EP0081205A1 - Internal combustion wobble plate engine - Google Patents

Internal combustion wobble plate engine Download PDF

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Publication number
EP0081205A1
EP0081205A1 EP82111151A EP82111151A EP0081205A1 EP 0081205 A1 EP0081205 A1 EP 0081205A1 EP 82111151 A EP82111151 A EP 82111151A EP 82111151 A EP82111151 A EP 82111151A EP 0081205 A1 EP0081205 A1 EP 0081205A1
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EP
European Patent Office
Prior art keywords
internal combustion
shaft
swash plate
combustion engine
valve
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EP82111151A
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German (de)
French (fr)
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EP0081205B1 (en
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Dieter Lehmann
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Individual
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Individual
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Priority to AT82111151T priority Critical patent/ATE20687T1/en
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    • 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
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/02—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis with wobble-plate
    • 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
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/10—Control of working-fluid admission or discharge peculiar thereto
    • F01B3/101—Control of working-fluid admission or discharge peculiar thereto for machines with stationary cylinders
    • F01B3/102—Changing the piston stroke by changing the position of the swash plate
    • 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
    • F02B75/26—Engines with cylinder axes coaxial with, or parallel or inclined to, main-shaft axis; Engines with cylinder axes arranged substantially tangentially to a circle centred on main-shaft axis

Definitions

  • the invention relates to a swashplate internal combustion engine with a variable displacement, the swashplate in the machine housing being pivotable relative to the main engine shaft about an axis running at right angles to the main engine shaft.
  • Such a swash plate internal combustion engine is known for example from DE-OS 15 76 187.
  • several cylinders are arranged in the stationary machine housing with their axes lying on a conical jacket, the pistons of which are articulated on the swash plate via piston rods and spherical bearings.
  • the swash plate is gimbal-mounted via a ring in a non-rotating bell, but axially displaceable relative to the housing, and is supported via radial and axial rolling bearings against an annular, rotating swash plate, which in turn is mounted on the latter via journals of a shaft that can be rotated in slide bushings .
  • the swashplate has a joint on its circumference, which forms a guide and with which it is mounted in a flywheel, which is supported in the housing pot on axially and radially acting roller bearings.
  • the longitudinally displaceable shaft has its main bearing points in the center of the cardanic suspension of the swash plate and in the sliding seat opposite a hub of the flywheel.
  • the motor drive is carried out via this hub as the main motor shaft.
  • the main engine shaft cannot be made in one piece in this embodiment, but must have the additional axially displaceable shaft with the pivot bearing, which in turn must be connected to the main engine shaft in a rotationally fixed manner.
  • the stroke change is controlled by axially shifting a pivot point of the non-rotating part of the swashplate on the main motor axis and a related slanted position of the swashplate axis.
  • the object of the present invention is to propose a swashplate internal combustion engine of the generic type which, with simple means, has a pivot bearing which is free of play even after a long period of operation.
  • the displacement should be able to be carried out with a constant or almost constant compression ratio.
  • the circumferential part of the swash plate can be pivoted about a pivot axis which is firmly connected to the main engine shaft and is eccentrically transverse to the main engine shaft. This allows a one-piece design of the main engine shaft to be used.
  • the eccentric arrangement of the swivel axis with a large distance to the axis of rotation of the main engine shaft also reduces the forces generated by the torque of the engine.
  • the eccentricity of the swivel axis can be selected so that the compression ratio remains the same or almost the same when the displacement changes within defined limits.
  • the freedom from play of the swivel axis which can be achieved according to the invention, is important because when switching to overrun operation, shocks otherwise occur which can destroy the swivel bearing.
  • the advantages of such an internal combustion engine which consist in the fact that they operate in part-load operation, as e.g. is given in a motor vehicle in city traffic, with a displacement capacity adapted to the required output more economically, i.e. works with lower fuel consumption, can be used over long operating times.
  • a special embodiment of the invention is characterized in that the non-rotating part of the swash plate is connected in a rotationally fixed manner to the machine housing via a double shaft joint.
  • the double shaft joint is preferably mounted axially displaceably on the machine housing with a pivot pin in the direction of the central axis of the main motor shaft.
  • the circumferential part of the swash plate can be connected via an articulated rod to an adjusting piston which is mounted concentrically in the main engine shaft.
  • This adjusting piston is axially adjustable, for example, via a screw drive in the direction of the central axis of the main engine shaft.
  • the adjustment drive can be relieved in that the adjustment piston can be acted upon hydraulically or pneumatically in the direction of the swash plate.
  • valve control in the swash plate internal combustion engine according to the invention with an intake valve and an exhaust valve for each cylinder in the cylinder head is particularly simple in that the valve stems of the intake and exhaust valve of a cylinder are axially driven by a common control cam.
  • the valve lift of the intake valve and exhaust valve can be positively controlled by the control cam.
  • the intake and exhaust valves of all cylinders can be driven together by a main shaft driven by the main engine shaft.
  • the outlet valves and possibly inlet valves can expediently be opened via the control cam against the action of a closing spring.
  • the exhaust valve is kept closed in spite of a valve clearance of the exhaust valve in the control cam disc, particularly during the suction stroke.
  • valve control of the swash plate internal combustion engine according to the invention thus differs significantly from the construction of conventional internal combustion engines with crank drive.
  • engines with crank drive the central axes of the cylinders intersect the main engine shaft at right angles.
  • the cylinder axes and the central axis of the main motor shaft are preferably substantially or exactly parallel.
  • the inlet and outlet valve can thus be driven by the same control cam will.
  • An optionally provided positively controlled valve train does not require valve springs, which means that the engine is safe against engine damage due to over-revving.
  • a fixed engine housing 1 there is, preferably in an odd number, cylinders 2 with pistons 3, the axes of which are parallel to the central axis 4 of an engine main shaft 14.
  • the pistons 3 are connected in an articulated manner to a non-rotating part 7 of a swash plate via connecting rods 6.
  • the piston-side ends of the connecting rods 6 are each attached to the non-rotating part 7 of the swash plate via a ball joint 45 and the opposite ends via a cardan shaft joint 46.
  • the non-rotating part 7 of the swash plate is itself connected to the motor housing 1 in a rotationally fixed manner via a cardan double shaft joint 8.
  • the double-shaft joint 8 with a pivot pin 44 pointing towards the cylinder head 5 is easily pivotable and in because of a ball-groove bearing Direction of the central axis 4 of the main motor shaft 14 axially displaceably mounted in a sleeve portion of the fixed motor housing 1.
  • a peripheral part 9 of the swash plate is rotatably connected to the non-rotating part 7 of the swash plate via an axial slide bearing 10 and a radial bearing 11 on a swash plate axis 12.
  • the center of the cardanic suspension of the non-rotating part of the swash plate deviates as little as possible from the central axis 4 when the swash plate is pivoted about the swivel axis 13.
  • the circumferential part 9 of the swash plate is pivotally connected to the main motor shaft 14 by means of a swivel axis 13 lying transversely (at right angles) eccentrically to the main motor shaft 14, specifically via a flywheel 47.
  • the stroke of the pistons 3 is reduced by pivoting the rotating part 9 of the swash plate about the pivot axis 13 in the direction of the cylinders 2 and the pistons 3. This reduces the displacement of the engine.
  • the peripheral part 9 of the swash plate is connected in the area of the central axis 4 via an articulated rod 18 to an adjusting piston 17, which is pivotably articulated on both sides in a common plane.
  • the adjusting piston 17 is mounted concentrically axially displaceably in the main engine shaft 14.
  • the main motor shaft 14 itself is mounted in roller bearings 15 and 16 in the motor housing 1.
  • the displacement is adjusted by means of the adjusting piston 17 via a toothed rack 19, the axis of which extends eccentrically transversely to the central axis 4 and which engages a threaded sleeve 20 coaxial with the central axis 4, which in turn is operatively connected to the motor housing 1 via a helical thread 21.
  • the adjusting piston 17 is axially displaced relative to the main engine shaft 14 via a thrust bearing 22, a pressure ring 23 and connecting rods 24.
  • the adjustment of the rack 19 is optimized with a known control drive so that the engine works with the smallest possible displacement for the power required and thus works most economically.
  • a pneumatic or hydraulic pressure medium can be applied to the rear end face of the adjusting piston 17 via a pressure medium channel 48, as a result of which a counterforce to the forces of the pistons 3 is exerted, which reduces the adjusting forces to be used to change the displacement.
  • the motor is driven via the shaft end 25 of the main motor shaft 14.
  • the gas exchange in the cylinders 2 is controlled via exhaust valves 27 and intake valves 26.
  • a valve lifter 29 with a lock nut 30 is fastened via an adjustment thread.
  • the valve lifter 29 has a laterally facing control pin 31, which engages in a control cam 32, and a (opposite) radially projecting link pin 33, which secures the valve lifter 29 against rotation by a link guide 34.
  • a toothed belt pulley 36 is fastened, which via a toothed belt 37, a drive pulley 38, a parallel shaft 39 running parallel to the main motor shaft 14, a drive wheel 40, an intermediate wheel 41 and a Main shaft gear 42 can be driven from the main motor shaft 14.
  • the control cam 32 is 27 arranged to the centers of the shafts 28 of the intake valve 26 and the exhaust valve so that the angle between the connecting lines of the cam center and the centers of the shafts is 28 the intake valve 26 and the exhaust valve 27 is about 90 0th With this arrangement, intake valve 26 and exhaust valve 27 can be driven by the same cam 32.
  • All control cams 32 for all cylinders 2 are driven via the common toothed belt 37.
  • the exhaust valve is controlled Cam 32 openable against the action of a closing spring 43.
  • the exhaust valve 27 is thus kept closed by the closing spring 43 during the suction stroke, although sufficient valve clearance is set between the control cam 32 and the control pin 31 of the valve lifter 29.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • Valve Device For Special Equipments (AREA)
  • Preparation Of Compounds By Using Micro-Organisms (AREA)
  • Pharmaceuticals Containing Other Organic And Inorganic Compounds (AREA)
  • Transmission Devices (AREA)
  • Molds, Cores, And Manufacturing Methods Thereof (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
  • Diaphragms For Electromechanical Transducers (AREA)

