EP0856638A1 - Adjustable radial piston machine - Google Patents

Adjustable radial piston machine Download PDF

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Publication number
EP0856638A1
EP0856638A1 EP97120962A EP97120962A EP0856638A1 EP 0856638 A1 EP0856638 A1 EP 0856638A1 EP 97120962 A EP97120962 A EP 97120962A EP 97120962 A EP97120962 A EP 97120962A EP 0856638 A1 EP0856638 A1 EP 0856638A1
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EP
European Patent Office
Prior art keywords
piston machine
radial piston
rotor
cam ring
pump
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
EP97120962A
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German (de)
French (fr)
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EP0856638B1 (en
Inventor
Wilhelm Dworak
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Moog GmbH
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Robert Bosch GmbH
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Publication date
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Publication of EP0856638A1 publication Critical patent/EP0856638A1/en
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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
    • F01B13/00—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion
    • F01B13/04—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder
    • F01B13/06—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder in star arrangement
    • F01B13/061—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder in star arrangement the connection of the pistons with the actuated or actuating element being at the outer ends of the cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/12—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members
    • F04B49/123—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members by changing the eccentricity of one element relative to another element
    • F04B49/128—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members by changing the eccentricity of one element relative to another element by changing the eccentricity of the cylinders, e.g. by moving a cylinder block
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/06—Control
    • F04B1/07—Control by varying the relative eccentricity between two members, e.g. a cam and a drive shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/10—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary
    • F04B1/107—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary with actuating or actuated elements at the outer ends of the cylinders
    • F04B1/1071—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary with actuating or actuated elements at the outer ends of the cylinders with rotary cylinder blocks

