EP0318967A2 - Radial piston engine - Google Patents

Radial piston engine Download PDF

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Publication number
EP0318967A2
EP0318967A2 EP88119996A EP88119996A EP0318967A2 EP 0318967 A2 EP0318967 A2 EP 0318967A2 EP 88119996 A EP88119996 A EP 88119996A EP 88119996 A EP88119996 A EP 88119996A EP 0318967 A2 EP0318967 A2 EP 0318967A2
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EP
European Patent Office
Prior art keywords
guide body
cylinder cover
radial piston
piston engine
engine according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP88119996A
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German (de)
French (fr)
Other versions
EP0318967A3 (en
EP0318967B1 (en
Inventor
Mattias Dr.-Ing. Szewczyk
Hans-Jürgen Pöting
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Paul Pleiger Maschinenfabrik GmbH and Co KG
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Paul Pleiger Maschinenfabrik GmbH and Co KG
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Priority to AT88119996T priority Critical patent/ATE75817T1/en
Publication of EP0318967A2 publication Critical patent/EP0318967A2/en
Publication of EP0318967A3 publication Critical patent/EP0318967A3/en
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Publication of EP0318967B1 publication Critical patent/EP0318967B1/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
    • F01B1/00—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements
    • F01B1/06—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements with cylinders in star or fan arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B1/00—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements
    • F01B1/06—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements with cylinders in star or fan arrangement
    • F01B1/062—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements with cylinders in star or fan arrangement the connection of the pistons with an actuating or actuated element being at the inner ends of the cylinders

Definitions

  • the invention relates to a radial piston motor according to the preamble of claim 1.
  • Radial piston motors of this type are known in various embodiments (e.g. DE-OS 34 30 362), the control of the fluid loading of the individual pistons being accomplished in each case by an elaborately designed device which requires a considerable amount of space and increases the weight and cost of a radial piston motor, the Control has a drive that is independent of the working piston movement, which can result in disturbances in the interaction between the working piston movement and the control movement.
  • the invention has for its object to design a radial piston engine of the type mentioned so that there is a self-control of the working piston with a simple and space-saving design.
  • 1 and 2 denotes an eccentric arranged on the output shaft 1 'of the radial piston motor, on the outer periphery of cup-shaped working pistons 2 rest with the closed side.
  • the working pistons 2 are guided by positive guide rings 3 on the eccentric circumference and they are each arranged in a radially extending, cylindrical extension 4 of the housing of the radial piston motor, these cylindrical extensions 4 being arranged in a star shape around the eccentric 1.
  • annular bearing surface 7 in the form of a radially outwardly convex spherical partial surface against which a complementarily designed bearing surface 8 of a cylinder cover 9 rests, which is attached to the cylindrical extension by means of screws 10 (FIG. 3) 4 of the housing is attached.
  • a rod-shaped control element 15 is slidably guided in a continuous bore 14 extending transversely to the eccentric axis and is connected to the guide body 5 via a ball joint 16.
  • a radially outwardly projecting pin 17 is attached to the guide body 5, which engages with a spherical joint body at its free end in a correspondingly shaped recess in the center of the rod-shaped control element 15.
  • Both sides of the ball joint 16 are rod-shaped at the free ends Control 15 piston-shaped lugs 18, 18 'formed.
  • annular groove 19 or 20 is formed in the cylinder cover 9, one of which is connected to a fluid inlet channel and the other to a return channel, as shown in FIG. 3 by dashed lines.
  • These channels are formed in the cylinder cover 9 and are connected to associated bores in the housing of the radial piston motor.
  • the continuous transverse bore 14 in the cylinder cover 9 is closed at both ends with a plug 21, 21 '.
  • the space between the end faces of the control element 15 and the plug 21, 21 ' is connected via a bore 22, 22' to the interior of the housing.
  • the working piston 2 is pivoted by the rotation of the eccentric 1, for example, into the position shown by dashed lines in FIG. 1, the guide body 5 immersed in the piston 2 being pivoted accordingly.
  • the control element 15 is shifted to the left from the central position shown in FIG. 1 via the ball joint 16, so that the annular groove 20 is released and the annular groove 19 remains closed. Due to the exposed annular groove 20, the pressure fluid can act on the piston 2, for example, via the bore 14, its enlarged central section 23 and the openings 6 in the guide body 5.
  • FIG. 4 explains the pressure relief of the guide body 5 in the embodiment according to FIGS. 1 and 2.
  • the force distribution indicated by arrows at 24 is obtained, with the reduction in the force application on both sides results from the width of the bearing surface 8, at which the compressive force corresponds internally to the maximum pressure present and externally to the value 0 that prevails in the interior of the housing.
  • its bearing surface 7 is designed wider than the bearing surface 8 in the cylinder cover 9.
  • the force distribution shown at 25 results from the pressure fluid acting on the piston 2.
  • d1 the inner diameter of the bearing surface 8 in the cylinder cover and the outer diameter d2 is designated.
  • d3 indicates the diameter of the portion of the guide body 5 engaging in the piston 2.
  • d1 and d2 can be chosen arbitrarily so that the force distribution F1 greater than F2 or F2 greater than F1 can be designed, depending on what is considered appropriate in the individual case.
  • a relief chamber 26 is formed in a manner known per se, which with the Interior of the piston communicates.
  • the output shaft 1 ' is mounted on bearings 27 in the housing of the radial piston motor.
  • Fig. 2 are designated 28, 28 'ring channels in the housing of the radial piston engine, which are connected to the channels 19, 20 in the cylinder cover and the main connections for incoming and outgoing fluid.
  • 2 and 3 show an arrangement of the channels for incoming and outgoing fluid, in which the two channels are accommodated side by side in one of the cylindrical projections 4 of the housing. If channels with a larger cross section are provided, these can then be arranged individually on one of the cylindrical lugs 4.
  • a control slide can also be provided in the cylinder cover 9, which executes a pivoting movement due to the pendulum movement of the guide body 5 and releases and blocks channels running perpendicular to the direction of the pivoting movement.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hydraulic Motors (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
  • Reciprocating Pumps (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • Compressor (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Valve Device For Special Equipments (AREA)
  • Paper (AREA)
  • Pulleys (AREA)
  • Actuator (AREA)

