EP1062414A1 - Perfectionnement d'un moteur a combustion interne a injection - Google Patents
Perfectionnement d'un moteur a combustion interne a injectionInfo
- Publication number
- EP1062414A1 EP1062414A1 EP99907676A EP99907676A EP1062414A1 EP 1062414 A1 EP1062414 A1 EP 1062414A1 EP 99907676 A EP99907676 A EP 99907676A EP 99907676 A EP99907676 A EP 99907676A EP 1062414 A1 EP1062414 A1 EP 1062414A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- prechamber
- piston
- protuberance
- cylinder head
- housing
- 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- Withdrawn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
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
- F02B19/00—Engines characterised by precombustion chambers
- F02B19/02—Engines characterised by precombustion chambers the chamber being periodically isolated from its cylinder
- F02B19/04—Engines characterised by precombustion chambers the chamber being periodically isolated from its cylinder the isolation being effected by a protuberance on piston or cylinder head
-
- 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
- F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
- F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two
-
- 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
- F02B75/12—Other methods of operation
- F02B2075/125—Direct injection in the combustion chamber for spark ignition engines, i.e. not in pre-combustion chamber
-
- 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
- F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
- F02B75/18—Multi-cylinder engines
- F02B2075/1804—Number of cylinders
- F02B2075/184—Number of cylinders ten
-
- 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
- F02B23/00—Other engines characterised by special shape or construction of combustion chambers to improve operation
- F02B23/08—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition
- F02B23/10—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition with separate admission of air and fuel into cylinder
- F02B23/101—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition with separate admission of air and fuel into cylinder the injector being placed on or close to the cylinder centre axis, e.g. with mixture formation using spray guided concepts
-
- 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
- F02B3/00—Engines characterised by air compression and subsequent fuel addition
- F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F1/00—Cylinders; Cylinder heads
- F02F1/24—Cylinder heads
- F02F2001/244—Arrangement of valve stems in cylinder heads
- F02F2001/245—Arrangement of valve stems in cylinder heads the valve stems being orientated at an angle with the cylinder axis
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Definitions
- the present invention relates to an improvement to an internal combustion engine with injection into the cylinder, operating according to any cycle, for example four-stroke or two-stroke.
- French patent application No. 2 338 385 already discloses a two-stroke internal combustion engine comprising at least one cylinder in which a reciprocating piston moves, a combustion chamber with variable volume being defined in the cylinder between the piston and the surface facing the cylinder head, at least one intake valve and at least one exhaust valve being placed in the cylinder head opposite the piston.
- the axis of each valve generally forms an angle between about 30 and 60 °, preferably about 45 °, with the axis of the cylinder.
- the injector is generally provided in the center of the cylinder head to inject fuel directly into the cylinder under high pressure.
- the injector is arranged to spray the fuel into the cylinder in jets or in continuous or discontinuous layers, in order to obtain a homogeneous mixture of the fuel with the air supplied via the intake valve.
- the object of the invention is to eliminate the aforementioned drawbacks and to propose an internal combustion injection engine which makes it possible to reduce the consumption of gasoline at idle or at low load, while reducing the formation of NOx, and without altering the engine operation at medium or full load.
- the subject of the invention is an internal combustion injection engine, operating for example according to the four-stroke or two-stroke cycle, comprising at least one cylinder in which a reciprocating piston moves, a variable volume combustion being defined in the cylinder between the piston and the surface facing the cylinder head, the cylinder head comprising a housing facing the piston, in which housing opens a fuel injector, the piston comprising a protuberance at the right of this housing intended to close off, at least partially, when the piston is in the vicinity of the top dead center of its stroke, the opening of the abovementioned housing, characterized in that the piston defines, at top dead center, a combustion prechamber in the housing at least partially closed by said protuberance and a main combustion chamber in the remaining volume of the cylinder located around said protuberance, f ace that, when the engine is idling or at low load, the fuel injected essentially into the prechamber to mix with the air, the remaining volume of the main combustion chamber containing essentially air, whereas, when the engine running at full
- the combustion prechamber is arranged substantially in the center of the cylinder head to reduce the risk of defoimation of the piston.
- the ignited gases leaving the prechamber at the start of the downward driving stroke of the piston will be distributed in the main chamber isotropically in all directions due to the central position from the prechamber, to ignite the rest of the fuel.
