EP1601859A1 - Radial-piston motor - Google Patents

Radial-piston motor

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Publication number
EP1601859A1
EP1601859A1 EP03785895A EP03785895A EP1601859A1 EP 1601859 A1 EP1601859 A1 EP 1601859A1 EP 03785895 A EP03785895 A EP 03785895A EP 03785895 A EP03785895 A EP 03785895A EP 1601859 A1 EP1601859 A1 EP 1601859A1
Authority
EP
European Patent Office
Prior art keywords
piston
housing
fluid
control element
cavity
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
EP03785895A
Other languages
German (de)
French (fr)
Other versions
EP1601859B1 (en
Inventor
Alfred Dieter Marian
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.)
Pleiger Maschinenbau & Co KG GmbH
Original Assignee
Pleiger Maschinenbau & Co KG GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Pleiger Maschinenbau & Co KG GmbH filed Critical Pleiger Maschinenbau & Co KG GmbH
Publication of EP1601859A1 publication Critical patent/EP1601859A1/en
Application granted granted Critical
Publication of EP1601859B1 publication Critical patent/EP1601859B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
    • F02B75/18—Multi-cylinder engines
    • F02B75/22—Multi-cylinder engines with cylinders in V, fan, or star arrangement
    • F02B75/222—Multi-cylinder engines with cylinders in V, fan, or star arrangement with cylinders in star arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F01B15/00—Reciprocating-piston machines or engines with movable cylinders other than provided for in group F01B13/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
    • F01B9/04—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft
    • F01B9/06—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft the piston motion being transmitted by curved surfaces
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/0403—Details, component parts specially adapted of such engines
    • F03C1/0435—Particularities relating to the distribution members

