DE19651175C2 - Counter-piston two-stroke internal combustion engine with direct fuel injection into the cylinder and adjustable rotation and turbulence of the charge air - Google Patents
Counter-piston two-stroke internal combustion engine with direct fuel injection into the cylinder and adjustable rotation and turbulence of the charge airInfo
- Publication number
- DE19651175C2 DE19651175C2 DE19651175A DE19651175A DE19651175C2 DE 19651175 C2 DE19651175 C2 DE 19651175C2 DE 19651175 A DE19651175 A DE 19651175A DE 19651175 A DE19651175 A DE 19651175A DE 19651175 C2 DE19651175 C2 DE 19651175C2
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- cylinder
- piston
- counter
- internal combustion
- combustion engine
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Classifications
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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
- F02B23/00—Other engines characterised by special shape or construction of combustion chambers to improve operation
- F02B23/02—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition
- F02B23/06—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition the combustion space being arranged in working piston
- F02B23/0636—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition the combustion space being arranged in working piston the combustion space having a substantially flat and horizontal bottom
- F02B23/0639—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition the combustion space being arranged in working piston the combustion space having a substantially flat and horizontal bottom the combustion space having substantially the shape of a cylinder
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B23/00—Other engines characterised by special shape or construction of combustion chambers to improve operation
- F02B23/02—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition
- F02B23/06—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition the combustion space being arranged in working piston
- F02B23/0618—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition the combustion space being arranged in working piston having in-cylinder means to influence the charge motion
- F02B23/0627—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition the combustion space being arranged in working piston having in-cylinder means to influence the charge motion having additional bores or grooves machined into the piston for guiding air or charge flow to the piston bowl
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B23/00—Other engines characterised by special shape or construction of combustion chambers to improve operation
- F02B23/02—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition
- F02B23/06—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition the combustion space being arranged in working piston
- F02B23/0636—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition the combustion space being arranged in working piston the combustion space having a substantially flat and horizontal bottom
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B23/00—Other engines characterised by special shape or construction of combustion chambers to improve operation
- F02B23/02—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition
- F02B23/06—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition the combustion space being arranged in working piston
- F02B23/0678—Unconventional, complex or non-rotationally symmetrical shapes of the combustion space, e.g. flower like, having special shapes related to the orientation of the fuel spray jets
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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
- F02B25/02—Engines characterised by using fresh charge for scavenging cylinders using unidirectional scavenging
- F02B25/08—Engines with oppositely-moving reciprocating working pistons
-
- 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
- F02B75/28—Engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B75/00—Other engines
- F02B75/02—Engines characterised by their cycles, e.g. six-stroke
- F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
- F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B2275/00—Other engines, components or details, not provided for in other groups of this subclass
- F02B2275/14—Direct injection into combustion chamber
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
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)
Description
Gegenkolben-Zweitakt-Verbrennungsmotor mit Direkteinspritzung des Kraft stoffes in den Zylinder und regelbarer Rotation und Turbulenz der Ladeluft.Counter-piston two-stroke internal combustion engine with direct fuel injection material in the cylinder and adjustable rotation and turbulence of the charge air.
Gegenkolben-Zweitakt-Verbrennungsmotoren sind seit langer Zeit bekannt. Sie wurden überwiegend als Dieselmotoren betrieben (Patent 220 124 vom 27.09. 1907) aber auch als Benzinmotoren (DE-PS 906 633, DE-PS 43 35 515, Motor technische Zeitschrift 52, 1991). Bei Viertaktmotoren wird versucht, mit Hilfe teilweise abschaltbarer Drallkanäle zu der erforderlichen Turbulenz der Ladeluft für eine homogene Gemischbildung zu kommen. Bei Zweitaktmotoren besteht als genereller Nachteil die schwer überschaubare Vermischung von Frischgas und Abgas während des Ladungswechsels. Eine steuerbare Beeinflussung von Rotation und Turbulenz der Zylinderladung ist nicht bekannt.Counter-piston two-stroke internal combustion engines have been known for a long time. she were mainly operated as diesel engines (Patent 220 124 dated September 27. 1907) but also as petrol engines (DE-PS 906 633, DE-PS 43 35 515, engine technical journal 52, 1991). With four-stroke engines, an attempt is made to help swirl channels that can be partially switched off to the required turbulence of the charge air to come for a homogeneous mixture formation. With two-stroke engines as a general disadvantage the mixing of fresh gas and Exhaust gas during the gas exchange. A controllable influencing of Rotation and turbulence of the cylinder charge is unknown.