Definitions

  • the invention is based on an adjustable radial piston machine (pump or motor) according to the preamble of claim 1.
  • radial piston machines are already known for example from DE 41 43 152.9 A1.
  • This radial piston machine has an engine which is formed by a rotatably mounted rotor with radially arranged working cylinders. Pistons are movably guided in the working cylinders and are supported on a cam ring that surrounds the rotor.
  • the cam ring is guided in the housing in a linearly movable manner and for this purpose interacts with a hydraulically actuated piston / cylinder unit.
  • the disadvantage here is that the working cylinders generated during operation of the radial piston machine hydraulic forces on the rotor are not in balance are located. As a result, the bearing of the rotor with its Frictional force that affects mechanical efficiency the radial piston machine deteriorated. Furthermore leads the frictional force to a temperature load or to a Wear, which in extreme cases for eating or mechanical destruction of the engine components.
  • the adjustable radial piston machine with the characterizing features of claim 1 has a rotor on which the attacking hydraulic forces keep the balance. As a result, almost no frictional force is generated at the bearing point of the rotor, which improves the mechanical efficiency of the radial piston machine. Furthermore, thermal stress and wear on the engine of the radial piston machine are largely avoided.
  • a cam ring which is arranged concentrically to the rotor and which is pivotally mounted about its axis of symmetry for its adjustment. The pivoting movement is controlled by a piston / cylinder unit, which is arranged transversely to the cam ring, which makes the radial piston machine much narrower. Such a pivoting movement of the cam ring divides a rotor revolution into two successive working strokes for the working cylinders, so that the swallowing or delivery volume of the radial piston machine is doubled with unchanged size.
  • Figure 1 shows this in a simplified representation adjustable engine of an inventive Radial piston machine in longitudinal section
  • Figure 2 is a Cross-section of the engine along section line II-II shown schematically in FIG.
  • FIG. 1 shows a simplified representation of the engine 10 of a radial piston machine in longitudinal section, the illustration of a housing of the radial piston machine, in the interior of which the engine 10 is normally arranged, has been omitted for the sake of simplicity.
  • One of the essential assemblies of the engine 10 is a rotor 11 which has through radial bores which form cylinders 12.
  • the rotor 11 has an even number of cylinders 12, but this is not absolutely necessary.
  • Working pistons 13 are movably guided in the cylinders 12.
  • the rotor 11 is rotatably supported with its hub 14 on a control pin 15, which is arranged in a manner not shown in the stationary manner in the housing of the radial piston machine.
  • inlet and outlet channels 16 are formed, which end in circumferential control slots 17a-d.
  • These upstream and downstream control slots 17a-d arranged alternately one behind the other in the area of the bearing point of the rotor 11 interact with and control the rotating cylinders 12.
  • the rotor 11 is driven or driven via a housing-side shaft, not shown, which is connected to the rotor 11 in a rotationally fixed manner by a clutch 18.
  • a centrifugal force acting on the working piston 13 due to the rotary movement of the rotor 11 causes the working piston 13 to rest against a cam ring 19 with its ends facing away from the control pin 15.
  • the cam ring 19 is arranged concentrically with the rotor 11 and surrounds it circumferentially.
  • the cam ring 19 has on its outer circumference two radially projecting bearing pins 20 (FIG. 2) which are arranged in the direction of a transverse axis Q, which is also an axis of symmetry of the cam ring 19.
  • These journals 20 permit a pivoting movement of the lifting ring 19 about the transverse axis Q, the maximum pivoting angle W of which is matched to the diameter of the working piston 13 by the width of the lifting ring 19 such that it is preferably approximately twice as large as the diameter of the working piston 13, is limited.
  • the instantaneous swivel angle W depends on the current operating conditions of the radial piston machine and is regulated by an adjusting device 22 arranged axially in the housing.
  • this adjusting device 22 can be controlled mechanically, electromechanically, pneumatically or hydraulically and, as the actuating element, has a tappet 23 which acts on the end face of the circumferential cross section of the cam ring 19.
  • the lifting ring 19 is reset by a spring device (not shown), which at the same time ensures that the lifting ring 19 rests securely on the tappet 23 of the adjusting device 22.
  • FIG. 2 shows the engine 10 described above in a cross section, on the basis of which the mode of operation of the radial piston machine is explained below.
  • the distance A assumes minimum values and in the direction of the vertical axis H running perpendicular to the transverse axis Q maximum values. Accordingly, the working piston 13 is forced two periodic strokes during a rotor revolution, each of which extends over 180 degrees. The maximum stroke of these stroke movements is determined by the size of the swivel angle W.
  • the two identical lifting movements per revolution of the rotor 11 have their inner reversal points in the direction of the transverse axis Q and their outer reversal points in the direction of the vertical axis H.
  • the cylinders 12 are coupled to an inlet or outlet channel 16 via the control slots 17a-d in coordination with the direction of movement of their working pistons 13.
  • the control slots 17a-d were arranged on the control pin 15 in such a way that two opposing cylinders 12 are each subjected to the same pressure level.
  • Partitions 24 between the control slots 17a-d, together with the hub 14 of the rotor 11, serve for the sealing separation between the inlet and outlet channels 16.
  • the lifting movements of the working piston 13 thus allow a pressure medium flow from the inlet to the outlet channel 16 or vice versa, during which pressure energy is given or removed from the pressure medium depending on the operating mode of the radial piston machine as a pump or motor and converted into a drive torque.
  • the dimension of the displaced pressure medium depends on the current operating conditions of the radial piston machine and can be regulated via the swivel angle W of the lifting ring 19 (FIG. 1). Since two opposing cylinders 12 are always subjected to an identical pressure level during their stroke movements, the hydraulic forces generated on the rotor 11 have the same amount, but opposite directions of action. The rotor 11 thus rotates in a force-balanced manner on the control pin 15, so that frictional forces which promote wear and reduce efficiency are avoided.

Abstract

The lift ring(19) upon which the working pistons(13) bear is located concentric to the rotor(11) and pivots around one of its symmetry axes(Q,H). The lift ring on its periphery has radial bearing journals(20) located opposite each other. The adjusting unit acting upon the lift ring is located axially parallel to it and acts upon the lift ring's end face. The adjusting unit is mechanically, electromechanically, pneumatically or hydraulically controlled.

Description

Stand der TechnikState of the art

Die Erfindung geht von einer vestellbaren Radialkolbenmaschine (Pumpe oder Motor) entsprechend der Gattung des Anspruchs 1 aus.
Derartige Radialkolbenmaschinen sind beispielsweise aus der DE 41 43 152.9 A1 bereits bekannt. Diese Radialkolbenmaschine weist ein Triebwerk auf, das von einem drehbar gelagerten Rotor mit radial angeordneten Arbeitszylindern gebildet wird. In den Arbeitszylindern sind Kolben beweglich geführt, die sich an einem Hubring, der den Rotor umschließt, abstützen. Der Hubring ist zur Verstellung der Radialkolbenmaschine linear beweglich im Gehäuse geführt und wirkt hierzu mit einer hydraulisch beaufschlagten Kolben-/Zylindereinheit zusammen. Bei entsprechender Ansteuerung der Kolben-/Zylindereinheit werden die zwischen dem Hubring und dem Rotor vorhandene Exzentrizität und damit die Betriebsparameter der Radialkolbenmaschine verändert.The invention is based on an adjustable radial piston machine (pump or motor) according to the preamble of claim 1.
Such radial piston machines are already known for example from DE 41 43 152.9 A1. This radial piston machine has an engine which is formed by a rotatably mounted rotor with radially arranged working cylinders. Pistons are movably guided in the working cylinders and are supported on a cam ring that surrounds the rotor. For the adjustment of the radial piston machine, the cam ring is guided in the housing in a linearly movable manner and for this purpose interacts with a hydraulically actuated piston / cylinder unit. When the piston / cylinder unit is actuated appropriately, the eccentricity between the cam ring and the rotor and thus the operating parameters of the radial piston machine are changed.

