EP1195503A2 - Verbrennungsmotor - Google Patents
Verbrennungsmotor Download PDFInfo
- Publication number
- EP1195503A2 EP1195503A2 EP01123546A EP01123546A EP1195503A2 EP 1195503 A2 EP1195503 A2 EP 1195503A2 EP 01123546 A EP01123546 A EP 01123546A EP 01123546 A EP01123546 A EP 01123546A EP 1195503 A2 EP1195503 A2 EP 1195503A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- piston
- combustion chamber
- combustion
- air
- cylinder
- 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.)
- Withdrawn
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
- F02B33/00—Engines characterised by provision of pumps for charging or scavenging
- F02B33/02—Engines with reciprocating-piston pumps; Engines with crankcase pumps
- F02B33/06—Engines with reciprocating-piston pumps; Engines with crankcase pumps with reciprocating-piston pumps other than simple crankcase pumps
- F02B33/08—Engines with reciprocating-piston pumps; Engines with crankcase pumps with reciprocating-piston pumps other than simple crankcase pumps with the working-cylinder head arranged between working and pumping 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
- 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
- F01B9/06—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 the piston motion being transmitted by curved surfaces
-
- 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
- F02B75/02—Engines characterised by their cycles, e.g. six-stroke
-
- 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
- F01B9/06—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 the piston motion being transmitted by curved surfaces
- F01B2009/061—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 the piston motion being transmitted by curved surfaces by cams
- F01B2009/065—Bi-lobe cams
Definitions
- the invention relates to an internal combustion engine with a combustion chamber for the clocked Combustion of a fuel to form a combustion gas, one connected to the combustion chamber via a controllable combustion chamber outlet valve, separate expansion chamber that has a slidably mounted Piston for converting the energy of the combustion gas into mechanical work or has energy, and one or more as piston-cylinder units trained compressor pumps for filling the combustion chamber with compressed air, each having an air inlet valve.
- Internal combustion engines are known in different embodiments, for example than conventional petrol or diesel engines. Are also known Internal combustion engines with one of the combustion chamber in which the fuel is burned in a clocked manner to form a combustion gas, separate expansion chamber, the one with the combustion chamber via a controllable inlet valve connected is. A piston is slidably mounted in the expansion chamber, by means of the energy of the combustion gas in mechanical energy or work is implemented.
- Such internal combustion engines are, for example, from EP 0 957 250 A2, AT-PS 172 823, CH-PS 202 930, FR-PS 820 750, the DE-PS 4 136 223 and US-PS 4,716,720 known.
- the advantage of these internal combustion engines consists in particular in the fact that the combustion combustion gas formed in the expansion stroke in the expansion chamber completely can relax, making the energy of the combustion gas better can be exploited.
- Filling the combustion chamber with a fuel-air mixture can be done at atmospheric pressure or compressed.
- the air in the combustion chamber is already known to have its own compressor pump to use, for example from DE-PS 4 136 223 and the US-PS 4,716,720.
- Another aspect of the invention relates to an internal combustion engine with a Combustion chamber for the timed combustion of a fuel to form a Combustion gas, one with the combustion chamber via a controllable combustion chamber exhaust valve connected, separate expansion chamber, the one slidably mounted piston for converting energy of the combustion gas in mechanical work or energy, and one or more than Piston-cylinder units designed compressor pumps for filling the Combustion chamber with compressed air, with the respective air inlet valve in the Compressor pump provided a check valve biased in the closing direction is, which comprises a valve plate arranged on a valve stem.
- Such an internal combustion engine is, for example, from that already mentioned DE 4 136 223 C1 known.
- a type of "air spring” is thus provided which measures the closing force of the valve pretends.
- the spring constant of this air spring is adjustable.
- the check valve opens only when the closing force in the cylinder of the compressor pump Existing negative pressure is exceeded and the size of the opening depends of the closing force given by the air spring compared to the negative pressure in the cylinder of the compressor pump.
