EP0593064A1 - Internal combustion engine - Google Patents

Internal combustion engine Download PDF

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Publication number
EP0593064A1
EP0593064A1 EP93116664A EP93116664A EP0593064A1 EP 0593064 A1 EP0593064 A1 EP 0593064A1 EP 93116664 A EP93116664 A EP 93116664A EP 93116664 A EP93116664 A EP 93116664A EP 0593064 A1 EP0593064 A1 EP 0593064A1
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EP
European Patent Office
Prior art keywords
piston
internal combustion
combustion engine
engine according
prechamber
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EP93116664A
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German (de)
French (fr)
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EP0593064B1 (en
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Franz Rupp
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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
    • 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
    • F02B33/10—Engines with reciprocating-piston pumps; Engines with crankcase pumps with reciprocating-piston pumps other than simple crankcase pumps with the pumping cylinder situated between working cylinder and crankcase, or with the pumping cylinder surrounding working cylinder
    • F02B33/12—Engines with reciprocating-piston pumps; Engines with crankcase pumps with reciprocating-piston pumps other than simple crankcase pumps with the pumping cylinder situated between working cylinder and crankcase, or with the pumping cylinder surrounding working cylinder the rear face of working piston acting as pumping member and co-operating with a pumping chamber isolated from crankcase, the connecting-rod passing through the chamber and co-operating with movable isolating member
    • 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
    • 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 an internal combustion engine, in particular a two-stroke engine, with the features of the preamble of the main claim.
  • a separate prechamber is provided between the piston and the crankshaft, the volume of which is changed by the piston movement. Since the crankshaft is outside of this prechamber, the dead volume, which is caused by the piston movement in conventional engines, cannot be changed remains, can be significantly reduced. In extreme cases, the dead volume can be reduced to the volume of the overflow channel. This creates the possibility that the fresh gas is pre-compressed to a much higher pressure in the prechamber than in the known internal combustion engines. If this fresh gas, pre-compressed to a high pressure, flows into the combustion chamber, not only is a better cylinder filling achieved, but also a more effective cylinder purging is achieved. The residual gas content in the bunk room can be reduced to a minimum.
  • the fresh gas consists only of sucked-in air, it can be accepted that a part of this pre-compressed air flowing into the combustion chamber is released into the open again via the outlet duct, whereby the advantage is achieved that the exhaust gases from the combustion chamber to an even greater extent be rinsed out. Nevertheless, the filling volume remains high due to the relatively high pressure of the pre-compressed fresh gas.
  • US 2,354,357 shows an engine in which the boundary wall located between the piston and the crankshaft can be displaced by a gear. Although the precompression ratio can be changed as a result, the design effort for this is very high.
  • a disadvantage of such a motor structure is that the precompression of the fresh gas in the prechamber is limited to a fixed value, or According to US 2,354,357 high structural precautions must be taken to change the pre-compression ratio.
  • the invention is therefore based on the object of providing an internal combustion engine of the type mentioned at the beginning in which an optimal pre-compression can be set in a simple manner and adjusted in a simple manner.
  • the pre-compression is set to the desired value by the arrangement of the cover in the piston. If the value of the pre-compression is to be changed, then only the piston has to be exchanged for another piston with a differently arranged cover.
  • the space enclosed by the piston crown and cover serves as an insulation space, which prevents the gas in the prechamber from heating up undesirably.
  • the boundary wall is provided in the area of the cylinder base. This divides the entire cylinder from the piston into the prechamber and into the displacement and combustion chamber. Their respective volumes depend directly on the position of the piston in the cylinder and on the position of the cover. The densifications both in the antechamber and in the displacement and combustion chamber are therefore exclusively in the cylinder.
  • the internal combustion engine is designed as a boxer engine, in particular at least two cylinders lying opposite one another.
  • This has the advantage that the energy for the main compression, pre-compression and for the suction is transferred directly from one piston to the other piston via the piston rod without the crankshaft having to be interposed. At the crankshaft, only the power to be delivered is then omitted.
  • bearings of all drive units can be dimensioned smaller, since only the power to be output is discharged from the piston-piston rod system.
