EP0217813B1 - Rotary piston machine with periodically variable rotation speeds - Google Patents

Rotary piston machine with periodically variable rotation speeds Download PDF

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Publication number
EP0217813B1
EP0217813B1 EP86901323A EP86901323A EP0217813B1 EP 0217813 B1 EP0217813 B1 EP 0217813B1 EP 86901323 A EP86901323 A EP 86901323A EP 86901323 A EP86901323 A EP 86901323A EP 0217813 B1 EP0217813 B1 EP 0217813B1
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EP
European Patent Office
Prior art keywords
piston
segment
chamber
section
case
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EP86901323A
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German (de)
French (fr)
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EP0217813A1 (en
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Arthur SCHÖNHOLZER
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/02—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F01C1/063—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents with coaxially-mounted members having continuously-changing circumferential spacing between them
    • F01C1/077—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents with coaxially-mounted members having continuously-changing circumferential spacing between them having toothed-gearing type drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/02—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F01C1/063—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents with coaxially-mounted members having continuously-changing circumferential spacing between them
    • 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
    • F02B1/00—Engines characterised by fuel-air mixture compression
    • F02B1/02—Engines characterised by fuel-air mixture compression with positive ignition
    • F02B1/04—Engines characterised by fuel-air mixture compression with positive ignition with fuel-air mixture admission into 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
    • F02B53/00—Internal-combustion aspects of rotary-piston or oscillating-piston engines
    • F02B2053/005—Wankel 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
    • F02B2075/027—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle four