Abstract

In the case of a radial piston engine having a cup-shaped piston, resting on the circumference of an eccentric shaft, in which piston there engages in each case a guide body which is supported in a pendular manner radially outwards on the housing, and with fluid channels in the cylinder cover for the inlet and outlet of the pressure fluid, in order to control the operating pistons automatically with a simple and space-saving construction, a control element (15), which is connected in a hinged manner to the guide body (5), for controlling the inlet and outlet channels (19, 20) is guided in an adjustable manner in the cylinder cover (9) or in a suitable component of the housing. <IMAGE>

Description

Die Erfindung betrifft einen Radialkolbenmotor nach dem Oberbegriff des Anspruchs 1.The invention relates to a radial piston motor according to the preamble of claim 1.

Radialkolbenmotoren dieser Art sind in verschiedenen Aus­führungsformen bekannt (z.B. DE-OS 34 30 362), wobei jeweils die Steuerung der Fluidbeaufschlagung der einzelnen Kolben durch eine aufwendig gestaltete Vorrichtung bewerk­stelligt wird, die einen erheblichen Platzbedarf hat und Gewicht sowie Kosten eines Radialkolbenmotors erhöht, wobei die Steuerung einen von der Arbeitskolbenbewegung unabhängigen Antrieb aufweist, wodurch Störungen im Zusammenspiel von Arbeitskolbenbewegung und Steuerbewegung auftreten können.Radial piston motors of this type are known in various embodiments (e.g. DE-OS 34 30 362), the control of the fluid loading of the individual pistons being accomplished in each case by an elaborately designed device which requires a considerable amount of space and increases the weight and cost of a radial piston motor, the Control has a drive that is independent of the working piston movement, which can result in disturbances in the interaction between the working piston movement and the control movement.

Aus der DE-PS 22 44 920 ist eine Bauweise bekannt, bei der die Steuerung der Fluidbeaufschlagung durch die Bewegung der Arbeitskolben direkt erfolgt. Hierbei ist ein gewisser Platzbedarf in jedem einzelnen Zylinder erforderlich.From DE-PS 22 44 920 a construction is known in which the control of the fluid exposure is carried out directly by the movement of the working piston. A certain amount of space is required in each individual cylinder.

Der Erfindung liegt die Aufgabe zugrunde, einen Radialkolben­motor der eingangs angegebenen Art so auszubilden, daß sich eine Selbststeuerung der Arbeitskolben bei einfachem und platzsparendem Aufbau ergibt.The invention has for its object to design a radial piston engine of the type mentioned so that there is a self-control of the working piston with a simple and space-saving design.

