EP0856638B1 - Verstellbare Radialkolbenmaschine - Google Patents
Verstellbare Radialkolbenmaschine 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
Links
Images
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 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.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
Description
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.
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.
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.
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.
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.
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,
wobei der Hubring konzentrisch zum Rotor (11) angeordnet ist,
dadurch gekennzeichnet, daß der Hubring (19) um eine seiner Symmetrieachsen (Q,H) schwenkbar gelagert ist. - 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.
- 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.
- Verstellbare Radialkolbenmaschine (Pumpe oder Motor) nach Anspruch 3, dadurch gekennzeichnet, daß die Verstelleinrichtung (22) mechanisch, elektromechanisch, pneumatisch oder hydraulisch ansteuerbar ist.
- 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.
- 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.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19703155A DE19703155C2 (de) | 1997-01-29 | 1997-01-29 | Verstellbare Radialkolbenmaschine |
DE19703155 | 1997-01-29 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0856638A1 EP0856638A1 (de) | 1998-08-05 |
EP0856638B1 true EP0856638B1 (de) | 2002-07-17 |
Family
ID=7818651
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP97120962A Expired - Lifetime EP0856638B1 (de) | 1997-01-29 | 1997-11-28 | Verstellbare Radialkolbenmaschine |
Country Status (3)
Country | Link |
---|---|
US (1) | US5878648A (de) |
EP (1) | EP0856638B1 (de) |
DE (2) | DE19703155C2 (de) |
Families Citing this family (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19843120C1 (de) * | 1998-09-21 | 1999-12-30 | Bosch Gmbh Robert | Verstellbare Radialkolbenmaschine |
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 (de) * | 2009-12-17 | 2011-06-22 | ZF Friedrichshafen AG, 88046 | Verfahren zur Bestimmung des Schluckvolumens einer Radialkolbenmaschine |
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 (de) * | 1934-05-22 | 1939-01-19 | Elek K Benedek Dr | Sternkolbenpumpe |
GB1408861A (en) * | 1971-12-23 | 1975-10-08 | Lucas Industries Ltd | Rotary hydraulic machines |
DE3433289A1 (de) * | 1984-09-11 | 1986-03-20 | Rudolf 7031 Holzgerlingen Bock | Hydraulische radialkolbenmaschine |
JPS61142373A (ja) * | 1984-12-13 | 1986-06-30 | Nippon Denso Co Ltd | 可変容量ポンプ |
GB2254373A (en) * | 1991-04-03 | 1992-10-07 | Echarren Uzabel Ricardo | Rotary cylinder i.c.engine,pump or compressor. |
DE4143152C2 (de) * | 1991-12-28 | 2001-08-23 | Bosch Gmbh Robert | Radialkolbenmaschine |
US5651301A (en) * | 1994-12-13 | 1997-07-29 | Unipat Aktiengessellschaft | Hydrostatic piston machines |
-
1997
- 1997-01-29 DE DE19703155A patent/DE19703155C2/de not_active Expired - Fee Related
- 1997-11-28 EP EP97120962A patent/EP0856638B1/de not_active Expired - Lifetime
- 1997-11-28 DE DE59707727T patent/DE59707727D1/de 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 (de) | 1998-08-05 |
DE19703155C2 (de) | 1999-01-07 |
DE19703155A1 (de) | 1998-07-30 |
DE59707727D1 (de) | 2002-08-22 |
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