Definitions

  • the invention relates to a device for driving an output shaft according to the preamble of claim 1.
  • Otto engines are generally known. There, a crankshaft or camshaft is driven by several pistons, the piston movement of which is radial to the shaft axis. It has turned out to be disadvantageous here that several pistons have to be provided in order to achieve a certain output of the engine, each piston having its own cylinder, its own inlets and outlets and also its own ignition system. Secondly, the transmission of force in the radial direction to a camshaft is always in need of improvement.
  • the Otto engines are designed as reciprocating piston engines or rotary piston engines and work in four-stroke or two-stroke processes. The four-stroke process includes suction, compression, ignition and combustion, as well as pushing out.
  • the rotary piston engine is known, the piston of which executes a continuously circular movement.
  • the Wankel motor should be mentioned here, in which a rotary piston, which is eccentrically mounted in a trochoidal housing and which has the shape of an equilateral triangle, rotates by rotating about a center which itself simultaneously performs a rotary movement.
  • the four-stroke process takes place in the working spaces between the rotary piston and the housing wall, increases and decreases in size and with the help of inlet and outlet slots in the housing wall, which are controlled by the rotary piston, carry out the charge exchange, i.e. suck in, compress, expand and push out.
  • EP-0 062 087 A1 discloses a rotary piston engine according to the preamble of claim 1, in which the first piston part is connected to a hollow shaft and the second piston part is connected to the output shaft guided inside the hollow shaft.
  • Hollow shaft and output shaft are non-positively connected by a gear made of elliptical gears.
  • a gear made of elliptical gears are non-positively connected by a gear made of elliptical gears.
  • such a transmission is not an ideal solution in more ways than one, in particular the manufacture and precise adjustment of the transmission is much more problematic than when circular gears are used.
  • a combination of several axially successive piston units is not readily possible.
  • a rotary piston engine is also known (FR-A-2 138 581), in which two pairs of pistons are connected to a pair of planet gears, which are mounted diametrically opposite one another on a yoke coupled to the output shaft.
  • This solution is u. a. due to the continuous output axis extremely complicated and structurally complex.
  • the inventor has set itself the goal of developing a new drive unit that works with a small number of components and yet has a very high efficiency, is light and compact, and does not require a camshaft or crankshaft.
  • the surface friction for the piston is also to be reduced, while the work cycles are multiplied.
  • the piston parts should preferably be shaped such that they have at least one cylinder section and one segment section in succession. Of course, this arrangement can also be multiplied. Each cylinder or segment section is then a cylinder or. Assigned segment section of the other piston part. This creates a piston that has a prism-like appearance.
  • each piston part should be connected to a planet gear, which in turn forms a non-positive connection with a sun gear, which is coupled to the rotor.
  • a planet gear which in turn forms a non-positive connection with a sun gear, which is coupled to the rotor.
  • the construction parts are very simple, in the majority cylindrical.
  • the engine runs like a turbine and has low vibrations, the piston speed is relatively low and there are no sealing problems. Overall, the engine is expected to have a long service life and economy.
  • the engine will also find its way into the area of high-performance engines, such as racing and aircraft engines. Diesel engines designed in this way are also conceivable.
  • piston parts 1 and 2 of a drive unit R are enclosed by a cylindrical housing part 3, here only schematically, but shown in more detail in FIGS.
  • This housing part 3 is closed on the one hand by an end plate 4 by means of fastening elements 5, which has a round bore 6 in the center for receiving a bearing 7.
  • an axial pin 8 of a disk 9 rotates, which is firmly connected to the one piston part 2 by means of screws 10.
  • Zen other piston part 1 does not touch the disc 9; here only a stop pin 11 passes through an elongated hole 12 to allow axial movement of piston part 1 relative to piston part 2.
  • the piston part 1 is firmly connected to a turntable 14, which, however, does not touch the piston part 2.
  • the connection between the turntable 14 and the piston part 1 is effected via a toggle lever element 15, on the other end of which a gear 16 is fitted eccentrically.
  • the piston part 2 is also connected eccentrically to a toothed wheel 18 via a toggle lever element 17, a recess 19 in the turntable 14 allowing the toggle lever element 17 to move freely.
  • Both gears 16 and 18 are in engagement with an internal toothing 38 of a ring 39 which is fixedly connected to the housing part 3 and at the same time rotate around a sun gear 20 which is connected to an output shaft 21, so that ultimately this output shaft 21 is connected to the one consisting of the two gear wheels 16, 18 planetary set formed a frictional connection.
  • This frictional engagement of the internal toothing 38 with the toothed wheels 16, 18 and the sun gear 20 inevitably and in the control sense controls the four cycles of suction, compression, ignition, ejection during a rotation of 360 °. Accordingly, the relationship of these parts to each other is of great constructive importance.
  • the output shaft 21 rotates axially in a bearing 22 in the turntable 14.
  • Further bearings 23 and 24 for the rotor 21 and gear axles 25 are provided in a turntable 26, which is arranged in a main bearing 27, which the turntable 26 is opposite to a further housing shell 28 supports.
  • This housing shell 28 is screwed on the one hand to the housing part 3, on the other hand covered by an end plate 30 which contains a further pivot bearing 29 for the output shaft 21.
  • the end plate 30 passes through a crank 31 in further bearings 32 and 33, which meshes a drive disk 35 with a gear 34.
  • each piston part 1 and 2 consists of a cylinder section 40 with a segment cutout 41 and an attached or molded segment section 42.
  • An angle w of the segment cutout 41 is greater than an angle v of the segment section 42 around the common one Piston axis A.
  • the ratio of the angles w and v to one another determines the power of the drive, since a finished piston consists of two piston parts 1 and 2 arranged in mirror image and thus four combustion chambers 43 are formed, only two of which are indicated in FIG. The greater the difference between the two angles w and v, the greater is the combustion chamber 43 or the opening angle z.
  • FIG. 5 shows a modification of a piston, in which a groove 44 is formed in the cylinder section 40 at the base of the segment cutout 41, in which the segment section 42 rests with a beaded piping 45.
  • the beaded piping 45 is formed with an apex groove 46 which forms a sealing strip (not shown) can record, the functions of which resemble a known piston ring.
  • FIG. 6 now shows the mode of operation of the piston of a four-cylinder rotor, only the interaction of a cylinder section 40 with a segment section 42 being shown. All in all, each element described below is present twice for the entire piston. With a rotation through 360 °, two work cycles (compression and explosion cycles) are provided for each combustion chamber, the ignition system being indicated at 48.
  • the spark plugs are also within the scope of the invention on an inner surface in the segment ment cutout 41, that is to say to be arranged in the combustion chamber 43, as a result of which the combustion is improved, but at the expense of good access to the spark plugs.
  • outlets 49 and inlets 50 are provided opposite each other.
  • the first position according to FIG. 6 shows that fuel is drawn into one combustion chamber 43a, while the other 43b is just being ignited.
  • the chamber 43b is opened, while the chamber 43a is compressed, while the piston rotation movement about the axis A is accelerated.
  • Both chambers are in the 2nd position.
  • the fuel gases can be removed from the chamber 43b into the outlet 49, at the same time the ignition takes place in the chamber 43a.
  • the gases from this ignition are again removed from chamber 43a through the subsequent outlet, with new fuel being drawn into chamber 43b, as shown in the 111th position.
  • chamber 43b is reignited as chamber 43a passes outlet 50.
  • the chamber 43a is ignited while the chamber 43b passes the outlet 49.
  • chamber 43a is at outlet 49 when chamber 43b draws in again.
  • the next position is again the l. Position. This completes a rotation through 360 °; the changes necessary to the chambers 43a and 43b are carried out in particular by the ignition and the movement of the gear wheels 16 and 18.
  • a total of thirty-two cycles are performed per revolution, eight of which are working cycles. This is six work cycles more than with a known Otto or Wankel engine with a significantly lower surface friction, since a corresponding Otto or Wankel engine would have to have an approximately 40 to 50% larger piston area.
  • the piston speed is significantly lower than that of the previously known engines, namely by around 20 to 30%. A maximum piston speed of 8 to 10 m / sec will be necessary.
  • the inlet and outlet are inevitably done by the rotor rotation with high suction and flushing performance. There are no moving parts, such as valves, that need to be serviced.
  • the entire drive unit can be cooled with water or oil in appropriate cavities.

Abstract

The device for driving a drive shaft (21) by means of a piston and an intermediary driving mechanism is characterized by a piston consisting of two parts (1, 2) which form together a combustion chamber (43). Both piston parts (1, 2) rotate about an axis (A) by varying the size of the combustion chamber (43).

Description

Vorrichtung zum Antreiben einer AbtriebswelleDevice for driving an output shaft

Die Erfindung betrifft eine Vorrichtung zum Antreiben einer Abtriebswelle gemäss dem Oberbegriff des Anspruchs 1.The invention relates to a device for driving an output shaft according to the preamble of claim 1.