Abstract

1. A variable displacement wobble-plate internal combustion engine the wobble-plate of which is pivotable in the machine casing (1) relative to the motor main shaft (14) about an axis intersecting, at right angles, the center axis (4) of the motor main shaft (14), with the rotating part (9) of the wobble-plate being pivotable about a pivot axis (13) rotating with the motor main shaft (14) and being eccentrically disposed transverse of the motor main shaft (14), on a flywheel (47) formed at the end of the motor main shaft (14), and with the non-rotating part (7) of the wobble-plate, via a dual-shaft joint (8) being rigidly connected to the maschine casing (1), characterized in that the motor main shaft (14) is supported and borne on one side of the machine casing (1) only and that the flywheel (47) formed at the end of the motor main shaft (14) is disposed in flying manner, and that a pinion rigidly connected to the flywheel (47) forms the pivot axis (13).

Description

Die Erfindung betrifft eine Taumelscheiben-Brennkraftmaschine mit veränderbarem Hubraum, dessen Taumelscheibe in dem Maschinengehäuse relativ zu der Motorhauptwelle um eine rechtwinklig zur Motorhauptwelle verlaufende Achse schwenkbar ist.The invention relates to a swashplate internal combustion engine with a variable displacement, the swashplate in the machine housing being pivotable relative to the main engine shaft about an axis running at right angles to the main engine shaft.