- At least two pistons in the schematic representation according to FIG. 1 are preferably driven on the Synchronous pistons 1 acting from opposite sides of shaft 2 intended.
- One, two or more pairs of such opposing, each synchronously clocked pairs of pistons 1 in each Cylinders may be provided.
- At least the opposite pistons or all pistons can have the same inner and outer cam surfaces 3, 4 of the cam mechanism and explained in more detail later separate thrust links in the form of rollers 6 arranged on the piston rods act on the driven shaft 2.
- Each piston 1 has at least one combustion chamber 7 for clocked combustion assigned to a fuel.
- the combustion chamber is made of a jacket surrounded by heat-insulating material. Ignition takes place only in the start phase the fuel-air mixture with a spark plug 9. Heat continuously the walls of the combustion chamber 7 above the autoignition temperature of the fuel (to over 700 ° C) and the ignition of the fuel takes place directly when it is injected into the combustion chamber 7, if it is on the walls thereof occurs. Water is preferably injected together with the fuel, in order to lower the combustion temperature, which in particular leads to a reduction in NOx leads.
- the fuel and water injectors are shown in Fig. 1 only shown schematically as unit 10, the supply of the fuel indicated by the arrow V and the supply of water by the arrow VI are.
- the combustion chamber 7 is connected to a controllable combustion chamber outlet valve 11 an expansion chamber 12 separated from the combustion chamber 7, which is designed as a cylinder space in which the piston 1 is slidably mounted is.
- a heat-insulating layer 14 is 15, preferably made of a ceramic material, on the inside of the cylinder head 16 and on the expansion chamber 12 facing the top of the Piston 1 arranged. Only the cylinder wall 17 has no such thermal insulation on.
- a piston seal 18 made of plastic can be used can (preferably made of graphite-Teflon, which up to about 250 ° C permanent temperature is stable). Such a piston seal 18 is water-lubricable.
- the air inlet valve 24 comprises a valve plate 26, which is connected to a valve stem 27 is arranged.
- the valve stem 27 simultaneously forms one with a piston 28 connected piston rod of a piston-cylinder unit 31.
- the cylinder chamber 32 This piston-cylinder unit is filled with air, the air pressure being one in Closing direction of the air inlet valve 24 causes force.
- a unit 33 comprising an air pump can be changed.
- This air pressure poses thus a kind of "air spring", the spring constant of which can be changed.
- the air intake valve opens only when the negative pressure in the cylinder chamber 25, the closing force of the Air intake valve 24 overcomes.
- the expansion chamber exhaust valve 30 includes those in the longitudinal direction of the cylinder sliding cylinder wall 17.
- the cylinder wall 17 against one in one annular groove in the cylinder head 16 arranged sealing ring 35 pressed, namely against the force of one in the opening direction of the expansion chamber outlet valve acting spring 34.
- the open position there is an annular outlet opening Approved.
- a cam control is provided to act on the displaceable cylinder wall 17 in the position pressed against the sealing ring 35 .
- a cam control is provided to act on the displaceable cylinder wall 17 in the position pressed against the sealing ring 35.
- the combustion chamber exhaust valve 11 is also controlled by a cam actuated, a roller 46 which is on a lever arm of a pivotable Lever 47 is mounted, rolls over a cam disc 48.
- the one on this cam disc 48 arranged cams operate with the other lever arm the lever 47 connected pin 49 and the lever 50 the combustion chamber exhaust valve 11th
- Various conventionally designed pumping devices can be used for injecting the fuel and the water into the combustion chamber 7 and for injecting the water into the expansion chamber 12, for example cam pumps driven by the shaft 2.
- a roller 6 is rotatably mounted. This is arranged between inner and outer cam surfaces 3, 4. The distance between the two cam surfaces 3, 4 is slightly larger than the diameter of the roller 6, so that the roller 6, which acts as a thrust member of the cam mechanism, can roll either on the inner cam surface 3 or the outer cam surface 4.