Diese Aufgabe wird durch die Merkmale im Kennzeichen des Anspruchs 1 gelöst. Durch die Anordnung eines Steuerelementes im Zylinderdeckel, das durch die Pendelbewegung des Führungs­körpers des zugeordneten Arbeitskolbens verstellt wird, er­gibt sich eine indirekte Selbststeuerung der Arbeitskolben bei geringem Bauvolumen der Steuerung, verbunden mit geringem Gewicht und günstigen Herstellungskosten.This object is achieved by the features in the characterizing part of claim 1. The arrangement of a control element in the cylinder cover, which is adjusted by the pendulum movement of the guide body of the associated working piston, results in an indirect self-control of the working piston with a small construction volume of the control, combined with low weight and low manufacturing costs.

Vorteilhafte Ausgestaltungen der Erfindung sind in den weiteren Ansprüchen und in der nachfolgenden Beschreibung angegeben.Advantageous embodiments of the invention are specified in the further claims and in the description below.

Eine beispielsweise Ausführungsform der Erfindung wird nach­folgend anhand der Zeichnung näher erläutert. Es zeigen

  • Fig. 1 einen Längsschnitt durch einen Zylinder mit Kolbenanordnung,
  • Fig. 2 einen senkrecht zum Längsschnitt nach Fig.1 verlaufenden Längsschnitt durch den Zylinder,
  • Fig. 3 eine Draufsicht auf den Zylinderdeckel, und
  • Fig. 4 die Kraftverteilung an einem schematisch dargestellten Führungskörper mit Kolben.
An example embodiment of the invention is explained in more detail below with reference to the drawing. Show it
  • 1 shows a longitudinal section through a cylinder with a piston arrangement,
  • 2 shows a longitudinal section through the cylinder perpendicular to the longitudinal section according to FIG. 1,
  • Fig. 3 is a plan view of the cylinder cover, and
  • Fig. 4 shows the force distribution on a schematically illustrated guide body with pistons.

In den Fig. 1 und 2 ist mit 1 ein auf der Abtriebswelle 1′ des Radialkolbenmotors angeordneter Exzenter bezeichnet, auf dessen Außenumfang topfförmig ausgebildete Arbeitskolben 2 mit der geschlossenen Seite anliegen. Die Arbeitskolben 2 sind durch Zwangsführungsringe 3 auf dem Exzenterumfang geführt und sie sind jeweils in einem sich radial erstrecken­den, zylinderförmigen Ansatz 4 des Gehäuses des Radialkolben­motors angeordnet, wobei diese zylinderförmigen Ansätze 4 sternförmig um den Exzenter 1 angeordnet sind. In den Kolben 2 greift ein Führungskörper 5 ein, der in seiner Achsrichtung mit Durchbrechungen 6 für den Durchtritt des unter Druck stehenden Fluids versehen ist, mit dem der Kolben 2 beaufschlagt wird. Am radial außen liegenden Ende ist der Führungskörper 5 mit einer ringförmigen Lagerfläche 7 in der Form einer radial nach außen konvexen Kugelteilfläche versehen, an der eine komplementär gestaltete Lagerfläche 8 eines Zylinderdeckels 9 anliegt, der mittels Schrauben 10 (Fig. 3) auf dem zylinderförmigen Ansatz 4 des Gehäuses befestigt ist. An einer Ringschulter des Führungskörpers 5 liegt ein ringförmig gestaltetes Feder­element 11 mit diametral gegenüberliegenden Ansätzen 12 an, die über Stifte 13 am Gehäuse befestigt sind. Der Führungs­körper 5 wird durch dieses Federelement mit seiner Lagerflä­che 7 an der Lagerfläche 8 des Zylinderdeckels anliegend gehalten.1 and 2, 1 denotes an eccentric arranged on the output shaft 1 'of the radial piston motor, on the outer periphery of cup-shaped working pistons 2 rest with the closed side. The working pistons 2 are guided by positive guide rings 3 on the eccentric circumference and they are each arranged in a radially extending, cylindrical extension 4 of the housing of the radial piston motor, these cylindrical extensions 4 being arranged in a star shape around the eccentric 1. A guide body 5, which is provided in its axial direction with openings 6 for the passage of the pressurized fluid with which the piston 2 is acted upon, engages in the piston 2. At the radially outer end of the guide body 5 is provided with an annular bearing surface 7 in the form of a radially outwardly convex spherical partial surface against which a complementarily designed bearing surface 8 of a cylinder cover 9 rests, which is attached to the cylindrical extension by means of screws 10 (FIG. 3) 4 of the housing is attached. A ring-shaped spring element 11 with diametrically opposite lugs 12, which are fastened to the housing via pins 13, bears against an annular shoulder of the guide body 5. The guide body 5 is held by this spring element with its bearing surface 7 in contact with the bearing surface 8 of the cylinder cover.

