EP0370999A1 - Two-stroke internal combustion engine - Google Patents

Two-stroke internal combustion engine Download PDF

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Publication number
EP0370999A1
EP0370999A1 EP89890302A EP89890302A EP0370999A1 EP 0370999 A1 EP0370999 A1 EP 0370999A1 EP 89890302 A EP89890302 A EP 89890302A EP 89890302 A EP89890302 A EP 89890302A EP 0370999 A1 EP0370999 A1 EP 0370999A1
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EP
European Patent Office
Prior art keywords
flow
internal combustion
combustion engine
stroke internal
guide surfaces
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Withdrawn
Application number
EP89890302A
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German (de)
French (fr)
Inventor
Diethard Dipl.-Ing. Plohberger
Karl Dipl.-Ing. Wojik
Klaus Dr. Landfahrer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
AVL List GmbH
Original Assignee
AVL List GmbH
AVL Gesellschaft fuer Verbrennungskraftmaschinen und Messtechnik mbH
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Publication of EP0370999A1 publication Critical patent/EP0370999A1/en
Withdrawn legal-status Critical Current

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    • 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 
    • F02F1/18—Other cylinders
    • F02F1/22—Other cylinders characterised by having ports in cylinder wall for scavenging or charging
    • 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
    • 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

Definitions

  • the invention relates to a two-stroke internal combustion engine with piston-controlled inlet channels for the fresh charge, which have a plurality of flow control surfaces in the region of their sections directly adjoining the cylinder and with at least one outlet channel for the combustion gases.
  • the object of the invention is to avoid these disadvantages and to prevent the flushing flow from deviating from the specified direction both in the vertical and in the horizontal direction.
  • the invention consists primarily in the fact that the flow guide surfaces are at an angle, preferably at right angles, to one another and thus form a flow straightener.
  • the number of flow guide surfaces for the flushing flow is thus increased many times over compared to the version without a flow straightener, so that the flushing medium emerging from the flushing channel essentially adheres to the direction specified by the duct and flow straightener.
  • the flow straighteners according to the invention result in increased friction losses in the flushing flow, these are more than compensated for by the considerable reduction in fresh charge losses, which is clearly shown in an improvement in engine performance and in fuel consumption and exhaust gas emissions.
  • the flow guide surfaces can be arranged flat and in parallel in at least two groups and in groups at such angles to one another that they form closed flow channels.
  • Flow channels with differently sized and differently shaped cross sections can thus be produced in a simple manner and the behavior of the flushing flow can thus be largely predetermined.
  • An advantageous embodiment according to the invention consists in that the part of the intake manifold adjoining the cylinder is made cylindrical and the flow straightener is inserted as one piece in it.
  • the fresh charge losses to be avoided can also be favorably influenced by the fact that the imaginary extensions of the flow control surfaces, which are arranged parallel to the cylinder axis, converge centrally to a point in the cylinder at the half opposite the outlet.
  • the flow channels formed can be rectangular in cross section, preferably square, but also hexagonal in cross section and honeycomb-shaped to form the flow straightener.
  • the flow guide surfaces be made very thin-walled and preferably made of sheet metal.
  • a two-stroke internal combustion engine of known design is shown in half, the cylinder being designated 1, the cylinder head 2 and the piston 3.
  • the piston 3 controls the outlet channel 4 and the two inlet channels 5 arranged on both sides of the outlet channel 4.
  • the rinsing flow when the piston 3 is moved downwards in accordance with the arrow 6 is indicated by the flow lines 7.
  • the flow is deflected from the theoretical flow direction given by the channel boundaries 8, forming vortices, which are denoted by 7'. This causes increased friction and fresh charge losses.
  • flow guide surfaces 11 are arranged in the area 9 of the elbow 10 of the inlet channels 5 and run parallel to the cylinder axis 12. Transversely to this, flow guide surfaces 13 are provided, which together with the flow guide surfaces 11 form flow channels 14, which cause the flow illustrated by the arrows 15 to remain unaffected by the piston edge 3 '. This also eliminates the unfavorable effects in terms of engine performance, fresh charge losses and exhaust gas emissions.
  • FIGS. 5 and 6 shows two variants according to the invention, which have in common that the areas 9 of the elbows 10 of the inlet channels 5 are cylindrical and therefore the manufacture and assembly of the flow straightener 16 is simplified.
  • inflow channels 18 and 19 are provided on both sides of the outlet channel 4, which are also equipped with flow guide surfaces 11, 13 and 20, 21 in the area 9 of the manifold 10.
  • the inlet channels 18 are directed against the cylinder wall 22 opposite the outlet channel 4, whereas the inlet channels 19 are directed approximately against the axis 12 of the cylinder.
  • the version a) has flow channels with a square cross section
  • the version b) has flow channels 14 ', which are arranged in a honeycomb-like manner and are hexagonal.
  • the embodiment according to c) has flow channels 14 ⁇ with a rectangular cross section, which are arranged offset in the vertical direction by half the length of the cross section. The selection of the best version is generally determined by experiment.