Der im Patentanspruch 1 angegebenen Erfindung liegt das Problem zugrunde, die Vorteile des Zweitaktmotors in Bezug auf geringe Reibungsverluste und niedrige Drehzahl (kein Leerhub wie beim Viertakter) mit einer Ladeluftversorgung zu verbinden, die alle Voraussetzungen für die homogene Vermischung des einge spritzten Kraftstoffes und eine effiziente Verbrennung in allen Lastzuständen schafft.The invention specified in claim 1 is based on the problem that Advantages of the two-stroke engine in terms of low friction losses and low Speed (no idle stroke as with the four-stroke engine) with a charge air supply combine all the requirements for the homogeneous mixing of the turned injected fuel and efficient combustion in all load conditions creates.
Das Problem wird durch die in den Patentansprüchen 1 bis 15 aufgeführten Merkmale gelöst.The problem is solved by those listed in claims 1 to 15 Features resolved.
Die mit der Erfindung erzielten Vorteile bestehen insbesondere darin, daß die Bewegung der Ladeluftmasse (Rotation und Turbulenz) beliebig veränderbar ist und der vom Lastzustand des Motors abhängigen Kraftstoffeinspritzung so an gepasst wird, daß eine homogene Kraftstoff-Luft-Mischung entsteht. Durch die Form des Brennraumes wird die Luftbewegung vor und während des Einspritz vorganges noch einmal verstärkt, damit die Luftgeschwindigkeit größer wird als die Kraftstoffgeschwindigkeit.The advantages achieved by the invention are in particular that the Movement of the charge air mass (rotation and turbulence) can be changed as desired and the fuel injection dependent on the load state of the engine fit that a homogeneous fuel-air mixture is created. Through the The shape of the combustion chamber is the air movement before and during the injection process intensified again so that the air speed is greater than the fuel speed.
Erreicht wird dies mit einem Gegenkolben-Zweitaktmotor mit Gleichstrom spülung, bei dem die Ladeluft durch am Zylinderumfang gleichmässig verteilte Einlaßschlitze A an einer Seite des langen Zylinders (Fig. 1) eintritt. This is achieved with a counter-piston two-stroke engine with DC purging, in which the charge air enters through uniformly distributed inlet slots A on one side of the long cylinder ( Fig. 1).
Die Stege zwischen den Schlitzen haben eine unsymmetrische Form, wie in Fig. 1 gezeigt. Strömt die Luft in Richtung R (Fig. 1), dann ist der Widerstand in allen Schlitzen gering und die Rotationsgeschwindigkeit der Luft im Zylinder groß. Strömt die Luft in umgekehrter Rotationsrichtung L (Fig. 2), dann ist der Widerstand groß und bei den Abreißkanten E und F (Fig. 2) entstehen Turbulenzen. Bei radialer Einströmung treffen alle Luftstrahlen im Zylinder auf einander und erzeugen eine hohe Turbulenz ohne Vorzugsrichtung nach R oder L (Fig. 3). Der Richtungsbereich zwischen R und L ist stufenlos veränderbar, da die Luftversorgung durch ein Ladeluft-Gebläse erfolgt und der Lufteintritt in den Ringspalt G (Fig. 1, 2, 3) zwischen Gehäuse und Zylinder über ein Regel klappensystem H (Fig. 1, 2, 3) erfolgt. Wird das Druckverhältnis zwischen Ladeluft und Abgas verändert, dann ändert sich die Luftgeschwindigkeit und die Turbulenz sowie die Zylinderfüllung. Diese kann dadurch bis in den Bereich Ab gasrückhaltung abgesenkt werden.The webs between the slots have an asymmetrical shape, as shown in Fig. 1. If the air flows in the direction R ( Fig. 1), the resistance in all slots is low and the speed of rotation of the air in the cylinder is high. If the air flows in the opposite direction of rotation L ( FIG. 2), the resistance is high and turbulence occurs at the tear-off edges E and F ( FIG. 2). With radial inflow, all air jets in the cylinder meet and generate high turbulence with no preferred direction according to R or L ( Fig. 3). The directional range between R and L is infinitely variable, since the air is supplied by a charge air blower and the air enters the annular gap G ( Fig. 1, 2, 3) between the housing and cylinder via a control valve system H ( Fig. 1, 2 , 3) takes place. If the pressure ratio between charge air and exhaust gas is changed, the air speed and turbulence as well as the cylinder charge change. This can be lowered down to the gas retention area.