Eine solche Taumelscheiben-Brennkraftmaschine ist beispielsweise aus der DE-OS 15 76 187 bekannt. Bei der bekannten Maschine sind in dem stillstehenden Maschinengehäuse mehrere, mit ihren Achsen auf einem Kegelmantel liegende Zylinder angeordnet, deren Kolben über Kolbenstangen und sphärische Lager an der Taumelscheibe angelenkt sind. Die Taumelscheibe ist kardanisch über einen Ring in einer nicht-umlaufenden, aber axial gegenüber dem Gehäuse verschieblichen Glocke aufgehängt und über radial und axial wirkende Wälzlager gegen eine ringförmige, umlaufende Schiefscheibe abgestützt, die ihrerseits über in Gleitbuchsen drehbare Zapfen einer Welle auf der letzteren gelagert ist. Die Schiefscheibe trägt an ihrem Umfang ein Gelenk, das eine Führung bildet und mit dem sie in einer Schwungscheibe gelagert ist, die im Gehäusetopf auf axial und radial wirkenden Wälzlagern abgestützt ist. Die längsverschiebbare Welle hat ihre Hauptlagerstellen im Mittelpunkt der kardanischen Aufhängung der Taumelscheibe und im Schiebesitz gegenüber einer Nabe der Schwungscheibe. Über diese Nabe erfolgt als Motorhäuptwelle der Kraftantrieb. Die Motorhauptwelle kann bei dieser Ausführung nicht einteilig ausgeführt werden, sondern muß die zusätzliche axial verschiebliche Welle mit dem Schwenklager haben, die wiederum drehfest mit der Motorhauptwelle verbunden sein muß.Such a swash plate internal combustion engine is known for example from DE-OS 15 76 187. In the known machine, several cylinders are arranged in the stationary machine housing with their axes lying on a conical jacket, the pistons of which are articulated on the swash plate via piston rods and spherical bearings. The swash plate is gimbal-mounted via a ring in a non-rotating bell, but axially displaceable relative to the housing, and is supported via radial and axial rolling bearings against an annular, rotating swash plate, which in turn is mounted on the latter via journals of a shaft that can be rotated in slide bushings . The swashplate has a joint on its circumference, which forms a guide and with which it is mounted in a flywheel, which is supported in the housing pot on axially and radially acting roller bearings. The longitudinally displaceable shaft has its main bearing points in the center of the cardanic suspension of the swash plate and in the sliding seat opposite a hub of the flywheel. The motor drive is carried out via this hub as the main motor shaft. The main engine shaft cannot be made in one piece in this embodiment, but must have the additional axially displaceable shaft with the pivot bearing, which in turn must be connected to the main engine shaft in a rotationally fixed manner.

Bei einer aus der DE-OS 26 33 618 bekannten Taumelscheiben-Brennkraftmaschine wird durch axiales Verschieben eines Anlenkpunktes des nicht-umlaufenden Teiles der Taumelscheibe auf der Motorhauptachse und einer damit verbundenen kulissengeführten Schrägstellung der Taumelscheibenachse die Hubveränderung gesteuert.In a swashplate internal combustion engine known from DE-OS 26 33 618, the stroke change is controlled by axially shifting a pivot point of the non-rotating part of the swashplate on the main motor axis and a related slanted position of the swashplate axis.

Aufgabe der vorliegenden Erfindung ist es, eine Taumelscheiben-Brennkraftmaschine der gattungsgemäßen Art vorzuschlagen, die mit einfachen Mitteln eine auch nach langer Betriebszeit spielfreie Schwenklagerung aufweist. Dabei soll die Hubraumveränderung bei gleichbleibendem oder nahezu gleichbleibenden Verdichtungsverhältnis vorgenommen werden können.The object of the present invention is to propose a swashplate internal combustion engine of the generic type which, with simple means, has a pivot bearing which is free of play even after a long period of operation. The displacement should be able to be carried out with a constant or almost constant compression ratio.

Diese Aufgabe wird erfindungsgemäß dadurch gelöst, daß der umlaufende Teil der Taumelscheibe um eine mit der Motorhauptwelle fest verbundenen, exzentrisch quer zur Motorhauptwelle liegende Schwenkachse schwenkbar ist. Dadurch kann eine einteilige Ausführung der Motorhauptwelle verwendet werden.This object is achieved in that the circumferential part of the swash plate can be pivoted about a pivot axis which is firmly connected to the main engine shaft and is eccentrically transverse to the main engine shaft. This allows a one-piece design of the main engine shaft to be used.

Die exzentrische Anordnung der Schwenkachse mit großem Abstand zur Drehachse der Motorhauptwelle verringert darüber hinaus die auftretenden Kräfte durch das Drehmoment des Motors.The eccentric arrangement of the swivel axis with a large distance to the axis of rotation of the main engine shaft also reduces the forces generated by the torque of the engine.

Die Exzentrizität der Schwenkachse ist so wählbar, daß das Verdichtungsverhältnis bei Veränderung des Hubraumes in festgelegten Grenzen gleich oder nahezu gleich bleibt. Die erfindungsgemäß erzielbare Spielfreiheit der Schwenkachse ist wichtig, weil bei einem Wechsel auf Schubbetrieb sonst Schläge auftreten, die die Schwenklagerung zerstören können. Erfindungsgemäß können die Vorteile einer solchen Brennkraftmaschine, die darin bestehen, daß sie im Teillastbetrieb, wie er z.B. bei einem Kraftfahrzeug im Stadtverkehr gegeben ist, mit einer der geforderten Leistung angepaßten Hubraumgröße wirtschaftlicher, d.h. mit geringerem Treibstoffverbrauch arbeitet, über lange Betriebszeiten ausgenutzt werden kann.The eccentricity of the swivel axis can be selected so that the compression ratio remains the same or almost the same when the displacement changes within defined limits. The freedom from play of the swivel axis, which can be achieved according to the invention, is important because when switching to overrun operation, shocks otherwise occur which can destroy the swivel bearing. According to the invention, the advantages of such an internal combustion engine, which consist in the fact that they operate in part-load operation, as e.g. is given in a motor vehicle in city traffic, with a displacement capacity adapted to the required output more economically, i.e. works with lower fuel consumption, can be used over long operating times.