Nachteilig dabei ist, daß sich die von den Arbeitszylindern beim Betrieb der Radialkolbenmaschine erzeugten hydraulischen Kräfte auf den Rotor nicht im Gleichgewicht befinden. Dadurch wird die Lagerstelle des Rotors mit seiner Reibungskraft belastet, die den mechanischen Wirkungsgrad der Radialkolbenmaschine verschlechtert. Desweiteren führt die Reibungskraft zu einer Temperaturbelastung bzw. zu einem Verschleiß, der im Extremfall zum Fressen bzw. zur mechanischen Zerstörung der Triebwerksbauteile führen kann.The disadvantage here is that the working cylinders generated during operation of the radial piston machine hydraulic forces on the rotor are not in balance are located. As a result, the bearing of the rotor with its Frictional force that affects mechanical efficiency the radial piston machine deteriorated. Furthermore leads the frictional force to a temperature load or to a Wear, which in extreme cases for eating or mechanical destruction of the engine components.

Vorteile der ErfindungAdvantages of the invention

Demgegenüber weist die verstellbare Radialkolbenmaschine mit den kennzeichnenden Merkmalen des Anspruchs 1 einen Rotor auf, an dem sich die angreifenden hydraulischen Kräfte das Gleichgewicht halten. Dadurch wird an der Lagerstelle des Rotors nahezu keine Reibungskraft erzeugt, wodurch sich der mechanische Wirkungsgrad der Radialkolbenmaschine verbessert. Ferner wird eine Temperaturbelastung und ein Verschleiß des Triebwerks der Radialkolbenmaschine weitstgehend vermieden.
Diese Vorteile werden durch einen Hubring ermöglicht, der konzentrisch zum Rotor angeordnet ist und der zu seiner Verstellung schwenkbar um seine Symmetrieachse gelagert ist. Die Schwenkbewegung wird durch eine Kolben-/Zylinder-einheit gesteuert, die quer zum Hubring angeordnet ist, wodurch die Radialkolbenmaschine wesentlich schmaler baut. Durch eine derartige Schwenkbewegung des Hubrings wird eine Rotorumdrehung in jeweils zwei aufeinanderfolgende Arbeitshübe für die Arbeitszylinder unterteilt, so daß sich das Schluck- bzw. das Fördervolumen der Radialkolbenmaschine bei unveränderter Baugröße verdoppelt.In contrast, the adjustable radial piston machine with the characterizing features of claim 1 has a rotor on which the attacking hydraulic forces keep the balance. As a result, almost no frictional force is generated at the bearing point of the rotor, which improves the mechanical efficiency of the radial piston machine. Furthermore, thermal stress and wear on the engine of the radial piston machine are largely avoided.
These advantages are made possible by a cam ring which is arranged concentrically to the rotor and which is pivotally mounted about its axis of symmetry for its adjustment. The pivoting movement is controlled by a piston / cylinder unit, which is arranged transversely to the cam ring, which makes the radial piston machine much narrower. Such a pivoting movement of the cam ring divides a rotor revolution into two successive working strokes for the working cylinders, so that the swallowing or delivery volume of the radial piston machine is doubled with unchanged size.

Weitere Vorteile oder vorteilhafte Weiterbildungen ergeben sich aus den Unteransprüchen oder der Beschreibung. Further advantages or advantageous further developments result itself from the subclaims or the description.

Zeichnungdrawing

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert.An embodiment of the invention is in the drawing shown and in the following description explained.

Figur 1 zeigt in einer vereinfachten Darstellung das verstellbare Triebwerk einer erfindungsgemäßen Radialkolbenmaschine im Längsschnitt, in Figur 2 ist ein Querschnitt des Triebwerks entlang der Schnittlinie II-II nach Figur 1 schematisch dargestellt.Figure 1 shows this in a simplified representation adjustable engine of an inventive Radial piston machine in longitudinal section, in Figure 2 is a Cross-section of the engine along section line II-II shown schematically in FIG.