Die Kolbenböden K aus isolierendem und die Wärmestrahlung reflektierendem Material sind so geformt, daß sich bei Annäherung zweier Kolben eine zentrale Wirbelkammer W bildet (Fig. 4). Der Durchmesser dieser Wirbelkammer ist kleiner als der Zylinderdurchmesser, wodurch sich die Drehzahl des Luftwirbels entsprechend erhöht. Im Bereich der oberen Totpunkte nähern sich die kreis ringförmigen Stirnflächen S der beiden Kolben (Fig. 4) auf wenige Zehntel milimeter, wirken dadurch als Quetschflächen und befördern die dazwischen befindliche Luft mit erhöhter Geschwindigkeit in die Wirbelkammer. Durch Schußkanäle J (Fig. 4) wird der Kraftstoff direkt in die Wirbelkammer gespritzt. Die am Ende der Schußkanäle austretenden und zerstäubenden Strahlspitzen werden durch die intensive Luftbewegung sofort und stetig weggetragen. Dadurch wird eine homogene Gemischbildung gefördert und die bei der Ver brennung durch Luftmangel entstehenden Schadstoffe Kohlenmonoxid, Ruß und unverbrannte Kohlenwasserstoffe werden vermindert. Mit der einsetzenden Ver brennung wird die Wirbelkammer zur alleinigen Brennkammer. Der hochge zogene Umfang der beiden Wirbelkammerhälften (Fig. 4) deckt im Bereich der höchsten Verbrennungstemperaturen die wärmeabführenden Zylinderwände weitgehend ab und sorgt für einen guten thermischen Wirkungsgrad.The piston crowns K made of insulating material and reflecting the heat radiation are shaped such that a central swirl chamber W is formed when two pistons approach each other ( FIG. 4). The diameter of this vortex chamber is smaller than the cylinder diameter, which increases the speed of the vortex accordingly. In the area of the top dead centers, the circular ring-shaped end faces S of the two pistons ( FIG. 4) approach to a few tenths of a millimeter, thereby acting as squeezing areas and conveying the air in between into the swirl chamber at an increased speed. The fuel is injected directly into the swirl chamber through shot channels J ( FIG. 4). The jet tips emerging and atomizing at the end of the shot channels are immediately and continuously carried away by the intensive air movement. This promotes a homogeneous mixture formation and the pollutants carbon monoxide, soot and unburned hydrocarbons that are created during combustion due to lack of air are reduced. With the onset of combustion, the swirl chamber becomes the sole combustion chamber. The raised circumference of the two halves of the swirl chamber ( FIG. 4) largely covers the heat-dissipating cylinder walls in the region of the highest combustion temperatures and ensures good thermal efficiency.
Eine hohe Literleistung durch Erhöhung der Drehzahl des Gegenkolben-Zweitakt- Motors kann erreicht werden, wenn pro Zylinder zwei Einspritzdüsen verwendet werden, die nacheinander zum Einsatz kommen. A high liter output by increasing the speed of the counter-piston two-stroke The engine can be achieved by using two injectors per cylinder that are used one after the other.