Definitions

  • the invention relates to a radial piston motor according to the preamble of claim 1.
  • a radial piston motor of this type is known from EP 318 967, the control element controlling the piston application being rod-shaped and being arranged so as to be displaceable along its axis in a bore running transversely to the eccentric axis in the cylinder cover.
  • the guide body engaging the piston displaces the rod-shaped control element in such a way that either the pressure line or the return line is released.
  • the pressure line and the return line lead from the cylinders of the radial piston motor to a tank for the pressure fluid.
  • a line leads from the housing to the tank, which removes the lecl fluid from the housing of the radial piston motor, which is collected in the housing.
  • the invention has for its object to design a radial piston engine of the type specified so that its efficiency is improved.
  • the large volume of leakage fluid in the housing dampens the fluid column ejected from the cylinder, so that no decompression shocks occur, as is the case with the known design.
  • the leakage fluid chamber of the housing has a damping effect on the pulsating fluid flow, which results in a low-vibration and thus low-noise operation of the radial piston motor is achieved. This eliminates the usual decompression noises.
  • FIG. 1 shows a section through a cylinder with a piston arrangement
  • FIG. 2 shows a partial view of an embodiment according to the invention.
  • 1 shows a radial piston engine according to the prior art in a partial section through a cylinder.
  • 1 designates an eccentric arranged on the output shaft W of the radial piston motor, on the outer circumference of which cup-shaped working pistons 2 rest with the closed side.
  • the working pistons 2 are each arranged in a radially extending, cylindrical projection 4 of the housing 4 'of the radial piston engine, these cylindrical projections 4 being arranged in a star shape around the eccentric 1.
  • a guide body 5 engages in the piston 2, the alignment of which is provided with openings 6 for the passage of the pressurized fluid with which the piston 2 is acted upon.
  • 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 bears.
  • annular bearing surface 7 On an annular shoulder of the guide body 5 is an annular spring element with diametrically opposite lugs, which are attached to the housing via pins, not shown. 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.
  • a relief chamber on the bearing surface of the piston is designated, which is connected to the interior of the piston 2.
  • 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 and 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.
  • this piston-shaped Lugs 18, 18 'each have an annular groove 19 or 20 formed in the cylinder cover 9, of which the annular groove 19 is connected to a schematically indicated pressure line D through which pressurized fluid is supplied to the cylinder or working piston 2.
  • the annular groove 20 is connected to a return line R, which leads from the housing or from the annular groove 20 to the tank for the pressurized fluid, in order for the fluid expelled from the piston chamber into the tank after the working stroke of the piston 2 and a corresponding adjustment movement of the control element 15 recirculate.
  • a return line R which leads from the housing or from the annular groove 20 to the tank for the pressurized fluid, in order for the fluid expelled from the piston chamber into the tank after the working stroke of the piston 2 and a corresponding adjustment movement of the control element 15 recirculate.
  • the continuous transverse bore 14 in the cylinder cover 9 for the control element is closed at both ends with a plug 21, 21 '.
  • the intermediate space between the end faces of the control element 15 and sealing plugs 21, 21 ' is connected to the interior of the housing via a bore 22 or 22' in order to guide the leakage fluid emerging at the control element into the space outside the piston 2 into the housing.
  • a leakage line, not shown, returns the leakage fluid caught in the housing of the radial piston motor back into the fluid tank.