In jedem Zylinderdeckel 9 ist in einer durchgehenden, quer zur Exzenterachse verlaufenden Bohrung 14 jeweils ein stangen­förmiges Steuerelement 15 verschiebbar geführt, das über ein Kugelgelenk 16 mit dem Führungskörper 5 verbunden ist. Bei dem dargestellten Ausführungsbeispiel ist am Führungskörper 5 ein radial nach außen vorstehender Stift 17 befestigt, der mit einem kugelförmigen Gelenkkörper an seinem freien Ende in eine entsprechend gestaltete Ausnehmung in der Mitte des stangenförmigen Steuerelementes 15 eingreift. Beiderseits des Kugelgelenks 16 sind an den freien Enden des stangenförmigen Steuerelements 15 kolbenförmige Ansätze 18, 18′ ausgebildet. Im Verschiebebereich dieser kolbenförmigen Ansätze 18, 18′ ist jeweils eine Ringnut 19 bzw. 20 im Zylinderdeckel 9 aus­gebildet, von denen eine mit einem Fluidzulaufkanal und die andere mit einem Rücklaufkanal verbunden ist, wie Fig. 3 durch gestrichelte Linien zeigt. Diese Kanäle sind im Zylinderdeckel 9 ausgebildet und stehen mit zugeordneten Bohrungen im Gehäuse des Radialkolbenmotors in Verbindung. Die durchgehende Quer­bohrung 14 im Zylinderdeckel 9 ist an beiden Enden mit einem Verschlußstopfen 21, 21′ verschlossen. Der Zwischenraum zwi­schen Stirnseiten des Steuerelements 15 und Verschlußstop­fen 21, 21′ ist über eine Bohrung 22, 22′ mit dem Innenraum des Gehäuses verbunden.In each cylinder cover 9, a rod-shaped control element 15 is slidably guided in a continuous bore 14 extending transversely to the eccentric axis and is connected to the guide body 5 via a ball joint 16. In the illustrated embodiment, a radially outwardly projecting pin 17 is attached to the guide body 5, which engages with a spherical joint body at its free end in a correspondingly shaped recess in the center of the rod-shaped control element 15. Both sides of the ball joint 16 are rod-shaped at the free ends Control 15 piston-shaped lugs 18, 18 'formed. In the displacement area of these piston-shaped lugs 18, 18 ', an annular groove 19 or 20 is formed in the cylinder cover 9, one of which is connected to a fluid inlet channel and the other to a return channel, as shown in FIG. 3 by dashed lines. These channels are formed in the cylinder cover 9 and are connected to associated bores in the housing of the radial piston motor. The continuous transverse bore 14 in the cylinder cover 9 is closed at both ends with a plug 21, 21 '. The space between the end faces of the control element 15 and the plug 21, 21 'is connected via a bore 22, 22' to the interior of the housing.

Beim Betrieb des Radialkolbenmotors wird der Arbeitskolben 2 durch die Drehung des Exzenters 1 beispielsweise in die durch gestrichelte Linien in Fig. 1 wiedergegebene Stellung ver­schwenkt, wobei der in den Kolben 2 eintauchende Führungs­körper 5 entsprechend verschwenkt wird. Hierbei wird über das Kugel­gelenk 16 das Steuerelement 15 aus der dargestellten Mittelstellung in Fig. 1 nach links verschoben, so daß die Ringnut 20 freigegeben wird und die Ringnut 19 weiter abgeschlossen bleibt. Durch die freiliegende Ringnut 20 kann das Druckfluid beispielsweise über die Bohrung 14, deren erweiterten Mittelabschnitt 23 und die Durchbrechun­gen 6 im Führungskörper 5 den Kolben 2 beaufschlagen. Bei der folgenden Pendelbewegung des Kolbens 2 in die entgegengesetzte Richtung wird durch die entsprechende Pendelbewegung des Führungskörpers 5 die Ringnut 20 abgesperrt und die Ringnut 19 freigegeben, so daß das Fluid durch die Kolbenbewegung radial nach außen in den Rücklauf abströmen kann. Auf diese Weise wird durch die Bewegung des Arbeitskolbens 2 eine indirekte Selbststeuerung der Fluidbeaufschlagung erzielt.During operation of the radial piston motor, the working piston 2 is pivoted by the rotation of the eccentric 1, for example, into the position shown by dashed lines in FIG. 1, the guide body 5 immersed in the piston 2 being pivoted accordingly. In this case, the control element 15 is shifted to the left from the central position shown in FIG. 1 via the ball joint 16, so that the annular groove 20 is released and the annular groove 19 remains closed. Due to the exposed annular groove 20, the pressure fluid can act on the piston 2, for example, via the bore 14, its enlarged central section 23 and the openings 6 in the guide body 5. In the subsequent pendulum movement of the piston 2 in the opposite direction, the ring groove 20 is blocked by the corresponding pendulum movement of the guide body 5 and the ring groove 19 is released, so that the fluid can flow radially outward into the return flow due to the piston movement. In this way, an indirect self-control of the fluid supply is achieved by the movement of the working piston 2.