Beschreibung des AusführungsbeispielsDescription of the embodiment

Figur 1 zeigt in einer vereinfachten Darstellung das Triebwerk 10 einer Radialkolbenmaschine im Längsschnitt, wobei auf die Darstellung eines Gehäuses der Radialkolbenmaschine, in dessen Innenraum das Triebwerk 10 normalerweise angeordnet ist, der Einfachheit halber verzichtet wurde. Eine der wesentlichen Baugruppen des Triebwerks 10 stellt ein Rotor 11 dar, der durchgehende Radialbohrungen aufweist, die Zylinder 12 bilden. Im Ausführungsbeispiel weist der Rotor 11 eine geradzahlige Anzahl von Zylindern 12 auf, was jedoch nicht zwingend erforderlich ist. In den Zylindern 12 sind Arbeitskolben 13 beweglich geführt. Der Rotor 11 ist mit seiner Nabe 14 drehbar auf einem Steuerzapfen 15 gelagert, der auf nicht gezeichnete Art und Weise ortsfest im Gehäuse der Radialkolbenmaschine angeordnet ist. Im Steuerzapfen 15 sind Zu- bzw. Ablaufkanäle 16 ausgebildet, die in umfangseitigen Steuerschlitzen 17a-d enden. Diese im Bereich der Lagerstelle des Rotors 11 abwechsend hintereinander angeordneten zu- bzw. ablaufseitigen Steuerschlitze 17a-d wirken mit den vorbeirotierenden Zylindern 12 zusammen und steuern diese.
Abhängig von der Betriebsweise der Radialkolbenmaschine als Pumpe oder Motor erfolgt der An- bzw. Antrieb des Rotors 11 über eine nicht gezeichnete gehäuseseitige Welle, die mit dem Rotor 11 durch eine Kupplung 18 drehfest verbunden ist. Eine aufgrund der Drehbewegung des Rotors 11 auf die Arbeitskolben 13 einwirkende Fliehkraft bewirkt die Anlage der Arbeitskolben 13 mit ihren vom Steuerzapfen 15 abgewandten Enden an einem Hubring 19. Der Hubring 19 ist konzentrisch zum Rotor 11 angeordnet und umschließt diesen umfangsseitig. Zu seiner Lagerung im Gehäuse der Radialkolbenmaschine hat der Hubring 19 an seinem Außenumfang zwei radial abstehende und in Richtung einer Querachse Q, die gleichzeitig eine Symmetrieachse des Hubrings 19 ist, angeordnete Lagerzapfen 20 (Figur 2).
Diese Lagerzapfen 20 erlauben um die Querachse Q eine Schwenkbewegung des Hubrings 19, deren maximaler Schwenkwinkel W durch die Breite des Hubrings 19, die auf den Durchmesser der Arbeitskolben 13 derart abgestimmt ist, daß sie bevorzugterweise ca. doppelt so groß ist wie der Durchmesser der Arbeitskolben 13, begrenzt wird. Der augenblickliche Schwenkwinkel W ist von den momentanen Betriebsbedingungen der Radialkolbenmaschine abhängig und wird durch eine axial im Gehäuse angeordnete Verstelleinrichtung 22 geregelt. Diese Verstelleinrichtung 22 kann hierzu mechanisch, elektromechanisch, pneumatisch oder hydraulisch angesteuert sein und weist als Betätigungselement einen Stößel 23 auf, der stirnseitig auf den Umfangsquerschnitt des Hubrings 19 einwirkt. Die Rückstellung des Hubrings 19 erfolgt über eine nicht dargestellte Federeinrichtung, die gleichzeitig für eine sichere Anlage des Hubrings 19 am Stößel 23 der Verstelleinrichtung 22 sorgt. Als Federeinrichtung ist beispielsweise eine vorgespannte Drehfeder denkbar, die sich mit ihrem ersten Ende an zumindest einem Lagerzapfen 20 und mit ihrem zweiten Ende am Gehäuse der Radialkolbenmaschine abstützt.
Figur 2 zeigt oben beschriebenes Triebwerk 10 in einem Querschnitt, anhand dem im Folgenden die Wirkungsweise der Radialkolbenmaschine erläutert wird.Figure 1 shows a simplified representation of the engine 10 of a radial piston machine in longitudinal section, the illustration of a housing of the radial piston machine, in the interior of which the engine 10 is normally arranged, has been omitted for the sake of simplicity. One of the essential assemblies of the engine 10 is a rotor 11 which has through radial bores which form cylinders 12. In the exemplary embodiment, the rotor 11 has an even number of cylinders 12, but this is not absolutely necessary. Working pistons 13 are movably guided in the cylinders 12. The rotor 11 is rotatably supported with its hub 14 on a control pin 15, which is arranged in a manner not shown in the stationary manner in the housing of the radial piston machine. In the control pin 15 inlet and outlet channels 16 are formed, which end in circumferential control slots 17a-d. These upstream and downstream control slots 17a-d arranged alternately one behind the other in the area of the bearing point of the rotor 11 interact with and control the rotating cylinders 12.
Depending on the mode of operation of the radial piston machine as a pump or motor, the rotor 11 is driven or driven via a housing-side shaft, not shown, which is connected to the rotor 11 in a rotationally fixed manner by a clutch 18. A centrifugal force acting on the working piston 13 due to the rotary movement of the rotor 11 causes the working piston 13 to rest against a cam ring 19 with its ends facing away from the control pin 15. The cam ring 19 is arranged concentrically with the rotor 11 and surrounds it circumferentially. For its mounting in the housing of the radial piston machine, the cam ring 19 has on its outer circumference two radially projecting bearing pins 20 (FIG. 2) which are arranged in the direction of a transverse axis Q, which is also an axis of symmetry of the cam ring 19.
These journals 20 permit a pivoting movement of the lifting ring 19 about the transverse axis Q, the maximum pivoting angle W of which is matched to the diameter of the working piston 13 by the width of the lifting ring 19 such that it is preferably approximately twice as large as the diameter of the working piston 13, is limited. The instantaneous swivel angle W depends on the current operating conditions of the radial piston machine and is regulated by an adjusting device 22 arranged axially in the housing. For this purpose, this adjusting device 22 can be controlled mechanically, electromechanically, pneumatically or hydraulically and, as the actuating element, has a tappet 23 which acts on the end face of the circumferential cross section of the cam ring 19. The lifting ring 19 is reset by a spring device (not shown), which at the same time ensures that the lifting ring 19 rests securely on the tappet 23 of the adjusting device 22. As a spring device, for example, a prestressed torsion spring is conceivable, which is supported with its first end on at least one bearing journal 20 and with its second end on the housing of the radial piston machine.
FIG. 2 shows the engine 10 described above in a cross section, on the basis of which the mode of operation of the radial piston machine is explained below.