  • FIG. 2 shows an embodiment according to the invention in which the annular groove 20 is connected to the large-volume cavity 27 of the housing 4, 4 'via a short bore 30 of large cross section, a return line R between the annular groove 20 and the fluid tank not being present, so that the fluid expelled from the piston chamber after the working stroke is conducted directly into the cavity 27 of the housing, from which the fluid is conducted back into the fluid tank almost without pressure via a return line R, which is indicated schematically in FIG.
  • the short bore 30 of large cross-section represents a substantially lower resistance when the fluid is ejected from the cylinder for the piston 2 than the return line R in the known design, which has a certain length and is inevitably provided with deflections, as a result of which the flow resistance of the fluid in the return line R is increased.
  • both the pressure line D and the return line R are closed by the control element 15, so that in the hollow piston 2 a Fluid column is clamped under pressure.
  • the rotary movement of the eccentric 1 into the position shown by dashed lines in FIG. 1 causes the piston 2 with the guide body 5 to be pivoted to the left, as shown in FIG. 1 by dashed lines, the control element 15 being shifted to the left and the passage 14 to the annular groove 20 is released.
  • a decompression blow occurs in that the pressurized fluid column in the working piston 2 is connected to the return line R, which opposes the fluid flow to a resistance. This also results in a corresponding noise development and an undesirable heat development when the fluid is expelled through the piston into the return line R. This affects the efficiency of the radial piston motor.
  • the fluid column clamped in the working piston 2 is connected to the large-volume cavity 27 of the housing during the displacement movement of the control element 15 to the left via the short bore 30 with a large cross-section, so that none of the piston 2 during the ejection movement significant resistance must be overcome.
  • the large volume of the cavity 27 in the housing compared to the volume of the hollow piston 2 has a damping effect on the relaxation of the pressure column in the piston, so that noise is avoided because no decompression shock occurs.
  • the heat generated is considerably reduced by the minimal resistance when flowing through the bore 30.
  • the design according to FIG. 2 results in a significant improvement in efficiency compared to the known design according to FIG. 1.
  • the discharge of the fluid ejected from the piston space into a large-volume cavity or into the leakage space of the housing can also be provided in another design of the radial piston motor, in which the control element is designed in a different way. It is essential here that after the working stroke of the piston, the fluid is conducted from the piston chamber over a large cross-section with only minimal flow resistance into a large-volume cavity.
  • a plurality of bores can also be provided which have a large overall cross section and connect the pressurizing surface of the piston to the cavity 27, from which the return line guides the fluid back to the fluid tank almost without pressure.
  • the large-volume cavity into which the piston ejects the fluid after the working stroke can also be designed and arranged in a different way than indicated in FIG. 1.
  • the control element 15 provided between the pressurizing surface of the piston and the cavity 27 is also preferably designed such that when the connection between the pressurizing surface of the piston and the cavity 27 is released, there is no great resistance to the fluid flow.
  • the cross section of the bore 30 or a plurality of bores is designed such that the diameter of the flow cross section is greater than the bore length in order to keep the flow resistance as low as possible.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Abstract

The invention relates to a radial-piston motor comprising pistons (2) that lie on the periphery of an eccentric (1). A respective guide body (5), which is mounted radially towards the exterior of the housing (4, 9) in order to oscillate, engages with said pistons. The invention is characterised in that the cylinder cover (9) or a corresponding component of the housing contains a control element (15) for controlling the supply and drain conduits (19, 20) and that the drain conduit (20) is connected to the cavity (27) of the housing (4, 4'), enabling the fluid that is discharged from the piston (2) after the working stroke of the latter to be drained via the cavity (27) of the housing.