Abstract

Bei bekannten Zweitakt-Brennkraftmaschine mit vom Kolben (3) gesteuerten Einlaßkanälen (5) für die Frischladung und mindestens einem Auslaßkanal (4) für die Verbrennungsgase ergibt sich durch den Einfluß der Kolbenkante (3') eine Abweichung der tatsächlichen Strömungsrichtung (7) von der durch die Kanalbegrenzungen (8) gegebenen theoretischen Strömungsrichtung. Dabei wird die Spülströmung mehr in Richtung des Auslaßkanals (4) und des Zylinderkopfes (2) umgelenkt, was erhöhte Frischladungsverluste verursacht. Dieser Umstand führt zu einer deutlichen Verschlechterung des Spülerfolges und damit der Motorleistung, des Kraftstoffverbrauches sowie der Abgasemissionen. Diese Nachteile werden erfindungsgemäß dadurch vermieden, daß die Strömungsleitflächen (11,13;20,21) im Winkel, vorzugsweise im rechten Winkel, zueinander stehen und so einen Strömungsgleichrichter (16) bilden.In known two-stroke internal combustion engines with inlet channels (5) controlled by the piston (3) for the fresh charge and at least one outlet channel (4) for the combustion gases, the influence of the piston edge (3 ') results in a deviation of the actual flow direction (7) from the given by the channel boundaries (8) theoretical flow direction. The flushing flow is deflected more in the direction of the outlet duct (4) and the cylinder head (2), which causes increased fresh charge losses. This leads to a significant deterioration in the washing result and thus the engine performance, fuel consumption and exhaust emissions. According to the invention, these disadvantages are avoided in that the flow guide surfaces (11, 13; 20, 21) are at an angle, preferably at right angles, to one another and thus form a flow straightener (16).

Description

Die Erfindung bezieht sich auf eine Zweitakt-Brennkraftma­schine mit vom Kolben gesteuerten Einlaßkanälen für die Frischladung, die im Bereich ihrer unmittelbar an den Zylinder anschließenden Abschnitte mehrere Strömungsleitflächen aufwei­sen und mit mindestens einem Auslaßkanal für die Verbrennungs­gase.The invention relates to a two-stroke internal combustion engine with piston-controlled inlet channels for the fresh charge, which have a plurality of flow control surfaces in the region of their sections directly adjoining the cylinder and with at least one outlet channel for the combustion gases.