Eine besondere Ausgestaltung der Erfindung zeichnet sich dadurch aus, daß der nicht-umlaufende Teil der Taumelscheibe über ein Doppelwellengelenk mit dem Maschinengehäuse drehfest verbunden ist.A special embodiment of the invention is characterized in that the non-rotating part of the swash plate is connected in a rotationally fixed manner to the machine housing via a double shaft joint.

Das Doppelwellengelenk ist vorzugsweise mit einem Gelenkzapfen in Richtung der Mittelachse der Motorhauptwelle axial verschieblich an dem Maschinengehäuse gelagert.The double shaft joint is preferably mounted axially displaceably on the machine housing with a pivot pin in the direction of the central axis of the main motor shaft.

Ferner kann im Rahmen des Erfindungsgedankens der umlaufende Teil der Taumelscheibe über eine Gelenkstange mit einem konzentrisch in der Motorhauptwelle gelagerten Verstellkolben verbunden sein.Furthermore, within the scope of the inventive concept, the circumferential part of the swash plate can be connected via an articulated rod to an adjusting piston which is mounted concentrically in the main engine shaft.

Dieser Verstellkolben ist beispielsweise über einen Gewindetrieb in Richtung der Mittelachse der Motorhauptwelle axial verstellbar.This adjusting piston is axially adjustable, for example, via a screw drive in the direction of the central axis of the main engine shaft.

Der Verstellantrieb kann dadurch entlastet werden, daß der Verstellkolben hydraulisch oder pneumatisch in Richtung der Taumelscheibe beaufschlagbar ist.The adjustment drive can be relieved in that the adjustment piston can be acted upon hydraulically or pneumatically in the direction of the swash plate.

Die Ventilsteuerung bei der erfindungsgemäßen Taumelscheiben-Brennkraftmaschine mit einem Einlaßventil und einem Auslaßventil für jeden Zylinder in dem Zylinderkopf ergibt sich besonders einfach dadurch, daß die Ventilschäfte von Einlaß- und Auslaßventil eines Zylinders von einer gemeinsamen Steuerkurvenscheibe axial antreibbar sind.The valve control in the swash plate internal combustion engine according to the invention with an intake valve and an exhaust valve for each cylinder in the cylinder head is particularly simple in that the valve stems of the intake and exhaust valve of a cylinder are axially driven by a common control cam.

Der Ventilhub von Einlaßventil und Auslaßventil kann von der Steuerkurvenscheibe zwangsgesteuert sein.The valve lift of the intake valve and exhaust valve can be positively controlled by the control cam.

Vorteilhafterweise sind die Einlaß- und Auslaßventile aller Zylinder gemeinsam von einer von der Motorhauptwelle angetriebenen Königswelle antreibbar.Advantageously, the intake and exhaust valves of all cylinders can be driven together by a main shaft driven by the main engine shaft.

Die Auslaßventile und gegebenenfalls Einlaßventile sind zweckmäßigerweise über die Steuerkurvenscheibe gegen die Wirkung einer Schließfeder öffenbar. Dadurch wird insbesondere auch beim Saughub das Auslaßventil trotz eines Ventilspieles des Auslaßventiles in der Steuerkurvenscheibe geschlossen gehalten.The outlet valves and possibly inlet valves can expediently be opened via the control cam against the action of a closing spring. As a result, the exhaust valve is kept closed in spite of a valve clearance of the exhaust valve in the control cam disc, particularly during the suction stroke.

Die erfindungsgemäße Ventilsteuerung der Taumelscheiben-Brennkraftmaschine unterscheidet sich damit wesentlich von der Konstruktion herkömmlicher Brennkraftmaschinen mit Kurbeltrieb. Bei Motoren mit Kurbeltrieb schneiden die Mittelachsen der Zylinder rechtwinklig die Motorhauptwelle. Bei der erfindungsgemäßen Taumelscheiben-Brennkraftmaschine liegen die Zylinderachsen und die Mittelachse der Hauptmotorwelle vorzugsweise im wesentlichen oder genau parallel. Ein- und Auslaßventil können dadurch von der gleichen Steuerkurvenscheibe angetrieben werden. Ein gegebenenfalls vorgesehener zwangsgesteuerter Ventiltrieb benötigt keine Ventilfedern, womit der Motor sicher gegen Motorschäden durch Überdrehen ist.The valve control of the swash plate internal combustion engine according to the invention thus differs significantly from the construction of conventional internal combustion engines with crank drive. In engines with crank drive, the central axes of the cylinders intersect the main engine shaft at right angles. In the swash plate internal combustion engine according to the invention, the cylinder axes and the central axis of the main motor shaft are preferably substantially or exactly parallel. The inlet and outlet valve can thus be driven by the same control cam will. An optionally provided positively controlled valve train does not require valve springs, which means that the engine is safe against engine damage due to over-revving.

Weitere Ziele, Merkmale, Vorteile und Anwendungsmöglichkeiten der vorliegenden Erfindung ergeben sich aus der nachfolgenden Beschreibung eines Ausführungsbeispieles anhand der beiliegenden Zeichnung. Dabei bilden alle beschriebenen und/oder bildlich dargestellten Merkmale für sich oder in beliebiger sinnvoller Kombination den Gegenstand der vorliegenden Erfindung, auch unabhängig von ihrer Zusammenfassung in den Ansprüchen oder deren Rückbeziehung.Further objectives, features, advantages and possible uses of the present invention result from the following description of an exemplary embodiment with reference to the accompanying drawing. All of the described and / or illustrated features, alone or in any meaningful combination, form the subject matter of the present invention, regardless of how they are summarized in the claims or their relationship.

Es zeigt:

  • Fig. 1 im Axialschnitt eine Ausführungsform einer die Erfindung aufweisenden Taumelscheiben-Brennkraftmaschine, und
  • Fig. 2 eine Draufsicht auf den Zylinderkopf.
It shows:
  • Fig. 1 in axial section an embodiment of a swash plate internal combustion engine having the invention, and
  • Fig. 2 is a plan view of the cylinder head.