Allgemein bekannt sind die sogenannten Otto-Motoren. Dort wird eine Kurbel- bzw. Nockenwelle über mehrere Kolben angetrieben, deren Kolbenbewegung radial zur Wellenachse verläuft. Nachteilig hat sich hier herausgestellt, dass einmal um eine bestimmte Leistung des Motors zu erreichen mehrere Kolben vorgesehen sein müssen, wobei jeder Kolben seinen eigenen Zylinder, seine eigenen Ein- und Auslässe und auch seine eigene Zündanlage besitzt. Zum andern ist die Kraftübertragung in radialer Richtung auf eine Nockenwelle immerverbesserungsbedürftig. Die Otto-Motoren sind als Hubkolbenmaschinen oder Kreiselkolbenmotoren ausgebildet und arbeiten im Viertakt- oder Zweitaktverfabren. Das Viertaktverfabren umfasst das Ansaugen, Verdichten, Zünden und Verbrennen, sowie Ausschieben.The so-called Otto engines are generally known. There, a crankshaft or camshaft is driven by several pistons, the piston movement of which is radial to the shaft axis. It has turned out to be disadvantageous here that several pistons have to be provided in order to achieve a certain output of the engine, each piston having its own cylinder, its own inlets and outlets and also its own ignition system. Secondly, the transmission of force in the radial direction to a camshaft is always in need of improvement. The Otto engines are designed as reciprocating piston engines or rotary piston engines and work in four-stroke or two-stroke processes. The four-stroke process includes suction, compression, ignition and combustion, as well as pushing out.

Des weiteren ist der Kreiskolbenmotor bekannt, dessen Kolben eine stetig kreisende Bewegung ausführt. Als Ausführungsform sei hier der Wankelmotor erwähnt, bei dem ein in einem trochoidenförmigen Gehäuse exzentrisch gelagerter Drehkolben, der die Form eines gleichseitigen Dreiecks bat, umläuft, indem er sich um einen Mittelpunkt dreht, der selber gleichzeitig eine Drehbewegung ausführt. Der Arbeitsvorgang nach dem Viertaktverfahren findt in den zwischen Drebkolben und Gehäusewand liegenden Arbeitsräurmen statt, aie sich vergrössem und verkleinern und mit Hilfe von Ein- und Auslasschlitzen in der Gehäusewand, die vom Drebkolben gesteuert werden, den Ladungswechsel durchführen, also ansaugen, verdichten, expandieren und ausschieben. Die Vorteile des Kreiskolbenmotors gegenüber dem Hubkolbenmotor liegen insbesondere in der geringeren Anzahl von Bauteilen, im Wegfall von hin-und hergehenden Massen, im Wegfall von Ventilantrieb, geringere Baugrösse und geringeres Gewicht. Andererseits sind sie jedoch mit erheblichen Herstellungskosten und einer aufwendigen Abdichtung belastet, weisen einen ungünstigen Brennraum mit hoben Wärmeverlusten auf und haben insbesondere einen hoben Anteil an unverbrannten Kohlenwasserstoffen und HC im Abgas.Furthermore, the rotary piston engine is known, the piston of which executes a continuously circular movement. As an embodiment, the Wankel motor should be mentioned here, in which a rotary piston, which is eccentrically mounted in a trochoidal housing and which has the shape of an equilateral triangle, rotates by rotating about a center which itself simultaneously performs a rotary movement. The four-stroke process takes place in the working spaces between the rotary piston and the housing wall, increases and decreases in size and with the help of inlet and outlet slots in the housing wall, which are controlled by the rotary piston, carry out the charge exchange, i.e. suck in, compress, expand and push out. The advantages of the rotary piston engine compared to the reciprocating piston engine lie in particular in the smaller number of components, in the elimination of reciprocating masses, in the elimination of the valve drive, the smaller size and the lower weight. On the other hand, however, they are burdened with considerable manufacturing costs and a complex seal, have an unfavorable combustion chamber with high heat losses and in particular have a high proportion of unburned hydrocarbons and HC in the exhaust gas.

Aus der EP - 0 062 087 A1 ist ein Drehkolbenmotor gemäss dem Oberbegriff des Anspruchs 1 bekannt, bei dem der erste Kolbenteil mit einer Hohlwelle verbunden ist und der zweite Kolbenteil mit der innerhalb der Hohlwelle geführten Abtriebswelle. Hohlwelle und Abtriebswelle sind durch ein Getriebe aus elliptischen Zahnrädern kraftschlüssig verbunden. Ein derartiges Getriebe stellt jedoch in mehr als einer Hinsicht keine ideale Lösung dar, insbesondere ist die Herstellung und präzise Abstimmung des Getriebes wesentlich problematischer als bei Verwendung kreisrunder Zahnräder. Ausserdem ist eine Kombination mehrerer axial aufeinanderfolgender Kolbeneinheiten nicht ohne weiteres möglich.EP-0 062 087 A1 discloses a rotary piston engine according to the preamble of claim 1, in which the first piston part is connected to a hollow shaft and the second piston part is connected to the output shaft guided inside the hollow shaft. Hollow shaft and output shaft are non-positively connected by a gear made of elliptical gears. However, such a transmission is not an ideal solution in more ways than one, in particular the manufacture and precise adjustment of the transmission is much more problematic than when circular gears are used. In addition, a combination of several axially successive piston units is not readily possible.