  • the piston rod preferably engages in the middle of the piston. This achieves a symmetrical flow of force that reduces the tendency of the piston to tilt to a minimum. This has the advantage that the piston itself is relatively flat can be, in the extreme case it is only designed as a disk receiving the piston rings.
  • the piston rod is preferably via sealing elements, e.g. a shaft seal or the like. in the boundary wall sealing. These sealing elements allow an optimal sealing of the prechamber so that relatively high pressures can already be achieved in it. Sealing the crankcase against excess pressure is only necessary to the extent that no fluids can escape from the crankcase.
  • the crankcase can also be provided with a vent.
  • the piston rod is connected to the crankshaft via a link, rocker arm or the like.
  • the reciprocating movement of the piston rod is converted into a rotary movement via this backdrop.
  • the prechamber is provided with an inlet channel having an inlet valve, and in a further development the displacement and combustion chamber is provided with an outlet channel having an outlet valve.
  • the inflowing and outflowing gases can be precisely controlled via the valves so that no backflows occur.
  • the valves are advantageously designed as check valves or flaps.
  • the volume of the antechamber can be changed.
  • the compression ratio or the absolute pressure in the combustion chamber can be set to optimum values.
  • extremely high pressures can be achieved for diesel engines.
  • the volume of the displacement and combustion chamber preferably corresponds to 0.5 to 2 times the volume of the prechamber.
  • 1 to 4 show a piston-cylinder unit denoted by 1. 2 and 2 'denotes a cylinder, 3 and 3' a piston and 4 and 4 'a cylinder head.
  • the piston 3 executes linearly oscillating movements in the cylinder 2 in the usual way. He divides the cylinder interior into a stroke and combustion chamber 5 located in front of the piston 3 and a space located behind the piston 3. The combustion takes place in the stroke and combustion chamber 5, wherein a spark plug 6 and possibly an injection nozzle 7 can protrude into the stroke and combustion chamber 5. Furthermore, an inlet channel 8 and an outlet channel 9 are provided, each of which can be closed via a valve 10 or 11. The valves 10 and 11 can be designed as check valves or flaps.
  • a connecting element 12 engages the piston 3 and connects the piston 3 to a crankshaft 13, which is shown schematically in FIGS. 5 and 6. Such a structure is usually used in two-stroke engines.
  • the connecting element 12 is in Figure 2, in which the State of the art is shown as a connecting rod 14 which transmits the oscillating movements of the piston 3 to the crankshaft 13.
  • the connecting rod 14 carries out pivoting movements around the piston pin bearing 15 and oscillating movements in a known manner.
  • the connecting rod 14 requires a space to be kept clear or dead space behind the piston 3.
  • the space 16 behind the piston is connected to the lifting and combustion chamber 5 via an overflow channel 17 when the piston 3 assumes its bottom dead center.
  • the connecting element 12 is designed as a piston rod 18, which connects the piston 3 to the crankshaft 13.
  • This piston rod 18 only performs linearly oscillating movements in the direction of arrow 19. No additional space next to the piston rod 18 is required for this, which is also readily apparent from FIG. 1.
  • the space located behind the piston 30 is closed off by a boundary wall 20, as a result of which a prechamber 21 is formed.
  • This prechamber 21 is therefore enclosed by the piston 3, the rear end of the cylinder 2 and the boundary wall 20.
  • the overflow channel 17 opens into this antechamber 21.
  • the piston rod 18 is sealed in the boundary wall 20 by a sealing element 22, which is e.g. is a shaft seal.
  • the cover 23 is located approximately in the middle of the piston, as a result of which the space 24 is reduced and the volume of the prechamber 21 is increased.
  • FIG. 5 In the basic diagram of an exemplary embodiment of the internal combustion engine according to the invention shown in FIG. 5, it is designed as a boxer engine.
  • the two cylinders 2 and 2 ' lie opposite one another and the two pistons 3 and 3' are connected via a common piston rod 18.
  • FIG. 5 no lateral forces or tilting movements act on the pistons 3 or 3 'and that the inertial forces are significantly reduced due to the missing connecting rods.
  • the boxer design of the internal combustion engine results in a design that is smaller by the connecting rod bearing width.
  • the exhaust gas located in the lifting and combustion chamber 5 is expelled and the fresh gas pre-compressed in the prechamber 21 via the overflow channel 17 blown into the stroke and combustion chamber 5. Since the fresh gas flows into the lifting and combustion chamber 5 at a relatively high pressure, optimal purging is achieved. If no fuel has yet been added to the fresh gas, this can in part also be blown out again via the blow-out channel 9 to further improve the purging. In any case, the high pre-compression of the fresh gas causes the stroke and combustion chamber 5 to be filled quickly and thoroughly after the valve 11 is closed.
  • a charging device for example an exhaust gas turbocharger or the like.
  • FIG. 6 the backdrop 25 is shown in section and the sliding insert 26, which surrounds the bearing 27 of the crankshaft 13 designed in the manner of a connecting rod bearing, is clearly recognizable.
  • the two oscillating movements of the link 25 and the sliding insert 26 overlap for the rotary movement of the crankshaft 13.

