EP0856638B1 - Adjustable radial piston machine - Google Patents
Adjustable radial piston machine Download PDFInfo
- Publication number
- EP0856638B1 EP0856638B1 EP97120962A EP97120962A EP0856638B1 EP 0856638 B1 EP0856638 B1 EP 0856638B1 EP 97120962 A EP97120962 A EP 97120962A EP 97120962 A EP97120962 A EP 97120962A EP 0856638 B1 EP0856638 B1 EP 0856638B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- piston machine
- rotor
- radial
- engine
- lifting ring
- 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.)
- Expired - Lifetime
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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
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- 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
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- 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
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- 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 relates to an adjustable radial piston machine (Pump or motor) according to the Genus of claim 1.
- Such radial piston machines are for example from the DE-A-3 433 289 is already known.
- This Radial piston machine has an engine that by a rotatable rotor with radially arranged Working cylinders is formed. Are in the working cylinders Pistons movably guided on a cam ring, which the Support the rotor.
- the cam ring is for adjustment the radial piston machine guided in the housing in a linearly movable manner and acts for this with a hydraulically loaded Piston / cylinder unit together. With appropriate Actuation of the piston / cylinder unit are between the cam ring and the rotor space and thus changed the operating parameters of the radial piston machine.
- 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 continuous 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 shaft (not shown) on the housing which is connected to the rotor 11 by a clutch 18 in a rotationally fixed manner.
- 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 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 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 ,
- 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.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
Description
Die Erfindung geht von einer vestellbaren Radialkolbenmaschine (Pumpe oder Motor) entsprechend der Gattung des Anspruchs 1 aus.The invention relates to an adjustable radial piston machine (Pump or motor) according to the Genus of claim 1.
Derartige Radialkolbenmaschinen sind beispielsweise aus der DE-A-3 433 289 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 Raum und damit die Betriebsparameter der Radialkolbenmaschine verändert.Such radial piston machines are for example from the DE-A-3 433 289 is already known. This Radial piston machine has an engine that by a rotatable rotor with radially arranged Working cylinders is formed. Are in the working cylinders Pistons movably guided on a cam ring, which the Support the rotor. The cam ring is for adjustment the radial piston machine guided in the housing in a linearly movable manner and acts for this with a hydraulically loaded Piston / cylinder unit together. With appropriate Actuation of the piston / cylinder unit are between the cam ring and the rotor space and thus changed the operating parameters of the radial piston machine.
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.
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.
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.
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. Abtrieb 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 wieder
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.1 shows a simplified representation of the
Depending on the mode of operation of the radial piston machine as a pump or motor, the
These
FIG. 2 shows the
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
The lifting movements of the working
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
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 gleitbzw.
wälzgelagert ist.In this connection it should be mentioned that a particularly effective force compensation is achieved at the bearing point of the
In particular, for the lowest possible pulsation in the flow rate or in the delivered drive torque of the radial piston machine, the highest possible number of
Claims (6)
- Adjustable radial-piston machine (pump or engine) having a housing, in the interior of which a power unit (10) is arranged, which power unit comprises a rotor (11), which is coupled in a rotationally fixed manner to an outwardly projecting shaft, has radially arranged cylinders (12) and working pistons (13) guided movably therein and is mounted rotatably on a stationary control journal (15), the control journal (15) having in each case at least one feed and discharge channel (16) which opens into piston ports (17a - d), and having a lifting ring (19), which surrounds the rotor (11), on which the working pistons (13) are supported and which interacts with an adjustment device (22) in order to adjust the radial-piston machine, the lifting ring being arranged concentrically with respect to the rotor (11), characterized in that the lifting ring (19) is mounted so that it can pivot about one of its axes of symmetry (Q, H).
- Adjustable radial-piston machine (pump or engine) according to Claim 1, characterized in that the pivotable lifting ring (19) has, on its circumference, radial bearing journals (20) which are arranged opposite one another.
- Adjustable radial-piston machine (pump or engine) according to one of Claims 1 or 2, characterized in that the adjustment device (22) which acts on the lifting ring (19) is arranged axially parallel with respect to the lifting ring (19) and acts on the end face of the lifting ring (19).
- Adjustable radial-piston machine (pump or engine) according to Claim 3, characterized in that the adjustment device (22) can be actuated mechanically, electromechanically, pneumatically or hydraulically.
- Adjustable radial-piston machine (pump or engine) according to one of Claims 1 to 4, characterized in that the rotor (11) of the radial-piston machine has in particular an even number of cylinders (12), in that the cylinders (12) are arranged at uniform angular intervals, and in that in each case two opposite cylinders (12), during the rotary movement of the rotor (11), are acted on by an identical pressure level.
- Adjustable radial-piston machine (pump or engine) according to one of Claims 1 to 5, characterized in that in each case two feed and discharge channels (16) are formed in the control journal (15) of the radial-piston machine and are arranged so as to follow one another alternately in the direction of rotation of the rotor (11).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19703155A DE19703155C2 (en) | 1997-01-29 | 1997-01-29 | Adjustable radial piston machine |
DE19703155 | 1997-01-29 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0856638A1 EP0856638A1 (en) | 1998-08-05 |
EP0856638B1 true EP0856638B1 (en) | 2002-07-17 |
Family
ID=7818651
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP97120962A Expired - Lifetime EP0856638B1 (en) | 1997-01-29 | 1997-11-28 | Adjustable radial piston machine |
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Country | Link |
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US (1) | US5878648A (en) |
EP (1) | EP0856638B1 (en) |
DE (2) | DE19703155C2 (en) |
Families Citing this family (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
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. |
NL2024476B1 (en) * | 2019-12-17 | 2021-09-02 | Delft Offshore Turbine B V | Turbine and multi piston pump |
Family Cites Families (7)
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 |
JPS61142373A (en) * | 1984-12-13 | 1986-06-30 | Nippon Denso Co Ltd | Variable capacity pump |
GB2254373A (en) * | 1991-04-03 | 1992-10-07 | Echarren Uzabel Ricardo | Rotary cylinder i.c.engine,pump or compressor. |
DE4143152C2 (en) * | 1991-12-28 | 2001-08-23 | Bosch Gmbh Robert | Radial piston machine |
US5651301A (en) * | 1994-12-13 | 1997-07-29 | Unipat Aktiengessellschaft | Hydrostatic piston machines |
-
1997
- 1997-01-29 DE DE19703155A patent/DE19703155C2/en not_active Expired - Fee Related
- 1997-11-28 EP EP97120962A patent/EP0856638B1/en not_active Expired - Lifetime
- 1997-11-28 DE DE59707727T patent/DE59707727D1/en not_active Expired - Fee Related
- 1997-12-30 US US09/001,234 patent/US5878648A/en not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
US5878648A (en) | 1999-03-09 |
EP0856638A1 (en) | 1998-08-05 |
DE19703155C2 (en) | 1999-01-07 |
DE19703155A1 (en) | 1998-07-30 |
DE59707727D1 (en) | 2002-08-22 |
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