- the protuberance has a profile complementary to the housing so that it closes with play and partially penetrates into the prechamber at the end of the upward stroke of the piston.
- the prechamber may have a substantially conical, cylindrical or hemispherical shape.
- the prechamber opens onto a frustoconical peripheral surface of the cylinder head.
- the cylinder head has a concave internal surface in the form of a spherical cap, the polar zone of which defines the opening of the prechamber.
- the protuberance has a substantially frustoconical or cylindrical shape.
- the protrusion can be connected to a flat peripheral annular surface of the piston.
- the protuberance is connected to a peripheral concave annular surface, of axial section substantially in the form of an arc of a circle.
- the protuberance is connected to an intermediate concave annular surface, of axial section substantially in the form of an arc of a circle, said intermediate surface in turn connecting to the small base of a peripheral frustoconical annular surface, the large base is directed opposite the cylinder head.
- the air intake pipe is arranged to introduce into the main chamber droplets of water suspended in 4 air.
- the intake manifold opens into the main chamber so that the water droplets are rotated inside the cylinder around its axis, under the effect of their speed of introduction, and are pressed at the periphery of the chamber by centrifugal force.
- the water droplets are intended to evaporate during combustion to reduce the temperature and thus reduce the production of NOx.
- a concentration of the air / fuel mixture will be obtained in the center of the chamber, which promotes combustion, while the water droplets intended to reduce the temperature are confined to the periphery of the cylinder.
- the protuberance has a concave recess at its top facing the prechamber, to promote the mixing of air and fuel in the prechamber.
- the injector preferably opens at the top of the prechamber.
- the piston has a concave upper annular face substantially semi-circular in axial section, around the central protuberance.
- the prechamber is provided with a spark plug.
- the protrusion may not completely close the prechamber leaving a peripheral space to allow the gases ignited by the spark plug to exit the prechamber and ignite the mixture in the main chamber.
- the main bedroom is also provided with a spark plug. In the latter case, the spark plug of the prechamber can be removed by providing a compression ratio in the prechamber sufficient to cause self-ignition therein.
- the protuberance consists at least in part of an insert of refractory material such as ceramic in line with the prechamber and / or the surface of the prechamber is covered with a ceramic element.
- the roof of the cylinder head is concave, so as to define the abovementioned housing between the top of the cylinder head and the top of the protuberance of the piston, only when the piston is in the vicinity of its top dead center.
- the roof of the cylinder head has a hollow surface to define the aforementioned housing, whatever the position of the piston.
- FIG. 1 is a partial schematic view in section of a cylinder of a two-stroke injection engine according to the invention, near the top dead center;
- FIG. 2 is a view similar to Figure 1, showing a spark plug in the prechamber, the intake and exhaust valves being omitted;
- FIG. 3 is a view similar to Figure 2, showing the injection of fuel into the prechamber when the engine is idling, according to an alternative embodiment of the shape of the piston and the prechamber;
- - Figure 4 shows the cylinder of Figure 3 during the injection of fuel at full or medium engine load;
- Figure 5 is a view similar to Figure 3, showing the movement of gases leaving the prechamber and resulting from the chase, after top dead center;
- FIG. 6 is a view similar to Figure 2, but showing another embodiment of the piston
- Figure 7 is a view similar to Figure 6, showing the introduction of water droplets into the main cylinder chamber;
- FIG. 8 is a view similar to Figure 6, showing an additional spark plug at the main cylinder chamber;
- FIG. 9 is a view similar to Figure 8, the spark plug of the prechamber having been deleted;
- FIG. 12 is a partial schematic view in section of a cylinder, without piston, according to an alternative embodiment of the invention.
- FIG. 13 is a partial diagram in section of a cylinder of another embodiment of the engine of the invention.
- the engine operates here following the two-stroke cycle and 6 comprises at least one cylinder 1 in which a piston 2 alternately moves to define, between the upper face 2a of the piston 2, the internal side walls of the cylinder 1 and the internal surface of a cylinder head 3, a main combustion chamber 4
- the piston 2 is articulated at 5a to a connecting rod 5 which is itself articulated at 5b at the crank of a crankshaft 6, to transform the reciprocating rectilinear movement of the piston 2 into a rotational movement of the shaft 6a of the crankshaft, the crank 5b describing a circle
- the cylinder head 3 is provided with an intake valve 8 which is intended to come to press in a sealed manner against its seat 9a in order to close off an air intake manifold 9 and to deviate from its seat 9a for supplying fresh air to the combustion chamber 4.