Beispiel: 3-Zylinder-Zweitakt-Gegenkolbenmotor mit einer 6-Zylinder-Einspritz pumpe und 2 Einspritzdüsen pro Zylinder. Die maximale Motordrehzahl erhöht sich damit auf das Doppelte der Einspritzpumpen-Grenzdrehzahl. Durch die erhöhte Motordrehzahl werden die Kräfte der oszillierenden Massen größer und wirken dämpfend auf die Gaskräfte. Der Motor kann mit geringerem Gewicht hergestellt werden.Example: 3-cylinder two-stroke counter-piston engine with a 6-cylinder injection pump and 2 injectors per cylinder. The maximum engine speed increases double the injection pump speed limit. Through the increased engine speed, the forces of the oscillating masses become larger and have a dampening effect on gas forces. The engine can be lighter in weight getting produced.
Die Verwendungsmöglichkeit mehrerer Düsen pro Zylinder kann auch dazu be nutzt werden, die Gesamteinspritzmenge aufzuteilen, um kürzere Einspritzzeiten zu erreichen. Einspritzbeginn und -dauer der einzelnen Teilmengen können variiert werden.The possibility of using several nozzles per cylinder can also be used be used to divide the total injection quantity in order to shorten injection times to reach. Injection start and duration of the individual subsets can can be varied.
Die Zylinder bilden auf ihrer Einlaßseite mit dem Gehäuse einen Ringraum G (Fig. 1, 2, 3), in dem die Ladeluft stömungsstabilisiert und gleichmässig ver teilt wird. Für das gleichmässige Einströmen in die Zylinder sind die Einlaß schlitze A (Fig. 1, 2, 3) gleich groß und liegen in einer Ebene. Auf der Auslaß seite sind die Schlitze symmetrisch (Fig. 5), und die dazwischen liegenden Stege M sind wegen der Wärmebelastung flüssigkeitsgekühlt, haben eine strömungsgünstige Form und eine möglichst kleine Oberfläche. Zur Ver besserung der Wärmeabfuhr besitzt der Zylinder mehrere Leitrippen Q (Fig. 5), welche auch für die gleichmässige Durchströmung der Auslaßstege M sorgen.The cylinders form on their inlet side with the housing an annular space G ( Fig. 1, 2, 3) in which the charge air is flow-stabilized and evenly divided ver. For the uniform inflow into the cylinder, the inlet slots A ( Fig. 1, 2, 3) are the same size and are in one plane. On the outlet side, the slots are symmetrical ( Fig. 5), and the webs M in between are liquid-cooled due to the heat load, have a streamlined shape and the smallest possible surface. To improve heat dissipation, the cylinder has several guide ribs Q ( Fig. 5), which also ensure the uniform flow through the outlet webs M.
Durch die gegenläufige Bewegung von je 2 Kolben in einem Zylinder entstehen in axialer Richtung nur geringe freie Reibungskräfte. Der Zylinder kann deswegen ausschließlich mit Hilfe der erforderlichen Dichtungselemente D (Fig. 6) fixiert werden. Diese übernehmen auch die Belastungen durch die Kolbenseitenkräfte und dienen zur Schwingungs- und Geräuschdämpfung. Kontakt-, Spalt- und Reibungskorrosion wird verhindert und Wärmedehnungen werden ausgeglichen. Damit können verschiedenartige Werkstoffe für Zylinder und Gehäuse problemlos verwendet werden.Due to the opposite movement of 2 pistons in a cylinder, only small free frictional forces arise in the axial direction. The cylinder can therefore only be fixed using the required sealing elements D ( Fig. 6). These also take over the loads from the piston side forces and serve to dampen vibrations and noise. Contact, crevice and friction corrosion is prevented and thermal expansion is compensated. Different materials for cylinders and housings can be used without any problems.