Fig. 4 erläutert die Druckentlastung des Führungskörpers 5 bei der Ausgestaltung nach den Fig. 1 und 2. Bei Anliegen des Fluiddrucks auf der radial außen liegenden Stirnseite des Führungskörpers 5 ergibt sich die durch Pfeile bei 24 wiedergegebene Kraftverteilung, wobei sich die beidseitige Verringerung des Kraftangriffs durch die Breite der Lager­fläche 8 ergibt, an der die Druckkraft innen dem maximal anliegenden Druck und außen dem Wert 0 entspricht, der im Inneren des Gehäuses herrscht. Mit Rücksicht auf die Pendel­bewegung des Führungskörpers 5 ist dessen Lagerfläche 7 brei­ter gestaltet als die Lagerfläche 8 im Zylinderdeckel 9. An der radial innen liegenden Stirnseite des Führungskörpers 5 ergibt sich die bei 25 wiedergegebene Kraftverteilung durch das den Kolben 2 beaufschlagende Druckfluid. Mit d₁ ist der Innendurchmesser der Lagerfläche 8 im Zylinderdeckel und mit d₂ deren Außendurchmesser bezeichnet. d₃ gibt den Durchmesser des in den Kolben 2 eingreifenden Abschnitts des Führungs­körpers 5 an.FIG. 4 explains the pressure relief of the guide body 5 in the embodiment according to FIGS. 1 and 2. When the fluid pressure is applied to the radially outer end face of the guide body 5, the force distribution indicated by arrows at 24 is obtained, with the reduction in the force application on both sides results from the width of the bearing surface 8, at which the compressive force corresponds internally to the maximum pressure present and externally to the value 0 that prevails in the interior of the housing. With regard to the oscillating movement of the guide body 5, its bearing surface 7 is designed wider than the bearing surface 8 in the cylinder cover 9. On the radially inner end face of the guide body 5, the force distribution shown at 25 results from the pressure fluid acting on the piston 2. With d₁ the inner diameter of the bearing surface 8 in the cylinder cover and the outer diameter d₂ is designated. d₃ indicates the diameter of the portion of the guide body 5 engaging in the piston 2.

Wird der Außendurchmesser d₃ des Führungskörpers 5 im Verhält­nis zum Außen- und Innendurchmesser der Lagerfläche 8 so aus­gelegt, daß

Figure imgb0001
so ergibt sich eine Kraftvertei­lung F₁=F₂. Dies bedeutet eine hundertprozentige Entlastung des Führungskörpers 5 bei Druckbeaufschlagung des Arbeits­kolbens 2.If the outer diameter d₃ of the guide body 5 in relation to the outer and inner diameter of the bearing surface 8 is designed so that
Figure imgb0001
 so there is a force distribution F₁ = F₂. This means a 100% relief of the guide body 5 when the working piston 2 is pressurized.

d₁ und d₂ können beliebig gewählt werden, so daß die Kraft­verteilung F₁ größer als F₂ oder F₂ größer als F₁ ausgelegt werden kann, je nachdem, was im Einzelfall als zweckmäßig angesehen wird.d₁ and d₂ can be chosen arbitrarily so that the force distribution F₁ greater than F₂ or F₂ greater than F₁ can be designed, depending on what is considered appropriate in the individual case.

