EP0187930A2 - Multiple cylinder internal-combustion engine - Google Patents

Multiple cylinder internal-combustion engine Download PDF

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Publication number
EP0187930A2
EP0187930A2 EP85115114A EP85115114A EP0187930A2 EP 0187930 A2 EP0187930 A2 EP 0187930A2 EP 85115114 A EP85115114 A EP 85115114A EP 85115114 A EP85115114 A EP 85115114A EP 0187930 A2 EP0187930 A2 EP 0187930A2
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EP
European Patent Office
Prior art keywords
crank
longitudinal axis
cylinder
cylinders
pairs
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP85115114A
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German (de)
French (fr)
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EP0187930A3 (en
EP0187930B1 (en
Inventor
Hamann Lutz
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Ficht GmbH
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Ficht GmbH
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Priority to AT85115114T priority Critical patent/ATE44802T1/en
Publication of EP0187930A2 publication Critical patent/EP0187930A2/en
Publication of EP0187930A3 publication Critical patent/EP0187930A3/en
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Publication of EP0187930B1 publication Critical patent/EP0187930B1/en
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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
    • F02B75/00—Other engines
    • F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
    • F02B75/18—Multi-cylinder engines
    • F02B75/24—Multi-cylinder engines with cylinders arranged oppositely relative to main shaft and of "flat" type
    • F02B75/246—Multi-cylinder engines with cylinders arranged oppositely relative to main shaft and of "flat" type with only one crankshaft of the "pancake" type, e.g. pairs of connecting rods attached to common crankshaft bearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B1/00—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements
    • F01B1/08—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements with cylinders arranged oppositely relative to main shaft and of "flat" type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
    • F01B9/02—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with crankshaft
    • F01B9/023—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with crankshaft of Bourke-type or Scotch yoke
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
    • F01B9/02—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with crankshaft
    • F01B9/026—Rigid connections between piston and rod; Oscillating 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
    • F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
    • F02B75/18—Multi-cylinder engines
    • F02B75/22—Multi-cylinder engines with cylinders in V, fan, or star arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
    • F02B75/18—Multi-cylinder engines
    • F02B75/22—Multi-cylinder engines with cylinders in V, fan, or star arrangement
    • F02B75/222—Multi-cylinder engines with cylinders in V, fan, or star arrangement with cylinders in star arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
    • F02B75/18—Multi-cylinder engines
    • F02B2075/1804—Number of cylinders
    • F02B2075/1816—Number of cylinders four