Es ist auch ein Drehkolbenmotor bekannt (FR - A - 2 138 581), bei welchen zwei Kolbenpaare mit je einem Paar von Planetenzahnrädem verbunden sind, die einander diametral gegenüberliegend auf einem mit der Abtriebsachse gekoppelten Joch montiert sind. Diese Lösung ist u. a. aufgrund derdurchgehenden Abtriebsachse äusserst kompliziert und konstruktiv aufwendig.A rotary piston engine is also known (FR-A-2 138 581), in which two pairs of pistons are connected to a pair of planet gears, which are mounted diametrically opposite one another on a yoke coupled to the output shaft. This solution is u. a. due to the continuous output axis extremely complicated and structurally complex.

Der Erfinder hat sich zum Ziel gesetzt, ein neues Antriebsagsregat zu entwickeln, welches mit einer geringen Anzahl an Bauteilen arbeitet und dennoch einen sehr hohen Wirkungsgrad hat, leicht und kompakt ist, und ohne Nocken- und Kurbelwelle auskommt. Insbesondere soll auch die Oberflächenreibung für den Kolben verringert werden, dagegen die Arbeitstakte vervielfacht.The inventor has set itself the goal of developing a new drive unit that works with a small number of components and yet has a very high efficiency, is light and compact, and does not require a camshaft or crankshaft. In particular, the surface friction for the piston is also to be reduced, while the work cycles are multiplied.

Diese Aufgabe wird durch die Erfindung, wie sie in den Ansprüchen gekennzeichnet ist, gelöst.This object is achieved by the invention as characterized in the claims.

Hierzu hat sich am wirkungsvollsten die Ausbildung eines Kolbenteils als Zylinderabschnitt mit einem Segmentausschnitt erwiesen, in den der zweite Kolbenteil als Segmentabschnitt eingesetz ist, wobei der Winkel des Segmentausschnitts grösser ist als der Winkel des Segmentabschnitts. Durch diese Winkelunterschiede wird die Weite der Verbrennungskammer bestimmt, wodurch ebenfalls selbstverständlich die Leistung des Motors verändert werden kann. Beim Umlaufen der beiden Kolbenteile um 360° soll ebenfalls ein Viertakt durchgeführt werden, nämlich Ansaugen, Verdichten, Zünden, Ausstossen. Bevorzugt ist dieser Viertakt zumindest zweimal je Drehung um 360° vorgesehen, jedoch ist eine Erhöhung denkbar und liegt ebenfalls im Rahmen der Erfindung.The most effective way of doing this has been to design a piston part as a cylinder section with a segment cutout, into which the second piston part is inserted as a segment section, the angle of the segment cutout being greater than the angle of the segment section. The width of the combustion chamber is determined by these angular differences, which of course also allows the performance of the engine to be changed. When rotating the two piston parts through 360 °, a four-stroke cycle should also be carried out, namely suction, compression, ignition, and ejection. This four-stroke cycle is preferably provided at least twice per 360 ° rotation, but an increase is conceivable and is also within the scope of the invention.

Bevorzugt sollen die Kolbenteile so geformt sein, dass sie nacheinander zumindest einen Zylinderabschnitt und einen Segmentabschnitt aufweisen. Selbstverständlich kann diese Anordnung auch vervielfacht werden. Jedem Zylinder- bzw. Segmentabschnitt ist dann ein Zylinder-bzw. Segmentabschnitt des anderen Kolbenteils zugeordnet. Auf diese Weise entsteht ein Kolben, welcher ein prismaartiges Aussehen hat.The piston parts should preferably be shaped such that they have at least one cylinder section and one segment section in succession. Of course, this arrangement can also be multiplied. Each cylinder or segment section is then a cylinder or. Assigned segment section of the other piston part. This creates a piston that has a prism-like appearance.

Für die Kraftübertragung soll jeder Kolbenteil mit einem Planetenzahnrad verbunden sein, welches wiederum eine kraftschlüssige Verbindung mit einem Sonnenrad eingeht, das an den Läufer gekoppelt ist. Dies ist ein weiterer entscheidender Punkt der Erfindung, da hier die übliche Kurbelwelle entfällt. Das Planetengetriebe ist bereits eine Stufe des Getriebes selbst. Deswegen kann die ganze Antriebseinheit sehr kompakt gebaut werden.For the power transmission, each piston part should be connected to a planet gear, which in turn forms a non-positive connection with a sun gear, which is coupled to the rotor. This is another crucial point of the invention, since the usual crankshaft is omitted here. The planetary gear is already a stage of the gear itself. That is why the entire drive unit can be made very compact.

Die Konstruktionsteile sind sehr einfach gestaltet, in der Mehrheitzylinderförmig. Der Lauf des Motors ist turbinenartig und vibrationsarm, die Kolbengeschwindigkeit relativ gering, Dichtungsprobleme treten keine auf. Insgesamt lässt der Motor eine hohe Lebensdauer und Wirtschaftlichkeit erwarten.The construction parts are very simple, in the majority cylindrical. The engine runs like a turbine and has low vibrations, the piston speed is relatively low and there are no sealing problems. Overall, the engine is expected to have a long service life and economy.