Bei solchen bekannten Brennkraftmaschinen mit Umkehrspülung und vom Kolben gesteuerten Ein- und Auslaßkanälen ergibt sich durch den Einfluß der Kolbenkante eine Abweichung der tatsäch­lichen Strömungsrichtung von der durch die Kanalbegrenzungen gegebenen theoretischen Strömungsrichtung. Dabei wird die Spülströmung mehr in Richtung des Auslaßkanals und des Zy­linderkopfes umgelenkt, was erhöhte Frischladungsverluste ver­ursacht. Dieser Umstand führt zu einer deutlichen Verschlech­terung des Spülerfolges und damit der Motorleistung, des Kraftstoffverbrauches sowie der Abgasemissionen.In such known internal combustion engines with reverse purging and piston-controlled inlet and outlet channels, the influence of the piston edge results in a deviation of the actual flow direction from the theoretical flow direction given by the channel limits. The purge flow is deflected more towards the exhaust port and the cylinder head, which causes increased fresh charge losses. This leads to a significant deterioration in the washing result and thus the engine performance, fuel consumption and exhaust emissions.

Es ist auch die Anwendung von Leitschaufeln im Einlaßkanal ei­nes kurbelkastengespülten Zweitaktmotors bekannt. Zweck hiebei ist die Verbesserung der Richtwirkung des Einlaßkanals zur Verhinderung des Einströmens von Frischgemisch in das Kurbel­gehäuse des Motors. Der Einlaßkanal ist zu diesem Zweck mit Leitschaufeln in vertikaler Richtung unterteilt. Die beabsich­tigte Wirkung wird hiedurch jedoch nur zum kleineren Teil er­reicht.The use of guide vanes in the inlet duct of a crankcase-flushed two-stroke engine is also known. The purpose of this is to improve the directivity of the inlet channel to prevent fresh mixture from flowing into the crankcase of the engine. For this purpose, the inlet duct is divided in the vertical direction with guide vanes. However, the intended effect is only achieved to a minor extent.

Der Erfindung liegt die Aufgabe zugrunde, diese Nachteile zu vermeiden und das Abweichen der Spülströmung von der vorge­gebenen Richtung sowohl in vertikaler als auch in horizontaler Richtung zu verhindern. Die Erfindung besteht in erster Linie darin, daß die Strömungsleitflächen im Winkel, vorzugsweise im rechten Winkel, zueinander stehen und so einen Strömungs­gleichrichter bilden. Damit wird die Anzahl der Strö­mungsleitflächen für die Spülströmung gegenüber der Ausführung ohne Strömungsgleichrichter um ein Vielfaches erhöht, sodaß das aus dem Spülkanal austretende Spülmedium im wesentlichen die vom Kanal und Strömungsgleichrichter vorgegebene Richtung einhält. Durch die erfindungsgemäßen Strömungsgleichrichter treten zwar erhöhte Reibungsverluste bei der Spülströmung auf, jedoch werden diese durch die erhebliche Verminderung der Frischladeverluste mehr als aufgewogen, was sich in einer Ver­besserung der Motorleistung sowie des Kraftstoffverbrauches und der Abgasemissionen deutlich zeigt.The object of the invention is to avoid these disadvantages and to prevent the flushing flow from deviating from the specified direction both in the vertical and in the horizontal direction. The invention consists primarily in the fact that the flow guide surfaces are at an angle, preferably at right angles, to one another and thus form a flow straightener. The number of flow guide surfaces for the flushing flow is thus increased many times over compared to the version without a flow straightener, so that the flushing medium emerging from the flushing channel essentially adheres to the direction specified by the duct and flow straightener. Although the flow straighteners according to the invention result in increased friction losses in the flushing flow, these are more than compensated for by the considerable reduction in fresh charge losses, which is clearly shown in an improvement in engine performance and in fuel consumption and exhaust gas emissions.

In weiterer Ausgestaltung der Erfindung können die Strömungs­leitflächen eben und in mindestens zwei Gruppen jeweils paral­lel und gruppenweise in solchen Winkeln zueinander angeordnet sein, daß sie geschlossene Strömungskanäle bilden. Es können so Strömungskanäle mit verschieden großen und verschieden ge­formten Querschnitten auf einfache Weise hergestellt und damit das Verhalten der Spülströmung weitgehend vorbestimmt werden.In a further embodiment of the invention, the flow guide surfaces can be arranged flat and in parallel in at least two groups and in groups at such angles to one another that they form closed flow channels. Flow channels with differently sized and differently shaped cross sections can thus be produced in a simple manner and the behavior of the flushing flow can thus be largely predetermined.