Definitions

  • the invention relates to a multi-cylinder internal combustion engine according to the preamble of claim 1.
  • each piston requires its own crank pin within the crankshaft, so that a large overall length for the crankshaft very quickly results with the resulting difficulties in its storage.
  • manufacture of such cranked crankshafts is expensive.
  • the overall length of the entire engine is also large iFurthermore, two cylinder internal combustion piston machines with axially are ü b succumbing arranged working cylinders known as the so-called boxer engines, the reciprocating piston via a rigid piston rod with centrally located K urbelschleifentrieb kinematically coupled. see. DE-PS 409 919. They are advantageous over multi-cylinder internal combustion piston machines with conventional connecting rod crank mechanisms.
  • the kinematics of the crank loop drive Thanks to the kinematics of the crank loop drive, the dwell times at the top and bottom dead center are extended, which has a favorable effect on the flushing and charging processes and the combustion process. Furthermore, the rectilinear movement of the two piston rods enables an effective sealing of the cylinder space from the crankcase by means of partition walls which are only penetrated by the piston rods, the bearings of which can be sealed relatively easily. These partitions also result in a rigid construction for the motor housing, and the dynamic forces occurring on the crank loop drive can be absorbed in the motor housing without any problems. The overall frictional forces are reduced in that the crank loop frame itself does not need to be stored. All of these measures shorten the overall motor length. The effective sealing of the interior of the crank loop drive from the cylinder chambers with their chemically aggressive climate increases the service life of the internal combustion engine.
  • the object of the invention is to achieve further conceptual improvements by means of a new design of the boxer engine type mentioned, in particular to create multi-cylinder internal combustion engines using the boxer principle, the pistons of which are coupled to one another via rigid piston rods and can act on a crank pin as far as possible .
  • the invention thus achieves an astonishingly simple manner in a compact engine design and a large number of bearings are saved, as a result of which the power-to-weight ratio is improved and the construction volume is reduced, and in particular the construction length is shortened.
  • constructive simplifications are achieved with respect to the crank output, which also makes engine production cheaper, since only crankshaft cranking with a crank pin is required for a four-cylinder engine.
  • the balancing masses can be reduced and the smooth running of the internal combustion engine improves. This also increases the lifespan.
  • the so-called modular principle can be carried out in a simple manner, so that motors of different power ranges can be realized with the same structural units.
  • the first pair of cylinders consists of the two working cylinders 1 and 2, which lie opposite one another with the same axis. In them run pistons 3 and 4, on which piston rods 5 and 6 are rigidly attached. These are, on the other hand, firmly connected to a crank loop frame 7, which includes a rectilinear link 8, the longitudinal axis L8 of which is directed at an angle of 90 ° transversely to the longitudinal axis L1, 2 of the two working cylinders 1 and 2.
  • Figure 3 the first pair of cylinders consists of the two working cylinders 1 and 2, which lie opposite one another with the same axis. In them run pistons 3 and 4, on which piston rods 5 and 6 are rigidly attached. These are, on the other hand, firmly connected to a crank loop frame 7, which includes a rectilinear link 8, the longitudinal axis L8 of which
  • the second pair of cylinders consists of the two working cylinders 11 and 12, which likewise lie opposite one another with the same axis.
  • Working pistons 13 and 14 run in them, on which piston rods 15 and 16 are rigidly attached.
  • crank loop frame 17 which includes a rectilinear link 18, the longitudinal axis L 18 of which is directed at an angle of 90 ° transverse to the longitudinal axis L11, 12 of the two working cylinders 11 and 12.
  • a sliding block 19 moves in the backdrop 18 and is likewise rotatably mounted on the crank pin 10 of the crank mechanism 20.
  • the two longitudinal axes L8 and L18 of the two scenes 8 and 18 also intersect perpendicularly.
  • crank loop frames 7 and 17 lie side by side on the crank pin 10 of the crank drive 20.
  • the synchronism of all four working pistons achieved by the selected arrangement of two crank loops on a crank pin has the advantage that the balancing mass corresponds to the translationally moving mass of a conventional two-cylinder unit.
  • the centrifugal force in each crankshaft position is just as large as the resulting mass of two two-cylinder units. All that remains is a residual mass force, resulting from the small distance between the piston rods, which are offset by 90 °, and the masses that move with them in a translatory manner.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
  • Valve Device For Special Equipments (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)

Abstract

1. Four-cylinder internal-combustion engine having two cylinders (1/2, 11/12) at a time arranged in pairs and coaxially opposite, the longitudinal axes (L1/L2, L11/L12) of the two cylinder pairs (1/2, 11/12) being arranged at an angle of 90 degrees to each other, having a transmission device to convert the translatory movement of the pistons (3/4, 13/14) which slide in the cylinders (1/2, 11/12) and their piston rods (5/6, 15/16) connected rigidly to them into a rotatory movement of an output shaft (21), comprising two frame parts (7, 17) arranged consecutively in the direction of the longitudinal axis (23) of the output shafty (21) and each associated with a cylinder pair (1/2, 11/12), to each of which two piston rods (5/6, 15/16) of a cylinder pair (1/2, 11/12) are fastened immovably by their ends remote from the pistons (3/4, 13/14) and which each exhibit a straight sliding block (8, 18) extending at right angles to the longitudinal axis (L1/L2, L11/l12) of the respective associated cylinder pair (1/2, 11/12), and an eccentric part of the output shaft (21) having a longitudinal axis (24) parallel to its longitudinal axis (24) parallel to its longitudinal axis (23), which slides in the sliding blocks (8, 18) of both frame parts (7, 17), and having at least one balance weight (22), characterized in that the output shaft (21) is constructed as a crankshaft (21) and the eccentric part (10) as a crank pin (10), that the two cylinder pairs (1/2, 11/12) are arranged consecutively in the direction of the longitudinal axis (23) of the crankshaft (21) and that balance weights (22) diametrically opposite the crank pin (10) are provided at both ends of the latter for a virtually total compensation of the reciprocating masses, the balance weights (22) corresponding to an effective radius of the mass, corresponding to the crank radius of one the two masses of one of the two cylinder pairs (1/2, 11/12) in translatory motion.

Description

Die Erfindung bezieht sich auf eine Mehrzylinder-Brennkraftkolbenmaschine nach dem Oberbegriff des Patentanspruches 1.The invention relates to a multi-cylinder internal combustion engine according to the preamble of claim 1.