Das Gehäuse zur Aufnahme der Zylinder und der beiden Kurbeltriebe besteht aus 2 Teilen. Die Trennfläche T fällt mit den Zylinderachsen C zusammen (Fig. 7). Der Kraftfluß zwischen den Kurbelwellen bleibt ungestört. Die so gestaltete Gehäuseteilung ermöglicht es auch, die Auslaßkanäle vollständig mit einer Isolierung N zu versehen (Fig. 5), um eine unnötige Erwärmung des Gehäuses durch die Abgase zu vermeiden.The housing for receiving the cylinders and the two crank mechanisms consists of two parts. The interface T coincides with the cylinder axes C ( Fig. 7). The power flow between the crankshafts remains undisturbed. The housing division designed in this way also makes it possible to provide the outlet channels completely with insulation N ( FIG. 5) in order to avoid unnecessary heating of the housing by the exhaust gases.
Ein Ausführungsbeispiel der Erfindung ist in den Zeichnungen dargestellt und wird im folgenden näher beschrieben.An embodiment of the invention is shown in the drawings and will described in more detail below.
Es zeigenShow it
Fig. 1 einen Motorzylinder
mit dem die einströmende Luft in Richtung R steuernden Klappen
system H, dem Ringspalt G, in dem die Luft strömungsstabilisiert und
gleichmässig verteilt wird und die Einlaßschlitze A.
Der Luftwiderstand in den Einlaßschlitzen, die als Düsen wirken, ist
gering und die Rotationsgeschwindigkeit der Ladeluftsäule im Zylinder
ist groß. Fig. 1 an engine cylinder with the incoming air controlled in direction R flap system H, the annular gap G, in which the air flow is stabilized and is uniformly distributed and the inlet slots A.
The air resistance in the inlet slots, which act as nozzles, is low and the speed of rotation of the charge air column in the cylinder is high.
Fig. 2 den gleichen Motorzylinder mit der in Richtung L einströmenden Luft. Die Einlaßschlitze A er zeugen einen hohen Luftwiderstand und an den Abreißkanten E und F beginnt Wirbelbildung. Die Rotationsgeschwindigkeit wird kleiner, die Gesamtverwirbelung intensiver. Fig. 2 shows the same engine cylinder with the air flowing in the direction L. The inlet slots A he create a high air resistance and vortex formation begins at the tear-off edges E and F. The speed of rotation becomes slower, the total turbulence more intense.
Fig. 3 den gleichen Motorzylinder
mit radial einströmender Luft. Der Luftwiderstand in den Einlaß
schlitzen ist gering. Im Zylinder wird keine Rotation der Ladeluftsäule
erzeugt, aber die Verwirbelung ist durch die aufeinandertreffenden
Luftstrahlen stark.
Die Zustände von Fig. 1 über Fig. 2 bis zu Fig. 3 sind stufenlos
veränderbar. Fig. 3 shows the same engine cylinder with radially inflowing air. The air resistance in the inlet slits is low. No rotation of the charge air column is generated in the cylinder, but the turbulence is strong due to the colliding air jets.
The states from FIG. 1 to FIG. 2 to FIG. 3 can be changed continuously.
Fig. 4 einen Motorzylinder mit im OT-Bereich befindlichen Kolben. Die Kolbenböden K aus isolierendem und die Wärmestrahlung reflektierendem Material bilden eine zentrale Wirbelkammer W, die durch Schußkanäle J mit den (nicht gezeigten) Einspritzdüsen in Verbindung stehen. Die Rotationsge schwindigkeit der Luft ist im Fall der Fig. 1 größer als die Ge schwindigkeit des Kraftstoffstrahles. Durch den Umfang der Wirbel kammer W, die gleichzeitig Brennkammer ist, wird die Zylinderwand weitgehend abgeschirmt. Die Kreisringflächen S dienen als Quetsch flächen. Fig. 4 shows an engine cylinder with pistons located in the TDC area. The piston crowns K made of insulating material and reflecting the heat radiation form a central swirl chamber W, which are connected by shot channels J to the injection nozzles (not shown). The speed of rotation of the air in the case of FIG. 1 is greater than the speed of the fuel jet. Due to the size of the vortex chamber W, which is also the combustion chamber, the cylinder wall is largely shielded. The circular ring surfaces S serve as squeezing surfaces.