Description

Radialkolb enmotor Radial piston motor
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.
Ein Radialkolbenmotor dieser Art ist aus EP 318 967 bekannt, wobei das die Kolbenbeaufschlagung steuernde Steuerelement stangenförmig ausgebildet und in einer quer zur Exzenterachse verlaufenden Bohrung im Zylinderdeckel längs seiner Achse verschiebbar angeordnet ist. Der mit dem Kolben in Eingriff stehende Führungskörper verschiebt das stangenförmige Steuerelement derart, dass entweder die Druckleitung oder die Rücklaufleitung frei gegeben wird. Von den Zylindern des Radialkolbenmotors führt die Druckleitung und die Rücklaufleitung zu einem Tank für das Druckfluid. Zugleich führt vom Gehäuse eine Leitung zum Tank, die aus dem Gehäuse des Radialkolbenmotors das Lecl fluid abführt, das im Gehäuse gesammelt wird.A radial piston motor of this type is known from EP 318 967, the control element controlling the piston application being rod-shaped and being arranged so as to be displaceable along its axis in a bore running transversely to the eccentric axis in the cylinder cover. The guide body engaging the piston displaces the rod-shaped control element in such a way that either the pressure line or the return line is released. The pressure line and the return line lead from the cylinders of the radial piston motor to a tank for the pressure fluid. At the same time, a line leads from the housing to the tank, which removes the lecl fluid from the housing of the radial piston motor, which is collected in the housing.
Der Erfindung liegt die Aufgabe zugrunde, einen Radialkolbenmotor der eingangs angegebenen Art so auszubilden, dass dessen Wirkungsgrad verbessert wird.The invention has for its object to design a radial piston engine of the type specified so that its efficiency is improved.
Dies wird erfϊndungsgemäß durch die Merkmale im kennzeichnenden Teil des Anspruchs 1 erreicht. Dadurch, dass nach Beendigung der Druckbeaufschlagung des Kolbens eine Verbindung mit einem Hohlraum großen Volumens bzw. mit dem Leckfluidraum im Gehäuse freigegeben wird, wird das durch den Kolben aus dem Zylinder ausgestoßene Fluid unmittelbar in den Leckfluidraum des Gehäuses geleitet, der ein sehr großes Volumen im Verhältnis zu der Fluidsäule im Zylinder hat. Damit muss der Kolben beim Ausstoßen des Fluids aus dem Zylinder nicht mehr den Leitungswiderstand der Rücklaufleitung überwinden, wodurch sich eine Verbesserung des Wirkungsgrads des Radialkolbenmotors ergibt. Diese Verbesserung des Wirkungsgrads ist verbunden mit einer Verminderung der Geräusch- und Wärmeentwicklung. Der großvolumige Leckfluidraum im Gehäuse ergibt eine Dämpfung der aus dem Zylinder ausgestoßenen Fluidsäule, so dass auch keine Dekompressionsschläge mehr auftreten, wie dies bei der bekannten Bauform der Fall ist. Der Leckfluidraum des Gehäuses wirkt dämpfend auf den pulsierend abfließenden Fluidstrom, wodurch eine schwingungsarme und somit geräuscharme Arbeitsweise des Radialkolbenmotors erzielt wird. Üblicherweise auftretende Dekompressionsgeräusche entfallen damit.This is achieved according to the invention by the features in the characterizing part of claim 1. Characterized in that a connection with a cavity of large volume or with the leakage fluid space in the housing is released after the end of the pressurization of the piston, the fluid ejected by the piston from the cylinder is directed directly into the leakage fluid space of the housing, which has a very large volume in the Relation to the fluid column in the cylinder. This means that the piston no longer has to overcome the line resistance of the return line when the fluid is ejected from the cylinder, which results in an improvement in the efficiency of the radial piston motor. This improvement in efficiency is associated with a reduction in noise and heat. The large volume of leakage fluid in the housing dampens the fluid column ejected from the cylinder, so that no decompression shocks occur, as is the case with the known design. The leakage fluid chamber of the housing has a damping effect on the pulsating fluid flow, which results in a low-vibration and thus low-noise operation of the radial piston motor is achieved. This eliminates the usual decompression noises.
Die Erfindung wird beispielsweise anhand der Zeichnung näher erläutert. Es zeigenThe invention is explained in more detail for example with reference to the drawing. Show it
Fig. 1 einen Schnitt durch einen Zylinder mit Kolbenanordnung und Fig. 2 eine Teilansicht einer erfϊndungsgemäßen Ausgestaltung.1 shows a section through a cylinder with a piston arrangement, and FIG. 2 shows a partial view of an embodiment according to the invention.
