EP0754268B1 - Zweitakt dieselbrennkraftmaschine mit einem spiralförmigen luftanzugskanal - Google Patents

Zweitakt dieselbrennkraftmaschine mit einem spiralförmigen luftanzugskanal Download PDF

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Publication number
EP0754268B1
EP0754268B1 EP96900828A EP96900828A EP0754268B1 EP 0754268 B1 EP0754268 B1 EP 0754268B1 EP 96900828 A EP96900828 A EP 96900828A EP 96900828 A EP96900828 A EP 96900828A EP 0754268 B1 EP0754268 B1 EP 0754268B1
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EP
European Patent Office
Prior art keywords
cylinder
port
disposed
diesel engine
admission port
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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.)
Expired - Lifetime
Application number
EP96900828A
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English (en)
French (fr)
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EP0754268A1 (de
Inventor
Pierre-Antoine Jeandupeux
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Individual
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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
    • F02B25/00—Engines characterised by using fresh charge for scavenging cylinders
    • F02B25/14—Engines characterised by using fresh charge for scavenging cylinders using reverse-flow scavenging, e.g. with both outlet and inlet ports arranged near bottom of piston stroke
    • 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
    • F02B2275/00—Other engines, components or details, not provided for in other groups of this subclass
    • F02B2275/14—Direct injection into 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
    • 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