In einem feststehenden Motorgehäuse 1 befindet sich, vorzugsweise in ungerader Zahl, Zylinder 2 mit Kolben 3, deren Achsen parallel zur Mittelachse 4 einer Motorhauptwelle 14 liegen.In a fixed engine housing 1 there is, preferably in an odd number, cylinders 2 with pistons 3, the axes of which are parallel to the central axis 4 of an engine main shaft 14.

Die Kolben 3 sind über Pleuelstangen 6 gelenkig mit einem nicht-umlaufenden Teil 7 einer Taumelscheibe verbunden. Dabei sind die kolbenseitigen Enden der Pleuelstangen 6 jeweils über ein Kugelgelenk 45 und die gegenüberliegenden Enden über ein kardanisches Wellengelenk 46 an dem nicht-umlaufenden Teil 7 der Taumelscheibe angebracht. Der nicht-umlaufende Teil 7 der Taumelscheibe ist selbst über ein kardanisches Doppelwellengelenk 8 mit dem Motorgehäuse 1 drehfest verbunden. Dabei ist das Doppelwellengelenk 8 mit einem zum Zylinderkopf 5 weisenden Gelenkzapfen 44 aufgrund einer Kugel-Rillen-Lagerung leicht schwenkbar und in Richtung der Mittelachse 4 der Motorhauptwelle 14 axial verschiebbar in einem Hülsenabschnitt des feststehenden Motorgehäuses 1 gelagert. Ein umlaufender Teil 9 der Taumelscheibe ist über ein Axialgleitlager 10 und ein Radiallager 11 auf einer Taumelscheibenachse 12 drehbar mit dem nicht-umlaufenden Teil 7 der Taumelscheibe verbunden. Der Mittelpunkt der kardanischen Aufhängung des nicht-umlaufenden Teils der Taumelscheibe weicht beim Schwenken der Taumelscheibe um die Schwenkachse 13 geringstmöglich von der Mittelachse 4 ab. Der umlaufende Teil 9 der Taumelscheibe ist über eine quer (rechtwinklig) exzentrisch zur Motorhauptwelle 14 liegenden Schwenkachse 13 mit der Motorhauptwelle 14, und zwar über eine Schwungscheibe 47 schwenkbar verbunden. Durch Schwenken des umlaufenden Teils 9 der Taumelscheibe um die Schwenkachse 13 in Richtung der Zylinder 2 und der Kolben 3 verkleinert sich der Hub der Kolben 3. Damit wird der Hubraum des Motors reduziert. Für die Ausführung der Schwenkbewegung ist der umlaufende Teil 9 der Taumelscheibe im Bereich der Mittelachse 4 über eine Gelenkstange 18 mit einem Verstellkolben 17 verbunden, die auf beiden Seiten in einer gemeinsamen Ebene verschwenkbar angelenkt ist. Der Verstellkolben 17 ist konzentrisch in der Motorhauptwelle 14 axial verschiebbar gelagert. Die Motorhauptwelle 14 selbst ist in Wälzlagern 15 und 16 in dem Motorgehäuse 1 gelagert. Die Hubraumverstellung mittels des Verstellkolbens 17 erfolgt über eine Zahnstange 19, deren Achse exzentrisch quer zur Mittelachse 4 verläuft und die an einer zur Mittelachse 4 koaxialen Gewindehülse 20 angreift, die ihrerseits über ein Steilgewinde 21 mit dem Motorgehäuse 1 in Wirkverbindung steht. Von der sich axial verschiebenden Gewindehülse 20 aus wird über ein Drucklager 22, einen Druckring 23 und Verbindungsstangen 24 der Verstellkolben 17 relativ zur Motorhauptwelle 14 axial verschoben.The pistons 3 are connected in an articulated manner to a non-rotating part 7 of a swash plate via connecting rods 6. The piston-side ends of the connecting rods 6 are each attached to the non-rotating part 7 of the swash plate via a ball joint 45 and the opposite ends via a cardan shaft joint 46. The non-rotating part 7 of the swash plate is itself connected to the motor housing 1 in a rotationally fixed manner via a cardan double shaft joint 8. The double-shaft joint 8 with a pivot pin 44 pointing towards the cylinder head 5 is easily pivotable and in because of a ball-groove bearing Direction of the central axis 4 of the main motor shaft 14 axially displaceably mounted in a sleeve portion of the fixed motor housing 1. A peripheral part 9 of the swash plate is rotatably connected to the non-rotating part 7 of the swash plate via an axial slide bearing 10 and a radial bearing 11 on a swash plate axis 12. The center of the cardanic suspension of the non-rotating part of the swash plate deviates as little as possible from the central axis 4 when the swash plate is pivoted about the swivel axis 13. The circumferential part 9 of the swash plate is pivotally connected to the main motor shaft 14 by means of a swivel axis 13 lying transversely (at right angles) eccentrically to the main motor shaft 14, specifically via a flywheel 47. The stroke of the pistons 3 is reduced by pivoting the rotating part 9 of the swash plate about the pivot axis 13 in the direction of the cylinders 2 and the pistons 3. This reduces the displacement of the engine. For the execution of the swiveling movement, the peripheral part 9 of the swash plate is connected in the area of the central axis 4 via an articulated rod 18 to an adjusting piston 17, which is pivotably articulated on both sides in a common plane. The adjusting piston 17 is mounted concentrically axially displaceably in the main engine shaft 14. The main motor shaft 14 itself is mounted in roller bearings 15 and 16 in the motor housing 1. The displacement is adjusted by means of the adjusting piston 17 via a toothed rack 19, the axis of which extends eccentrically transversely to the central axis 4 and which engages a threaded sleeve 20 coaxial with the central axis 4, which in turn is operatively connected to the motor housing 1 via a helical thread 21. From the axially displacing threaded sleeve 20, the adjusting piston 17 is axially displaced relative to the main engine shaft 14 via a thrust bearing 22, a pressure ring 23 and connecting rods 24.