- the cylinder head 3 has an exhaust valve 10 which is intended to press against its seat l ia to close off an exhaust pipe 11 and s move away from its seat ia to let the burnt gases escape from the combustion chamber 4.
- the valves 8 and 10 slide in respective guides 12 and 13.
- several intake valves could be provided and / or several exhaust valves.
- the inlet 9a and exhaust ia openings 1a open into the combustion chamber 4 at the level of a frustoconical internal peripheral surface 3a of the cylinder head 3, this frustoconical surface having an apex angle of approximately 130 °.
- the respective axes 14 and 15 of each valve are arranged symmetrically, at 25 ° from the axis 16 of the cylinder.
- the engine can be of the supercharged type, with a compressor, a pump or a fan for supplying the combustion chamber 4 with supercharged air.
- the frustoconical internal peripheral surface 3a of the cylinder head 3 is extended in its center by a housing 17 defining a prechamber at the top of which a fuel injector 18 is provided axially.
- This prechamber 17 has here a shape in inverted or frustoconical cup 3b, the opening of which is directed towards the piston 2.
- the piston 2 has on its upper surface 2a, at its center, a protuberance 19 whose profile is substantially complementary to the housing 17 . 7
- This protuberance 19 defines a peripheral space with the opening of the prechamber so as to only partially close the latter at top dead center.
- This protrusion 19 therefore has a substantially frustoconical shape whose small base is oriented towards the prechamber 17, the top 19a of the protrusion 19 having a substantially concave shape.
- a spark plug 20 is provided on a side wall of the central frustoconical surface 3b of the cylinder head 3 to carry out the ignition at the level of the prechamber 17.
- the piston 2 is shown substantially in the vicinity of its top dead center, where the apex 19a of the protuberance 19 practically blocks the opening of the prechamber 17.
- the height of the protrusion 19 is indicated by h and by H the height of the prechamber 17.
- h is less than H, but in FIG. 3, h is greater than H and, in FIG. 6 , h is substantially equal to H.
- the prechamber 17 is formed here by a central internal surface 103b in the shape of a dome or hemisphere connecting to the small base of the frustoconical peripheral surface 3a of the cylinder head 3.
- the injector 18 is placed at the polar zone of this hemispherical surface 103b in the extension of the axis 16 of the cylinder.
- the central protuberance 19 is not connected to a flat peripheral annular surface 2a, but to a concave annular surface 102a, of axial section substantially in the shape of an arc of a circle, to facilitate the circulation of gases in the main chamber 4.
- the engine is idling, and the fuel injection, shown by dashed lines 21, by the injector 18 takes place in the vicinity of the top dead center of the piston 2, when the apex 19a of the protuberance 9 substantially seals the opening of the hemispherical prechamber 17.
- the fuel injection takes place only in the closed prechamber 17, where a homogeneous air / fuel mixture can be easily obtained.
- the jet of fuel 21 is directed towards the concave surface 19a at the top of the protuberance 19, the fuel will be distributed uniformly through the prechamber 17.
- the engine operates at full or medium load and the fuel injection, shown by phantom 121, by the injector 18 takes place during the upward stroke of the piston 2 to distribute the fuel in the chamber main variable volume 8 4 and the prechamber 17. Thanks to the curved profiles 102a and 19a of the upper surface of the piston 2, the fuel will tend to be distributed uniformly in the chamber 4 to promote the homogeneity of the mixture.
- the arrows 22 represent the movement of the ignited gases leaving the prechamber 17, at the start of the driving stroke of the piston 2.
- the ignited gases 22 leaving the prechamber 17 have enough energy to ignite the rest of the mixture in the main chamber 4, which reduces the delay in inflammation.
- the outgoing ignited gases 22 mix with the air present in the main chamber 4.
- the piston 2 has on its upper face, surrounding the protuberance 19, an annular concave shape 202a, the profile of which has a radius of curvature less than that of the profile 102a, so that a portion of frustoconical annular surface 202b comes to marry the shape of the surface 103a of the cylinder head 3, in the vicinity of the top dead center, on the periphery of the piston 2, in order to drive the mixture towards the center of the chamber 4 as indicated by the arrows 122.