Fig. 1 zeigt in einem Teilschnitt durch einen Zylinder einen Radialkolbenmotor nach dem Stand der Technik. Mit 1 ist ein auf der Abtriebswelle W des Radialkolbenmotors angeordneter Exzenter bezeichnet, auf dessen Außenumfang topfförmig ausgebildete Arbeitskolben 2 mit der geschlossenen Seite anliegen. Die Arbeitskolben 2 sind jeweils in einem sich radial erstreckenden, zylinderfb'rmigen Ansatz 4 des Gehäuses 4' 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 Ausrichtung 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. An einer Ringschulter des Führungskörpers 5 liegt ein ringförmig gestaltetes Federelement mit diametral gegenüberliegenden Ansätzen an, die über nicht dargestellte Stifte am Gehäuse befestigt sind. Der Führungskörper 5 wird durch dieses Federelement mit seiner Lagerfläche 7 an der Lagerfläche 8 des Zylinderdeckels anliegend gehalten. Mit 26 ist eine Entlastungskammer an der Auflagefläche des Kolbens bezeichnet, die mit dem Innenraum des Kolbens 2 in Verbindung steht.1 shows a radial piston engine according to the prior art in a partial section through a cylinder. 1 designates an eccentric arranged on the output shaft W of the radial piston motor, on the outer circumference of which cup-shaped working pistons 2 rest with the closed side. The working pistons 2 are each arranged in a radially extending, cylindrical projection 4 of the housing 4 'of the radial piston engine, these cylindrical projections 4 being arranged in a star shape around the eccentric 1. A guide body 5 engages in the piston 2, the alignment of which is provided with openings 6 for the passage of the pressurized fluid with which the piston 2 is acted upon. At the radially outer end, 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 bears. On an annular shoulder of the guide body 5 is an annular spring element with diametrically opposite lugs, which are attached to the housing via pins, not shown. 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. With 26 a relief chamber on the bearing surface of the piston is designated, which is connected to the interior of the piston 2.
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 Ausfuhrungsbeispiel 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 stangenformigen Steuerelementes 15 eingreift. Beiderseits des Kugelgelenks 16 sind an den freien Enden des stangenformigen Steuerelements 15 kolbenförmige Ansätze 18 und 18' ausgebildet. Im Verschiebebereich dieser kolbenförmigen Ansätze 18, 18' ist jeweils eine Ringnut 19 bzw. 20 im Zylinderdeckel 9 ausgebildet, von denen die Ringnut 19 mit einer schematisch angedeuteten Druckleitung D verbunden ist, durch die dem Zylinder bzw. Arbeitskolben 2 unter Druck stehendes Fluid zugeführt wird.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 exemplary embodiment shown, a radially outwardly projecting pin 17 is attached to the guide body 5 and 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. Piston-shaped lugs 18 and 18 'are formed on both sides of the ball joint 16 at the free ends of the rod-shaped control element 15. In the displacement area of this piston-shaped Lugs 18, 18 'each have an annular groove 19 or 20 formed in the cylinder cover 9, of which the annular groove 19 is connected to a schematically indicated pressure line D through which pressurized fluid is supplied to the cylinder or working piston 2.
Die Ringnut 20 ist mit einer Rücklaufleitung R verbunden, die vom Gehäuse bzw. von der Ringnut 20 aus zum Tank für das Druckfluid führt, um nach dem Arbeitshub des Kolbens 2 und einer entsprechenden Verstellbewegung des Steuerelementes 15 das aus dem Kolbenraum ausgestoßene Fluid in den Tank zurückzuleiten. Hierdurch muss von dem Kolben 2 bei der Ausstoßbewegung der Widerstand dieser Rücklaufleitung R überwunden werden.The annular groove 20 is connected to a return line R, which leads from the housing or from the annular groove 20 to the tank for the pressurized fluid, in order for the fluid expelled from the piston chamber into the tank after the working stroke of the piston 2 and a corresponding adjustment movement of the control element 15 recirculate. As a result, the resistance of this return line R must be overcome by the piston 2 during the ejection movement.
Die durchgehende Querbohrung 14 im Zylinderdeckel 9 für das Steuerelement ist an beiden Enden mit einem Verschlussstopfen 21, 21 ' verschlossen. Der Zwischenraum zwischen Stirnseiten des Steuerelementes 15 und Verschlussstopfen 21, 21' ist über eine Bohrung 22 bzw. 22' mit dem Innenraum des Gehäuses verbunden, um das am Steuerelement austretende Leck- fluid in den Raum außerhalb der Kolben 2 in das Gehäuse zu leiten. Eine nicht dargestellte Leckleitung leitet das im Gehäuse des Radialkolbenmotors aufgefangene Leckfluid in den Fluidtank zurück.The continuous transverse bore 14 in the cylinder cover 9 for the control element is closed at both ends with a plug 21, 21 '. The intermediate space between the end faces of the control element 15 and sealing plugs 21, 21 'is connected to the interior of the housing via a bore 22 or 22' in order to guide the leakage fluid emerging at the control element into the space outside the piston 2 into the housing. A leakage line, not shown, returns the leakage fluid caught in the housing of the radial piston motor back into the fluid tank.