Durch die DE-PS 241 538 ist eine Mehrzylinder-Brennkraftmaschine bekanntgeworden, deren vier Zylinder in einer Ebene befindlich angeordnet sind, wobei die Arbeitskolben jeweils zweier nebeneinander liegender Zylinder durch jeweils einen Kurbelschleifenrahmen gekoppelt sind. Dabei sind die beiden Kurbelschleifenrahmen koaxial zueinanderliegend angeordnet und ihre Kulissen befinden sich in deckungsgleicher Anordnung, so daß die vier Arbeitskolben der paarweise gegenüberliegenden Zylinder sich stets in gleicher Richtung bewegen. Dieser Gleichlauf aller vier Arbeitskolben mit den Kurbelschleifenrahmen bedingt jedoch große bewegte Massen in einer Richtung, was wiederum große Ausgleichsmassen erfordert. Damit erhöht sich das Baugewicht der Maschinen mit allen nachteiligen Begleitumständen.From DE-PS 241 538 a multi-cylinder internal combustion engine has become known, the four cylinders of which are arranged in one plane, the working pistons each being coupled to two cylinders lying side by side by a crank loop frame. The two crank loop frames are arranged coaxially to each other and their scenes are in a congruent arrangement, so that the four working pistons of the pairs of opposing cylinders always move in the same direction. However, this synchronization of all four working pistons with the crank loop frames requires large moving masses in one direction, which in turn requires large compensating masses. This increases the construction weight of the machines with all adverse circumstances.

Bei Mehrzylinder-Brennkraftmaschinen, deren Kolben über übliche Pleuel auf die Kurbelwelle weisen, erfordert jeder Kolben einen eigenen Kurbelzapfen innerhalb der Kurbelwelle, so daß sich sehr schnell eine große Baulänge für die Kurbelwelle mit den daraus resultierenden Schwierigkeiten bei ihrer Lagerung ergibt. Außerdem ist die Herstellung solcher vielfach gekröpfter Kurbelwellen teuer. Auch wird die Baulänge des gesamten Motors groß iFerner sind zwei Zylinder-Brennkraftkolbenmaschinen mit achsgleich gegen- überliegend angeordneten Arbeitszylindern als sog. Boxermotore bekannt, deren hin- und hergehende Arbeitskolben über eine starre Kolbenstange mit dem mittig gelegenen Kurbelschleifentrieb kinematisch gekoppelt sind; vgl. DE-PS 409 919. Sie sind gegenüber Mehrzylinder-Brennkraftkolbenmaschinen mit herkömmlichem Pleuel-Kurbeltrieb vorteilhaft. So werden durch die Kinematik des Kurbelschleifentriebes die Verweilzeiten im oberen und unteren Totpunkt verlängert, was sich günstig auf die Spül- und Ladungsvorgänge und den Verbrennungsablauf auswirkt. Ferner ermöglicht die geradlinige Bewegung der beiden Kolbenstangen eine wirkungsvolle Abdichtung des Zylinderraumes gegenüber dem Kurbelgehäuse durch Trennwände, die nur von den Kolbenstangen durchsetzt werden, deren Lagerungen relativ einfach abgedichtet werden können. Diese Trennwände bewirken außerdem eine steife Bauart für das Motorgehäuse, und die am Kurbelschleifentrieb auftretenden dynamischen Kräfte können im Motorengehäuse problemlos aufgenommen werden. Auch werden die Reibungskräfte insgesamt dadurch verringert, daß der Kurbelschleifenrahmen selbst nicht gelagert zu werden braucht. Durch alle diese Maßnahmen verkürzt sich die motorische Baulänge. Die wirksame Abdichtung des Innenraumes des Kurbelschleifentriebes gegenüber den Zylinderräumen mit deren chemisch aggressivem Klima erhöht die Lebensdauer der Brennkraftmaschine.In multi-cylinder internal combustion engines, the pistons of which have the usual connecting rods to the crankshaft, each piston requires its own crank pin within the crankshaft, so that a large overall length for the crankshaft very quickly results with the resulting difficulties in its storage. In addition, the manufacture of such cranked crankshafts is expensive. The overall length of the entire engine is also large iFurthermore, two cylinder internal combustion piston machines with axially are ü b succumbing arranged working cylinders known as the so-called boxer engines, the reciprocating piston via a rigid piston rod with centrally located K urbelschleifentrieb kinematically coupled. see. DE-PS 409 919. They are advantageous over multi-cylinder internal combustion piston machines with conventional connecting rod crank mechanisms. Thanks to the kinematics of the crank loop drive, the dwell times at the top and bottom dead center are extended, which has a favorable effect on the flushing and charging processes and the combustion process. Furthermore, the rectilinear movement of the two piston rods enables an effective sealing of the cylinder space from the crankcase by means of partition walls which are only penetrated by the piston rods, the bearings of which can be sealed relatively easily. These partitions also result in a rigid construction for the motor housing, and the dynamic forces occurring on the crank loop drive can be absorbed in the motor housing without any problems. The overall frictional forces are reduced in that the crank loop frame itself does not need to be stored. All of these measures shorten the overall motor length. The effective sealing of the interior of the crank loop drive from the cylinder chambers with their chemically aggressive climate increases the service life of the internal combustion engine.