Dabei wird davon ausgegangen, daß der auf dem Steuerzapfen 15 gelagerte Rotor 11 eine Drehbewegung D entgegengesetzt zum Uhrzeigersinn ausführt. Aufgrund dieser Drehbewegung D streben die Arbeitskolben 13 radial nach außen, bis sie mit ihren aus dem Rotor 11 herausragenden Enden an der Innenwandung des Hubrings 19 anliegen. Da der Hubring 19, entsprechend der Darstellung gemäß Figur 1, mit dem Rotor 11 einen Schwenkwinkel W einschließt, weist die Innenwandung des Hubrings 19 zum Rotor 11 einen vom momentanen Drehwinkel des Rotors 11 abhängigen Abstand A auf, der sich im Verlauf einer Rotorumdrehung periodisch verändert. In Richtung der Querachse Q des Rotors 11 nimmt der Abstand A minimale und in Richtung der senkrecht zur Querachse Q verlaufenden Hochachse H maximale Werte an. Dementsprechend werden den Arbeitskolben 13 während einer Rotorumdrehung zwei periodische Hubbewegungen aufgezwungen, die sich jeweils über 180 Winkelgrad erstrecken. Der Maximalhub dieser Hubbewegungen ist durch die Größe des Schwenkwinkels W bestimmt. Die beiden gleichartigen Hubbewegungen pro Umdrehung des Rotors 11 haben in Richtung der Querachse Q ihre inneren und in Richtung der Hochachse H ihre äußeren Umkehrpunkte. Während diesen Hubbewegungen sind die Zylinder 12 in Abstimmung mit der Bewegungsrichtung ihrer Arbeitskolbens 13 mit einem Zu- bzw. Ablaufkanal 16 über die Steuerschlitze 17a-d gekoppelt. Die Steuerschlitze 17a-d wurden dabei so am Steuerzapfen 15 angeordnet, daß jeweils zwei gegenüberliegende Zylinder 12 mit demselben Druckniveau beaufschlagt sind. Trennstege 24 zwischen den Steuerschlitzen 17a-d dienen dabei zusammen mit der Nabe 14 des Rotors 11 zur dichtenden Abtrennung zwischen den Zu- bzw Ablaufkanälen 16.
Die Hubbewegungen der Arbeitskolben 13 erlauben somit eine Druckmittelströmung vom Zu- zum Ablaufkanal 16 bzw. umgekehrt, während der dem Druckmittel in Abhängigkeit von der Betriebsart der Radialkolbenmaschine als Pumpe oder Motor eine Druckenergie erteilt bzw. entzogen und in ein Antriebsmoment umgewandelt wird.It is assumed that the rotor 11 mounted on the control pin 15 executes a rotational movement D counterclockwise. Because of this rotational movement D, the working pistons 13 strive radially outward until their ends protruding from the rotor 11 rest against the inner wall of the cam ring 19. Since the cam ring 19, as shown in FIG. 1, includes a swivel angle W with the rotor 11, the inner wall of the cam ring 19 from the rotor 11 has a distance A which is dependent on the instantaneous angle of rotation of the rotor 11 and which changes periodically in the course of a rotor revolution . In the direction of the transverse axis Q of the rotor 11, the distance A assumes minimum values and in the direction of the vertical axis H running perpendicular to the transverse axis Q maximum values. Accordingly, the working piston 13 is forced two periodic strokes during a rotor revolution, each of which extends over 180 degrees. The maximum stroke of these stroke movements is determined by the size of the swivel angle W. The two identical lifting movements per revolution of the rotor 11 have their inner reversal points in the direction of the transverse axis Q and their outer reversal points in the direction of the vertical axis H. During these stroke movements, the cylinders 12 are coupled to an inlet or outlet channel 16 via the control slots 17a-d in coordination with the direction of movement of their working pistons 13. The control slots 17a-d were arranged on the control pin 15 in such a way that two opposing cylinders 12 are each subjected to the same pressure level. Partitions 24 between the control slots 17a-d, together with the hub 14 of the rotor 11, serve for the sealing separation between the inlet and outlet channels 16.
The lifting movements of the working piston 13 thus allow a pressure medium flow from the inlet to the outlet channel 16 or vice versa, during which pressure energy is given or removed from the pressure medium depending on the operating mode of the radial piston machine as a pump or motor and converted into a drive torque.