Die Verstellung der Zahnstange 19 wird mit an sich bekanntem Regelantrieb so optimiert, daß der Motor mit dem für die jeweils erforderliche Leistung geringstmöglichem Hubraum und damit am wirtschaftlichsten arbeitet. Die rückwärtige Stirnseite des Verstellkolbens 17 ist über einen Druckmittelkanal 48 mit einem pneumatischen oder hydraulischen Druckmedium beaufschlagbar, wodurch eine Gegenkraft zu den Kräften der Kolben 3 ausgeübt wird, welche die zur Hubraumänderung aufzuwendenden Verstellkräfte verringert. Der Abtrieb des Motors erfolgt über das Wellenende 25 der Motorhauptwelle 14.The adjustment of the rack 19 is optimized with a known control drive so that the engine works with the smallest possible displacement for the power required and thus works most economically. A pneumatic or hydraulic pressure medium can be applied to the rear end face of the adjusting piston 17 via a pressure medium channel 48, as a result of which a counterforce to the forces of the pistons 3 is exerted, which reduces the adjusting forces to be used to change the displacement. The motor is driven via the shaft end 25 of the main motor shaft 14.

Der Gaswechsel in den Zylindern 2 wird über Auslaßventile 27 und Einlaßventile 26 gesteuert. Auf dem jeweiligen Schaft 28 des Auslaßventils 27 ist über ein Verstellgewinde ein Ventilheber 29 mit einer Kontermutter 30 befestigt. Der Ventilheber 29 hat einen seitlich weisenden Steuerstift 31, der in eine Steuerkurvenscheibe 32 eingreift, und einen (gegenüberliegend) radial abstehenden Kulissenstift 33, der durch eine Kulissenführung 34 den Ventilheber 29 gegen Verdrehung sichert. Auf der Achse 35 der Steuerkurvenscheibe 32, welche ebenfalls parallel zur Mittelachse 4 verläuft, ist eine Zahnriemenscheibe 36 befestigt, die über einen Zahnriemen 37, eine Antriebsscheibe 38, eine parallel zur Motorhauptwelle 14 verlaufende Königswelle 39, ein Antriebsrad 40, ein Zwischenrad 41 und ein Hauptwellenrad 42 von der Motorhauptwelle 14 aus antreibbar ist. Die Steuerkurvenscheibe 32 ist zu den Mitten der Schäfte 28 des Einlaßventils 26 und des Auslaßventils 27 so angeordnet, daß der Winkel zwischen den Verbindungslinien der Steuerkurvenmitte und den Mitten der Schäfte 28 des Einlaßventils 26 und des Auslaßventils 27 etwa 900 beträgt. Mit dieser Anordnung können Einlaßventil 26 und Auslaßventil 27 von der gleichen Steuerkurvenscheibe 32 angetrieben werden. Der Antrieb aller Steuerkurvenscheiben 32 für sämtliche Zylinder 2 erfolgt über den gemeinsamen Zahnriemen 37. Insbesondere das Auslaßventil ist über die Steuerkurvenscheibe 32 gegen die Wirkung einer Schließfeder 43 öffenbar. Von der Schließfeder 43 wird somit das Auslaßventil 27 beim Saughub geschlossen gehalten, obwohl zwischen der Steuerkurvenscheibe 32 und dem Steuerstift 31 des Ventilhebers 29 ein hinreichendes Ventilspiel eingestellt ist.The gas exchange in the cylinders 2 is controlled via exhaust valves 27 and intake valves 26. On the respective shaft 28 of the outlet valve 27, a valve lifter 29 with a lock nut 30 is fastened via an adjustment thread. The valve lifter 29 has a laterally facing control pin 31, which engages in a control cam 32, and a (opposite) radially projecting link pin 33, which secures the valve lifter 29 against rotation by a link guide 34. On the axis 35 of the control cam 32, which also runs parallel to the central axis 4, a toothed belt pulley 36 is fastened, which via a toothed belt 37, a drive pulley 38, a parallel shaft 39 running parallel to the main motor shaft 14, a drive wheel 40, an intermediate wheel 41 and a Main shaft gear 42 can be driven from the main motor shaft 14. The control cam 32 is 27 arranged to the centers of the shafts 28 of the intake valve 26 and the exhaust valve so that the angle between the connecting lines of the cam center and the centers of the shafts is 28 the intake valve 26 and the exhaust valve 27 is about 90 0th With this arrangement, intake valve 26 and exhaust valve 27 can be driven by the same cam 32. All control cams 32 for all cylinders 2 are driven via the common toothed belt 37. In particular, the exhaust valve is controlled Cam 32 openable against the action of a closing spring 43. The exhaust valve 27 is thus kept closed by the closing spring 43 during the suction stroke, although sufficient valve clearance is set between the control cam 32 and the control pin 31 of the valve lifter 29.

Mit Hilfe des erfindungsgemäßen Prinzips ist es nicht nur mög- lich, eine im Aufbau einfache und damit in seiner Herstellung kostengünstige Taumelscheiben-Brennkraftmaschine hoher Betriebsdauer zu schaffen, deren Hubraum veränderlich ist, sondern auch kostengünstig die Produktion von Motoren mit serienverschiedenen fest eingestellten Hubraums wirtschaftlicher zu gestalten. Im letzteren Fall brauchen lediglich die Mittel, die die Schwenkbarkeit der Taumelscheibe gewährleisten, weggelassen und durch unverstellbare, noch kostengünstigere Mittel ersetzt zu werden.With the help of the inventive principle, it is not only possible, I l, a simple in construction and to create therefore inexpensive to manufacture, swash-plate engine high operating time, the displacement is variable, but also cost production economic of engines with different fixed displacement to design. In the latter case, only the means which ensure the swiveling of the swash plate need be omitted and replaced by non-adjustable, even more cost-effective means.