Die Erfindung hat sich die Aufgabe gestellt, durch eine neue Bauform der genannten Boxermotorgattung weitere, konzeptionelle Verbesserungen zu erreichen, insbesondere unter Anwendung des Boxer-Prinzips Mehrzylinder-Brennkraftmaschinen zu schaffen, deren über starre Kolbenstangen miteinander gekoppelten Kolben möglichst auf einen Kurbelza"pfen wirken können.The object of the invention is to achieve further conceptual improvements by means of a new design of the boxer engine type mentioned, in particular to create multi-cylinder internal combustion engines using the boxer principle, the pistons of which are coupled to one another via rigid piston rods and can act on a crank pin as far as possible .

Diese Aufgabe ist gemäß der Erfindung durch die in den Patentansprüchen niedergelegten Merkmale gelöst.This object is achieved according to the invention by the features set out in the patent claims.

Durch die Erfindung wird also auf verblüffend einfache Weise eine kompakte Motorbauweise erreicht und werden eine Vielzahl von Lagerstellen eingespart, wodurch sich das Leistungsgewicht verbessert und das Bauvolumen verkleinert, dabei Insbesondere die Baulänge verkürzt. Außerdem werden konstruktive Vereinfachungen in bezug auf den Kurbelabtrieb erzielt, was auch die Motorfertigung verbilligt, da nur eine Kurbelwellenkröpfung mit einem Kurbelzapfen für einen Vierzylindermotor erforderlich ist. Durch die bauliche bzw. kinematische Trennung der beiden Kurbelschleifenrahmen für jedes gegenüberliegende Arbeitskolbenpaar und insbesondere die sternförmige Anordnung der beiden Arbeitszylinderpaare erfolgen bei einem Kurbelwellenumlauf bestimmte Gegenläufigkeiten der beiden senkrecht zueinander bewegten Massen, so daß ein teilweiser Massenausgleich zwischen diesen beiden Massensystemen auftritt. Die Ausgleichsmassen können verringert werden und die Laufruhe der Brennkraftmaschine verbessert sich. Damit erhöht sich auch die Lebensdauer. Ferner ist auf einfache Weise das sog. Baukastenprinzip durchführbar, so daß mit gleichen Baueinheiten Motoren unterschiedlicher Leistungsbereiche realisierbar sind.The invention thus achieves an astonishingly simple manner in a compact engine design and a large number of bearings are saved, as a result of which the power-to-weight ratio is improved and the construction volume is reduced, and in particular the construction length is shortened. In addition, constructive simplifications are achieved with respect to the crank output, which also makes engine production cheaper, since only crankshaft cranking with a crank pin is required for a four-cylinder engine. Due to the structural or kinematic separation of the two crank loop frames for each opposing pair of working pistons and in particular the star-shaped arrangement of the two pairs of working cylinders, certain counter-movements of the two masses moved perpendicular to one another take place during a crankshaft revolution, so that a partial mass balance occurs between these two mass systems. The balancing masses can be reduced and the smooth running of the internal combustion engine improves. This also increases the lifespan. Furthermore, the so-called modular principle can be carried out in a simple manner, so that motors of different power ranges can be realized with the same structural units.