Abstract

In an internal combustion engine with a cylinder (2), a piston (3) and a crankshaft (13), a prechamber (21), in which the fresh gas is precompressed before being fed into the swept/combustion chamber (5), is arranged in the cylinder (2) behind the piston (3). The crankshaft (13) is situated outside this prechamber (21). Optimum precompression and high pressures are thereby achieved. <IMAGE>

Description

Die Erfindung betrifft einen Verbrennungsmotor, insbesondere Zweitaktmotor, mit den Merkmalen des Oberbegriffs des Hauptanspruchs.The invention relates to an internal combustion engine, in particular a two-stroke engine, with the features of the preamble of the main claim.

Ein derartiger Aufbau eines Verbrennungsmotors ist aus den folgenden Druckschriften bekannt: DE 41 00 256 A1, DE 34 47 663 A1, DE 32 18 311 C2, US 4,512,291, US 4,373,474, DE 41 10 945 A1 und US 2,354,357.Such a structure of an internal combustion engine is known from the following publications: DE 41 00 256 A1, DE 34 47 663 A1, DE 32 18 311 C2, US 4,512,291, US 4,373,474, DE 41 10 945 A1 and US 2,354,357.

Bei diesen Motoren ist zwischen dem Kolben und der Kurbelwelle eine separate Vorkammer vorgesehen, deren Volumen durch die Kolbenbewegung verändert wird. Da die Kurbelwelle außerhalb dieser Vorkammer liegt, kann das Totvolumen, welches bei herkömmlichen Motoren durch die Kolbenbewegung unverändert bleibt, wesentlich verringert werden. Das Totvolumen kann im Extremfall auf das Volumen des Überströmkanals reduziert werden. Hierdurch wird die Möglichkeit geschaffen, daS bereits in der Vorkammer das Frischgas auf einen wesentlich höheren Druck vorverdichtet wird als bei den bekannten Verbrennungsmotoren. Strömt dieses auf einen hohen Druck vorverdichtete Frischgas in den Brennraum ein, so wird nicht nur eine bessere Zylinderfüllung erzielt, sondern auch eine effektivere Zylinderspülung erreicht. Der Restgasanteil im Bennraum kann auf Minimum reduziert werden. Besteht das Frischgas lediglich aus angesaugter Luft, so kann in Kauf genommen werden, daß ein Teil dieser in den Brennraum einströmenden vorverdichteten Luft über den Auslaßkanal wieder ins Freie tritt, wodurch der Vorteil erzielt wird, daß die Abgase aus dem Brennraum zu einem noch höheren Anteil ausgespült werden. Dennoch bleibt aufgrund des relativ hohen Druckes des vorverdichteten Frischgases das Füllvolumen hoch.In these engines, a separate prechamber is provided between the piston and the crankshaft, the volume of which is changed by the piston movement. Since the crankshaft is outside of this prechamber, the dead volume, which is caused by the piston movement in conventional engines, cannot be changed remains, can be significantly reduced. In extreme cases, the dead volume can be reduced to the volume of the overflow channel. This creates the possibility that the fresh gas is pre-compressed to a much higher pressure in the prechamber than in the known internal combustion engines. If this fresh gas, pre-compressed to a high pressure, flows into the combustion chamber, not only is a better cylinder filling achieved, but also a more effective cylinder purging is achieved. The residual gas content in the bunk room can be reduced to a minimum. If the fresh gas consists only of sucked-in air, it can be accepted that a part of this pre-compressed air flowing into the combustion chamber is released into the open again via the outlet duct, whereby the advantage is achieved that the exhaust gases from the combustion chamber to an even greater extent be rinsed out. Nevertheless, the filling volume remains high due to the relatively high pressure of the pre-compressed fresh gas.

Die US 2,354,357 zeigt einen Motor, bei dem die zwischen dem Kolben und der Kurbelwelle sich befindende Begrenzungswand durch ein Getriebe verlagert werden kann. Zwar ist dadurch das Vorverdichtungsverhältnis veränderbar, jedoch ist der konstruktive Aufwand hierfür sehr hoch.US 2,354,357 shows an engine in which the boundary wall located between the piston and the crankshaft can be displaced by a gear. Although the precompression ratio can be changed as a result, the design effort for this is very high.

Als nachteilig kann bei einem deratigen Motoraufbau angesehen werden, daß die Vorverdichtung des Frischgases in der Vorkammer auf einen festen Wert begrenzt ist, bzw. entsprechend der US 2,354,357 hohe bauliche Vorkehrungen getroffen werden müssen um das Vorverdichtungsverhältnis zu ändern.A disadvantage of such a motor structure is that the precompression of the fresh gas in the prechamber is limited to a fixed value, or According to US 2,354,357 high structural precautions must be taken to change the pre-compression ratio.

Der Erfindung liegt daher die Aufgabe zugrunde, einen Verbrennungsmotor der eingangs genannten Art bereitzustellen, bei dem auf einfache Weise eine optimale Vorverdichtung eingestellt und auf einfache Weise verstellt werden kann.The invention is therefore based on the object of providing an internal combustion engine of the type mentioned at the beginning in which an optimal pre-compression can be set in a simple manner and adjusted in a simple manner.

Diese Aufgabe wird erfindungsgemäß durch die kennzeichnenden Merkmale des Hauptanspruchs gelöst.This object is achieved by the characterizing features of the main claim.

Durch die Anordnung des Deckels im Kolben wird die Vorverdichtung auf den gewünschten Wert eingestellt. Soll der Wert der Vorverdichtung geändert werden, so muß lediglich der Kolben gegen einen anderen Kolben mit anders angeordnetem Deckel ausgestauscht werden. Außerdem dient der vom Kolbenboden und Deckel eingeschlossene Raum als Isolationsraum, der ein unerwünschtes Aufheizen des in der Vorkammer sich befindenden Gases verhindert.The pre-compression is set to the desired value by the arrangement of the cover in the piston. If the value of the pre-compression is to be changed, then only the piston has to be exchanged for another piston with a differently arranged cover. In addition, the space enclosed by the piston crown and cover serves as an insulation space, which prevents the gas in the prechamber from heating up undesirably.

Bei einer Weiterbildung ist vorgesehen, daß die Begrenzungswand im Bereich des Zylinderfußes vorgesehen ist. Hierdurch wird der gesamte Zylinder vom Kolben in die Vorkammer und in den Hub- und Brennraum unterteilt. Deren jeweililgen Volumina hängen direkt von der Lage des Kolbens im Zylinder und von der Lage des Deckels ab. Die Verdichtungen sowohl in der Vorkammer als auch im Hub- und Brennraum erfolgen demnach ausschließlich im Zylinder.In a further development it is provided that the boundary wall is provided in the area of the cylinder base. This divides the entire cylinder from the piston into the prechamber and into the displacement and combustion chamber. Their respective volumes depend directly on the position of the piston in the cylinder and on the position of the cover. The densifications both in the antechamber and in the displacement and combustion chamber are therefore exclusively in the cylinder.