Bezugszeichenliste:Reference symbol list:

  • 1 Motorgehäuse1 motor housing
  • 2 Zylinder2 cylinders
  • 3 Kolben3 pistons
  • 4 Mittelachse4 central axis
  • 5 Zylinderkopf5 cylinder head
  • 6 Pleuelstangen6 connecting rods
  • 7 nicht-umlaufender Teil der Taumelscheibe7 non-rotating part of the swash plate
  • 8 Doppelwellengelenk8 double shaft joint
  • 9 umlaufender Teil der Taumelscheibe9 circumferential part of the swash plate
  • 10 Axialgleitlager10 axial plain bearings
  • 11 Radiallager11 radial bearings
  • 12 Taumelscheibenachse12 swashplate axis
  • 13 Schwenkachse13 swivel axis
  • 14 Motorhauptwelle14 main engine shaft
  • 15 Wälzlager15 rolling bearings
  • 16 Wälzlager16 rolling bearings
  • 17 Verstellkolben17 adjusting pistons
  • 18 Gelenkstange18 articulated rod
  • 19 Zahnstange19 rack
  • 20 Gewindehülse20 threaded sleeve
  • 21 Steilgewinde21 high helix threads
  • 22 Drucklager22 thrust bearings
  • 23 Druckring23 pressure ring
  • 24 Verbindungsstangen24 connecting rods
  • 25 Wellenende25 shaft end
  • 26 Einlaßventil26 inlet valve
  • 27 Auslaßventil27 exhaust valve
  • 28 Schaft28 shaft
  • 29 Ventilheber29 valve lifter
  • 30 Kontermutter30 lock nut
  • 31 Steuerstift31 control pin
  • 32 Steuerkurvenscheibe32 cam disc
  • 33 Kulissenstift33 setting pin
  • 34 Kulissenführung34 Scenic tour
  • 35 Steuerkurvenachse35 cam axis
  • 36 Zahnriemenscheibe36 toothed belt pulley
  • 37 Zahnriemen37 timing belt
  • 38 Antriebsscheibe38 drive pulley
  • 39 Königswelle39 royal wave
  • 40 Antriebsrad40 drive wheel
  • 41 Zwischenrad41 idler gear
  • 42 Hauptwellenrad42 main shaft gear
  • 43 Schließfeder43 closing spring
  • 44 Gelenkzapfen44 pivot pin
  • 45 Kugelgelenk45 ball joint
  • 46 Wellengelenk46 shaft joint
  • 47 Schwungscheibe47 flywheel
  • 48 Druckmittelkanal48 pressure medium channel

Claims (10)

1. Taumelscheiben-Brennkraftmaschine mit veränderbarem Hubraum, deren Taumelscheibe in dem Maschinengehäuse relativ zu der Motorhauptwelle um eine rechtwinklig zur Motorhauptwelle verlaufende Achse schwenkbar ist, dadurch gekennzeichnet, daß der umlaufende Teil (9) der Taumelscheibe um eine mit der Motorhauptwelle (14) fest verbundenen, exzentrisch quer zur Motorhauptwelle (14) liegende Schwenkachse (13) schwenkbar ist.1. swash plate internal combustion engine with variable displacement, the swash plate in the machine housing relative to the engine main shaft is pivotable about an axis extending at right angles to the engine main shaft, characterized in that the rotating part (9) of the swash plate around a fixed to the engine main shaft (14) , Eccentrically transverse to the main engine shaft (14) lying pivot axis (13) is pivotable. 2. Taumelscheiben-Brennkraftmaschine nach Anspruch 1, dadurch gekennzeichnet, daß der nicht-umlaufende Teil (7) der Taumelscheibe über ein Doppelwellengelenk (8) mit dem Maschinengehäuse (1) drehfest verbunden ist.2. Swashplate internal combustion engine according to claim 1, characterized in that the non-rotating part (7) of the swashplate via a double shaft joint (8) with the machine housing (1) is rotatably connected. 3. Taumelscheiben-Brennkraftmaschine nach Anspruch 2, dadurch gekennzeichnet, daß das Doppelwellengelenk (8) mit einem Gelenkzapfen (44) in Richtung der Mittelachse (4) der Motorhauptwelle (14) axial verschieblich an dem Motorgehäuse (1) gelagert ist.3. Swashplate internal combustion engine according to claim 2, characterized in that the double shaft joint (8) with an articulated pin (44) in the direction of the central axis (4) of the main engine shaft (14) is axially displaceably mounted on the motor housing (1). 4. Taumelscheiben-Brennkraftmaschine nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß der umlaufende Teil (9) der Taumelscheibe über eine Gelenkstange (18) mit einem konzentrisch in der Motorhauptwelle (14) gelagerten Verstellkolben (17) verbunden ist.4. Swashplate internal combustion engine according to one of claims 1 to 3, characterized in that the circumferential part (9) of the swashplate is connected via an articulated rod (18) with an adjusting piston (17) mounted concentrically in the main motor shaft (14). 5. Taumelscheiben-Brennkraftmaschine nach Anspruch 4, dadurch gekennzeichnet, daß der Verstellkolben (17) über einen Gewindetrieb (19, 21) in Richtung der Mittelachse (4) der Motorhauptwelle (14) axial verstellbar ist.5. swash plate internal combustion engine according to claim 4, characterized in that the adjusting piston (17) via a screw drive (19, 21) in the direction of the central axis (4) of the main motor shaft (14) is axially adjustable. 6. Taumelscheiben-Brennkraftmaschine nach Anspruch 4 oder 5, dadurch gekennzeichnet, daß der Verstellkolben (17) hydraulisch oder pneumatisch in Richtung der Taumelscheibe druckbeaufschlagbar ist.6. swash plate internal combustion engine according to claim 4 or 5, characterized in that the adjusting piston (17) can be pressurized hydraulically or pneumatically in the direction of the swash plate. 7. Taumelscheiben-Brennkraftmaschine nach einem der Ansprüche 1 bis 6, mit einem Einlaßventil und einem Auslaßventil für jeden Zylinder in den Zylinderkopf, dadurch gekennzeichnet, daß die Ventilschäfte (28) von Einlaß- und Auslaßventil (26, 27) eines Zylinders (2) von einer gemeinsamen Steuerkurvenscheibe (32) axial antreibbar sind.7. Swashplate internal combustion engine according to one of claims 1 to 6, with an intake valve and an exhaust valve for each cylinder in the cylinder head, characterized in that the valve stems (28) of the intake and exhaust valve (26, 27) of a cylinder (2) can be driven axially by a common cam disc (32). 8. Taumelscheiben-Brennkraftmaschine nach Anspruch 7, dadurch gekennzeichnet, daß der Ventilhub von Einlaßventil (26) und Auslaßventil (27) von der Steuerkurvenscheibe (32) zwangsgesteuert ist.8. swash plate internal combustion engine according to claim 7, characterized in that the valve lift of the inlet valve (26) and outlet valve (27) of the control cam (32) is positively controlled. 9. Taumelscheiben-Brennkraftmaschine nach Anspruch 7 oder 8, dadurch gekennzeichnet, daß die Einlaß- und Auslaßventile (26, 27) aller Zylinder (2) gemeinsam von einer von der Motorhauptwelle (14) angetriebenen Königswelle (39) antreibbar sind.9. swash plate internal combustion engine according to claim 7 or 8, characterized in that the inlet and exhaust valves (26, 27) of all cylinders (2) together from one of the engine main shaft (14) driven king shaft (39) can be driven. 10. Taumelscheiben-Brennkraftmaschine nach einem der Ansprüche 7 bis 9, dadurch gekennzeichnet, daß das Auslaßventil (27) und gegebenenfalls Einlaßventil (26) über die Steuerkurvenscheibe (32) gegen die Wirkung einer Schließfeder (43) öffenbar sind.10. Swashplate internal combustion engine according to one of claims 7 to 9, characterized in that the outlet valve (27) and optionally the inlet valve (26) on the control cam (32) against the action of a closing spring (43) can be opened.
EP82111151A 1981-12-04 1982-12-02 Internal combustion wobble plate engine Expired EP0081205B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT82111151T ATE20687T1 (en) 1981-12-04 1982-12-02 SWASH-PLATE INTERNAL ENGINE.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3148027A DE3148027C2 (en) 1981-12-04 1981-12-04 Swashplate internal combustion engine
DE3148027 1981-12-04