Fig. 5 den Auslaß-Bereich eines Motorzylinders mit den die Auslaßöffnungen bildenden, wassergekühlten Stegen. Ein Teilstrom des Kühlwassers wird durch die Leitrippen Q abgezweigt und durchfließt die Auspuffstege. Die Isolierschicht N vermindert den Wärmeübergang auf das Motorgehäuse. Fig. 5 shows the outlet area of an engine cylinder with the water-cooled webs forming the outlet openings. A partial flow of the cooling water is branched off by the guide ribs Q and flows through the exhaust webs. The insulating layer N reduces the heat transfer to the motor housing.
Fig. 6 einen Schnitt durch die Zylinderbefestigung mittels der multifunktionalen Dichtelemente D. Eine metallische Be rührung zwischen Zylinder und Gehäuse existiert nicht. Die Dicht elemente D sind elastisch und nehmen unterschiedliche Wärme dehnungen auf. Fig. 6 shows a section through the cylinder attachment by means of the multifunctional sealing elements D. There is no metallic contact between the cylinder and the housing. The sealing elements D are elastic and absorb different thermal expansions.
Fig. 7 das zweigeteilte Motorgehäuse für die Aufnahme der Zylinder. Der Kraftfluß P-P zwischen den Kurbel wellenlagern wird duch keine Trennfuge unterbrochen. Im montierten Zustand fallen die Flächen D mit der Zylinderachse C zusammen. Fig. 7 shows the two-part motor housing for receiving the cylinder. The power flow PP between the crankshaft bearings is interrupted by no parting line. When assembled, the surfaces D coincide with the cylinder axis C.
Claims (15)
Priority Applications (1)
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DE19651175A DE19651175C2 (en) | 1996-12-10 | 1996-12-10 | Counter-piston two-stroke internal combustion engine with direct fuel injection into the cylinder and adjustable rotation and turbulence of the charge air |
Applications Claiming Priority (1)
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DE19651175A DE19651175C2 (en) | 1996-12-10 | 1996-12-10 | Counter-piston two-stroke internal combustion engine with direct fuel injection into the cylinder and adjustable rotation and turbulence of the charge air |
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DE19651175A1 DE19651175A1 (en) | 1998-06-25 |
DE19651175C2 true DE19651175C2 (en) | 1999-12-30 |
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DE10352243B4 (en) * | 2003-11-04 | 2009-02-19 | Golle, Hermann, Dr.-Ing. | Counter-piston engine with a cylinder crankcase (ZKG) split in the plane of the crankshaft centers |
US10180115B2 (en) | 2010-04-27 | 2019-01-15 | Achates Power, Inc. | Piston crown bowls defining combustion chamber constructions in opposed-piston engines |
US8800528B2 (en) | 2010-04-27 | 2014-08-12 | Achates Power, Inc. | Combustion chamber constructions for opposed-piston engines |
US9512779B2 (en) | 2010-04-27 | 2016-12-06 | Achates Power, Inc. | Swirl-conserving combustion chamber construction for opposed-piston engines |
US8820294B2 (en) | 2010-08-16 | 2014-09-02 | Achates Power, Inc. | Fuel injection spray patterns for opposed-piston engines |
CN103562515B (en) | 2011-05-18 | 2018-12-04 | 阿凯提兹动力公司 | The combustion chamber structure of opposed-piston engine |