Vorteilhaft ist die vom Hub- und Brennraum abgewandte Seite des Kolbens verschlossen. Diese verschlossene Seite bildet eine Begrenzungswand für die Vorkammer. Dabei kann der Kolben hohl ausgeführt sein, was den Vorteil hat, daß dieser Hohlraum als thermischer Isolator zwischen dem Hub- und Brennraum und der Vorkammer dient.The side of the piston facing away from the stroke and combustion chamber is advantageously closed. This closed side forms a boundary wall for the antechamber. The piston can be made hollow, which has the advantage that this cavity serves as a thermal insulator between the stroke and combustion chamber and the prechamber.

Bei einem bevorzugten Ausführungsbeispiel ist der Verbrennungsmotor als Boxermotor ausgebildet, wobei insbesondere wenigstens zwei Zylinder einander gegenüberliegen. Dies hat den Vorteil, daß die Energie für die Hauptverdichtung, Vorverdichtung und für das Ansaugen direkt über die Kolbenstange vom einen Kolben auf den anderen Kolben übertragen wird, ohne daß die Kurbelwelle zwischengeschaltet werden muß. An der Kurbelwelle entfällt dann lediglich noch die abzugebende Leistung. Hierdurch können Lagerungen aller Antriebsaggregate kleiner dimensioniert werden, da lediglich die abzugebende Leistung aus dem Kolben-Kolbenstangensystem ausgeleitet wird.In a preferred exemplary embodiment, the internal combustion engine is designed as a boxer engine, in particular at least two cylinders lying opposite one another. This has the advantage that the energy for the main compression, pre-compression and for the suction is transferred directly from one piston to the other piston via the piston rod without the crankshaft having to be interposed. At the crankshaft, only the power to be delivered is then omitted. As a result, bearings of all drive units can be dimensioned smaller, since only the power to be output is discharged from the piston-piston rod system.

Bevorzugt greift die Kolbenstange in der Mitte des Kolbens an. Hierdurch wird ein symmetrischer Kraftfluß erzielt, der Kippneigungen des Kolbens auf ein Minimum reduziert. Dies hat den Vorteil, daß der Kolben selbst relativ flach gestaltet werden kann, wobei er im Extremfall nur noch als eine die Kolbenringe aufnehmende Scheibe ausgebildet ist.The piston rod preferably engages in the middle of the piston. This achieves a symmetrical flow of force that reduces the tendency of the piston to tilt to a minimum. This has the advantage that the piston itself is relatively flat can be, in the extreme case it is only designed as a disk receiving the piston rings.

Bevorzugt ist die Kolbenstange über Dichtungselemente, z.B. eine Schaftdichtung oder dgl. in der Begrenzungswand dichtend geführt. Diese Dichtungselemente erlauben eine optimale Abdichtung der Vorkammer, so daß in dieser bereits relativ hohe Drücke erzielt werden können. Eine Abdichtung des Kurbelgehäuses gegen Überdruck ist nur noch so weit erforderlich, daß keine Fluide aus dem Kurbelgehäuse austreten können. Das Kurbelgehäuse kann auch mit einer Entlüftung versehen sein.The piston rod is preferably via sealing elements, e.g. a shaft seal or the like. in the boundary wall sealing. These sealing elements allow an optimal sealing of the prechamber so that relatively high pressures can already be achieved in it. Sealing the crankcase against excess pressure is only necessary to the extent that no fluids can escape from the crankcase. The crankcase can also be provided with a vent.

Für die Übertragung der abzugebenden Leistung an den Abtrieb ist die Kolbenstange über eine Kulisse, Schwinge oder dgl. mit der Kurbelwelle verbunden. Über diese Kulisse wird die hin- und hergehende Bewegung der Kolbenstange in eine Drehbewegung umgesetzt.For the transmission of the power to be output to the output, the piston rod is connected to the crankshaft via a link, rocker arm or the like. The reciprocating movement of the piston rod is converted into a rotary movement via this backdrop.

Bei einem Ausführungsbeispiel ist die Vorkammer mit einem ein Einlaßventil aufweisenden Einlaßkanal, und bei einer Weiterbildung der Hub- und Brennraum mit einem ein Auslaßventil aufweisenden Auslaßkanal versehen. Über die Ventile können die ein- bzw. abströmenden Gase exakt gesteuert werden, so daß keine Rückströmungen auftreten. Vorteilhaft sind die Ventile als Rückschlagventile oder Klappen ausgebildet.In one embodiment, the prechamber is provided with an inlet channel having an inlet valve, and in a further development the displacement and combustion chamber is provided with an outlet channel having an outlet valve. The inflowing and outflowing gases can be precisely controlled via the valves so that no backflows occur. The valves are advantageously designed as check valves or flaps.

Bei einer bevorzugten Weiterbildung ist das Volumen der Vorkammer veränderbar. Hierdurch kann das Verdichtungsverhältnis bzw. der Absolutdruck in der Brennkammer auf optimale Werte eingestellt werden. Insbesondere sind für Dieselmotoren extrem hohe Drücke erzielbar.In a preferred development, the volume of the antechamber can be changed. In this way, the compression ratio or the absolute pressure in the combustion chamber can be set to optimum values. In particular, extremely high pressures can be achieved for diesel engines.

Bevorzugt entspricht das Volumen des Hub- und Brennraums dem 0,5 bis 2-fachen Volumen der Vorkammer.The volume of the displacement and combustion chamber preferably corresponds to 0.5 to 2 times the volume of the prechamber.