- the shaft 2 When the roller 6 rolls on the inner cam surface 3 during the downward movement of the piston 1 from the top dead center to the bottom dead center, the shaft 2 is supplied with energy (by the excess pressure of the expanding combustion gas) if the roller 6 on the downward movement of the piston rolls outer curve surface 4, the shaft 2 drives the piston (this allows the combustion gas in the expansion chamber 12 to be diluted to below atmospheric pressure, as will be explained further below). In contrast, when piston 1 moves upward from bottom dead center in the direction of top dead center, energy is supplied to shaft 2 when roller 6 rolls on outer cam surface 4.
- the inner and outer curved surfaces 3, 4 are each circumferentially closed outer surfaces.
- the curved surfaces 3, 4 each have three sections along their circumference, which are explained below with reference to the inner curved surface 3.
- the first section 53 the distance of the cam surface from the center of the shaft 2 decreases rapidly, then slowly. This section is associated with the downward movement of the piston from top dead center to bottom dead center. The initially rapid decrease in the distance corresponds to the initially rapid decrease in the pressure in the expansion chamber.
- a spring device 56 is provided between the piston 1 and the rod 5 actuated by the piston 1 and driving the shaft 2 via the cam mechanism described.
- This includes compression springs 57, which are designed here as disc springs.
- the compression springs are arranged between a pressure plate 58 fixed on the rod 5 and the rear side of the piston 1 facing away from the expansion chamber 12.
- at least three compression springs are provided, which are arranged at the corner points of an imaginary triangle; in the exemplary embodiment shown, four compression springs are provided at the corner points of an imaginary square, whereby the pressure plate 58 is formed by two crossing arms.
- the plate springs 57 are also biased by screws 59.
- the piston 1 therefore only moves in relation to the pressure plate 58 when a force exceeding this preload is exerted on the piston. This in turn prevents the piston from tilting during its upward movement due to the force acting asymmetrically on the piston 1 by the compressor piston 21.
- the piston rod 22 could engage centrally on the piston 1, ie, be aligned with the rod 5 (the combustion chamber 7 would have to be moved further to the side).
- a single, central compression spring 57 between the base of the piston 1 and the rod 5 would suffice, the prestressing of the spring also being omitted.
- the spring device is designed such that it in a first phase the downward movement of the piston 1 thereon from the combustion gas opening the combustion chamber exhaust valve 11 on the piston 1 Can absorb pressure peaks and stores them as potential energy. This will the maximum pressure exerted on the rod 5 is reduced, as is the case with the 2 can be seen.
- the pressure without the spring device 56 would be exerted on the rod (and which rests on the piston 1) is by the dashed line 60 shown. Due to the spring device, the Pressure curve corresponding to the solid line 61. The maximum pressure is therefore much lower.
- the in the first phase of the downward movement of the Piston energy stored by the spring device is hatched by the Surface 62 shown. In a further phase of the downward movement of the piston at a lower pressure of the combustion gas, this is stored potential energy in turn is delivered to the rod 5. This delivered Energy corresponds to area 63.
- the clock cycle of the internal combustion engine thus runs as follows:
- the Piston 1 After the fuel-air mixture has completely burned off, the Piston 1 is still at top dead center OT, the expansion chamber exhaust valve 30 closed and the combustion chamber exhaust valve 11 open. As a result, the pressure in the expansion chamber 12 initially rises rapidly on and then gradually sinks again with the piston 1 running downwards from. At full load, the pressure in expansion chamber 12 is a preferred one Operation just dropped to atmospheric pressure when the piston 1 has reached bottom dead center UT. In this case, at partial load the engine has already reached atmospheric pressure while the piston 1 is still on its way from top dead center to bottom dead center. In As a result, the pressure in the expansion chamber drops in partial load operation 12 under atmospheric pressure. The combustion gas is thereby "diluted" before the implosion phase is initiated.
- the implosion phase is initiated as soon as piston 1 has reached bottom dead center UT, by injecting cooling water into the expansion chamber 12.
- the Piston 1 is pulled up by this vacuum and moves now from bottom dead center towards top dead center.