Auf der Auflagefläche des Kolbens am Exzenter ist in an sich bekannter Weise eine Entlastungskammer 26 ausgebildet, die mit dem Innenraum des Kolbens in Verbindung steht.On the bearing surface of the piston on the eccentric, a relief chamber 26 is formed in a manner known per se, which with the Interior of the piston communicates.

Die Abtriebswelle 1′ ist über Lager 27 im Gehäuse des Radialkolbenmotors gelagert.The output shaft 1 'is mounted on bearings 27 in the housing of the radial piston motor.

In Fig. 2 sind mit 28, 28′ Ringkanäle im Gehäuse des Radial­kolbenmotors bezeichnet, die mit den Kanälen 19, 20 im Zylinderdeckel und den Hauptanschlüssen für zu- und ablaufendes Fluid verbunden sind. Fig. 2 und 3 zeigen eine Anordnung der Kanäle für zu- und ablaufendes Fluid, bei der die beiden Kanäle nebeneinander in einem der zylinder­förmigen Ansätze 4 des Gehäuses untergebracht sind. Werden Kanäle mit größerem Querschnitt vorgesehen, so können diese dann einzeln an je einem der zylindrischen Ansätze 4 an­geordnet werden.In Fig. 2 are designated 28, 28 'ring channels in the housing of the radial piston engine, which are connected to the channels 19, 20 in the cylinder cover and the main connections for incoming and outgoing fluid. 2 and 3 show an arrangement of the channels for incoming and outgoing fluid, in which the two channels are accommodated side by side in one of the cylindrical projections 4 of the housing. If channels with a larger cross section are provided, these can then be arranged individually on one of the cylindrical lugs 4.

Es sind verschiedene Abwandlungen der beschriebenen Bauweise möglich. So kann auch ein Steuerschieber im Zy­linderdeckel 9 vorgesehen werden, der durch die Pendel­bewegung des Führungskörpers 5 eine Schwenkbewegung ausführt und senkrecht zur Richtung der Schwenkbewegung verlaufende Kanäle freigibt und absperrt.Various modifications of the design described are possible. Thus, a control slide can also be provided in the cylinder cover 9, which executes a pivoting movement due to the pendulum movement of the guide body 5 and releases and blocks channels running perpendicular to the direction of the pivoting movement.

Claims (8)