Publications (2)

Publication Number Publication Date
EP0081205A1 true EP0081205A1 (en) 1983-06-15
EP0081205B1 EP0081205B1 (en) 1986-07-09

Family

ID=6147887

Family Applications (1)

Application Number Title Priority Date Filing Date
EP82111151A Expired EP0081205B1 (en) 1981-12-04 1982-12-02 Internal combustion wobble plate engine

Country Status (4)

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EP (1) EP0081205B1 (en)
JP (1) JPS58107816A (en)
AT (1) ATE20687T1 (en)
DE (2) DE3148027C2 (en)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0471451A1 (en) * 1990-08-11 1992-02-19 Jaguar Cars Limited Reciprocating piston device
WO2000053927A3 (en) * 1999-03-09 2002-05-02 Carlo Heylen Piston compressor
WO2007070651A1 (en) * 2005-12-14 2007-06-21 Chasin Lawrence C Rotating barrel type internal combustion engine

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19727987C2 (en) * 1997-07-01 1999-05-20 Dieter Dipl Ing Lehmann Two-stroke swashplate internal combustion engine

Citations (4)

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Publication number Priority date Publication date Assignee Title
GB117936A (en) * 1917-08-03 1918-08-06 James Whaley Improvements in Internal Combustion Engines.
DE1576187A1 (en) * 1967-07-26 1970-05-27 Pattas Dr Ing Konstantin Swashplate internal combustion engine
FR2224649A1 (en) * 1973-04-04 1974-10-31 Borg Warner
EP0035867A2 (en) * 1980-03-11 1981-09-16 Joseph Scalzo Wabbler plate engine mechanisms

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Publication number Priority date Publication date Assignee Title
GB308835A (en) * 1928-03-28 1930-06-30 Erich Ubslacker Improvements in power transmission gear for engines
DE2633618A1 (en) * 1976-07-27 1978-02-02 Josef Jobelius Piston engine designed for internal stepless torque variation - using axially movable motion conversion element to vary stroke
JPS53100340A (en) * 1977-02-16 1978-09-01 Caterpillar Tractor Co Universal joint
NL7900076A (en) * 1979-01-05 1980-07-08 Philips Nv DRIVING FOR A MACHINE WITH PISTON AND REVERSE PISTONS WITH VARIABLE STROKE.

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB117936A (en) * 1917-08-03 1918-08-06 James Whaley Improvements in Internal Combustion Engines.
DE1576187A1 (en) * 1967-07-26 1970-05-27 Pattas Dr Ing Konstantin Swashplate internal combustion engine
FR2224649A1 (en) * 1973-04-04 1974-10-31 Borg Warner
EP0035867A2 (en) * 1980-03-11 1981-09-16 Joseph Scalzo Wabbler plate engine mechanisms

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0471451A1 (en) * 1990-08-11 1992-02-19 Jaguar Cars Limited Reciprocating piston device
WO2000053927A3 (en) * 1999-03-09 2002-05-02 Carlo Heylen Piston compressor
WO2007070651A1 (en) * 2005-12-14 2007-06-21 Chasin Lawrence C Rotating barrel type internal combustion engine
US7677210B2 (en) 2005-12-14 2010-03-16 Chasin Lawrence C Rotating barrel type internal combustion engine

Also Published As

Publication number Publication date
DE3148027A1 (en) 1983-06-09
DE3148027C2 (en) 1986-07-24
JPS58107816A (en) 1983-06-27
ATE20687T1 (en) 1986-07-15
DE3271957D1 (en) 1986-08-14
EP0081205B1 (en) 1986-07-09

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