Vorteile, Merkmale und Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung, in der unter Bezugnahme auf die Zeichnung besonders bevorzugte Ausführungsbeispiele im einzelnen wiedergegeben sind. Dabei zeigen:

Figur 1
eine teilweise geschnittene Seitenansicht einer Kolben-Zylinder-Einheit einer ersten Ausführungsform der Erfindung;
Figur 2
eine Ansicht gemäß Figur 1 einer Kolben-Zylinder-Einheit gemäß dem Stand der Technik;
Figur 3
eine Ansicht gemäß Figur 1 mit geschnittenem Kolben;
Figur 4
eine Ansicht gemäß Figur 3 einer zweiten Ausführungsform;
Figur 5
einen Längsschnitt durch einen als Zwei-Zylinder-Boxermotor ausgebildeten Verbrennungsmotor; und
Figur 6
einen Schnitt VI-VI gemäß Figur 5 durch die Abtriebseinheit.
Advantages, features and details of the invention result from the following description, in which particularly preferred exemplary embodiments are shown in detail with reference to the drawing. Show:
Figure 1
a partially sectioned side view of a piston-cylinder unit of a first embodiment of the invention;
Figure 2
a view of Figure 1 of a piston-cylinder unit according to the prior art;
Figure 3
a view of Figure 1 with a cut piston;
Figure 4
a view of Figure 3 of a second embodiment;
Figure 5
a longitudinal section through an internal combustion engine designed as a two-cylinder boxer engine; and
Figure 6
a section VI-VI of Figure 5 through the output unit.

In den Figuren 1 bis 4 ist eine mit 1 bezeichnete Kolben-Zylinder-Einheit wiedergegeben. Dabei ist mit 2 und 2' ein Zylinder, mit 3 und 3' ein Kolben und mit 4 und 4' ein Zylinderkopf bezeichnet. Der Kolben 3 führt in üblicher Weise linear oszillierende Bewegungen im Zylinder 2 aus. Dabei unterteilt er den Zylinderinnenraum in einen vor dem Kolben 3 liegenden Hub- und Brennraum 5 und einen hinter dem Kolben 3 liegenden Raum auf. Im Hub- und Brennraum 5 findet die Verbrennung statt, wobei in den Hub- und Brennraum 5 eine Zündkerze 6 und ggf. eine Einspritzdüse 7 ragen können. Ferner sind ein Einlaßkanal 8 und ein Auslaßkanal 9 vorgesehen, die jeweils über ein Ventil 10 bzw. 11 verschließbar sind. Die Ventile 10 und 11 können als Rückschlageventile oder Klappen ausgebildet sein. Am Kolben 3 greift ein Verbindungselement 12 an, welches den Kolben 3 mit einer in den Figuren 5 und 6 schematisch dargestellten Kurbelwelle 13 verbindet. Ein derartiger Aufbau wird in der Regel bei Zweitaktmotoren verwendet.1 to 4 show a piston-cylinder unit denoted by 1. 2 and 2 'denotes a cylinder, 3 and 3' a piston and 4 and 4 'a cylinder head. The piston 3 executes linearly oscillating movements in the cylinder 2 in the usual way. He divides the cylinder interior into a stroke and combustion chamber 5 located in front of the piston 3 and a space located behind the piston 3. The combustion takes place in the stroke and combustion chamber 5, wherein a spark plug 6 and possibly an injection nozzle 7 can protrude into the stroke and combustion chamber 5. Furthermore, an inlet channel 8 and an outlet channel 9 are provided, each of which can be closed via a valve 10 or 11. The valves 10 and 11 can be designed as check valves or flaps. A connecting element 12 engages the piston 3 and connects the piston 3 to a crankshaft 13, which is shown schematically in FIGS. 5 and 6. Such a structure is usually used in two-stroke engines.

Das Verbindungselement 12 ist in der Figur 2, in welcher der Stand der Technik dargestellt ist, als Pleuel 14 ausgebildet, welches die oszillierenden Bewegungen des Kolbens 3 auf die Kurbelwelle 13 überträgt. Dabei führt das Pleuel 14 in bekannter Weise Schwenkbewegungen um die Kolbenbolzenlagerung 15 und oszillierende Bewegungen aus. Hierfür benötigt das Pleuel 14 einen freizuhaltenden Raum oder Totraum hinter dem Kolben 3. Der hinter dem Kolben sich befindende Raum 16 ist über einen Überströmkanal 17 mit dem Hub- und Brennraum 5 dann verbunden, wenn der Kolben 3 seinen unteren Totpunkt einnimmt.The connecting element 12 is in Figure 2, in which the State of the art is shown as a connecting rod 14 which transmits the oscillating movements of the piston 3 to the crankshaft 13. The connecting rod 14 carries out pivoting movements around the piston pin bearing 15 and oscillating movements in a known manner. For this purpose, the connecting rod 14 requires a space to be kept clear or dead space behind the piston 3. The space 16 behind the piston is connected to the lifting and combustion chamber 5 via an overflow channel 17 when the piston 3 assumes its bottom dead center.