Fig. 2 zeigt eine erfindungsgemäße Ausgestaltung, bei der die Ringnut 20 über eine kurze Bohrung 30 von großem Querschnitt mit dem großvolumigen Hohlraum 27 des Gehäuses 4, 4' verbunden ist, wobei eine Rücklaufleitung R zwischen Ringnut 20 und Fluidtank nicht vorhanden ist, so dass das nach dem Arbeitshub aus dem Kolbenraum ausgestoßene Fluid unmittelbar in den Hohlraum 27 des Gehäuses geleitet wird, von dem aus das Fluid über eine in Fig.2 schematisch angedeutete Rücklaufleitung R nahezu drucklos zurück in den Fluidtank geleitet wird.2 shows an embodiment according to the invention in which the annular groove 20 is connected to the large-volume cavity 27 of the housing 4, 4 'via a short bore 30 of large cross section, a return line R between the annular groove 20 and the fluid tank not being present, so that the fluid expelled from the piston chamber after the working stroke is conducted directly into the cavity 27 of the housing, from which the fluid is conducted back into the fluid tank almost without pressure via a return line R, which is indicated schematically in FIG.
Die kurze Bohrung 30 von großem Querschnitt stellt beim Ausstoßen des Fluids aus dem Zylinder für den Kolben 2 einen wesentlich geringeren Widerstand dar als die Rücklaufleitung R bei der bekannten Bauform, die eine gewisse Länge hat und zwangsläufig mit Umlenkungen versehen ist, wodurch der Strömungswiderstand des Fluids in der Rücklaufleitung R erhöht wird.The short bore 30 of large cross-section represents a substantially lower resistance when the fluid is ejected from the cylinder for the piston 2 than the return line R in the known design, which has a certain length and is inevitably provided with deflections, as a result of which the flow resistance of the fluid in the return line R is increased.
In der Betriebsstellung des Kolbens in Fig. 1 ist sowohl die Druckleitung D wie auch die Rücklaufleitung R durch das Steuerelement 15 geschlossen, so dass in dem Hohlkolben 2 eine Fluidsäule unter Druck eingespannt ist. Durch die Drehbewegung des Exzenters 1 in die durch gestrichelte Linien in Fig. 1 wiedergegebene Stellung wird der Kolben 2 mit dem Führungskörper 5 nach links verschwenkt, wie dies Fig. 1 durch gestrichelte Linien zeigt, wobei das Steuerelement 15 nach links verschoben und der Durchlass 14 zu der Ringnut 20 freigegeben wird.In the operating position of the piston in FIG. 1, both the pressure line D and the return line R are closed by the control element 15, so that in the hollow piston 2 a Fluid column is clamped under pressure. The rotary movement of the eccentric 1 into the position shown by dashed lines in FIG. 1 causes the piston 2 with the guide body 5 to be pivoted to the left, as shown in FIG. 1 by dashed lines, the control element 15 being shifted to the left and the passage 14 to the annular groove 20 is released.
Bei der bekannten Bauform nach Fig. 1 tritt hierbei ein Dekompressionsschlag dadurch auf, dass die unter Druck stehende Fluidsäule im Arbeitskolben 2 mit der Rücklaufleitung R verbunden wird, die dem Fluidstrom einen Widerstand entgegensetzt. Hierdurch ergibt sich auch eine entsprechende Geräuschentwicklung und beim Ausstoß des Fluids durch den Kolben in die Rücklaufleitung R eine unerwünschte Wärmeentwicklung. Dadurch wird der Wirkungsgrad des Radialkolbenmotors beeinträchtigt.In the known design according to FIG. 1, a decompression blow occurs in that the pressurized fluid column in the working piston 2 is connected to the return line R, which opposes the fluid flow to a resistance. This also results in a corresponding noise development and an undesirable heat development when the fluid is expelled through the piston into the return line R. This affects the efficiency of the radial piston motor.
Bei der erfmdungsgemäßen Bauweise nach Fig. 2 wird dagegen die im Arbeitskolben 2 eingespannte Fluidsäule bei der Verschiebebewegung des Steuerelementes 15 nach links über die kurze Bohrung 30 mit großem Querschnitt mit dem großvolumigen Hohlraum 27 des Gehäuses verbunden, so dass vom Kolben 2 bei der Ausstoßbewegung kein nennenswerter Widerstand überwunden werden muss. Das gegenüber dem Volumen des Hohlkolbens 2 große Volumen des Hohlraums 27 im Gehäuse wirkt auf die Entspannung der Drucksäule im Kolben dämpfend, so dass eine Geräuschentwicklung vermieden wird, weil kein Dekompressionsschlag auftritt. Hinzu kommt, dass durch den minimalen Widerstand beim Durchströmen der Bohrung 30 die Wärmeentwicklung erheblich reduziert wird. Insgesamt ergibt sich durch die