- This surface 103a here has a concave shape substantially in the form of a spherical cap, the polar zone of which is opened by the housing 17, so that the main chamber 4 has a maximum volume for a minimum heat exchange surface, at top dead center.
- FIGS. 1 to 5 an alternative embodiment of the piston is shown, in which the protrusion 119 of the piston has an axial extension greater than the height of the frustoconical peripheral surface 3a of the cylinder head 3, so that the protuberance 119 can partially penetrate inside the prechamber 17, when the piston is in the vicinity of its top dead center.
- the piston of FIGS. 1 to 5 had an axial extension substantially equal to the height of the frustoconical surface 3a of the cylinder head 3.
- the ignited gases in the prechamber 17 will come out of it with a slight delay, the time that the protrusion 119 comes completely out of the prechamber 17, causing an increase in the volume of the prechamber 17 and therefore an expansion of the ignited gases.
- FIG. 7 there is also shown the air intake pipe 9 which is intended to introduce into the main chamber 4 droplets of water 23 suspended in the air admitted into the main chamber 4.
- the intake manifold 9 has a shape such that the air charged with water droplets is introduced into the main chamber 4 with a 9 rotational movement substantially coaxial with the cylinder 1, so as to press the water droplets on the periphery of the internal surface of the cylinder 1 by centrifugal force and to concentrate the lighter air in the center of the chamber 4.
- an additional spark plug 120 is provided at the level of the main chamber 4 in order to be able to light the main chamber 4 and the prechamber 17 at full or medium load at the same time, or with a slight offset.
- the spark plug of the prechamber 17 has been deleted, because the ignition in the latter is provided for to be done automatically by adjusting the difference in the compression ratio between the main chamber 4 and the prechamber 17.
- the invention applies to an engine whatever its cycle, the invention is particularly advantageous in a two-stroke engine with valves, because the protuberance of the piston does not risk, in this case, to interfere with the valves, because at near top dead center, all valves are closed.
- FIG. 10 shows an alternative embodiment of the piston for the engine of the invention.
- the piston 2 has a flat upper peripheral surface 2a, in the center of which is mounted a ceramic insert 219 defining the aforementioned protuberance.
- the protrusion 219 has a concave upper surface 219a, analogously to the protuberance 19 of FIG. 1.
- another variant of piston 2 has at the center of its flat upper surface 2a a protuberance 319 provided at its apex with 'a ceramic plate 319a defining a concave surface facing the prechamber 17 of the cylinder head 3.
- the frustoconical surface of the prechamber 17 of the cylinder head 3 is covered with a ceramic element 24 of complementary frustoconical shape, in the center of which is an orifice for the passage of the injector 18.
- the pistons of the figures 10 and 11 can be used in conjunction with cylinder 1 illustrated in FIG. 12.
- the inserts in 10 ceramic 219 and 319a as well as the ceramic element 24 are intended to thermally insulate the prechamber 17, in the vicinity of the top dead center, in order to minimize the energy losses, mainly when it is desired to obtain a self-ignition in the chamber 17, in the absence of the spark plug 20, as is the case in the embodiment of FIG. 9.
- the roof 3a of the cylinder head 3 no longer has a recess formed in the hollow on its surface, because here the housing 117 is formed only when the piston 2 arrives in the vicinity of its TDC, the housing 117 being thus defined between the top 19a of the protrusion 19 of the piston and the top of the roof 3 has the cylinder head 3.
- the jet of fuel coming from the injector 18 can rebound on the concave surface 19a of the protrusion 19 and remain confined in the housing 117, forming a rich zone near the spark plug 20.
- the protrusion 19 thus separates the housing 117 from the rest of the main chamber 4 of the cylinder.
- the effective volume of the housing 17 or 117 is less than 40%, preferably 10%, of the remaining volume of the main bedroom 4, in the vicinity of the TDC.
- the small volume of rich mixture thus formed generates, once ignited, enough energy, to make an engine idle, and allows, for low engine loads, switch on the lean mixture in the main bedroom. Otherwise, the lean mixture in the main chamber could not be ignited by the candle, since the energy supplied by the spark would not be sufficient to initiate combustion.
- the existence of the prechamber is also beneficial, since the ignited gases leaving the prechamber will have a high energy making it possible to mix and ignite quickly the rest of the fuel contained in the chamber.