Bei dem in der Figur 1 wiedergegebenen ersten Ausführungsbeispiel der Erfindung ist das Verbindungselement 12 als Kolbenstange 18 ausgeführt, welche den Kolben 3 mit der Kurbelwelle 13 verbindet. Diese Kolbenstange 18 führt lediglich linear oszillierende Bewegungen in Richtung des Pfeils 19 aus. Hierfür wird kein zusätzlicher Raum neben der Kolbenstange 18 benötigt, was ebenfalls leicht aus Figur 1 ersichtlich ist. Ferner ist erkennbar, daß der sich hinter dem Kolben 30 befindende Raum über eine Begrenzungswand 20 abgeschlossen ist, wodurch eine Vorkammer 21 gebildet wird. Diese Vorkammer 21 wird also vom Kolben 3, vom hinteren Ende des Zylinders 2 und der Begrenzungswand 20 umschlossen. In diese Vorkammer 21 mündet der Überströmkanal 17. Eine Abdichtung der Kolbenstange 18 in der Begrenzungswand 20 erfolgt über ein Dichtelement 22, welches z.B. eine Schaftdichtung ist.In the first exemplary embodiment of the invention shown in FIG. 1, the connecting element 12 is designed as a piston rod 18, which connects the piston 3 to the crankshaft 13. This piston rod 18 only performs linearly oscillating movements in the direction of arrow 19. No additional space next to the piston rod 18 is required for this, which is also readily apparent from FIG. 1. It can also be seen that the space located behind the piston 30 is closed off by a boundary wall 20, as a result of which a prechamber 21 is formed. This prechamber 21 is therefore enclosed by the piston 3, the rear end of the cylinder 2 and the boundary wall 20. The overflow channel 17 opens into this antechamber 21. The piston rod 18 is sealed in the boundary wall 20 by a sealing element 22, which is e.g. is a shaft seal.

In der Figur 3, in der der Kolben 3 geschnitten dargestellt ist, ist erkennbar, daß der Kolbenfuß über einen Deckel 23 verschlossen ist. Dieser Deckel 23 ist z.B. eingeschweißt und dient zur zusätzlichen Halterung der Kolbenstange 18. Über den Deckel 23 wird das Volumen der Vorkammer verringert, indem der sich im Kolben 30 befindende Raum 24 abgretrennt wird. Dieser Raum 24 kann als thermischer Isolationsraum verwendet werden.In Figure 3, in which the piston 3 is shown in section , it can be seen that the piston foot is closed by a cover 23. This cover 23 is welded in, for example, and is used to additionally hold the piston rod 18. The cover 23 is used to reduce the volume of the prechamber by separating the space 24 in the piston 30. This space 24 can be used as a thermal insulation space.

Beim Ausführungsbeispiel der Figur 4 befindet sich der Deckel 23 in etwa in der Mitte des Kolbens, wodurch der Raum 24 verringert und das Volumen der Vorkammer 21 vergrößert werden.In the exemplary embodiment in FIG. 4, the cover 23 is located approximately in the middle of the piston, as a result of which the space 24 is reduced and the volume of the prechamber 21 is increased.

Bei dem in der Figur 5 dargestellten Prinzipbild eines Ausführungsbeispiels des erfindungsgemäßen Verbennungsmotors ist dieser als Boxermotor ausgeführt. Dabei liegen die beiden Zylinder 2 und 2' einander gegenüber und die beiden Kolben 3 und 3' sind über eine gemeinsame Kolbenstange 18 verbunden. Aus Figur 5 wird deutlich, daß keine Seitenkräfte bzw. Kippbewegungen auf die Kolben 3 bzw. 3' wirken und daß die Massenkräfte durch die fehlenden Pleuelstangen wesentlich verringert sind. Außerdem ergibt sich durch die Boxerausführung des Verbrennungsmotors eine um die Pleuellagerbreite geringere Bauweise. An der Kolbenstange 18 ist außerdem eine Kulisse 25 mit Gleiteinsatz 26 befsetigt, mit der die oszillierenden Bewegungen auf die Kurbelwelle 13 übertragen werden.In the basic diagram of an exemplary embodiment of the internal combustion engine according to the invention shown in FIG. 5, it is designed as a boxer engine. The two cylinders 2 and 2 'lie opposite one another and the two pistons 3 and 3' are connected via a common piston rod 18. It is clear from FIG. 5 that no lateral forces or tilting movements act on the pistons 3 or 3 'and that the inertial forces are significantly reduced due to the missing connecting rods. In addition, the boxer design of the internal combustion engine results in a design that is smaller by the connecting rod bearing width. On the piston rod 18 there is also a link 25 with a sliding insert 26 with which the oscillating movements are transmitted to the crankshaft 13.