In der Zeichnung ist ein Ausführungsbeispiel gemäß der Erfindung anhand einer Vierzylinder-Brennkraftmaschine dargestellt, das nachfolgend beschrieben ist. Es zeigen

  • Figur 1 die Brennkraftmaschine nach der Erfindung in einer Schnittebene durch das eine Paar der achsgleich gegenüberliegenden Zylinder,
  • Figur 2 die Brennkraftmaschine nach Figur 1 in einer zur ersten Schnittebene parallelen Schnittebene durch das zweite Paar der achsgleich gegenüberliegenden Zylinder und
  • Figur 3 in vergrößerter Darstellung einen Querschnitt durch den Kurbelwellenbereich der Brennkraftmaschine nach Figur 1.
In the drawing, an embodiment according to the invention is shown using a four-cylinder internal combustion engine, which is described below. Show it
  • FIG. 1 shows the internal combustion engine according to the invention in a sectional plane through the one pair of axially opposite cylinders,
  • FIG. 2 shows the internal combustion engine according to FIG. 1 in a sectional plane parallel to the first sectional plane through the second pair of cylinders and, lying opposite one another
  • 3 shows an enlarged representation of a cross section through the crankshaft region of the internal combustion engine according to FIG. 1.

Wie Figur 1 zeigt, besteht das erste Zylinderpaar aus den beiden Arbeitszylindern 1 und 2, die achsgleich gegenüberliegen. In ihnen laufen Arbeitskolben 3 und 4, an denen Kolbenstangen 5 und 6 starr befestigt sind. Diese sind andererseits mit einem Kurbelschleifenrahmen 7 fest verbunden, der eine geradlinige Kulisse 8 einschließt, deren Längsachse L8 in einem Winkel von 90° quer zur Längsachse L1, 2 der beiden Arbeitszylinder 1 und 2 gerichtet ist. In der Kulisse 8 bewegt sich ein Gleitstein 9, der auf einem Kurbelzapfen 10 eines Kurbelabtriebes 20 mit seiner Kurbelwelle 21 drehbar gelagert ist , vgl. Figur 3.As FIG. 1 shows, the first pair of cylinders consists of the two working cylinders 1 and 2, which lie opposite one another with the same axis. In them run pistons 3 and 4, on which piston rods 5 and 6 are rigidly attached. These are, on the other hand, firmly connected to a crank loop frame 7, which includes a rectilinear link 8, the longitudinal axis L8 of which is directed at an angle of 90 ° transversely to the longitudinal axis L1, 2 of the two working cylinders 1 and 2. A sliding block 9, which is rotatably mounted on a crank pin 10 of a crank drive 20 with its crankshaft 21, moves in the backdrop 8, cf. Figure 3.

Das zweite Zylinderpaar besteht gemäß Figur 2 aus den beiden Arbeitszylindern 11 und 12, die ebenfalls achsgleich gegenüberliegen. In ihnen laufen Arbeitskolben 13 und 14, an denen Kolbenstangen 15 und 16 starr befestigt sind. Diese sind andererseits mit einem Kurbelschleifenrahmen 17 fest verbunden, der eine geradlinige Kulisse 18 einschließt, deren Längsachse L 18 in einem Winkel von 900 quer zur Längsachse L11, 12 der beiden Arbeitszylinder 11 und 12 gerichtet ist. In der Kulisse 18 bewegt sich ein Gleitstein 19, der ebenfalls auf dem Kurbelzapfen 10 des Kurbeltriebes 20 drehbar gelagert ist. Die beiden Längsachsen L8 und L18 der beiden Kulissen 8 und 18 kreuzen sich ebenfalls senkrecht.According to FIG. 2, the second pair of cylinders consists of the two working cylinders 11 and 12, which likewise lie opposite one another with the same axis. Working pistons 13 and 14 run in them, on which piston rods 15 and 16 are rigidly attached. These are, on the other hand, firmly connected to a crank loop frame 17, which includes a rectilinear link 18, the longitudinal axis L 18 of which is directed at an angle of 90 ° transverse to the longitudinal axis L11, 12 of the two working cylinders 11 and 12. A sliding block 19 moves in the backdrop 18 and is likewise rotatably mounted on the crank pin 10 of the crank mechanism 20. The two longitudinal axes L8 and L18 of the two scenes 8 and 18 also intersect perpendicularly.

Wie aus Figur 3 zu entnehmen ist, liegen beide Kurbelschleifenrahmen 7 und 17 nebeneinander auf dem Kurbelzapfen 10 des Kurbelabtriebes 20. Die Lagerung der Kurbelwelle 21 ist, da nicht zur Erfindung gehörig, weder beschrieben noch näher dargestellt.As can be seen from FIG. 3, the two crank loop frames 7 and 17 lie side by side on the crank pin 10 of the crank drive 20. The bearing of the crankshaft 21, since it is not part of the invention, is neither described nor shown in detail.

x Nimmt man die Drehrichtung R des Motors in Uhrzeigersinn an, so bewegen sich die beiden Arbeitskolben 13 und 14 nach rechts oben, während sich die beiden Arbeitskolben 3 und 4 nach rechts unten bewegen. Diese Bewegungen werden über die Kurbelschleifen 7 und 17 auf den Kurbelzapfen 10 der Kurbelwelle 21 übertragen, der dadurch eine Drehbewegung aufgezwungen wird.x Assuming the direction of rotation R of the motor clockwise, the two working pistons 13 and 14 move to the top right, while the two working pistons 3 and 4 move to the bottom right. These movements are transmitted via the crank loops 7 and 17 to the crank pin 10 of the crankshaft 21, which thereby forces a rotary movement.