Bauform nach Fig. 2 eine nennenswerte Verbesserung des Wirkungsgrads gegenüber der bekannten Bauform nach Fig. 1.In the construction according to the invention according to FIG. 2, on the other hand, the fluid column clamped in the working piston 2 is connected to the large-volume cavity 27 of the housing during the displacement movement of the control element 15 to the left via the short bore 30 with a large cross-section, so that none of the piston 2 during the ejection movement significant resistance must be overcome. The large volume of the cavity 27 in the housing compared to the volume of the hollow piston 2 has a damping effect on the relaxation of the pressure column in the piston, so that noise is avoided because no decompression shock occurs. In addition, the heat generated is considerably reduced by the minimal resistance when flowing through the bore 30. Overall, the design according to FIG. 2 results in a significant improvement in efficiency compared to the known design according to FIG. 1.
Bei der folgenden Pendelbewegung des Kolbens 2 in die entgegengesetzte Richtung wird durch die entsprechende Pendelbewegung des Führungskörpers 5 die Ringnut 20 vom Steuerelement 15 abgesperrt und die Ringnut 19 frei gegeben, wie dies Fig. 2 zeigt. Das unter Druck stehende Fluid strömt durch die Ringnut 19 und die Durchbrechungen 6 im Führungskörper 5 in den Kolben 2 und beaufschlagt diesen zum Weiterdrehen des Exzenters 1.In the subsequent pendulum movement of the piston 2 in the opposite direction, the ring groove 20 is blocked by the control element 15 by the corresponding pendulum movement of the guide body 5 and the ring groove 19 is released, as shown in FIG. 2. The pressurized fluid flows through the annular groove 19 and the openings 6 in the guide body 5 into the piston 2 and acts on the latter to further rotate the eccentric 1.
Das Abführen des aus dem Kolbenraum ausgestoßenen Fluids in einen großvolumigen Hohlraum bzw. in den Leckraum des Gehäuses kann auch bei einer anderen Bauform des Radialkolbenmotors vorgesehen sein, bei der das Steuerelement in anderer Weise ausgebildet ist. Wesentlich ist hierbei, dass nach dem Arbeitshub des Kolbens das Fluid aus dem Kolbenraum über einen großen Querschnitt mit nur minimalem Strömungswiderstand in einen großvolumigen Hohlraum geleitet wird.The discharge of the fluid ejected from the piston space into a large-volume cavity or into the leakage space of the housing can also be provided in another design of the radial piston motor, in which the control element is designed in a different way. It is essential here that after the working stroke of the piston, the fluid is conducted from the piston chamber over a large cross-section with only minimal flow resistance into a large-volume cavity.
Es sind verschiedene Abwandlungen der beschriebenen Bauweise möglich. So können anstelle einer einzelnen Bohrung 30 großen Querschnitts auch mehrere Bohrungen vorgesehen sein, die einen großen Gesamtquerschnitt aufweisen und die Druckbeaufschlagungsfläche des Kolbens mit dem Hohlraum 27 verbinden, von dem aus die Rücklaufleitung das Fluid nahezu drucklos zum Fluidtank zurückleitet. Auch kann der Hohlraum großen Volumens, in den der Kolben nach dem Arbeitshub das Fluid ausstößt, in anderer Weise ausgebildet und angeordnet sein als in Fig. 1 angegeben. Auch das zwischen Druckbeaufschlagungsfläche des Kolbens und Hohlraum 27 vorgesehene Steuerelement 15 wird vorzugsweise so gestaltet, dass es bei Freigabe der Verbindung zwischen Druckbeaufschlagungsfläche des Kolbens und Hohlraum 27 der Fluidströmung keinen großen Widerstand entgegensetzt.Various modifications of the design described are possible. Thus, instead of a single bore 30 of large cross section, a plurality of bores can also be provided which have a large overall cross section and connect the pressurizing surface of the piston to the cavity 27, from which the return line guides the fluid back to the fluid tank almost without pressure. The large-volume cavity into which the piston ejects the fluid after the working stroke can also be designed and arranged in a different way than indicated in FIG. 1. The control element 15 provided between the pressurizing surface of the piston and the cavity 27 is also preferably designed such that when the connection between the pressurizing surface of the piston and the cavity 27 is released, there is no great resistance to the fluid flow.
Der Querschnitt der Bohrung 30 bzw. mehrerer Bohrungen wird so ausgelegt, dass der Durchmesser des Strömungsquerschnitts größer ist als die Bohrungslänge, um den Strömungswiderstand möglichst gering zu halten. The cross section of the bore 30 or a plurality of bores is designed such that the diameter of the flow cross section is greater than the bore length in order to keep the flow resistance as low as possible.