Eine vorteilhafte Ausführung gemäß der Erfindung besteht darin, daß der an den Zylinder anschließende Teil der Einlaß­krümmer zylindrisch ausgeführt und der Strömungsgleichrichter als ein Stück in diesen eingesetzt ist.An advantageous embodiment according to the invention consists in that the part of the intake manifold adjoining the cylinder is made cylindrical and the flow straightener is inserted as one piece in it.

Die zu vermeidenden Frischladungsverluste können nach einem weiteren Merkmal der Erfindung auch dadurch günstig beeinflußt werden, daß die gedachten Verlängerungen der Strö­mungsleitflächen, welche parallel zur Zylinderachse angeordnet sind, zentrisch auf einen im Zylinder an der dem Auslaß gegenüberliegenden Hälfte liegenden Punkt zusammenlaufen. Im Rahmen der Erfindung können die gebildeten Strömungskanäle im Querschnitt rechteckig, vorzugsweise quadratisch, aber auch im Querschnitt sechseckig und bienenwabenartig zum Strömungs­gleichrichter zusammengesetzt sein.According to a further feature of the invention, the fresh charge losses to be avoided can also be favorably influenced by the fact that the imaginary extensions of the flow control surfaces, which are arranged parallel to the cylinder axis, converge centrally to a point in the cylinder at the half opposite the outlet. In the context of the invention, the flow channels formed can be rectangular in cross section, preferably square, but also hexagonal in cross section and honeycomb-shaped to form the flow straightener.

Schließlich empfiehlt es sich, die Strömungsleitflächen sehr dünnwandig auszuführen und vorzugsweise aus Blech herzustel­len.Finally, it is recommended that the flow guide surfaces be made very thin-walled and preferably made of sheet metal.

Die Erfindung wird nachfolgend anhand der Zeichnungen an eini­gen Ausführungsbeispielen näher erläutert. Es zeigen:

  • Fig. 1 schematisch eine Zweitakt-Brennkraftmaschine mit Umkehrspülung bekannter Bauart im Axialschnitt,
  • Fig. 2 ein Ausführungsbeispiel gemäß der Erfindung im Axialschnitt,
  • Fig. 3 und 4 je einen Schnitt nach der Linie III-IV in Fig. 1 und Fig. 2,
  • Fig. 5 ein anderes Ausführungsbeispiel gemäß der Er­findung im Axialschnitt,
  • Fig. 6 einen Schnitt nach der Linie VI-VI in Fig. 5 und Fig. 7a bis c ein Detail in drei verschiedenen Ausfüh­rungsformen.
    Gleiche Teile sind mit den selben Bezugszeichen versehen.
The invention is explained in more detail below with reference to the drawings using a few exemplary embodiments. Show it:
  • 1 schematically shows a two-stroke internal combustion engine with reverse purge of a known type in axial section,
  • 2 shows an embodiment according to the invention in axial section,
  • 3 and 4 each a section along the line III-IV in Fig. 1 and Fig. 2,
  • 5 shows another embodiment according to the invention in axial section,
  • Fig. 6 shows a section along the line VI-VI in Fig. 5 and Fig. 7a to c a detail in three different embodiments.
    The same parts are provided with the same reference numerals.