Nachfolgend wird die Funktion des Verbrennungsmotors kurz beschrieben. Von seinem Weg vom unteren Totpunkt in Richtung des oberen Totpunkts werden die in den Hub- und Brennraum 5 mündenden Öffnungen des Überströmkanals 17 und des Auslaßkanals 9 geschlossen und der Kolben verdichtet in üblicher Weise das sich im Hub- und Brennraum 5 befindende Frischgas. Nach dem Zünden des verdichteten Frischgases und nachdem der Kolben 3 den oberen Totpunkt überschritten hat, wird dieser in seine untere Totpunktlage gedrückt. Dabei wird einerseits das in die Vorkammer 21 angesaugte Frischgas vorverdichtet, wobei das Ventil 10 zuvor geschlossen worden ist. Außerdem wird der Kolben 3' von seiner unteren Totpunktlage in Richtung des oberen Totpunkts bewegt. Die Kraftübertragung vom Kolben 3 auf den Kolben 3' erfolgt direkt über die Kolbenstange 18 ohne Zwischenschaltung der Kurbelwelle 13. Im Bereich des unteren Totpunkts wird das im Hub- und Brennraum 5 befindliche Abgas ausgestoßen und das in der Vorkammer 21 vorverdichtete Frischgas über den Überströmkanal 17 in den Hub- und Brennraum 5 eingeblasen. Da das Frischgas mit einem relativ hohen Druck in den Hub- und Brennraum 5 einströmt, wird eine optimale Spülung erzielt. Ist dem Frischgas noch kein Kraftstoff beigemischt worden, so kann zu einer weiteren Verbesserung der Spülung dieses zum Teil auch wieder über den Ausblaskanal 9 ausgeblasen werden. Auf jeden Fall bewirkt die hohe Vorverdichtung des Frischgases ein schnelles und gründliches Füllen des Hub- und Brennraums 5 nach dem Schließen des Ventils 11.The function of the internal combustion engine is briefly described below. From his way from bottom dead center towards At the top dead center, the openings of the overflow duct 17 and the outlet duct 9 opening into the stroke and combustion chamber 5 are closed and the piston compresses the fresh gas located in the stroke and combustion chamber 5 in the usual way. After igniting the compressed fresh gas and after the piston 3 has passed top dead center, it is pressed into its bottom dead center position. On the one hand, the fresh gas drawn into the pre-chamber 21 is precompressed, the valve 10 having been closed beforehand. In addition, the piston 3 'is moved from its bottom dead center position in the direction of top dead center. The power transmission from the piston 3 to the piston 3 ′ takes place directly via the piston rod 18 without the crankshaft 13 being interposed. In the region of bottom dead center, the exhaust gas located in the lifting and combustion chamber 5 is expelled and the fresh gas pre-compressed in the prechamber 21 via the overflow channel 17 blown into the stroke and combustion chamber 5. Since the fresh gas flows into the lifting and combustion chamber 5 at a relatively high pressure, optimal purging is achieved. If no fuel has yet been added to the fresh gas, this can in part also be blown out again via the blow-out channel 9 to further improve the purging. In any case, the high pre-compression of the fresh gas causes the stroke and combustion chamber 5 to be filled quickly and thoroughly after the valve 11 is closed.

Eine weitere Verbesserung der Füllung kann dadurch erzielt werden, daß das Frischgas über eine Ladevorrichtung, z.B. einen Abgasturbolader oder dgl. in die Vorkammer 21 gefördert wird.This can further improve the filling be that the fresh gas is conveyed into the prechamber 21 via a charging device, for example an exhaust gas turbocharger or the like.

Über die Kulisse 25 und den Gleiteinsatz 26 wird das freiwerdende Moment auf die Kurbelwelle 13 übertragen. Dabei gleitet der Gleiteinsatz 26 in der Kulisse 25 in der in der Figur 5 wiedergegebenen Ansicht in vertikaler Richtung und die Kulisse 25 selbst oszilliert in horizontaler Richtung.The released torque is transmitted to the crankshaft 13 via the link 25 and the sliding insert 26. The slide insert 26 slides in the link 25 in the view shown in FIG. 5 in the vertical direction and the link 25 itself oscillates in the horizontal direction.

In der Figur 6 ist die Kulisse 25 im Schnitt dargestellt und der Gleiteinsatz 26, der die nach Art eines Pleuellagers ausgebildete Lagerung 27 der Kurbelwelle 13 umgreift, deutlich erkennbar. Die beiden oszillierenden Bewegungen der Kulisse 25 und des Gleiteinsatzes 26 überlagern sich zur Drehbewegung der Kurbelwelle 13.In FIG. 6, the backdrop 25 is shown in section and the sliding insert 26, which surrounds the bearing 27 of the crankshaft 13 designed in the manner of a connecting rod bearing, is clearly recognizable. The two oscillating movements of the link 25 and the sliding insert 26 overlap for the rotary movement of the crankshaft 13.

Claims (11)