Das Maß des verdrängten Druckmittels ist dabei von den augenblicklichen Einsatzbedingungen der Radialkolbenmaschine abhängig und kann über den Schwenkwinkel W des Hubrings 19 (Figur 1) reguliert werden.
Da zwei einander gegenüberliegende Zylinder 12 während ihren Hubbewegungen stets mit identischem Druckniveau beaufschlagt sind, weisen die erzeugten hydraulischen Kräfte auf den Rotor 11 zwar den selben Betrag, jedoch entgegengesetzte Wirkungsrichtungen auf. Der Rotor 11 rotiert damit kraftausgeglichen auf dem Steuerzapfen 15, so daß verschleißfördernde und Wirkungsgrad verschlechternde Reibungskräfte vermieden werden.The dimension of the displaced pressure medium depends on the current operating conditions of the radial piston machine and can be regulated via the swivel angle W of the lifting ring 19 (FIG. 1).
Since two opposing cylinders 12 are always subjected to an identical pressure level during their stroke movements, the hydraulic forces generated on the rotor 11 have the same amount, but opposite directions of action. The rotor 11 thus rotates in a force-balanced manner on the control pin 15, so that frictional forces which promote wear and reduce efficiency are avoided.

Selbstverständlich sind Änderungen bzw. Ergänzungen zum beschriebenen Ausführungsbeispiel denkbar, ohne vom Grundgedanken der Erfindung abzuweichen.Of course, changes or additions to described embodiment conceivable without Deviate basic ideas of the invention.