In Fig. 1 und 3 ist eine Zweitakt-Brennkraftmaschine bekannter Bauart zur Hälfte dargestellt, wobei der Zylinder mit 1, der Zylinderkopf mit 2 und der Kolben mit 3 bezeichnet ist. Der Kolben 3 steuert den Auslaßkanal 4 sowie die zwei zu beiden Seiten des Auslaßkanals 4 angeordneten Einströmkanäle 5. Die Spülströmung bei entsprechend dem Pfeil 6 nach abwärts beweg­ten Kolben 3 ist durch die Strömungslinien 7 angedeutet. Durch die Kolbenkante 3′ wird die Strömung, wie man sieht, von der durch die Kanalbegrenzungen 8 gegebenen theoretischen Strö­mungsrichtung abgelenkt, wobei sich Wirbel bilden, welche mit 7′ bezeichnet sind. Dadurch werden erhöhte Reibungs- und Frischladungsverluste verursacht.1 and 3, a two-stroke internal combustion engine of known design is shown in half, the cylinder being designated 1, the cylinder head 2 and the piston 3. The piston 3 controls the outlet channel 4 and the two inlet channels 5 arranged on both sides of the outlet channel 4. The rinsing flow when the piston 3 is moved downwards in accordance with the arrow 6 is indicated by the flow lines 7. Through the piston edge 3 ', the flow, as can be seen, is deflected from the theoretical flow direction given by the channel boundaries 8, forming vortices, which are denoted by 7'. This causes increased friction and fresh charge losses.

Gemäß der Erfindung werden im Bereich 9 des Krümmers 10 der Einlaßkanäle 5 Strömungsleitflächen 11 angeordnet, welche zur Zylinderachse 12 parallel verlaufen. Quer dazu sind Strömungs­leitflächen 13 vorgesehen, welche zusammen mit den Strömungs­leitflächen 11 Strömungskanäle 14 bilden, welche bewirken, daß die durch die Pfeile 15 veranschaulichte Strömung von der Kolbenkante 3′ unbeeinflußt bleibt. Dadurch entfallen auch die ungünstigen Wirkungen bezüglich Motorleistung, Frischladungsverluste und Abgasemissionen.According to the invention, flow guide surfaces 11 are arranged in the area 9 of the elbow 10 of the inlet channels 5 and run parallel to the cylinder axis 12. Transversely to this, flow guide surfaces 13 are provided, which together with the flow guide surfaces 11 form flow channels 14, which cause the flow illustrated by the arrows 15 to remain unaffected by the piston edge 3 '. This also eliminates the unfavorable effects in terms of engine performance, fresh charge losses and exhaust gas emissions.

In den Fig. 3 und 4 ist der durch den Strömungsgleichrichter mögliche größere Anstellwinkel α₂ der resultierenden Strö­mung R₂ im Vergleich zum Anstellwinkel α₁ der resultierenden Strömung R₁ bei der bekannten Ausführung dargestellt.3 and 4, the larger angle of attack α₂ of the resulting flow R₂ possible compared to the angle of attack α₁ of the resulting flow R₁ in the known embodiment is shown by the flow rectifier.

Die erfindungsgemäße Ausführung nach Fig. 5 und 6 zeigt zwei Varianten gemäß der Erfindung, welchen gemeinsam ist, daß die Bereiche 9 der Krümmer 10 der Einlaßkanäle 5 zylindrisch sind und daher die Herstellung sowie die Montage des Strö­mungsgleichrichters 16 vereinfacht ist. Bei der in der linken Hälfte dargestellten Ausführung verlaufen die Verlängerun­gen 11′ der Strömungsleitflächen 11 in einem Punkt 17 zusam­men, welcher sich in Fig. 6 in der unteren Hälfte des Zylin­ders 1, also auf der dem Auslaßkanal 4 abgewendeten Seite be­findet. Damit kann zusätzlich eine günstige Beeinflussung der Frischladungsverluste erreicht werden.The embodiment according to FIGS. 5 and 6 shows two variants according to the invention, which have in common that the areas 9 of the elbows 10 of the inlet channels 5 are cylindrical and therefore the manufacture and assembly of the flow straightener 16 is simplified. The one in the left Half shown embodiment, the extensions 11 'of the flow guide surfaces 11 together at a point 17, which is in Fig. 6 in the lower half of the cylinder 1, that is on the side facing away from the exhaust port 4. This can also have a favorable influence on the fresh charge losses.