Infolge der minimalen Reibungsflächen und des Leistungsgewichtes wird der Motor auch in den Bereich der Hochleistungstriebwerke Zugang finden, wie zum Beispiel der Renn- und Flugtriebwerke. Auch so ausgestaltete Dieselmotoren sind denkbar.As a result of the minimal friction surfaces and the power to weight ratio, the engine will also find its way into the area of high-performance engines, such as racing and aircraft engines. Diesel engines designed in this way are also conceivable.

Weitere Vorteile, Merkmale und Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung bevorzugter Ausführungsbeispiele sowie anhand der Zeichnung ; diese zeigt in

  • Figur 1 einen Querschnitt durch einen erfindungsgemässen Antrieb ;
  • Figur 2 eine Seitenansicht eines erfindungsgemässen Kolbenteils ;
  • Figur 3 eine Draufsicht auf den Kolbenteil nach Figur 2 ;
  • Figur 4 eine perspektivische Ansicht des Kolbenteils nach Figur 2 ;
  • Figur 5 einen Querschnitt durch einen zusammengesetzten Kolben aus zwei Kolbenteilen ;
  • Figur 6 eine schematische Darstellung der Arbeitsweise des erfindungsgemässen Antriebs.
Further advantages, features and details of the invention emerge from the following description of preferred exemplary embodiments and with reference to the drawing; this shows in
  • 1 shows a cross section through a drive according to the invention;
  • FIG. 2 shows a side view of a piston part according to the invention;
  • Figure 3 is a plan view of the piston part of Figure 2;
  • FIG. 4 shows a perspective view of the piston part according to FIG. 2;
  • Figure 5 shows a cross section through an assembled piston from two piston parts;
  • Figure 6 is a schematic representation of the operation of the drive according to the invention.

Nach Figur 1 sind, hier nur schematisch, jedoch in den Figuren 2 bis 6 näher gezeigte, Kolbenteil 1 und 2 einer Antriebseinheit R von einem zylindrischen Gehäuseteil 3 umfangen. Dieses Gehäuseteii 3 ist einerseits von einer Stirnplatte 4 mittels Befestigungselemente 5 verschlossen, welche mittig eine Rundbohrung 6 zur Aufnahme eines Lagers 7 aufweist. In diesem Lager 7 dreht ein axialer Zapfen 8 einer Scheibe 9, welche mittels Schrauben 10 fest mit dem einen Kolbenteil 2 verbunden ist. Zen anderen Kolbenteil 1 berührt die Scheibe 9 nicht; hier durchsetzt lediglich ein Anschlagbolzen 11 ein Langloch 12, um eine axiale Bewegung von Kolbenteil 1 gegenüber Kolbenteil 2 zuzulassen.According to FIG. 1, piston parts 1 and 2 of a drive unit R are enclosed by a cylindrical housing part 3, here only schematically, but shown in more detail in FIGS. This housing part 3 is closed on the one hand by an end plate 4 by means of fastening elements 5, which has a round bore 6 in the center for receiving a bearing 7. In this bearing 7, an axial pin 8 of a disk 9 rotates, which is firmly connected to the one piston part 2 by means of screws 10. Zen other piston part 1 does not touch the disc 9; here only a stop pin 11 passes through an elongated hole 12 to allow axial movement of piston part 1 relative to piston part 2.

Gegenüber der Scheibe 9 ist der Kolbenteil 1 mit einer Drehscheibe 14 fest verbunden, welche jedoch den Kolbenteil 2 nicht berührt. Die Verbindung zwischen Drehscheibe 14 und Kolbenteil 1 wird über ein Kniehebelelement 15 bewirkt, welchem andernends exentrisch ein Zahnrad 16 aufgesetzt ist. Auch der Kolbenteil 2 ist über ein Kniehebelelement 17 exzentrisch mit einem Zahnrad 18 verbunden, wobei in der Drehscheibe 14 eine Ausnehmung 19 eine Bewegungsfreiheit des Kniehebelelements 17 zulässt. Beide Zahnräder 16 und 18 stehen mit einer Innenzahnung 38 eines mit dem Gehäuseteil 3 fest verbundenen Ringes 39 in Eingriff und umlaufen zugleich ein Sonnenrad 20, welches mit einer Abtriebswelle 21 verbunden ist, so dass letztendlich diese Abtriebswelle 21 mit dem aus den beiden Zahnrädern 16, 18 gebildeten Planetensatz eine kraftschlüssige Verbindung eingeht. Diese Kraftschlüssigkeit der Innenzahnung 38 mit den zahnrädem 16,18 und dem Sonnenrad 20 bewirkt den geregelten Umlauf der Kolbeneinheit 1 und 2 zwangsläufig und steuertsinngemäss die vier Takte Ansaugen, Verdichten, Zünden, Ausstossen während einer Umdrehung von 360°. Dementsprechend ist auch das Verhältnis dieser Teile zueinander von grosser konstruktiver Bedeutung.Compared to the disk 9, the piston part 1 is firmly connected to a turntable 14, which, however, does not touch the piston part 2. The connection between the turntable 14 and the piston part 1 is effected via a toggle lever element 15, on the other end of which a gear 16 is fitted eccentrically. The piston part 2 is also connected eccentrically to a toothed wheel 18 via a toggle lever element 17, a recess 19 in the turntable 14 allowing the toggle lever element 17 to move freely. Both gears 16 and 18 are in engagement with an internal toothing 38 of a ring 39 which is fixedly connected to the housing part 3 and at the same time rotate around a sun gear 20 which is connected to an output shaft 21, so that ultimately this output shaft 21 is connected to the one consisting of the two gear wheels 16, 18 planetary set formed a frictional connection. This frictional engagement of the internal toothing 38 with the toothed wheels 16, 18 and the sun gear 20 inevitably and in the control sense controls the four cycles of suction, compression, ignition, ejection during a rotation of 360 °. Accordingly, the relationship of these parts to each other is of great constructive importance.