In diesem Zusammenhang zu erwähnen ist, daß ein besonders wirksamer Kraftausgleich an der Lagerstelle des Rotors 11 erreicht wird, wenn der Rotor 11 eine geradzahlige Anzahl von gleichmäßig über seinen Umfang verteilt angeordneten Zylindern 12 aufweist.
Insbesondere für eine möglichst geringe Pulsation im Förderstrom bzw. im abgegebenen Antriebsmoment der Radialkolbenmaschine ist eine möglichst hohe Anzahl von Zylindern 12 anzustreben, wobei eine besonders kompakte und dennoch robuste Bauweise für das Triebwerk 10 bei einer Zylinderzahl zwischen fünf und acht Zylindern 12 erreicht wird. Weiterhin vorstellbar ist es, die Reibung zwischen den Arbeitskolben 13 und dem Hubring 19 mittels eines mehrteiligen Hubrings 19 zu minimieren. Dieser mehrteilige Hubring 19 hat wenigstens einen mit den Arbeitskolben 13 umlaufenden Innenring, der gegenüber seinem Außenring gleit- bzw. wälzgelagert ist.In this connection it should be mentioned that a particularly effective force compensation is achieved at the bearing point of the rotor 11 if the rotor 11 has an even number of cylinders 12 arranged evenly distributed over its circumference.
In particular, for the lowest possible pulsation in the flow rate or in the output torque of the radial piston machine, the highest possible number of cylinders 12 is to be aimed for, whereby a particularly compact, yet robust design for the engine 10 is achieved with a number of cylinders between five and eight cylinders 12. It is also conceivable to minimize the friction between the working piston 13 and the cam ring 19 by means of a multi-part cam ring 19. This multi-part cam ring 19 has at least one inner ring which rotates with the working pistons 13 and which is mounted on a sliding or roller bearing with respect to its outer ring.

Claims (6)

Verstellbare Radialkolbenmaschine (Pumpe oder Motor) mit einem Gehäuse, in dessen Innenraum ein Triebwerk (10) angeordnet ist, das aus einem mit einer nach außen ragenden Welle drehfest gekoppelten Rotor (11) mit radial angeordneten Zylindern (12) und darin beweglich geführten Arbeitskolben (13) besteht, der drehbar auf einem ortsfesten Steuerzapfen (15) gelagert ist, wobei der Steuerzapfen (15) jeweils wenigstens einen in Steuerschlitzen (17a-d) mündenden Zu- bzw. Ablaufkanal (16) aufweist und mit einem den Rotor (11) umschließenden Hubring (19), an dem sich die Arbeitskolben (13) abstützen und der zur Verstellung der Radialkolbenmaschine mit einer Verstelleinrichtung (22) zusammenwirkt,
dadurch gekennzeichnet, daß der Hubring (19) konzentrisch zum Rotor (11) angeordnet und um eine seiner Symmetrieachsen (Q,H) schwenkbar gelagert ist.Adjustable radial piston machine (pump or motor) with a housing, in the interior of which an engine (10) is arranged, which consists of a rotor (11) rotatably coupled to an outwardly projecting shaft with radially arranged cylinders (12) and working pistons movably guided therein ( 13), which is rotatably mounted on a fixed control pin (15), the control pin (15) each having at least one inlet and outlet channel (16) opening into control slots (17a-d) and having a rotor (11) enclosing cam ring (19) on which the working pistons (13) are supported and which cooperates with an adjusting device (22) to adjust the radial piston machine,
characterized in that the cam ring (19) is arranged concentrically to the rotor (11) and is pivotally mounted about one of its axes of symmetry (Q, H). Verstellbare Radialkolbenmaschine (Pumpe oder Motor) nach Anspruch 1, dadurch gekennzeichnet, daß der schwenkbare Hubring (19) am Umfang radiale Lagerzapfen (20) aufweist, die gegenüberliegend zueinander angeordnet sind. Adjustable radial piston machine (pump or motor) after Claim 1, characterized in that the pivotable The lifting ring (19) has radial bearing journals (20) on the circumference, which are arranged opposite to each other. Verstellbare Radialkolbenmaschine (Pumpe oder Motor) nach einem der Ansprüche 1 oder 2, dadurch gekennzeichnet, daß die auf den Hubring (19) einwirkende Verstelleinrichtung (22) achsparallel zum Hubring (19) angeordnet ist und auf die Stirnfläche des Hubrings (19) einwirkt.Adjustable radial piston machine (pump or motor) after one of claims 1 or 2, characterized in that the adjusting device acting on the cam ring (19) (22) is arranged axially parallel to the cam ring (19) and on the end face of the cam ring (19) acts. Verstellbare Radialkolbenmaschine (Pumpe oder Motor) nach Anspruch 3, dadurch gekennzeichnet, daß die Verstelleinrichtung (22) mechanisch, elektromechanisch, pneumatisch oder hydraulisch ansteuerbar ist.Adjustable radial piston machine (pump or motor) after Claim 3, characterized in that the Adjusting device (22) mechanical, electromechanical, can be controlled pneumatically or hydraulically. Verstellbare Radialkolbemaschine (Pumpe oder Motor) nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß der Rotor (11) der Radialkolbenmaschine insbesondere eine geradzahlige Anzahl von Zylindern (12) aufweist, daß die Zylinder (12) in gleichen Winkelabständen zueinander angeordnet sind, und daß jeweils zwei gegenüberliegende Zylinder (12) im Verlauf der Drehbewegung des Rotors (11) mit identischem Druckniveau beaufschlagt sind.Adjustable radial piston machine (pump or motor) after one of claims 1 to 4, characterized in that the Rotor (11) of the radial piston machine, in particular one even number of cylinders (12) that the Cylinder (12) at equal angular distances from each other are arranged, and that each two opposite Cylinder (12) in the course of the rotary movement of the rotor (11) are subjected to an identical pressure level. Verstellbare Radialkolbenmaschine (Pumpe oder Motor) nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß im Steuerzapfen (15) der Radialkolbenmaschine jeweils zwei Zu- bzw. Ablaufkanäle (16) ausgebildet sind, die in Drehrichtung des Rotors (11) abwechselnd aufeinanderfolgend angeordnet sind.Adjustable radial piston machine (pump or motor) after one of claims 1 to 5, characterized in that in Control pin (15) of the radial piston machine each have two inlets or Drainage channels (16) are formed in the direction of rotation of the rotor (11) arranged alternately in succession are.
EP97120962A 1997-01-29 1997-11-28 Adjustable radial piston machine Expired - Lifetime EP0856638B1 (en)