Definitions

  • the principle of the invention relates to a diesel engine with two-stroke with volute air intake channel, and more particularly to a diesel engine which has a channel air intake which has a spiral shape and is arranged on part of the circumference of the wall of the cylinder, the intake channel which is arranged at the location of the bottom dead center of the piston being connected to the cylinder by channels of transfer which are separated by walls in the shape of blades.
  • two-stroke diesel engines operate on the principle that the air intake, which is the oxidizer, is constant, and the fuel injection is variable.
  • the action on the accelerator pedal adjusts the amount of fuel which is distributed.
  • the power of two-stroke diesel engines is dependent on the quality of the oxidizer-fuel mixture, the optimal power being obtained when each molecule of fuel can ally to an oxidizer molecule.
  • the mixing of the oxidizer in the cylinder is essential to ensure that an optimal proportion of fuel molecules can ally with molecules of oxidizer. Insufficient mixing of the oxidizer results in a lack of homogeneity of the oxidizer-fuel mixture which reflected in the fact that a certain proportion of the fuel is not burnt and by the fact that the engine whose combustion is incomplete, works with a large excess of oxidizer.
  • valve-light combinations for example, the lights being intended for the intake of oxidizer and the valves to the exhaust of the burnt gases or vice versa.
  • An embodiment known as the Schnurle principle has several lights which are arranged in a way symmetrical on each side of the cylinder. This form of execution has allowed to bring some increase in brewing and by therefore power and efficiency. However, the arrival symmetrical oxidant in the cylinder does not create sufficient mixing which again results in a strong loss of power and efficiency relative to power and optimal performance.
  • the aims of the present invention therefore consist in remedying to the aforementioned drawbacks of known diesel engines.
  • the two-stroke diesel engine with volute air intake channel comprises an air intake channel which is arranged over a large part of the circumference of the cylinder wall and which is connected to the cylinder by transfer channels which are separated from each other by vanes.
  • the air is propelled into the volute intake channel by a turbo-compressor for example.
  • the vanes separating the transfer channels are arranged at angles to the axis of the cylinder. In this way the air admitted when the piston is in bottom dead center, is propelled into the cylinder with a very strong vortex movement. This circular vortex movement is supplemented by an upward movement caused by the fact that the transfer channels gradually present an upward angle of the cylinder.
  • the first transfer channel is arranged so that the air is propelled horizontally into the cylinder and the last channel is arranged so that the air is propelled at an angle of 45 ° upwards by example.
  • the strong vortex and circular movement and the progressive upward mixing of the air thus created in the cylinder are further accentuated by the fact that the volume of air admitted into the cylinder becomes progressively concentrated, by the displacement of the piston towards the high, in the combustion chamber whose volume is much smaller than the cylinder.
  • the very strong mixing of the air thus created makes it possible to guarantee a very significant improvement in the homogeneity of the oxidizer-fuel mixture which makes it possible to approach optimum power and efficiency.
  • the very significant improvement in power and efficiency obtained by the principle of the invention allows, at power -equal supply compared to known two-stroke diesel engines, significantly reduce consumption and pollution.
  • the principle of the invention allows significantly increase engine power while avoiding, by complete combustion, that this increase in power does result in increased pollution.
  • Figures 1 and 2 are sectional views, respectively vertical and horizontal, cylinder and piston of an engine two-stroke diesel with an air intake channel in volute.
  • Figures 3, 4 and 5 are vertical section views of transfer channels, respectively at the start, in a portion intermediate and at the end of the air intake channel.
  • Figures 6 and 7 are sectional views, respectively vertical and horizontal, of an embodiment of a cylinder comprising an exhaust channel with closure device.
  • Figures 8 and 9 are sectional views, respectively vertical and horizontal, of a cylinder with a channel volute air intake and an exhaust channel which also has a scroll shape.
  • the wall of a cylinder 2 has an air intake channel 1 which has a scroll shape.
  • the air intake channel 1 is arranged on the much of the circumference of the cylinder wall 2.
  • the air intake channel 1 is connected to the inside of cylinder 2 by transfer channels, for example 3, 4 and 5.
  • the transfer channels are separated from each other by vanes, by example vanes 6, 7 and 8.
  • the vanes are arranged in a angle with respect to the central axis of the cylinder.
  • the canals of transfer are arranged at the bottom dead center of a piston 9, so that they are open when the piston found in bottom dead center.
  • the head of the piston 9 has a combustion chamber 10 in which the fuel-oxidant mixture takes place when the piston is in neutral high and when the fuel injector 11 injects the fuel.
  • combustion of the fuel-oxidant mixture occurs through self-ignition which is caused by the combined effects of the very strong pressure and temperature in the combustion chamber.
  • air, or oxidizer is powered in the intake channel 1 by a turbo-compressor, for example.
  • the air thus propelled into the intake channel 1 is propelled into cylinder 2 by the transfer channels.
  • the vanes that separate the transfer channels are arranged in a angle relative to the central axis of the cylinder so that the air is propelled inside the cylinder with a very strong vortex movement around the cylinder axis.
  • Air or oxidizer is allowed when the piston discovers the transfer.
  • the vortex movement of air or oxidizer is still greatly increased during the rise of the piston, due the difference in volume between the cylinder and the combustion.
  • the intake channel 1 has a volute shape and the intake channel becomes progressively smaller by so that the air pressure propelled by the channels which are sufficient at the end of the air intake channel.
  • Figure 3 shows a channel transfer 3 which is arranged at the start of the intake channel 1.
  • the upper and lower faces of the transfer channel 3 are arranged in the horizontal plane and in this case the air is propelled horizontally in the cylinder.
  • Figure 4 shows a transfer channel 4 which is arranged in a portion intermediate of the intake channel 1.
  • the upper faces and bottom of transfer channel 4 are arranged at an angle upwards from the horizontal plane.
  • Figure 5 shows a transfer channel 5 which is arranged at the end of the channel 1.
  • the upper and lower sides of the transfer 5 are arranged with a strong upward angle by compared to the horizontal plane.
  • the angle of the faces upper and lower transfer channels increase gradually from 0 ° for the first channel to 45 °, by example, for the last channel. In this way, in addition to the vortex movement around the cylinder axis, the air is gradually propelled up the cylinder which further strengthens the vortex movement.
  • the very strong vortex movement is amplified in the combustion chamber when the piston is in neutral high, and this strong vortex movement guarantees a optimal fuel-oxidizer mixture when fuel is distributed. This optimal mixture guarantees combustion complete which allows to obtain a very important improved performance which also results in significant pollution reduction.
  • the air intake channel 1 has a volute shape, or a spiral shape, the intake channel being progressively arranged downward in depending on the angle of the transfer channels.
  • Figures 1 and 2 do not show exhaust.
  • the exhaust is conventional and can consist of a valve arranged in the upper part of the cylinder by example.
  • Figures 6 and 7 show an embodiment of a cylinder 14 which also includes an injector 11, with a piston 9 which has a combustion chamber 10, the piston being in this case shown in top dead center.
  • the air intake channel 12, which is connected inside the cylinder by transfer channels, for example the first channel 13, is shorter than the intake channel shown in FIGS. 1 and 2.
  • An exhaust channel 15 is arranged, in the same horizontal plane, between the beginning and the end of the canal air intake. According to this form of execution, it is the fort eddy air movement which guarantees the evacuation of burnt gases.
  • This embodiment includes a obturation device 16 which temporarily closes the channel exhaust in the first intake phase so as to prevent some of the admitted air from escaping through the channel exhaust.
  • Figures 8 and 9 show an embodiment of a cylinder 16 which comprises an intake channel 17, which comprises transfer channels, for example transfer channel 18, which is shorter than on the forms of executions shown on Figures 1, 2, 6 and 7.
  • This embodiment comprises, on a part of the circumference of the cylinder, an exhaust channel 19 which is connected to the cylinder by transfer channels, the channel transfer 20 for example.
  • Channel transfer channels exhaust are separated by vanes which form an angle by relative to the central axis of the cylinder. This form of execution with exhaust channel can allow better evacuation of burnt gases, depending on the vortex movement of the air admitted.
  • the number of different transfer channels can be varied according to the different engine designs, as well as the angles of the blades or of the upper or lower faces of the transfer channels.
  • the principle of the invention is independent of the number of engine cylinder, the principle can be applied as well single cylinder engines than multiple engines cylinders.