1. Radialkolbenmotor mit auf dem Umfang einer Exzenterwelle anliegenden, topfförmigen Kolben, in die jeweils ein radial außen am Gehäuse pendelnd gelagerter Führungskörper eingreift, und mit Fluidkanälen im Zylinderdeckel für den Zu- und Ablauf des Druckfluids,
dadurch gekennzeichnet,
daß im Zylinderdeckel (9) oder einem entsprechenden Bauteil des Gehäuses ein mit dem Führungskörper (5) gelenkig ver­bundenes Steuerelement (15) zur Steuerung der Zu- und Ablaufkanäle (19,20) verstellbar geführt ist.1. radial piston motor with cup-shaped pistons resting on the circumference of an eccentric shaft, in each of which engages a guide body which is mounted on the outside in a radial manner on the housing, and with fluid channels in the cylinder cover for the inlet and outlet of the pressure fluid,
characterized,
that in the cylinder cover (9) or a corresponding component of the housing a control element (15) articulated to the guide body (5) for controlling the inlet and outlet channels (19, 20) is adjustably guided. 2. Radialkolbenmotor nach Anspruch 1,
dadurch gekennzeichnet,
daß der Führungskörper (5) mittels einer Kugelteil­fläche (7) pendelnd gelagert und durch ein Kugelgelenk (16) mit dem Steuerelement (15) verbunden ist.2. Radial piston engine according to claim 1,
characterized,
that the guide body (5) is pivotally mounted by means of a spherical partial surface (7) and is connected to the control element (15) by a ball joint (16). 3. Radialkolbenmotor nach den Ansprüchen 1 und 2,
dadurch gekennzeichnet,
daß das Steuerelement (15) stangenförmig ausgebildet und in einer quer zur Exzenterachse verlaufenden Bohrung (14) im Zylinderdeckel (9) längs seiner Achse verschiebbar ist.3. Radial piston engine according to claims 1 and 2,
characterized,
that the control element (15) is rod-shaped and is displaceable along its axis in a bore (14) in the cylinder cover (9) which extends transversely to the eccentric axis. 4. Radialkolbenmotor nach Anspruch 3,
dadurch gekennzeichne,
daß die quer verlaufende Bohrung (14) durchgehend im Zylinderdeckel (9) ausgebildet und an den Enden durch Verschlußstopfen (21,21′) verschlossen ist, wobei die Stirnräume beiderseits des Steuerelements (15) über Bohrungen (22,22′) mit dem Innenraum des Gehäuses verbund­den sind.4. Radial piston engine according to claim 3,
characterized by
that the transverse bore (14) is formed continuously in the cylinder cover (9) and is closed at the ends by sealing plugs (21, 21 '), the end spaces on both sides of the control element (15) via bores (22, 22') with the interior of the housing are connected. 5. Radialkolbenmotor nach Anspruch 3,
dadurch gekennzeichnet,
daß das stangenförmige Steuerelement (15) and den gegen­überliegenden Enden mit kolbenförmigen Ansätzen (18,18′) versehen ist, die im Bereich von Ringnuten (19,20) im Zylinderdeckel (9) verschiebbar sind.5. Radial piston engine according to claim 3,
characterized,
that the rod-shaped control element (15) is provided at the opposite ends with piston-shaped lugs (18, 18 ') which are displaceable in the area of annular grooves (19, 20) in the cylinder cover (9). 6. Radialkolbenmotor nach den vorhergehenden Ansprüchen,
dadurch gekennzeichnet,
daß der Führungskörper (5) mit einer radial nach außen konvexen Lagerfläche (7) versehen und die gegenüberliegen­de Lagerfläche (8) am Zylinderdeckel (9) konkav ausgebil­det ist.6. Radial piston engine according to the preceding claims,
characterized,
that the guide body (5) is provided with a radially outwardly convex bearing surface (7) and the opposite bearing surface (8) on the cylinder cover (9) is concave. 7. Radialkolbenmotor nach den vorhergehenden Ansprüchen,
dadurch gekennzeichnet,
daß der Führungskörper (5) durch ein Federelement (11) an der Lagerfläche (8) anliegend gehalten wird.7. Radial piston engine according to the preceding claims,
characterized,
that the guide body (5) by a spring element (11) is held against the bearing surface (8). 8. Radialkolbenmotor, insbesondere nach den vorhergehenden Ansprüchen,
dadurch gekennzeichnet,
daß der Außendurchmesser des Führungskörpers (5) dem mittleren Durchmesser der Lagerfläche (8) im Zylinder­deckel (9) zur Erzielung einer vollständigen Druckent­lastung entspricht.8. radial piston motor, in particular according to the preceding claims,
characterized,
that the outer diameter of the guide body (5) corresponds to the average diameter of the bearing surface (8) in the cylinder cover (9) in order to achieve complete pressure relief.
EP88119996A 1987-12-02 1988-11-30 Radial piston engine Expired - Lifetime EP0318967B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT88119996T ATE75817T1 (en) 1987-12-02 1988-11-30 RADIAL PISTON ENGINE.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3740891 1987-12-02
DE19873740891 DE3740891A1 (en) 1987-12-02 1987-12-02 RADIAL PISTON ENGINE

Publications (3)

Publication Number Publication Date
EP0318967A2 true EP0318967A2 (en) 1989-06-07
EP0318967A3 EP0318967A3 (en) 1989-12-27
EP0318967B1 EP0318967B1 (en) 1992-05-06

Family

ID=6341756

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88119996A Expired - Lifetime EP0318967B1 (en) 1987-12-02 1988-11-30 Radial piston engine

Country Status (15)

Country Link
US (1) US4926803A (en)
EP (1) EP0318967B1 (en)
JP (1) JPH01187302A (en)
KR (1) KR940001949B1 (en)
CN (1) CN1013507B (en)
AT (1) ATE75817T1 (en)
CA (1) CA1326213C (en)
DD (1) DD283668A5 (en)
DE (2) DE3740891A1 (en)
DK (1) DK673388A (en)
ES (1) ES2031218T3 (en)
FI (1) FI885508A (en)
RU (1) RU1833479C (en)
SE (1) SE500844C2 (en)
UA (1) UA13451A1 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2004057156A1 (en) * 2002-12-20 2004-07-08 Pleiger Maschinenbau Gmbh & Co. Kg Radial-piston motor
DE102004060198B3 (en) * 2004-12-14 2006-03-30 Pleiger Maschinenbau Gmbh & Co. Kg Control device for operation of radial piston motor has second sensor to detect of rotation of shaft, both sensors being connected to calculating unit