- the combustion chamber exhaust valve 11 is still kept moving, to enable the exchange of charges in the combustion chamber 7.
- the Full load of the engine corresponds to the maximum power output at the respective speed, for which the engine is designed.
- a throttled could Air intake valve z. B. also in the form of an electromagnetic valve become.
Landscapes
- 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)
- Output Control And Ontrol Of Special Type Engine (AREA)
Abstract
Description
Bei der inneren und bei der äußeren Kurvenfläche 3, 4 handelt es sich jeweils um eine umfangsgeschlossene Mantelfläche. Jeweils weisen die Kurvenflächen 3, 4 entlang ihres Umfangs drei Abschnitte auf, die im folgenden anhand der inneren Kurvenfläche 3 erläutert werden. Im ersten Abschnitt 53 nimmt der Abstand der Kurvenfläche vom Mittelpunkt der Welle 2 erst rasch, dann langsamer ab. Dieser Abschnitt ist der Abwärtsbewegung des Kolbens vom oberen Totpunkt zum unteren Totpunkt zugeordnet. Die anfänglich rasche Abnahme des Abstandes entspricht dabei der anfänglich raschen Abnahme des Drucks in der Expansionskammer. Im folgenden zweiten Abschnitt 54 nimmt der Abstand der Kurvenfläche 3 vom Wellenmittelpunkt wiederum zu. Dieser Abschnitt ist der Aufwärtsbewegung des Kolbens vom unteren Totpunkt zum oberen Totpunkt zugeordnet. Anschließend an den zweiten Abschnitt 54 folgt ein dritter Abschnitt 55, der einen konstanten maximalen Abstand vom Mittelpunkt der Welle 2 aufweist. Während des Ablaufs der Rolle 6 über diesen Abschnitt 55 der Kurvenfläche bleibt daher der Kolben bewegungslos am oberen Totpunkt OT stehen ("Wartephase"). Während dieser Zeit kann die vollständige Verbrennung des Treibstoffs in der Brennkammer 7 durchgeführt werden. Die drei Abschnitte 53, 54, 55 sind entlang des Umfangs der Kurvenfläche 3 zweimal vorgesehen, so daß während einer vollständigen Umdrehung der Welle 2 zwei vollständige Arbeitszyklen bzw. Taktzyklen des Motors durchgeführt werden. Die äußere Kurvenfläche 4 ist in analoger Weise in den Abschnitten 53, 54, 55 in entsprechende Abschnitte unterteilt.
Zur Vermeidung einer unsymmetrischen Belastung des Kolbens 1 bei dessen Aufwärtsbewegung könnte die Kolbenstange 22 zentral am Kolben 1 angreifen, d.h., mit der Stange 5 fluchten (wobei die Brennkammer 7 weiter seitlich verlegt werden müßte). In diesem Fall würde eine einzelne, zentrale Druckfeder 57 zwischen dem Boden des Kolbens 1 und der Stange 5 genügen, wobei die Vorspannung der Feder auch entfallen könnte.