Bei der in den Fig. 5 und 6 rechts dargestellten Ausfüh­rungsform sind zu beiden Seiten des Auslaßkanals 4 je zwei Einströmkanäle 18 und 19 vorgesehen, die ebenfalls mit Strö­mungsleitflächen 11,13 bzw. 20,21 im Bereich 9 des Krümmers 10 ausgerüstet sind. Die Einströmkanäle 18 sind dabei gegen die dem Auslaßkanal 4 gegenüberliegende Zylinderwand 22 gerichtet, wogegen die Einlaßkanäle 19 etwa gegen die Achse 12 des Zylin­ders gerichtet sind.In the embodiment shown on the right in FIGS. 5 and 6, two inflow channels 18 and 19 are provided on both sides of the outlet channel 4, which are also equipped with flow guide surfaces 11, 13 and 20, 21 in the area 9 of the manifold 10. The inlet channels 18 are directed against the cylinder wall 22 opposite the outlet channel 4, whereas the inlet channels 19 are directed approximately against the axis 12 of the cylinder.

In Fig. 7a) bis c) sind verschiedene mögliche Ausfüh­rungsformen des Strömungsgleichrichters 16 gezeigt, wie er sich an der Anschlußfläche des Krümmers 10 am Zylinder 1 dar­stellt. Die Ausführung a) besitzt Strömungskanäle mit quadra­tischem Querschnitt, die Ausführung b) weist Strö­mungskanäle 14′ auf, die bienenwabenartig angeordnet und sechseckig ausgeführt sind. Die Ausführung nach c) besitzt Strömungskanäle 14˝ mit rechteckigem Querschnitt, welche in vertikaler Richtung jeweils um die halbe Länge des Quer­schnitts versetzt angeordnet sind. Die Auswahl der besten Aus­führung wird im allgemeinen durch Versuche ermittelt.7a) to c) show various possible embodiments of the flow straightener 16 as it is represented on the connection surface of the manifold 10 on the cylinder 1. The version a) has flow channels with a square cross section, the version b) has flow channels 14 ', which are arranged in a honeycomb-like manner and are hexagonal. The embodiment according to c) has flow channels 14˝ with a rectangular cross section, which are arranged offset in the vertical direction by half the length of the cross section. The selection of the best version is generally determined by experiment.

Claims (7)