Wie aus der vorstehenden Beschreibung der neuen Brennkraftmaschine sofort zu ersehen ist, hat der durch die gewählte Anordnung von zwei Kurbelschleifen auf einen Kurbelzapfen erzielte Gleichlauf aller vier Arbeitskolben den Vorteil, daß die Ausgleichsmasse der der sich translatorisch bewegenden Masse einer üblichen Zwei-ZylinderEinheit entspricht. Dadurch ist die Fliehkraft in jeder Kurbelwellenstellung genau so große wie die resultierende Masse von zwei Zwei-Zylinder-Einheiten. Es verbleibt lediglich eine Restmassenkraft, resultierend aus dem geringen Abstand der um 90° vesetzt angeordneten Kolbenstangen und der sich mit diesen translatorisch bewegenden Massen.As can be seen immediately from the above description of the new internal combustion engine, the synchronism of all four working pistons achieved by the selected arrangement of two crank loops on a crank pin has the advantage that the balancing mass corresponds to the translationally moving mass of a conventional two-cylinder unit. As a result, the centrifugal force in each crankshaft position is just as large as the resulting mass of two two-cylinder units. All that remains is a residual mass force, resulting from the small distance between the piston rods, which are offset by 90 °, and the masses that move with them in a translatory manner.

Dieser Vorteil wird auch dann erzielt, wenn mehr als vier Zylinder, nämlich jeweils das geradzählige Vielfache von zwei, auf eine einzige Kurbelwelle in der beschriebenen Art und Weise wirken, die dann die entsprechende Anzahl von Kurbelzapfen aufweisen muß.This advantage is also achieved if more than four cylinders, namely the even multiple of two, act on a single crankshaft in the manner described, which must then have the corresponding number of crank pins.

Claims (3)