Claims

Ansprüche Expectations
1. Radialkolbenmotor mit auf dem Umfang eines Exzenters (1) anliegenden Kolben (2), die auf der radial außen liegenden Seite mit einem Druckfluid beaufschlagt werden, um dem Exzenter (1) eine Drehbewegung um die Achse einer Abtriebswelle (W) zu erteilen, wobei nach dem Arbeitshub des Kolbens dessen Druckbeaufschlagungsfläche durch ein Steuerelement (15) von der Druckleitung (D) abgesperrt und mit einer Rücklaufleitung (R) verbunden wird, dadurch gekennzeichnet, dass zwischen Rücklaufleitung (R) und Druckbeaufschlagungsfläche des Kolbens (2) ein Hohlraum (27) großen Volumens zwischengeschaltet ist, in den der Kolben (2) das Fluid über eine Verbindung (30) mit geringem Strömungswiderstand ausstößt.1. radial piston motor with pistons (2) resting on the circumference of an eccentric (1), which are acted upon by a pressure fluid on the radially outer side in order to give the eccentric (1) a rotary movement about the axis of an output shaft (W), after the working stroke of the piston, the pressure application surface of the piston is shut off by a control element (15) from the pressure line (D) and connected to a return line (R), characterized in that between the return line (R) and the pressure application surface of the piston (2) there is a cavity ( 27) large volume is interposed, into which the piston (2) ejects the fluid via a connection (30) with low flow resistance.
2. Radialkolbenmotor nach Anspruch 1, wobei als Hohlraum großen Volumens der Leckfluidraum (27) des Gehäuses (4) des Radialkolbenmotors vorgesehen ist.2. Radial piston engine according to claim 1, wherein the leakage fluid space (27) of the housing (4) of the radial piston engine is provided as a large volume cavity.
3. Radialkolbenmotor nach Anspruch 2, wobei die auf dem Umfang des Exzenters (1) anliegenden Kolben (2) jeweils mit einem radial nach außen am Gehäuse (4, 9) pendelnd gelagerten Führungskörper (5) in Eingriff stehen und im Zylinderdeckel (9) oder einem entsprechenden Bauteil des Gehäuses das Steuerelement (15) zur Steuerung der Zu- und Ablaufkanäle (19, 20) vorgesehen ist, und wobei der Ablaufkanal (20) mit dem Hohlraum (27) des Gehäuses (4) über wenigstens eine Bohrung (30) großen Querschnitts bzw. mehrere Bohrungen mit großem Gesamtquerschnitt verbunden ist.3. Radial piston engine according to claim 2, wherein the pistons (2) resting on the circumference of the eccentric (1) are each in engagement with a guide body (5) which is mounted so as to oscillate radially outwards on the housing (4, 9) and in the cylinder cover (9). or a corresponding component of the housing, the control element (15) is provided for controlling the inlet and outlet channels (19, 20), and the outlet channel (20) with the cavity (27) of the housing (4) via at least one bore (30 ) large cross-section or several holes with large overall cross-section is connected.
4. Radialkolbenmotor nach Anspruch 3, wobei 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.4. Radial piston engine according to claim 3, wherein in the cylinder cover (9) or a corresponding component of the housing a with the guide body (5) articulated control element (15) for controlling the inlet and outlet channels (19, 20) is adjustably guided.
5. Radialkolbenmotor nach einem der Ansprüche 3 und 4, wobei die Zu- und Ablaufkanäle für das den Kolben beaufschlagende Fluid als Ringnuten (19, 20) um ein Stangen- förmiges Steuerelement (15) ausgebildet sind, und wobei von der den Ablaufkanal bildenden Ringnut (20) die Bohrung (30) in den Hohlraum (27) des Gehäuses führt. 5. Radial piston engine according to one of claims 3 and 4, wherein the inlet and outlet channels for the fluid acting on the piston as annular grooves (19, 20) around a rod Shaped control element (15) are formed, and wherein the bore (30) leads from the annular groove (20) forming the drain channel into the cavity (27) of the housing.
EP03785895A 2002-12-20 2003-12-19 Radial-piston motor Expired - Lifetime EP1601859B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10260158 2002-12-20
DE10260158A DE10260158A1 (en) 2002-12-20 2002-12-20 Radial piston motor
PCT/EP2003/014617 WO2004057156A1 (en) 2002-12-20 2003-12-19 Radial-piston motor

Publications (2)

Publication Number Publication Date
EP1601859A1 true EP1601859A1 (en) 2005-12-07
EP1601859B1 EP1601859B1 (en) 2010-07-07

Family

ID=32404104

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03785895A Expired - Lifetime EP1601859B1 (en) 2002-12-20 2003-12-19 Radial-piston motor

Country Status (8)

Country Link
EP (1) EP1601859B1 (en)
JP (1) JP4637586B2 (en)
KR (1) KR101046808B1 (en)
CN (1) CN100436754C (en)
AT (1) ATE473352T1 (en)
AU (1) AU2003294919A1 (en)
DE (2) DE10260158A1 (en)
WO (1) WO2004057156A1 (en)

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1246647A (en) * 1967-09-29 1971-09-15 Riva Calzoni Spa Hydraulic motor
GB1326739A (en) * 1969-10-22 1973-08-15 Lucas Industries Ltd Fluid-operated motor
DE2253022C2 (en) * 1972-10-28 1974-12-12 G.L. Rexroth Gmbh, 8770 Lohr Radial piston machine
DE3740891A1 (en) * 1987-12-02 1989-06-22 Pleiger Maschf Paul RADIAL PISTON ENGINE
DE4114846A1 (en) * 1990-05-12 1991-11-14 Zahnradfabrik Friedrichshafen Radial piston hydraulic motor - has supply of pressure medium controlled by groove in motor shaft

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2004057156A1 *

Also Published As

Publication number Publication date
CN1729350A (en) 2006-02-01
DE50312869D1 (en) 2010-08-19
WO2004057156A1 (en) 2004-07-08
CN100436754C (en) 2008-11-26
KR101046808B1 (en) 2011-07-06
AU2003294919A1 (en) 2004-07-14
DE10260158A1 (en) 2004-07-01
JP4637586B2 (en) 2011-02-23
JP2006510842A (en) 2006-03-30
ATE473352T1 (en) 2010-07-15
KR20050091739A (en) 2005-09-15
EP1601859B1 (en) 2010-07-07

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