- 1
- Kolben
- 2
- Welle
- 3
- innere Kurvenfläche
- 4
- äußere Kurvenfläche
- 5
- Stange
- 6
- Rolle
- 7
- Brennkammer
- 9
- Zündkerze
- 10
- Einheit
- 11
- Brennkammer-Auslaßventil
- 12
- Expansionskammer
- 13
- Flansch
- 14
- wärmeisolierende Schicht
- 15
- wärmeisolierende Schicht
- 16
- Zylinderkopf
- 17
- Zylinderwand
- 18
- Kolbendichtung
- 19
- Einspritzdüse
- 20
- Kissen
- 21
- Verdichterkolben
- 22
- Kolbenstange
- 23
- Verdichterpumpe
- 24
- Lufteinlaßventil
- 25
- Zylinderraum
- 26
- Ventilteller
- 27
- Ventilschaft
- 28
- Kolben
- 29
- Luftauslaßventil
- 30
- Expansionskammer-Auslaßventil
- 31
- Kolben-Zylinder-Einheit
- 32
- Zylinderraum
- 33
- Einheit
- 34
- Feder
- 35
- Dichtring
- 36
- Drehachse
- 37
- Hebel
- 38
- Stift
- 40
- Leitungsstück
- 41
- Wasserabscheider
- 42
- Wassertank
- 43
- Auspuff
- 44
- Rolle
- 45
- Nockenscheibe
- 46
- Rolle
- 47
- Hebel
- 48
- Nockenscheibe
- 49
- Stift
- 50
- Hebel
- 53
- erster Abschnitt
- 54
- zweiter Abschnitt
- 55
- dritter Abschnitt
- 56
- Federeinrichtung
- 57
- Druckfeder
- 58
- Druckplatte
- 59
- Schraube
- 60
- Linie
- 61
- Linie
- 62
- Fläche
- 63
- Fläche
Claims (4)
- Verbrennungsmotor mit einer Brennkammer zur getakteten Verbrennung eines Treibstoffs unter Bildung eines Verbrennungsgases, einer mit der Brennkammer über ein steuerbares Brennkammer-Auslaßventil verbundenen, separaten Expansionskammer, die einen verschiebbar gelagerten Kolben zur Umsetzung von Energie des Verbrennungsgases in mechanische Arbeit bzw. Energie aufweist, und einer oder mehreren als Kolben-Zylinder-Einheiten ausgebildeten Verdichterpumpen (23) zur Befüllung der Brennkammer mit verdichteter Luft, die jeweils ein Lufteinlaßventil aufweisen, dadurch gekennzeichnet, daß das Lufteinlaßventil (24) drosselbar ist und daß das Volumen des Zylinderraums (25) der Verdichterpumpe (23) oder, im Falle mehrerer Verdichterpumpen (23), das Gesamtvolumen der Zylinderräume der Verdichterpumpen um mindestens 25 %, vorzugsweise mindestens 50 % größer ist, als es einem Volumen für eine Befüllung der Brennkammer (7) mit einem Gemisch mit einer Luftzahl von λ = 1 bei einer bei Vollast des Motors eingebrachten Menge an Treibstoff entspricht.
- Verbrennungsmotor mit einer Brennkammer zur getakteten Verbrennung eines Treibstoffs unter Bildung eines Verbrennungsgases, einer mit der Brennkammer über ein steuerbares Brennkammer-Auslaßventil verbundenen, separaten Expansionskammer, die einen verschiebbar gelagerten Kolben zur Umsetzung von Energie des Verbrennungsgases in mechanische Arbeit bzw. Energie aufweist, und einer oder mehreren als Kolben-Zylinder-Einheiten ausgebildeten Verdichterpumpen (23) zur Befüllung der Brennkammer mit verdichteter Luft, wobei als jeweiliges Lufteinlaßventil in die Verdichterpumpe ein in Schließrichtung vorgespanntes Rückschlagventil vorgesehen ist, das einen an einem Ventilschaft angeordneten Ventilteller umfaßt, dadurch gekennzeichnet, daß das Lufteinlaßventil (24) drosselbar ist, wobei der Ventilschaft (27) mit einem Kolben (28) einer Kolben-Zylinder-Einheit (31) verbunden ist, welche einen Zylinderraum (32) aufweist, in dem ein in Schließrichtung des Lufteinlaßventils wirkender Luftdruck vorliegt, und wobei zur Änderung der Schließkraft des Lufteinlaßventils der Luftdruck im Zylinderraum (32) veränderbar ist.
- Verfahren zum Betreiben eines Verbrennungsmotors mit einer Brennkammer zur getakteten Verbrennung eines Treibstoffs unter Bildung eines Verbrennungsgases, einer mit der Brennkammer über ein steuerbares Brennkammer-Auslaßventil verbundenen, separaten Expansionskammer, die einen verschiebbar gelagerten Kolben zur Umsetzung von Energie des Verbrennungsgases in mechanische Arbeit bzw. Energie aufweist, und einer oder mehreren als Kolben-Zylinder-Einheiten ausgebildeten Verdichterpumpen (23) zur Befüllung der Brennkammer mit verdichteter Luft, die jeweils ein Lufteinlaßventil aufweisen, dadurch gekennzeichnet, daß die in die Brennkammer (7) einbrachte Luftmenge durch Steuerung des drosselbar ausgebildeten Lufteinlaßventils (24) gesteuert wird.