1. Mehrzylinder-Brennkraftkolbenmaschine, deren Arbeitszylinder jeweils paarweise und achsgleich gegenüberliegend angeordnet sind, mit Kurbelschleifentrieb zur Umwandlung der Translationsbewegung der Arbeitskolben und deren starr mit ihnen verbundenen Kolbenstangen in Rotationsbewegung des Kurbelabtriebes, wobei jeweils zwei Kolbenstangen mit ihren inneren Enden am Kurbelschleifenrahmen unbeweglich befestigt sind, in dessen geradliniger, senkrecht zur Längsachse des Arbeitszylinderpaares verlaufenden Kulisse der Kurbelzapfen des Kurbelabtriebes gleitet, dadurch gekennzeichnet , daß auf jedem Kurbelzapfen (10) die Kulissen (8 und 18) jeweils zweier Kurbelschleifenrahmen (7 und 17) laufen, die zur Verbindung jeweils zweier gegenüberliegender Arbeitskolben (3 und 4 sowie 13 und 14) von vier in Achsrichtung hintereinander angeordneten Arbeitszylindern (1 und 2 sowie 11 und 12) dienen, und daß die Längsachse der Kurbelwelle und damit auch des Kurbelzapfens (10) in Richtung der hintereinander angeordneten Zylinderpaare (1 und 2 sowie 11 und 12) verläuft, mit Hintereinanderanordnung auch der einem jeden Zylinderpaar mit achsgleich gegenüberliegenden Zylindern (1 und 2 sowie 11 und 12) zugeordneten Kurbelschleifenrahmen (7 und 17).1.Multi-cylinder internal combustion piston machine, the working cylinders of which are arranged in pairs and axially opposite one another, with crank-loop drive for converting the translational movement of the working pistons and their piston rods rigidly connected to them into rotational movement of the crank output, two piston rods each being immovably attached to the crank-loop frame with their inner ends, in its straight, perpendicular to the longitudinal axis of the pair of cylinders the crank pin of the crank drive slides, characterized in that on each crank pin (10) the scenes (8 and 18) each run two crank loop frames (7 and 17), which each connect two opposite Working pistons (3 and 4 as well as 13 and 14) of four working cylinders (1 and 2 as well as 11 and 12) arranged one behind the other serve in the axial direction, and that the longitudinal axis of the crankshaft and thus also of the crank pin (10) in the direction of the one behind the other r arranged cylinder pairs (1 and 2 as well as 11 and 12), with the one behind the other also the crank loop frame (7 and 17) assigned to each cylinder pair with axially opposite cylinders (1 and 2 as well as 11 and 12). 2. Mehrzylinder-Brennkraftkolbenmaschine nach Anspruch 1, dadurch gekennzeichnet, daß die Längsachsen (L1, 2 und L11, 12) jeweils zweier gegenüberliegender Arbeitszylinderpaare (1 und 2 sowie 11 und 12) einen Winkel von 90° einschließen und sich kreuzen und die Längsachse (L8 und L18) der auf dem Kurbelzapfen (10) gleitenden Kulissen (8 und 18) der beiden hintereinander angeordneten Kurbelschleifenrahmen (7 und 17) senkrecht zueinander gerichtet sind und sich dabei kreuzen.2. Multi-cylinder internal combustion engine according to claim 1, characterized in that the longitudinal axes (L1, 2 and L11, 12) each have two opposing pairs of working cylinders (1 and 2 and 11 and 12) an angle of 90 ° close and cross each other and the longitudinal axis (L8 and L18) of the sliding blocks (8 and 18) of the two crank loop frames (7 and 17) arranged one behind the other on the crank pin (10) are directed perpendicular to each other and cross each other. 3. Mehrzylinder-Brennkraftkolbenmaschine nach Anspruch 1, dadurch gekennzeichnet, daß mehrere jeweils das geradzählige Vielfache von zwei bildende Arbeitszylinder-Einheiten (1/2, 11/12) einer Kurbelwelle (21) mit einer entsprechenden Anzahl von Kurbelzapfen (10) zugeordnet sind.3. Multi-cylinder internal combustion engine according to claim 1, characterized in that several are each assigned an even multiple of two working cylinder units (1/2, 11/12) of a crankshaft (21) with a corresponding number of crank pins (10).
EP85115114A 1984-12-28 1985-11-28 Multiple cylinder internal-combustion engine Expired EP0187930B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85115114T ATE44802T1 (en) 1984-12-28 1985-11-28 MULTI-CYLINDER PISTON ENGINE.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3447663 1984-12-28
DE3447663A DE3447663A1 (en) 1984-12-28 1984-12-28 MULTI-CYLINDER COMBUSTION PISTON

Publications (3)

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EP0187930A2 true EP0187930A2 (en) 1986-07-23
EP0187930A3 EP0187930A3 (en) 1987-05-06
EP0187930B1 EP0187930B1 (en) 1989-07-19

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ID=6254042

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85115114A Expired EP0187930B1 (en) 1984-12-28 1985-11-28 Multiple cylinder internal-combustion engine

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EP (1) EP0187930B1 (en)
JP (1) JPS61157726A (en)
AT (1) ATE44802T1 (en)
DE (2) DE3447663A1 (en)

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DE4007438C1 (en) * 1990-03-09 1991-06-27 Bayerische Motoren Werke Ag, 8000 Muenchen, De
DE4035562A1 (en) * 1990-11-08 1992-05-14 Zikeli Friedrich Dipl Ing Th Piston cross thrust ring and crank slide - involves ring and slide assemblable on pins on body of crankshaft
EP0915239A4 (en) * 1996-07-26 2001-03-14 Yugen Kaisha Sozoan Rotational motion mechanism and engine
WO2002097251A1 (en) * 2001-05-30 2002-12-05 Reinhold Ficht Portable electric generator comprising internal combustion engines for the combustion of biogas
DE102005024361A1 (en) * 2005-05-27 2006-12-07 Bayerische Motoren Werke Ag Drive unit for motor vehicle e.g. passenger motor vehicle has first and second internal combustion engine connected by clutch mechanism depending upon power required whereby internal combustion engine has hypocycloidic crank drive
US7210397B2 (en) 2001-04-27 2007-05-01 Peter Robert Raffaele Scotch yoke engine
US20120272758A1 (en) * 2010-06-29 2012-11-01 Matthew Byrne Diggs Double-acting scotch yoke assembly for x-engines
US8371210B2 (en) 1998-03-10 2013-02-12 Peter Robert Raffaele Reciprocating fluid machines
WO2013032431A1 (en) * 2011-08-29 2013-03-07 Diggs Matthew B Balanced x - engine assembly