1. Zweitakt-Brennkraftmaschine mit vom Kolben gesteuerten Einlaßkanälen für die Frischladung, die im Bereich ihrer unmittelbar an den Zylinder anschließenden Abschnitte meh­rere Strömungsleitflächen aufweisen und mit mindestens ei­nem Auslaßkanal für die Verbrennungsgase, dadurch gekenn­zeichnet , daß die Strömungsleitflächen (11,13; 20,21) im Winkel, vorzugsweise im rechten Winkel, zueinander stehen und so einen Strömungsgleichrichter (16) bilden.1. Two-stroke internal combustion engine with piston-controlled inlet channels for the fresh charge, which have a plurality of flow guide surfaces in the region of their sections directly adjoining the cylinder and with at least one outlet channel for the combustion gases, characterized in that the flow guide surfaces (11, 13; 20, 21 ) at an angle, preferably at right angles, to each other and thus form a flow straightener (16). 2. Zweitakt-Brennkraftmaschine nach Anspruch 1, dadurch ge­kennzeichnet , daß die Strömungsleitflächen (11,13;20,21) eben und in mindestens zwei Gruppen jeweils parallel und gruppenweise in solchen Winkeln zueinander angeordnet sind, daß sie geschlossene Strömungskanäle (14,14′ ,14˝) bilden.2. Two-stroke internal combustion engine according to claim 1, characterized in that the flow guide surfaces (11, 13; 20, 21) are arranged flat and in at least two groups in parallel and in groups at such angles to one another that they have closed flow channels (14, 14 ') , 14˝) form. 3. Zweitakt-Brennkraftmaschine nach Anspruch 1 oder 2, da­durch gekennzeichnet , daß der an den Zylinder (1) an­schließende Teil (9) der Einlaßkrümmer (10) zylindrisch ausgeführt und der Strömungsgleichrichter (16) als ein Stück in diesen eingesetzt ist.3. Two-stroke internal combustion engine according to claim 1 or 2, characterized in that the cylinder (1) adjoining part (9) of the intake manifold (10) is cylindrical and the flow straightener (16) is used as a piece in this. 4. Zweitakt-Brennkraftmaschine nach einem der Ansprü­che 1 bis 3, dadurch gekennzeichnet , daß die gedachten Verlängerungen (11′) der Strömungsleitflächen (11) eines Einlaßkanals (5), welche parallel zur Zylinderachse (12) angeordnet sind, zentrisch auf einen im Zylinder (1) und der dem Auslaßkanal (4) gegenüberliegenden Hälfte liegen­den Punkt (17) zusammenlaufen.4. Two-stroke internal combustion engine according to one of claims 1 to 3, characterized in that the imaginary extensions (11 ') of the flow guide surfaces (11) of an inlet channel (5), which are arranged parallel to the cylinder axis (12), centrally on one in the cylinder (1) and the point (17) lying opposite the outlet channel (4) meet half. 5. Zweitakt-Brennkraftmaschine nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet , daß der Strömungsgleich­richter (16) aus Strömungskanälen (14,14˝) mit viereckigem Querschnitt, vorzugsweise quadratischem Querschnitt, zu­sammengesetzt ist.5. Two-stroke internal combustion engine according to one of claims 1 to 4, characterized in that the flow straightener (16) from flow channels (14,14˝) with a square cross-section, preferably square cross-section, is composed. 6. Zweitakt-Brennkraftmaschine nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet , daß der Strömungsgleich­ richter (16) aus im Querschnitt sechseckigen Strömungskanälen (14′) bienenwabenartig zusammengesetzt ist.6. Two-stroke internal combustion engine according to one of claims 1 to 4, characterized in that the flow is equal judge (16) from hexagonal flow channels (14 ') is composed of a honeycomb. 7. Zweitakt-Brennkraftmaschine nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet , daß die Strömungsleitflä­chen (11,13;20,21) sehr dünnwandig ausgeführt sind, vor­zugsweise aus Blech bestehen.7. Two-stroke internal combustion engine according to one of claims 1 to 6, characterized in that the flow guide surfaces (11,13; 20,21) are made very thin-walled, preferably made of sheet metal.
EP89890302A 1988-11-24 1989-11-21 Two-stroke internal combustion engine Withdrawn EP0370999A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT0289288A AT402431B (en) 1988-11-24 1988-11-24 TWO-STROKE INTERNAL COMBUSTION ENGINE
AT2892/88 1988-11-24

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EP0370999A1 true EP0370999A1 (en) 1990-05-30

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EP89890302A Withdrawn EP0370999A1 (en) 1988-11-24 1989-11-21 Two-stroke internal combustion engine

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US (1) US5040496A (en)
EP (1) EP0370999A1 (en)
JP (1) JPH0367016A (en)
AT (1) AT402431B (en)

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CN102230421A (en) * 2011-05-25 2011-11-02 中国兵器工业集团第七○研究所 Air inlet device with two air inlet channels for two-stroke engine