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)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)

Claims (5)

  1. Zweitakt-Dieselmotor mit spiralförmigem Lufteinlaßkanal, der einen Zylinder (2) aufweist, welcher mit Eintrittskanälen versehen ist, die am unteren Totpunkt des Kolbens (9) angeordnet sind und der eine Verbrennungskammer (10) enthält, dadurch gekennzeichnet, daß ein spiralförmiger Lufteinlaßkanal (1) am Ort des unteren Totpunktes des Kolbens (9) entlang des größten Teils des Umfangs der Wand des Zylinders (2) angeordnet ist, wobei der Lufteinlaßkanal mit dem Zylinder über Eintrittskanäle verbunden ist, die voneinander mittels Schaufeln getrennt sind, die einen Winkel zur Mittenachse des Zylinders derart aufweisen, daß die den Lufteinlaßkanal und die Eintrittskanäle durchströmende Luft in den Zylinder mit einer starken Verwirbelung um die Mittenachse des Zylinders herum einströmt und daß die oberen und unteren Flächen der Eintrittskanäle zunehmend einen nach oben gerichteten Winkel aufweisen, wobei die oberen und unteren Flächen des Eintrittskanals, der am Anfang des Luftansaugkanals angeordnet ist, einen Winkel Null oder einen sehr kleinen Winkel aufweisen bezüglich der waagrechten Ebene und die oberen und unteren Flächen des Kanals, der am Ende des Lufteinlasskanals angeordnet ist, einen großen Winkel bezüglich der waagrechten Ebene aufweisen, sodass die zunehmend zum Oberteil des Zylinders hin strömende Luft eine Flotationsbewegung erzeugt.
  2. Dieselmotor nach Anspruch 1, dadurch gekennzeichnet, daß der spiralförmige Lufteinlaßkanal zunehmend von seinem Anfang hin zu seinem Ende abnimmt.
  3. Dieselmotor nach einem der Ansprüche 1 bis 2, dadurch gekennzeichnet, daß der Lufteinlaßkanal eine Spiralform aufweist, die zunehmend nach unten verläuft.
  4. Dieselmotor nach Anspruch 1, dadurch gekennzeichnet, daß ein Auslaßkanal in derselben waagrechten Ebene wie die Lufteintrittskanäle angeordnet ist und daß dieser Auslaßkanal entlang eines Teils des Umfangs der Wand des Zylinders zwischen dem Anfang und dem Ende des Lufteinlaßkanals angeordnet ist.
  5. Dieselmotor nach Anspruch 1, dadurch gekennzeichnet, daß ein Auslaßkanal an der Stelle des unteren Totpunktes des Kolbens an einem Teil des Umfangs der Wand des Zylinders angeordnet ist und daß dieser Auslaßkanal mit dem Zylinder über Durchlaßkanäle verbunden ist, die durch Schaufeln voneinander getrennt sind, welche einen Winkel mit der Mittenachse des Zylinders bilden, sodass die Abfuhr der verbrannten Gase als Funktion der im Zylinder erzeugten Verwirbelung erleichtert wird.
EP96900828A 1995-02-06 1996-02-06 Zweitakt dieselbrennkraftmaschine mit einem spiralförmigen luftanzugskanal Expired - Lifetime EP0754268B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
CH321/95 1995-02-06
CH32195A CH690307A5 (fr) 1995-02-06 1995-02-06 Moteur diesel à deux temps avec canal d'admission d'air en volute.
PCT/CH1996/000045 WO1996024757A1 (fr) 1995-02-06 1996-02-06 Moteur diesel a deux temps avec canal d'admission d'air en volute

Publications (2)

Publication Number Publication Date
EP0754268A1 EP0754268A1 (de) 1997-01-22
EP0754268B1 true EP0754268B1 (de) 1999-05-06

Family

ID=4184361

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96900828A Expired - Lifetime EP0754268B1 (de) 1995-02-06 1996-02-06 Zweitakt dieselbrennkraftmaschine mit einem spiralförmigen luftanzugskanal

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Country Link
EP (1) EP0754268B1 (de)
AU (1) AU4480296A (de)
CH (1) CH690307A5 (de)
DE (1) DE69602317T2 (de)
WO (1) WO1996024757A1 (de)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2496479A (en) * 2011-11-11 2013-05-15 Ecomotors Internat Inc Intake System for an Opposed-Piston Engine

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB321514A (en) * 1928-09-28 1929-11-14 Charles Gordon Curtis Improvements in or relating to two-cycle internal combustion engines
FR724741A (fr) * 1930-11-13 1932-05-02 Perfectionnement aux moteurs à combustion interne à deux temps
GB541368A (en) * 1939-08-04 1941-11-25 Sulzer Ag Improvements in or relating to cylinders for internal combustion engines operating on the two-stroke cycle
US3059626A (en) * 1960-03-15 1962-10-23 Nordberg Manufacturing Co Two-cycle scavenging system

Also Published As

Publication number Publication date
DE69602317D1 (de) 1999-06-10
CH690307A5 (fr) 2000-07-14
WO1996024757A1 (fr) 1996-08-15
DE69602317T2 (de) 2000-01-13
EP0754268A1 (de) 1997-01-22
AU4480296A (en) 1996-08-27

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