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GB8723712D0 (en) * 1987-10-09 1987-11-11 Collins Motor Corp Ltd Positive displacement fluid machines
GB8827835D0 (en) * 1988-11-29 1988-12-29 Collins Motor Corp Ltd Positive displacement fluid machines
GB8904058D0 (en) * 1989-02-10 1989-04-05 Jaguar Cars Internal combustion engine
GB8911747D0 (en) * 1989-05-22 1989-07-05 Collins Motor Corp Ltd Multi-cylinder positive displacement fluid machines
DE3940945A1 (en) * 1989-12-12 1990-12-20 Bayerische Motoren Werke Ag Engine assembly for motor vehicle - consists of several engines mounted in line with crankshafts connected by clutches
DE4137535C2 (en) * 1990-11-14 1998-09-24 Ficht Gmbh Machine set for energy supply
RU2035603C1 (en) * 1992-06-09 1995-05-20 Арцыбашев Александр Валентинович Internal combustion engine
GB2268563B (en) * 1992-07-08 1995-05-10 Chung Hsin Chen Power transmission mechanism
DE4234941C2 (en) * 1992-10-16 1995-05-18 Franz Rupp Internal combustion engine
DE19500854C2 (en) * 1994-01-21 1998-04-09 Beck Walter Reciprocating machine
DE4414769A1 (en) * 1994-04-27 1995-11-02 Ficht Gmbh Multicylinder drive unit for motorcycle
DE19635248C2 (en) 1996-08-30 2001-05-23 Ficht Gmbh & Co Kg LPG engine
FR2777944B1 (en) * 1998-04-24 2000-08-04 Michel Francois Cons Chatelain EXPLOSION, FLAT AND OPPOSITE CYLINDER ENGINE
DE19923021B4 (en) * 1998-05-20 2006-01-05 Brauers, Franz, Dr. Crank mechanism and crank mechanism arrangement

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FR2526863A1 (en) * 1982-05-14 1983-11-18 Ficht Gmbh SLIDING SYSTEM FOR AN INTERNAL COMBUSTION ENGINE COMPRISING AT LEAST TWO CYLINDERS MUTUALLY FACE
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Cited By (12)

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Publication number Priority date Publication date Assignee Title
DE4007438C1 (en) * 1990-03-09 1991-06-27 Bayerische Motoren Werke Ag, 8000 Muenchen, De
DE4035562A1 (en) * 1990-11-08 1992-05-14 Zikeli Friedrich Dipl Ing Th Piston cross thrust ring and crank slide - involves ring and slide assemblable on pins on body of crankshaft
DE4035562C2 (en) * 1990-11-08 1992-08-27 Friedrich Dipl.-Ing. Zikeli (Th), 7300 Esslingen, De
EP0915239A4 (en) * 1996-07-26 2001-03-14 Yugen Kaisha Sozoan Rotational motion mechanism and engine
US8371210B2 (en) 1998-03-10 2013-02-12 Peter Robert Raffaele Reciprocating fluid machines
US7210397B2 (en) 2001-04-27 2007-05-01 Peter Robert Raffaele Scotch yoke engine
WO2002097251A1 (en) * 2001-05-30 2002-12-05 Reinhold Ficht Portable electric generator comprising internal combustion engines for the combustion of biogas
DE102005024361A1 (en) * 2005-05-27 2006-12-07 Bayerische Motoren Werke Ag Drive unit for motor vehicle e.g. passenger motor vehicle has first and second internal combustion engine connected by clutch mechanism depending upon power required whereby internal combustion engine has hypocycloidic crank drive
US20120272758A1 (en) * 2010-06-29 2012-11-01 Matthew Byrne Diggs Double-acting scotch yoke assembly for x-engines
US8746206B2 (en) * 2010-06-29 2014-06-10 Matthew Byrne Diggs Double-Acting Scotch Yoke assembly for X-engines
WO2013032431A1 (en) * 2011-08-29 2013-03-07 Diggs Matthew B Balanced x - engine assembly
US9051833B2 (en) 2011-08-29 2015-06-09 Matthew Byrne Diggs X-engine assembly with perfect balance

Also Published As

Publication number Publication date
JPS61157726A (en) 1986-07-17
DE3571673D1 (en) 1989-08-24
DE3447663A1 (en) 1986-07-10
EP0187930A3 (en) 1987-05-06
EP0187930B1 (en) 1989-07-19
ATE44802T1 (en) 1989-08-15

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