- Verfahren nach Anspruch 3, dadurch gekennzeichnet, daß das Volumen des Zylinderraums (25) der Verdichterpumpe (23) oder, im Falle mehrerer Verdichterpumpen (23), das Gesamtvolumen der Zylinderräume der Verdichterpumpen um mindestens 25 %, vorzugsweise mindestens 50 % größer ist, als es einem Volumen für eine Befüllung der Brennkammer (7) mit einem Gemisch mit einer Luftzahl von λ = 1 bei einer bei Vollast des Motors eingebrachten Menge an Treibstoff entspricht.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AT16822000 | 2000-10-04 | ||
AT16822000 | 2000-10-04 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1195503A2 true EP1195503A2 (de) | 2002-04-10 |
EP1195503A3 EP1195503A3 (de) | 2003-04-16 |
Family
ID=3688643
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP01123546A Withdrawn EP1195503A3 (de) | 2000-10-04 | 2001-10-01 | Verbrennungsmotor |
Country Status (2)
Country | Link |
---|---|
US (1) | US20020179037A1 (de) |
EP (1) | EP1195503A3 (de) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8156919B2 (en) | 2008-12-23 | 2012-04-17 | Darrow David S | Rotary vane engines with movable rotors, and engine systems comprising same |
CN105051350B (zh) * | 2013-01-17 | 2018-09-25 | 尼马尔·穆利 | 内部冷却内燃机及其方法 |
EP3628816A1 (de) * | 2018-09-25 | 2020-04-01 | Fuelsave GmbH | Verbrennungsmotor mit verstellbarer verknüpfung von dessen motoreinheiten |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR820750A (fr) | 1936-01-06 | 1937-11-17 | Moteur à combustion interne | |
CH202930A (de) | 1936-04-14 | 1939-02-15 | Fitzgerald William Maurice Bar | Verbrennungskraftmaschine mit Fremdzündung. |
AT172823B (de) | 1949-11-28 | 1952-10-25 | Rudolf Ing Schulla | Brennkraftmaschine |
US4716720A (en) | 1980-09-08 | 1988-01-05 | Karl Eickmann | Combustion engine with exterior combustion chamber |
DE4136223C1 (de) | 1991-11-02 | 1992-12-24 | Ivan, Constantin, Prof. Dr.Rer.Nat., 4330 Muelheim, De | |
EP0957250A2 (de) | 1998-05-14 | 1999-11-17 | HMS Artist Scheier OEG | Verbrennungsmotor |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2453377A (en) * | 1944-01-25 | 1948-11-09 | Carburation Pour L Automobile | Throttle control for the primary and secondary charges of engines |
FR2416344A1 (fr) * | 1978-02-02 | 1979-08-31 | Kovacs Andre | Moteur a combustion interne a chambre de compression et de detente separees |
FR2607552B1 (fr) * | 1986-05-21 | 1991-07-19 | Innovations Atel Const | Moteur a explosion sans embiellage ni vilebrequin de type cylindres en etoile |
-
2001
- 2001-10-01 EP EP01123546A patent/EP1195503A3/de not_active Withdrawn
- 2001-10-03 US US09/970,526 patent/US20020179037A1/en not_active Abandoned
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR820750A (fr) | 1936-01-06 | 1937-11-17 | Moteur à combustion interne | |
CH202930A (de) | 1936-04-14 | 1939-02-15 | Fitzgerald William Maurice Bar | Verbrennungskraftmaschine mit Fremdzündung. |
AT172823B (de) | 1949-11-28 | 1952-10-25 | Rudolf Ing Schulla | Brennkraftmaschine |
US4716720A (en) | 1980-09-08 | 1988-01-05 | Karl Eickmann | Combustion engine with exterior combustion chamber |