US20130104848A1 (en) | 2011-10-27 | 2013-05-02 | Achates Power, Inc. | Fuel Injection Strategies in Opposed-Piston Engines with Multiple Fuel Injectors |
CN103216311B (en) * | 2013-04-07 | 2015-01-28 | 朱晓义 | Automobile engine and power device |
US9211797B2 (en) | 2013-11-07 | 2015-12-15 | Achates Power, Inc. | Combustion chamber construction with dual mixing regions for opposed-piston engines |
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DE490175C (en) * | 1930-01-24 | Aeg | Air or gas supply through cylinder slots in internal combustion engines, especially two-stroke diesel engines | |
GB520243A (en) * | 1938-10-15 | 1940-04-18 | John Howard Goodman | Internal combustion engines of the compression ignition type |
US3485221A (en) * | 1967-12-11 | 1969-12-23 | Ralph S Feeback | Omnitorque opposed piston engine |
US3712276A (en) * | 1970-09-08 | 1973-01-23 | B Foster | Engine and gas generator |
DE2325940A1 (en) * | 1973-05-22 | 1973-12-13 | Toyo Kogyo Co | FUEL INJECTION SYSTEM FOR ROTARY PISTON ENGINES |
DE2300407A1 (en) * | 1973-01-05 | 1974-07-11 | Elsbett Gmbh Geb | COMBUSTION MACHINE WITH AT LEAST TWO PISTONS EACH INTO A COMMON CYLINDER |
DE2700991A1 (en) * | 1977-01-12 | 1978-07-13 | Erich Tausend | Opposed piston two:stroke diesel engine - has cylinders at angle, common head, and exhaust pulse charge system with three way control valve |
DE2839051A1 (en) * | 1977-09-07 | 1979-03-15 | Nippon Soken | COUNTERPISTON, TWO-STROKE COMBUSTION MACHINE WITH DC FLUSHING |
GB1600049A (en) * | 1977-07-21 | 1981-10-14 | Piaggio & C Spa | Twostroke engine wiht layered charge |
DE3151293A1 (en) * | 1981-12-24 | 1983-07-07 | Robert Bosch Gmbh, 7000 Stuttgart | FUEL INJECTION SYSTEM FOR DIRECT FUEL INJECTION IN COMBUSTION ENGINES |
DE2854346C2 (en) * | 1978-08-02 | 1983-11-17 | Toyota Jidosha Kogyo K.K., Toyota, Aichi | Two-stroke diesel internal combustion engine |
DE3330774A1 (en) * | 1983-08-26 | 1985-03-14 | Robert Bosch Gmbh, 7000 Stuttgart | FUEL INJECTION DEVICE WITH PRIMARY AND MAIN INJECTION IN INTERNAL COMBUSTION ENGINES |
DE3940027A1 (en) * | 1989-12-04 | 1990-08-23 | Harry Steinke | Opposed piston two=stroke IC engine - uses supercharged air supply and fuel injection into cylinders |
US5081961A (en) * | 1989-08-01 | 1992-01-21 | Paul Marius A | Internal combustion engine with rotary exhaust control |
US5081963A (en) * | 1986-09-04 | 1992-01-21 | Galbraith Engineering Pty. Ltd. | Reciprocatory machines |
DE9209897U1 (en) * | 1992-07-23 | 1992-11-05 | Klug, Elmar, 8729 Knetzgau | Two-stroke internal combustion engine |
EP0586775A1 (en) * | 1992-09-11 | 1994-03-16 | New Sulzer Diesel Ag | Method to inject fuel in Diesel engines |
DE4407506A1 (en) * | 1994-03-07 | 1994-08-04 | Woyderski Georg Dipl Ing Fh | I.C. piston engine with two centre-symmetrical pistons |
DE4335515A1 (en) * | 1993-10-19 | 1995-04-20 | Otto C Pulch | Opposed-piston two-stroke internal combustion engine with spark ignition, direct fuel injection into the cylinder and stratified charge |
DE4340267A1 (en) * | 1993-11-26 | 1995-06-01 | Mahle Gmbh | Alloy piston for diesel engine |