Die Abtriebswelle 21 dreht axial in einem Lager 22 in der Drehscheibe 14. Weitere Lager 23 und 24 für den Läufer 21 und Zahnradachsen 25 sind in einer Drehscheibe 26 vorgesehen, welche in einem Hauptlager 27 angeordnet ist, das die Drehscheibe 26 gegenüber einer weiteren Gehäuseschale 28 abstützt. Diese Gehäuseschale 28 ist einerseits mit dem Gehäuseteil 3 verschraubt, andererseits von einer Endplatte 30 abgedeckt, welche ein weiteres Drehlager 29 für die Abtriebswelle 21 enthält. Ausserdem durchsetzt die Endplatte 30 eine Kurbel 31 in weiteren Lagern 32 und 33, welche mit einem Zahnrad 34 eine Antriebsscheibe 35 kämmt.The output shaft 21 rotates axially in a bearing 22 in the turntable 14. Further bearings 23 and 24 for the rotor 21 and gear axles 25 are provided in a turntable 26, which is arranged in a main bearing 27, which the turntable 26 is opposite to a further housing shell 28 supports. This housing shell 28 is screwed on the one hand to the housing part 3, on the other hand covered by an end plate 30 which contains a further pivot bearing 29 for the output shaft 21. In addition, the end plate 30 passes through a crank 31 in further bearings 32 and 33, which meshes a drive disk 35 with a gear 34.

In dem Gehäuseteil 3 sind im übrigen vier Gewindebohrungen 36 zum Einsetzen von Zündkerzen und je zwei gestrichelt angedeutet Ein- und Auslassschlitze 37 vorgesehen.In the housing part 3, four threaded bores 36 for inserting spark plugs and two inlet and outlet slots 37 each indicated by dashed lines are also provided.

Jedes Kolbenteil 1 und 2 besteht, wie in den Figuren 2 bis 4 dargestellt, aus einem Zylinderabschnitt 40, mit einem Segmentausschnitt41 und einem angesetzten oder angeformten Segmentabschnitt 42. Ein Winkel w des Segmentausschnitts 41 ist grösser als ein Winkel v des Segmentabschnitts 42 um die gemeinsame Kolbenachse A. Das Verhältnis der Winkel w und v zueinander bestimmt mit die Leistung des Antriebs, da ein fertiger Kolben aus zwei spiegelbildlich angeordneten Kolbenteilen 1 und 2 besteht und so vier Verbrennungskammern 43 gebildet sind, von denen in Figur 5 nur zwei angedeutet werden. Je grösser der Unterschied zwischen beiden Winkeln w und v ist, um so grösser ist auch die Verbrennungskammer 43 bzw. der Oeffnungswinkel z.As shown in FIGS. 2 to 4, each piston part 1 and 2 consists of a cylinder section 40 with a segment cutout 41 and an attached or molded segment section 42. An angle w of the segment cutout 41 is greater than an angle v of the segment section 42 around the common one Piston axis A. The ratio of the angles w and v to one another determines the power of the drive, since a finished piston consists of two piston parts 1 and 2 arranged in mirror image and thus four combustion chambers 43 are formed, only two of which are indicated in FIG. The greater the difference between the two angles w and v, the greater is the combustion chamber 43 or the opening angle z.

Im übrigen zeigt Figur 5 eine Modifikation eines Kolbens, bei welchem im Zylinderabschnitt 40 am Grunde des Segmentausschnitts 41 eine Rinne 44 eingeformt ist, in welcher der Segmentabschnitt 42 mit einem Wulstkeder 45 ruht Dem Wulstkeder 45 ist eine Scheitelnut 46 eingeformt, welche eine nicht gezeigte Dichtungsleiste aufnehmen kann, deren Funktionen einem bekannten Kolbenrin, ähneln.5 shows a modification of a piston, in which a groove 44 is formed in the cylinder section 40 at the base of the segment cutout 41, in which the segment section 42 rests with a beaded piping 45. The beaded piping 45 is formed with an apex groove 46 which forms a sealing strip (not shown) can record, the functions of which resemble a known piston ring.

Figur 6 zeigt nun die Arbeitsweise des Kolbens eines Vierkammedäufers, wobei nur das Zusammenspiel eines Zylinderabschnitts 40 mit einem Segmentabschnitt 42 dargestellt ist. Insgesamt sind für den ganzen Kolben betrachtet jedes nachfolgend beschriebene Element doppelt vorhanden. Bei einer Drehung um 360° sind für jede Verbrennungskammer zwei Arbeitstakte (Verdichtungs- und Explosionstakte) vorgesehen, wobei die Zündanlage mit 48 angedeutet ist. Im Rahmen der Erfindung liegt aber auch, die Zündkerzen an einer Innenfläche im Segmentausschnitt 41, das heisst in der Verbrennungskammer 43 anzuordnen, wodurch die Verbrennung, allerdings auf Kosten einer guten Zugänglichkeit zu den Zündkerzen, verbessert wird.FIG. 6 now shows the mode of operation of the piston of a four-cylinder rotor, only the interaction of a cylinder section 40 with a segment section 42 being shown. All in all, each element described below is present twice for the entire piston. With a rotation through 360 °, two work cycles (compression and explosion cycles) are provided for each combustion chamber, the ignition system being indicated at 48. However, the spark plugs are also within the scope of the invention on an inner surface in the segment ment cutout 41, that is to say to be arranged in the combustion chamber 43, as a result of which the combustion is improved, but at the expense of good access to the spark plugs.