Applications Claiming Priority (2)

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DE19703155A DE19703155C2 (en) 1997-01-29 1997-01-29 Adjustable radial piston machine
DE19703155 1997-01-29

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EP0856638B1 EP0856638B1 (en) 2002-07-17

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DE19843120C1 (en) * 1998-09-21 1999-12-30 Bosch Gmbh Robert Adjustable radial piston pump or motor
US6916158B2 (en) * 2003-04-30 2005-07-12 Actuant Corporation Radial piston pump
WO2006050233A1 (en) * 2004-10-28 2006-05-11 Nordson Corporation Rotary pump
GB0508107D0 (en) * 2005-04-22 2005-06-01 Univ Liverpool A pump
US7444989B2 (en) * 2006-11-27 2008-11-04 Caterpillar Inc. Opposed pumping load high pressure common rail fuel pump
GB2456809A (en) * 2008-01-24 2009-07-29 Tom Oswald Compressor
DE102009054876A1 (en) * 2009-12-17 2011-06-22 ZF Friedrichshafen AG, 88046 Method for determining the absorption volume of a radial piston machine
NL2004121C2 (en) * 2010-01-20 2011-07-21 Ceratec Ceramic Bearings B V Dispensing system and method for dispensing a fluid.

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GB1408861A (en) * 1971-12-23 1975-10-08 Lucas Industries Ltd Rotary hydraulic machines
DE3433289A1 (en) * 1984-09-11 1986-03-20 Rudolf 7031 Holzgerlingen Bock HYDRAULIC RADIAL PISTON MACHINE
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DE4143152A1 (en) 1991-12-28 1993-07-01 Bosch Gmbh Robert Radial piston machine with adjustable stroke ring - has oppositely placed sliding surfaces to engage grooves in stroke ring.

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Publication number Priority date Publication date Assignee Title
DE659943C (en) * 1934-05-22 1939-01-19 Elek K Benedek Dr Star piston pump
GB1408861A (en) * 1971-12-23 1975-10-08 Lucas Industries Ltd Rotary hydraulic machines
DE3433289A1 (en) * 1984-09-11 1986-03-20 Rudolf 7031 Holzgerlingen Bock HYDRAULIC RADIAL PISTON MACHINE
GB2254373A (en) * 1991-04-03 1992-10-07 Echarren Uzabel Ricardo Rotary cylinder i.c.engine,pump or compressor.
DE4143152A1 (en) 1991-12-28 1993-07-01 Bosch Gmbh Robert Radial piston machine with adjustable stroke ring - has oppositely placed sliding surfaces to engage grooves in stroke ring.

Also Published As

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EP0856638B1 (en) 2002-07-17
DE19703155A1 (en) 1998-07-30
US5878648A (en) 1999-03-09
DE19703155C2 (en) 1999-01-07
DE59707727D1 (en) 2002-08-22

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