DE19521378A1 (en) * | 1995-06-13 | 1996-12-19 | Elsbett L | Two=stroke diesel boxer engine with reduced performance loss |
-
1996
- 1996-12-10 DE DE19651175A patent/DE19651175C2/en not_active Expired - Fee Related
Patent Citations (21)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE490175C (en) * | 1930-01-24 | Aeg | Air or gas supply through cylinder slots in internal combustion engines, especially two-stroke diesel engines | |
GB520243A (en) * | 1938-10-15 | 1940-04-18 | John Howard Goodman | Internal combustion engines of the compression ignition type |
US3485221A (en) * | 1967-12-11 | 1969-12-23 | Ralph S Feeback | Omnitorque opposed piston engine |
US3712276A (en) * | 1970-09-08 | 1973-01-23 | B Foster | Engine and gas generator |
DE2300407A1 (en) * | 1973-01-05 | 1974-07-11 | Elsbett Gmbh Geb | COMBUSTION MACHINE WITH AT LEAST TWO PISTONS EACH INTO A COMMON CYLINDER |
DE2325940A1 (en) * | 1973-05-22 | 1973-12-13 | Toyo Kogyo Co | FUEL INJECTION SYSTEM FOR ROTARY PISTON ENGINES |
DE2700991A1 (en) * | 1977-01-12 | 1978-07-13 | Erich Tausend | Opposed piston two:stroke diesel engine - has cylinders at angle, common head, and exhaust pulse charge system with three way control valve |
GB1600049A (en) * | 1977-07-21 | 1981-10-14 | Piaggio & C Spa | Twostroke engine wiht layered charge |
DE2839051A1 (en) * | 1977-09-07 | 1979-03-15 | Nippon Soken | COUNTERPISTON, TWO-STROKE COMBUSTION MACHINE WITH DC FLUSHING |
DE2854346C2 (en) * | 1978-08-02 | 1983-11-17 | Toyota Jidosha Kogyo K.K., Toyota, Aichi | Two-stroke diesel internal combustion engine |
DE3151293A1 (en) * | 1981-12-24 | 1983-07-07 | Robert Bosch Gmbh, 7000 Stuttgart | FUEL INJECTION SYSTEM FOR DIRECT FUEL INJECTION IN COMBUSTION ENGINES |
DE3330774A1 (en) * | 1983-08-26 | 1985-03-14 | Robert Bosch Gmbh, 7000 Stuttgart | FUEL INJECTION DEVICE WITH PRIMARY AND MAIN INJECTION IN INTERNAL COMBUSTION ENGINES |
US5081963A (en) * | 1986-09-04 | 1992-01-21 | Galbraith Engineering Pty. Ltd. | Reciprocatory machines |
US5081961A (en) * | 1989-08-01 | 1992-01-21 | Paul Marius A | Internal combustion engine with rotary exhaust control |
DE3940027A1 (en) * | 1989-12-04 | 1990-08-23 | Harry Steinke | Opposed piston two=stroke IC engine - uses supercharged air supply and fuel injection into cylinders |
DE9209897U1 (en) * | 1992-07-23 | 1992-11-05 | Klug, Elmar, 8729 Knetzgau | Two-stroke internal combustion engine |
EP0586775A1 (en) * | 1992-09-11 | 1994-03-16 | New Sulzer Diesel Ag | Method to inject fuel in Diesel engines |
DE4335515A1 (en) * | 1993-10-19 | 1995-04-20 | Otto C Pulch | Opposed-piston two-stroke internal combustion engine with spark ignition, direct fuel injection into the cylinder and stratified charge |
DE4340267A1 (en) * | 1993-11-26 | 1995-06-01 | Mahle Gmbh | Alloy piston for diesel engine |
DE4407506A1 (en) * | 1994-03-07 | 1994-08-04 | Woyderski Georg Dipl Ing Fh | I.C. piston engine with two centre-symmetrical pistons |
DE19521378A1 (en) * | 1995-06-13 | 1996-12-19 | Elsbett L | Two=stroke diesel boxer engine with reduced performance loss |
Also Published As
Publication number | Publication date |
---|---|
DE19651175A1 (en) | 1998-06-25 |
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