Weiterhin sind sich jeweils gegenüberliegend Auslässe 49 sowie Einlässe 50 vorgesehen.Furthermore, outlets 49 and inlets 50 are provided opposite each other.

Die 1. Stellung nach Figur 6 zeigt, dass in die eine Verbrennungskammer 43a Kraftstoff eingesaugtwird, während bei der anderen 43b gerade die Zündung erfolgt. Hierdurch wird die Kammer 43b geöffnet, dagegen die Kammer 43a verdichtet, während die Kolbendrehbewegung um die Achse A beschleunigt wird. Beide Kammern gelangen in die II. Position. Die Brenngase können aus der Kammer 43b in den Auslass 49 entfernt werden, gleichzeitig erfolgt die Zündung in der Kammer 43a. Die Gase aus dieser Zündung werden wiederum aus der Kammer 43a durch den nachfolgenden Auslass entfernt, wobei neuer Brennstoff in die Kammer 43b eingesaugt wird, wie dies die 111. Position zeigt. In der IV. Position wird die Kammer 43b wieder gezündet, während die Kammer 43a den Auslass 50 passiert. In der V. Position erfolgt eine Zündung der Kammer 43a, während die Kammer 43b am Auslass 49 vorbeiläuft. Und schliesslich steht die Kammer 43a auf Auslass 49, wenn die Kammer 43b wieder ansaugt. Die nächste Position ist wieder die l. Position. Damit ist eine Drehung um 360° vollzogen, die entsprechend notwendigen Veränderungen der Kammern 43a bzw. 43b werden insbesondere von der Zündung und von der Bewegung der Zahnräder 16 und 18 durchgeführt.The first position according to FIG. 6 shows that fuel is drawn into one combustion chamber 43a, while the other 43b is just being ignited. As a result, the chamber 43b is opened, while the chamber 43a is compressed, while the piston rotation movement about the axis A is accelerated. Both chambers are in the 2nd position. The fuel gases can be removed from the chamber 43b into the outlet 49, at the same time the ignition takes place in the chamber 43a. The gases from this ignition are again removed from chamber 43a through the subsequent outlet, with new fuel being drawn into chamber 43b, as shown in the 111th position. In the IV position, chamber 43b is reignited as chamber 43a passes outlet 50. In the V position, the chamber 43a is ignited while the chamber 43b passes the outlet 49. And finally, chamber 43a is at outlet 49 when chamber 43b draws in again. The next position is again the l. Position. This completes a rotation through 360 °; the changes necessary to the chambers 43a and 43b are carried out in particular by the ignition and the movement of the gear wheels 16 and 18.

Insgesamt werden pro Umdrehung zweiunddreissig Takte geleistet, wovon achtArbeitstakte sind. Dies sind sechs Arbeitstakte mehr als bei einem bekannten Otto-oder Wankelmotor bei wesentlich geringerer Oberflächenreibung, da ein entsprechender Otto-oder Wankelmotor eine etwa 40 bis 50% grössere Kolbenfläche aufweisen müsste. Die Kolbengeschwindigkeit ist wesentlich tiefer als bei den bisher bekannten Motoren und zwar etwa um 20 bis 30%. Maximal wird eine Kolbengeschwindigkeit von 8 bis 10 m/sec notwendig sein.A total of thirty-two cycles are performed per revolution, eight of which are working cycles. This is six work cycles more than with a known Otto or Wankel engine with a significantly lower surface friction, since a corresponding Otto or Wankel engine would have to have an approximately 40 to 50% larger piston area. The piston speed is significantly lower than that of the previously known engines, namely by around 20 to 30%. A maximum piston speed of 8 to 10 m / sec will be necessary.

Der Ein- und Auslass erfolgt zwangsläufig durch die Rotordrehung mit hoher Ansaug- und Spülleistung. Dort sind keine beweglichen Teile, wie Ventile, vorhanden, welche gewartet werden müssen.The inlet and outlet are inevitably done by the rotor rotation with high suction and flushing performance. There are no moving parts, such as valves, that need to be serviced.

Die ganze Antriebseinheit kann in entsprechenden Hohlräumen mit Wasser oder Oel gekühlt werden.The entire drive unit can be cooled with water or oil in appropriate cavities.