Verbrennungsmotor, insbesondere Zweitaktmotor, mit wenigstens einem Zylinder (2), einem im Zylinder (2) angeordneten, hin- und herlaufenden, einen Hub- und Brennraum (5) abgrenzenden Kolben (3), einer Kurbelwelle (13) und einem die Kurbelwelle (13) mit dem Kolben (3) koppelnden Verbindungselement (12), wobei hinter dem Kolben (3) eine über einen Überströmkanal (17) mit dem Hub- und Brennraum (5) verbundene Vorkammer (21) vorgesehen ist, wobei wenigstens ein Abschnitt des Verbindungselements (12) als linear oszillierende Kolbenstange (18) ausgebildet ist, daß die Kolbenstange (18) durch eine zwischen Kolben (3) und Kurbelwelle (13) angeordnete Begrenzungswand (20) hindurchgeführt ist, und daß der Kolben (3), ein Teil des Zylinders (2) und die Begrenzungswand (20) die Vorkammer (21) umschließen, wobei die Kurbelwelle (13) außerhalb der Vorkammer (21) liegt, dadurch gekennzeichnet, daß der Kolben (3) im wesentlichen aus einem Kolbenmantel, einem Kolbenboden und einem im Bereich des Kolbenfußes vorgesehenen Deckel (23) besteht, wobei der Kolbenboden und der Deckel (23) einen Raum (24) einschließen.Internal combustion engine, in particular a two-stroke engine, with at least one cylinder (2), a reciprocating piston (3) arranged in the cylinder (2), delimiting a stroke and combustion chamber (5), a crankshaft (13) and a crankshaft ( 13) connecting element (12) coupling to the piston (3), a prechamber (21) connected to the lifting and combustion chamber (5) via an overflow channel (17) being provided behind the piston (3), at least a section of the Connecting element (12) is designed as a linearly oscillating piston rod (18) that the piston rod (18) is guided through a boundary wall (20) arranged between the piston (3) and crankshaft (13), and that the piston (3), part of the cylinder (2) and the boundary wall (20) enclose the prechamber (21), the crankshaft (13) being outside the prechamber (21), characterized in that the piston (3) essentially consists of a piston skirt, a piston crown and one in the area of the piston base provided cover (23), the piston crown and the cover (23) enclosing a space (24). Verbrennungsmotor nach Anspruch 1, dadurch gekennzeichnet, daß die Begrenzungswand (20) im Bereich des Zylinderfußes vorgesehen ist.Internal combustion engine according to claim 1, characterized in that the boundary wall (20) is provided in the region of the cylinder base. Verbrennungsmotor nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß die vom Hub- und Brennraum (5) abgewandte Seite des Kolbens (3) verschlossen ist.Internal combustion engine according to claim 1 or 2, characterized in that the side of the piston (3) facing away from the lifting and combustion chamber (5) is closed. Verbrennungsmotor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß er als Boxermotor ausgebildet ist, und insbesondere wenigstens zwei Zylinder (2,2') einander gegenüberliegen.Internal combustion engine according to one of the preceding claims, characterized in that it is designed as a boxer engine and in particular at least two cylinders (2, 2 ') lie opposite one another. Verbrennungsmotor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Kolbenstange (18) in der Mitte des Kolbens (3) angreift.Internal combustion engine according to one of the preceding claims, characterized in that the piston rod (18) acts in the middle of the piston (3). Verbennungsmotor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Kolbenstange (18) über Dichtungselemente (22), z.B. einer Schachtdichtung oder dgl., in der Begrenzungswand (20) dichtend geführt ist.Internal combustion engine according to one of the preceding claims, characterized in that the piston rod (18) via sealing elements (22), e.g. a shaft seal or the like. In the boundary wall (20) is sealingly guided. Verbennungsmotor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Kolbenstange (18) über eine Kulisse (25), Schwinge oder dgl. mit der Kurbelwelle (13) verbunden ist.Internal combustion engine according to one of the preceding claims, characterized in that the piston rod (18) is connected to the crankshaft (13) via a link (25), rocker arm or the like. Verbennungsmotor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Vorkammer (21) mit einem ein Einlaßventil (10) aufweisenden Einlaßkanal (8) versehen ist.Internal combustion engine according to one of the preceding claims, characterized in that the prechamber (21) is provided with an inlet duct (8) having an inlet valve (10). Verbennungsmotor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß der Hub- und Brennraum (5) mit einem ein Auslaßventil (11) aufweisenden Auslaßkanal (9) versehen ist.Internal combustion engine according to one of the preceding claims, characterized in that the lifting and combustion chamber (5) is provided with an outlet duct (9) having an outlet valve (11). Verbrennungsmotor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß das Volumen der Vorkammer (21) veränderbar ist.Internal combustion engine according to one of the preceding claims, characterized in that the volume of the prechamber (21) can be changed. Verbrennungsmotor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß das Volumen des Hub- und Brennraums (5) dem 0,5 bis 2-fachen Volumen der Vorkammer (21) entspricht.Internal combustion engine according to one of the preceding claims, characterized in that the volume of the lifting and combustion chamber (5) corresponds to 0.5 to 2 times the volume of the prechamber (21).
EP93116664A 1992-10-16 1993-10-15 Internal combustion engine Expired - Lifetime EP0593064B1 (en)

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DE4234941A DE4234941C2 (en) 1992-10-16 1992-10-16 Internal combustion engine

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WO2004022945A1 (en) * 2002-08-12 2004-03-18 Peter Pelz Reciprocating piston engine and piston therefor
WO2004022947A1 (en) * 2002-08-12 2004-03-18 Peter Pelz Reciprocating piston engine and method for controlling the same
RU2665763C1 (en) * 2017-03-16 2018-09-04 Александр Николаевич Сергеев Internal combustion engine and method of control thereof
RU2718463C1 (en) * 2019-03-20 2020-04-08 Александр Николаевич Сергеев Internal combustion engine and control method thereof
EP3507471A4 (en) * 2016-08-30 2020-06-03 Mercier, Cesar A two stroke engine with valves actuated by air pressure near bottom dead center
RU2740663C1 (en) * 2020-04-20 2021-01-19 Александр Николаевич Сергеев Internal combustion engine

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DE102004030184A1 (en) * 2004-06-22 2006-01-19 Helmut Obieglo Internal combustion engine has cylinder, piston, piston rod and eccentric shaft that form transmission structure
DE102009038850B4 (en) * 2009-08-26 2016-12-15 Theodor Appel Boxer engine with backdrop connecting rod

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Cited By (6)

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Publication number Priority date Publication date Assignee Title
WO2004022945A1 (en) * 2002-08-12 2004-03-18 Peter Pelz Reciprocating piston engine and piston therefor
WO2004022947A1 (en) * 2002-08-12 2004-03-18 Peter Pelz Reciprocating piston engine and method for controlling the same
EP3507471A4 (en) * 2016-08-30 2020-06-03 Mercier, Cesar A two stroke engine with valves actuated by air pressure near bottom dead center
RU2665763C1 (en) * 2017-03-16 2018-09-04 Александр Николаевич Сергеев Internal combustion engine and method of control thereof
RU2718463C1 (en) * 2019-03-20 2020-04-08 Александр Николаевич Сергеев Internal combustion engine and control method thereof
RU2740663C1 (en) * 2020-04-20 2021-01-19 Александр Николаевич Сергеев Internal combustion engine

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DE4234941C2 (en) 1995-05-18
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DE59304961D1 (en) 1997-02-13
ES2096834T3 (en) 1997-03-16

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