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Publication number Priority date Publication date Assignee Title
JP2602803Y2 (en) * 1992-10-08 2000-01-31 株式会社共立 Two-stroke engine cylinder
US5490483A (en) * 1994-02-23 1996-02-13 Daihatsu Motor Co., Ltd. Two-cycle internal combustion engine
JPH0988617A (en) * 1995-09-18 1997-03-31 Yamaha Motor Co Ltd Two-cycle engine
JP3630897B2 (en) * 1997-02-10 2005-03-23 株式会社共立 2-cycle internal combustion engine
US5769040A (en) * 1997-04-18 1998-06-23 Christner; Oval F. Two cycle internal combustion engine
AT4876U1 (en) * 2000-05-04 2001-12-27 Avl List Gmbh INTERNAL COMBUSTION ENGINE WITH AT LEAST TWO INLET CHANNELS PER CYLINDER
CN2424304Y (en) * 2000-06-15 2001-03-21 韩晓静 Novel two-stroke engine
US7307071B2 (en) 2001-12-04 2007-12-11 Onyx Pharmaceuticals, Inc RAF-MEK-ERK pathway inhibitors to treat cancer
DE102005019520B4 (en) * 2005-04-27 2017-05-04 Andreas Stihl Ag & Co. Kg Cylinder for a two-stroke engine
JP5024230B2 (en) * 2008-08-12 2012-09-12 日立工機株式会社 Stratified scavenging two-cycle engine and two-cycle engine tool
JP5060459B2 (en) * 2008-12-08 2012-10-31 株式会社やまびこ 2-cycle engine
DE102017206430A1 (en) * 2017-04-13 2018-10-18 Arno Leuschner Device for forwarding a gaseous volume flow in an internal combustion engine and method for operating an internal combustion engine and method for retrofitting an internal combustion engine

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH109360A (en) * 1922-12-23 1925-03-16 Georg Prof Held Two-stroke injection engine.
FR767274A (en) * 1933-02-23 1934-07-13 Sulzer Ag Two-stroke internal combustion engine, in which air is introduced into the engine cylinder through ports provided with attachments
DE651632C (en) * 1935-11-22 1937-10-21 Auto Union A G Internal combustion engine, in particular two-stroke internal combustion engine, with overflow slots controlled by the working piston

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB191319784A (en) * 1913-01-14 1913-10-16 Heinrich Borchers Improvements in the Scavenging of Two-stroke Cycle Internal Combustion Engines.
US1176096A (en) * 1915-04-21 1916-03-21 Oskar Richter Two-stroke-cycle internal-combustion engine.
CH112277A (en) * 1924-04-08 1925-10-16 Maschf Augsburg Nuernberg Ag Two-stroke internal combustion engine with slot scavenging.
US2016344A (en) * 1933-02-23 1935-10-08 Sulzer Ag Two stroke internal combustion engine
US2137344A (en) * 1936-04-08 1938-11-22 John J Mccarthy Directional intake control for internal combustion engines
US2244453A (en) * 1937-12-04 1941-06-03 Fottinger Hermann Scavenging of two-stroke cycle internal combustion engines
DE731097C (en) * 1940-03-07 1943-02-02 Auto Union A G Internal combustion engine, in particular two-stroke internal combustion engine, with inlet slots controlled by the working piston
US2406404A (en) * 1945-10-12 1946-08-27 Mcculloch Aviat Inc Internal-combustion engine
US2756731A (en) * 1951-06-13 1956-07-31 Wille Rudolf Air-guiding means in the intake conduit of an internal combustion engine
US2778348A (en) * 1953-11-25 1957-01-22 Gen Motors Corp Engine scavenging means
US3494335A (en) * 1968-05-03 1970-02-10 Brunswick Corp Internal combustion engine
DE3041560A1 (en) * 1980-11-04 1982-06-09 Ficht GmbH, 8011 Kirchseeon TWO-STROKE COMBUSTION PISTON WITH A CYLINDER RINSING DEVICE

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH109360A (en) * 1922-12-23 1925-03-16 Georg Prof Held Two-stroke injection engine.
FR767274A (en) * 1933-02-23 1934-07-13 Sulzer Ag Two-stroke internal combustion engine, in which air is introduced into the engine cylinder through ports provided with attachments
DE651632C (en) * 1935-11-22 1937-10-21 Auto Union A G Internal combustion engine, in particular two-stroke internal combustion engine, with overflow slots controlled by the working piston

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102230421A (en) * 2011-05-25 2011-11-02 中国兵器工业集团第七○研究所 Air inlet device with two air inlet channels for two-stroke engine

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US5040496A (en) 1991-08-20
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ATA289288A (en) 1996-09-15
AT402431B (en) 1997-05-26

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