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012063119A2 (en) * 2010-11-10 2012-05-18 R. & D. S.R.L. Radial cylinder hydraulic machine with improved oscillating radial cylinder

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE953850C (en) * 1954-11-18 1956-12-06 Eduard Woydt Dr Ing Fluid pump or motor
FR1540999A (en) * 1967-07-24 1968-10-04 Rotary piston machine or the like operating as a compressed fluid motor or the like and its various applications
FR1587399A (en) * 1967-09-29 1970-03-20 Riva Calzoni Spa HYDRAULIC MOTOR WITH RADIAL PROPELLERS
FR2296778A1 (en) * 1975-01-03 1976-07-30 Rexroth Sigma Radial-piston pump or motor - has cylinder heads of more than hemisphere section with centres held in fixed positions
GB2163222A (en) * 1984-08-17 1986-02-19 Pleiger Maschinenfabrik Gmbh & Radial piston engine

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Publication number Priority date Publication date Assignee Title
US1835138A (en) * 1928-12-17 1931-12-08 Lee M Bowman Internal-combustion engine
DE2157735A1 (en) * 1971-11-22 1973-05-24 Mathias Prof Dipl Ing Ott DISPLACEMENT PISTON MACHINE, IN PARTICULAR HYDROSTATIC OIL MOTOR OR PUMP WITH SWIVELING BUSHINGS
DE2244920B2 (en) * 1972-09-13 1974-07-11 Paul Pleiger Maschinenfabrik, 5812 Herbede Radial piston engine
DE2333103A1 (en) * 1973-06-29 1975-01-16 Rexroth Gmbh G L RADIAL PISTON MACHINE
DE3441966A1 (en) * 1984-11-16 1986-05-28 G. Düsterloh GmbH, 4322 Sprockhövel CONTROL FOR A HYDROSTATIC PISTON ENGINE
GB2185075B (en) * 1986-01-07 1989-10-25 John Douglas Woodward Fluid pump/motor
US4727794A (en) * 1987-01-20 1988-03-01 Kmicikiewicz Marek A Radial engine

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE953850C (en) * 1954-11-18 1956-12-06 Eduard Woydt Dr Ing Fluid pump or motor
FR1540999A (en) * 1967-07-24 1968-10-04 Rotary piston machine or the like operating as a compressed fluid motor or the like and its various applications
FR1587399A (en) * 1967-09-29 1970-03-20 Riva Calzoni Spa HYDRAULIC MOTOR WITH RADIAL PROPELLERS
FR2296778A1 (en) * 1975-01-03 1976-07-30 Rexroth Sigma Radial-piston pump or motor - has cylinder heads of more than hemisphere section with centres held in fixed positions
GB2163222A (en) * 1984-08-17 1986-02-19 Pleiger Maschinenfabrik Gmbh & Radial piston engine

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2004057156A1 (en) * 2002-12-20 2004-07-08 Pleiger Maschinenbau Gmbh & Co. Kg Radial-piston motor
CN100436754C (en) * 2002-12-20 2008-11-26 普莱格机械两合公司 Radial-piston motor
DE102004060198B3 (en) * 2004-12-14 2006-03-30 Pleiger Maschinenbau Gmbh & Co. Kg Control device for operation of radial piston motor has second sensor to detect of rotation of shaft, both sensors being connected to calculating unit

Also Published As

Publication number Publication date
ATE75817T1 (en) 1992-05-15
ES2031218T3 (en) 1992-12-01
DE3740891C2 (en) 1992-01-09
EP0318967A3 (en) 1989-12-27
US4926803A (en) 1990-05-22
DE3740891A1 (en) 1989-06-22
FI885508A0 (en) 1988-11-28
EP0318967B1 (en) 1992-05-06
UA13451A1 (en) 1997-02-28
SE8803957L (en) 1989-06-03
DD283668A5 (en) 1990-10-17
CN1034604A (en) 1989-08-09
DE3870819D1 (en) 1992-06-11
DK673388A (en) 1989-06-03
RU1833479C (en) 1993-08-07
SE8803957D0 (en) 1988-10-31
KR940001949B1 (en) 1994-03-12
FI885508A (en) 1989-06-03
JPH01187302A (en) 1989-07-26
DK673388D0 (en) 1988-12-02
CN1013507B (en) 1991-08-14
KR890010392A (en) 1989-08-08
SE500844C2 (en) 1994-09-19
CA1326213C (en) 1994-01-18

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