Claims (14)

1. Apparatus for driving a drive shaft (21) by means of at least one arragement of two piston portions (1, 2) which rotate around the same axis and form between themselves two combustion chambers (43) of variable volume and of which the first piston portion (1) has a cylindrical section (40) with a cut out segment (41) in which the second piston portion (2) is set as a segment section (42), characterised in that each of the piston portions (1, 2) is connected eccentrically with a planet gear (16, 18) which in each case meshes with an interior toothing (39) of a ring (39) fixed to a housing and an exterior toothing of a sun gear (20) which is coupled to the drive shaft (21).
2. Apparatus according to claim 1 characterised in that in the basin of the cut out segment (41) a base (44) is formed in which the segment section (42) rests with a bead (45).
3. Apparatus according to claim 2 characterised in that the bead (45) has an apical (42) which receives a sealing strip.
4. Apparatus according to one of claims 1 to 3 characterised in that the pistons turn in a housing part (3) which has at least one outlet (49) for exhaust gas and at least one inlet (50) for the fuel.
5. Apparatus according to claim 4 characterised in that an ingnition device is arranged on an innersur- face of a cut out segment (41) or an outer surface of a segment section (42), which together in each case form a combustion chamber (43) with an angle (z).
6. Apparatus according to claim 4 characterised in that at least one ignition arrangement (48) is arranged in the housing part (39).
7. Apparatus according to claim 6 characterised in that in each case two ignition arrangements (48), two outlets (49) and two inlets (50) lie opposite one another.
8. Apparatus according to one of claims 5 to 7 characterised in that the angle of the cut out segment (w) and of the segment section (v) and the arrangement of the ignition devices (48), of the outlets (49) and of the inlets (50) are so chosen that a first combustion chamber (43b) is ignited when a second is connected with the inlet (50), and that in the following position the first chamber (43b) is connected to the outlet (49) while the second chamber (43a) is ignited, and that in the further position then the first chamber (43b) is at the inlet (50) and the second (43a) at the outlet.
9. Apparatus according to claim 8 characterised in that the said positions can be achieved at least twice during one revolution of the piston through 360°.
10. Apparatus according to at least one of claims 1 to 9 characterised in that each cylindrical section (40) is connected with at least one segment section (42) to which is arranged in each case correspondingly a piston part with at least one segment section (42) and one cylindrical section (40).
11. Apparatus according to one of claims 1 to 10 characterised in that the connection between piston parts (1, 2) and planet gear (16, 18) occurs via cranked lever elements (15, 17).
12. Apparatus according to one of claims 1 to 11 characterised in that the planet gears are supported with gear axles (25) in bearings (24) which are parts of a rotating disc (26) whith turns in a main bearing (27) between a housing shell (28) and which is pierced by the drive shaft (21) at a further bearing (23).
13. Apparatus according to one of claims 1 to 12 charaterised in that the drive shaft (21) is rotatable at least for starting via a crank (31) and a cog (34) meshing with a drive disc (35).
14. Apparatus according to one of claims 1 to 13 characterised in that the piston parts (1, 2) are covered in each case at the end faces by discs (9, 14) which are fixedly connected with one piston part but which are free of contact with the other.
EP86901323A 1985-03-18 1986-03-06 Rotary piston machine with periodically variable rotation speeds Expired - Lifetime EP0217813B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH1195/85 1985-03-18
CH1195/85A CH667131A5 (en) 1985-03-18 1985-03-18 DEVICE FOR DRIVING AN OUTPUT SHAFT.

Publications (2)

Publication Number Publication Date
EP0217813A1 EP0217813A1 (en) 1987-04-15
EP0217813B1 true EP0217813B1 (en) 1991-05-02

Family

ID=4204727

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EP86901323A Expired - Lifetime EP0217813B1 (en) 1985-03-18 1986-03-06 Rotary piston machine with periodically variable rotation speeds

Country Status (6)

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US (1) US4788952A (en)
EP (1) EP0217813B1 (en)
JP (1) JPS62502274A (en)
AU (1) AU5457686A (en)
CH (1) CH667131A5 (en)
WO (1) WO1986005545A1 (en)

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Publication number Priority date Publication date Assignee Title
GB9024648D0 (en) * 1990-11-13 1991-01-02 Seymour Chalk Hugh A Rotary engine
AU673570B2 (en) * 1992-11-27 1996-11-14 Donald Clive Hiscock Gearing By Definition A Dveljagimmal
US7270092B2 (en) * 2005-08-12 2007-09-18 Hefley Carl D Variable displacement/compression engine
AU2008229566A1 (en) * 2007-03-22 2008-09-25 Felix Wirz Method and device for generating mechanical energy

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Publication number Priority date Publication date Assignee Title
US2816527A (en) * 1953-10-28 1957-12-17 Palazzo Quirino Rotary four-stroke engine
FR2138581B1 (en) * 1971-05-27 1973-05-25 Marchand Henri
FR2166529A5 (en) * 1971-12-28 1973-08-17 Gindre Henri
US4068985A (en) * 1976-04-06 1978-01-17 Baer John S Rotary engine or pump construction
JPS5231482A (en) * 1976-09-17 1977-03-09 Hitachi Ltd Escalator control unit
EP0062087A1 (en) * 1981-04-08 1982-10-13 Gerhard Rödiger Rotary-piston machine with periodically variable rotating speed

Also Published As

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JPH0335499B2 (en) 1991-05-28
AU5457686A (en) 1986-10-13
US4788952A (en) 1988-12-06
JPS62502274A (en) 1987-09-03
WO1986005545A1 (en) 1986-09-25
CH667131A5 (en) 1988-09-15
EP0217813A1 (en) 1987-04-15

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