DE4136223C1 (de) | 1991-11-02 | 1992-12-24 | Ivan, Constantin, Prof. Dr.Rer.Nat., 4330 Muelheim, De | |
EP0957250A2 (de) | 1998-05-14 | 1999-11-17 | HMS Artist Scheier OEG | Verbrennungsmotor |
Also Published As
Publication number | Publication date |
---|---|
US20020179037A1 (en) | 2002-12-05 |
EP1195503A3 (de) | 2003-04-16 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
DE102009029808B4 (de) | Verbrennungsmotor | |
DE4003729C2 (de) | Verbrennungsmotor für Wasserstoff | |
DE2510004A1 (de) | Steuereinrichtung fuer verbrennungsmotor | |
DE2941681A1 (de) | Brennkraftkolbenmaschine | |
DE2715302A1 (de) | Rotationskolben-brennkraftmaschine und verfahren zum beeinflussen ihrer arbeitsweise | |
DE2644389A1 (de) | Aufgeladene rotationskolben-brennkraftmaschine | |
DE102017120512B4 (de) | Verfahren zum Betreiben eines Wasserstoffmotors für ein Kraftfahrzeug | |
DE2523712A1 (de) | Doppelkolbenzweitaktbrennkraftmaschine | |
DE2009365A1 (de) | Kraftstoff-Einspritzvorrichtung für eine Diesemaschine | |
DE69003035T2 (de) | Vorrichtung zur Steuerung des Einlassanfangs des unter Druck stehenden Gemisches für eine Brennkraftmaschine und deren Verwendung bei der Zweitaktmaschine. | |
EP1195503A2 (de) | Verbrennungsmotor | |
DE102007039309B4 (de) | Rotationskolbenmaschine | |
DE102016005538B3 (de) | Zweitakt-Brennkraftmaschine | |
DE2325940A1 (de) | Kraftstoffeinspritzsystem fuer rotationskolbenmotoren | |
DE102019128935B4 (de) | Brennkraftmaschine und Verfahren zum Betrieb einer Brennkraftmaschine | |
DE3871789T2 (de) | Verfahren und einrichtung fuer eine zweitakt-brennkraftmaschine mit nachladung. | |
EP1152138A2 (de) | Verfahren zum Betreiben eines Verbrennungsmotors sowie Verbrennungsmotor | |
WO2001053659A1 (de) | Motor | |
DE10054523C2 (de) | Brennkraftmaschine | |
DE1751726A1 (de) | Anordnung fuer die Luft- bzw.Gemischzufuhr von Verbrennungsmaschinen | |
DE3133921A1 (de) | "zweitakt-verbrennungsmotor mit kraftstoffpumpengehaeuse mit verlaengerter extension und variablem verdichtungsraum" | |
EP0957250A2 (de) | Verbrennungsmotor | |
EP1092851A2 (de) | Verbrennungsmotor sowie Verfahren zum Betreiben einer Verbrennungskraftmaschine | |
DE3528620C2 (de) | ||
DE2722176A1 (de) | Verbrennungsmotor mit selbstzuendung |
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 |
|
AK | Designated contracting states |
Kind code of ref document: A2 Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR |
|
AX | Request for extension of the european patent |
Free format text: AL;LT;LV;MK;RO;SI |
|
PUAL | Search report despatched |
Free format text: ORIGINAL CODE: 0009013 |
|
AK | Designated contracting states |
Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR |
|
AX | Request for extension of the european patent |
Extension state: AL LT LV MK RO SI |
|
RIC1 | Information provided on ipc code assigned before grant |
Ipc: 7F 02B 33/08 B Ipc: 7F 02B 75/02 A |
|
AKX | Designation fees paid | ||
REG | Reference to a national code |
Ref country code: DE Ref legal event code: 8566 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN |
|
18D | Application deemed to be withdrawn |
Effective date: 20031019 |