- main combustion for example almost 90% of the fuel injected. This will reduce the ignition delay and reduce the rattling noise, because before the self-ignition starts, the flame front will have already swept the entire combustion chamber.
- the size of the prechamber and the height of the protuberance can be modified, so as to obtain a good compromise for the passage of combustion between a regime at 1 1 idle, and a low, medium or heavy load speed. In practice, the larger the volume of the prechamber, the more the combustion under low load will take place in the prechamber.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Combustion Methods Of Internal-Combustion Engines (AREA)
Abstract
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR9803045A FR2776016B1 (fr) | 1998-03-12 | 1998-03-12 | Perfectionnement d'un moteur a combustion interne a injection |
FR9803045 | 1998-03-12 | ||
PCT/FR1999/000531 WO1999046492A1 (fr) | 1998-03-12 | 1999-03-10 | Perfectionnement d'un moteur a combustion interne a injection |
Publications (1)
Publication Number | Publication Date |
---|---|
EP1062414A1 true EP1062414A1 (fr) | 2000-12-27 |
Family
ID=9523969
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP99907676A Withdrawn EP1062414A1 (fr) | 1998-03-12 | 1999-03-10 | Perfectionnement d'un moteur a combustion interne a injection |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP1062414A1 (fr) |
FR (1) | FR2776016B1 (fr) |
WO (1) | WO1999046492A1 (fr) |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19963175A1 (de) | 1999-12-27 | 2001-07-12 | Gruenenthal Gmbh | Verwendung von substituierten 4-Amino-1-phenylbutan-2-ol-Verbindungen als Arzneimittel |
US6478006B1 (en) * | 2000-07-04 | 2002-11-12 | Lars G. Hedelin | Working cycle for a heat engine, especially an internal combustion engine, and an internal combustion engine |
FR2849901B1 (fr) * | 2003-01-13 | 2005-03-11 | Renault Sa | Cylindre pour moteur a combustion interne et allumage par compression et moteur comprenant un tel cylindre |
FR2908824A1 (fr) * | 2006-11-17 | 2008-05-23 | Bernard Louis Guy Ruaud | Dispositif permettant de demarrer la combustion d'un melange air/carburant extrement pauvre dans les moteurs a allumage commande et injection directe haute pression |
NL1034362C2 (nl) * | 2007-09-11 | 2009-03-12 | Valcon Motor Company B V | Verbrandingsmotor alsmede een voertuig voorzien van een dergelijke verbrandingsmotor. |
CN104727924A (zh) * | 2013-12-21 | 2015-06-24 | 窦斌 | 一种分区燃烧的汽油机燃烧室 |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR593837A (fr) * | 1925-02-25 | 1925-09-01 | Dispositif permettant la pulvérisation pneumatique automatique des combustibles dans les moteurs à combustion interne | |
GB388262A (en) * | 1932-05-24 | 1933-02-23 | Alfred Wtseman Ltd | Improvements in or relating to the combustion chambers and pistons of internal combustion engines of the diesel or compression ignition type |
DE639705C (de) * | 1934-01-09 | 1936-12-11 | Eugen Thomas Jr | Luftverdichtende Einspritzbrennkraftmaschine |
FR2338385A1 (fr) | 1976-01-15 | 1977-08-12 | Melchior Jean | Perfectionnements aux moteurs a combustion interne a deux temps |
US4069794A (en) * | 1976-08-10 | 1978-01-24 | Robert Denney Jordan | Positive power control internal combustion engine |
EP0645529B1 (fr) * | 1993-09-28 | 1998-01-07 | Isuzu Ceramics Research Institute Co., Ltd. | Moteur à isolation thermique |
-
1998
- 1998-03-12 FR FR9803045A patent/FR2776016B1/fr not_active Expired - Fee Related
-
1999
- 1999-03-10 WO PCT/FR1999/000531 patent/WO1999046492A1/fr not_active Application Discontinuation
- 1999-03-10 EP EP99907676A patent/EP1062414A1/fr not_active Withdrawn
Non-Patent Citations (1)
Title |
---|
See references of WO9946492A1 * |
Also Published As
Publication number | Publication date |
---|---|
FR2776016B1 (fr) | 2000-06-30 |
WO1999046492A1 (fr) | 1999-09-16 |
FR2776016A1 (fr) | 1999-09-17 |
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Legal Events
Date | Code | Title | Description |
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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 |
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17P | Request for examination filed |
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