295234A1 (en) * | 1974-12-18 | 1976-07-16 | Energiagazdalkodasi Intezet | Twin cylinder free piston engine - has output shaft driven through worm and wheel from piston rods |
DE3531862A1 (en) * | 1985-09-06 | 1987-03-19 | Zott Kg | Reciprocating piston internal combustion engine |
DE3709790A1 (en) * | 1987-03-25 | 1988-10-13 | Sangchin Lee | GEAR DRIVE FOR CONVERTING THE ROTATION OF THE PISTONS IN THE CYLINDERS OF AN INTERNAL COMBUSTION ENGINE IN THE ROTATIONAL MOVEMENT OF A SHAFT |
DE4201569A1 (en) * | 1992-01-22 | 1993-07-29 | Kurt Dr Ing Werner | Two=stroke opposed-:piston engine without crank drive. - is started by moving magnet or linear motor, and drives rotary shaft via controlled slip coupling. |
DE4223490A1 (en) * | 1992-01-22 | 1994-01-20 | Kurt Dr Ing Werner | Two=stroke reciprocating piston engine - has neighbouring pistons with toothed racks, which are connected by shaft with gear, to form working unit |
US5673665A (en) * | 1995-11-11 | 1997-10-07 | Kia Motors Corporation | Engine with rack gear-type piston rod |
US5934243A (en) * | 1998-03-26 | 1999-08-10 | Kopystanski; George | Drive mechanism for a reciprocating piston engine |
US20020139323A1 (en) * | 2001-03-28 | 2002-10-03 | Kerrebrock Jack L. | Opposed piston linearly oscillating power unit |
WO2003016701A1 (en) * | 2001-08-20 | 2003-02-27 | Stoyan Stoimenov Kokudev | Combined piston engine |
WO2003087556A1 (en) * | 2002-04-09 | 2003-10-23 | Rodrigues Casimiro Moises | Internal-combustion engine |
US6904888B1 (en) * | 2004-03-01 | 2005-06-14 | Nuhim Heifets | Reciprocating piston device |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN104564336A (en) * | 2014-11-17 | 2015-04-29 | 李冠伟 | Gasoline vapor hybrid power multi-port gas supply and exhaust engine |
CN105927280A (en) * | 2016-04-06 | 2016-09-07 | 夏建国 | Steam engine |
Also Published As
Publication number | Publication date |
---|---|
JP2010506072A (en) | 2010-02-25 |
CN101495714A (en) | 2009-07-29 |
WO2007137525A3 (en) | 2008-01-17 |
US20090314252A1 (en) | 2009-12-24 |
RU2008148123A (en) | 2010-07-20 |
WO2007137525A2 (en) | 2007-12-06 |
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