EP1043504B1 - Vane pump with capacity control - Google Patents
Vane pump with capacity control Download PDFInfo
- Publication number
- EP1043504B1 EP1043504B1 EP00105641A EP00105641A EP1043504B1 EP 1043504 B1 EP1043504 B1 EP 1043504B1 EP 00105641 A EP00105641 A EP 00105641A EP 00105641 A EP00105641 A EP 00105641A EP 1043504 B1 EP1043504 B1 EP 1043504B1
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- EP
- European Patent Office
- Prior art keywords
- delivery
- vane pump
- ring
- casing
- volume
- 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
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
- F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
- F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
- F04C14/223—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam
- F04C14/226—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam by pivoting the cam around an eccentric axis
Definitions
- the invention relates to a variable-speed vane pump according to the preamble of the main claim.
- a pump is disclosed in US 5,800,131.
- Vane pumps of the generic type are previously known from the document DE-OS 2 015 744.
- vanes are arranged in radial slots in a rotor which is mounted in a housing and are guided so as to be capable of pushing, the outer ends of which slide in a cam ring comprising the vanes.
- the cam ring can be slidably mounted in a housing - see FIG. 4 - or pivoted on one side in a fixed bearing of the housing - see FIG. 2 - and is in each case pushed by spring force in the direction of maximum conveyance.
- the cam ring forms a hydraulic active surface which, when pressurized, urges it in the direction - zero - delivery - against the spring force
- the position of the cam ring which determines the delivery volume has to be held or adjusted against spring force by means of a separately regulated pressure.
- vane cell pumps of the type described above are filled and pushed out or conveyed via radial openings in the conveying space. The flow is deflected in a space of the cam ring which is radially adjacent to the delivery housing or towards axial openings in the housing which are not directly connected to the delivery space.
- a hollow bore and radially apertured axis of the cam ring can also serve as the axial opening.
- a disadvantage of this embodiment is that the area of overflow of oil under delivery pressure from the cam ring to the housing is sealed only by means of gap cross sections.
- the invention has for its object to provide an actuating arrangement for the cam ring for a variable-speed vane pump, which is mechanically compact and low-friction and in which the flow rate according to the operating state, for. B. for the lubrication of an internal combustion engine, is adjustable. According to the invention, this object is achieved by the means mentioned in the characterizing part of the main claim.
- FIG. 1 shows a vane pump 1 designed according to the invention.
- vanes 5 are arranged so that they can be pushed.
- the outer ends of the wings 5 slide in the inner contour 6 of a cam ring 7, which forms the delivery chamber 8 with variable delivery chambers 9.
- the cam ring 7 can be slidably mounted in the housing 10 - see FIG. 1 - or pivoted on one side in a fixed bearing 15 of the housing 10 - see FIG. 2.
- variable delivery chambers 9 are connected in a generally known manner during the suction and delivery process with axial suction or pressure slots or pockets in the housing 10, not shown.
- the cam ring 7 On its circumference, the cam ring 7 is sealed on one side with respect to the housing 10. In doing so, it forms a hydraulic active surface 7P which, in the pressurized state, presses it onto an actuating device 11 with a sliding and / or rotatable curve 12 counter-mounted in the housing 10.
- the interior of the housing 10 with the actuating device 11 is relieved of pressure.
- the rotatable and / or pushable curve 12, which is mounted in the housing 10, is connected to an actuator 13 for initiating a rotating and / or pushing movement. It acts directly - FIG. 2 - or indirectly - FIG. 1 - on a spring force F acting in the maximum delivery position, which, when the actuator 13 is not effective, urges the cam ring 7 via the curve 12 into a position of maximum delivery and, as in both Figures shown, holds.
- the actuator 13 shifts the curve 12 with respect to the support point A7 of the lifting ring 7 counter to or in the direction of the acting spring force F as a function of control signals S13 of a pressure control circuit 30, not shown in FIG. 1.
- the actuator 13 can be an electromagnet, an electric, hydraulic or pneumatic servomotor, which is controlled directly or indirectly by the pressure control circuit 30. 2 and 3, a hydraulic servomotor is shown.
- the adjusting device 11 has a rotatable curve 12 which is rotated via a toothed wheel and a toothed rack moved by the actuator 13 or by the spring force applied.
- the counter-bearing curve 12 in the housing 10 can be a hydrostatic support arrangement 20 directed against the reaction force of the cam ring 7, e.g. B. have a segment-shaped pocket 21 shown in FIG. 2, acted upon directly or indirectly by the delivery pressure.
- the cam ring 7 can be supported by means of a roller or ball arrangement 23 on the sliding and / or rotatable curve 12 mounted in the housing 10.
- the bearing point 15 is formed as a semicircular bearing recess 18, the cam ring 7 has a complementary bearing segment 73 which is pressed into the bearing recess 18 by the forces acting on the cam ring 7.
- the cam ring (7) is located in the region of its pivot axis (SA) in a deflection space (16) radially adjacent to the delivery space (6), which is connected axially with a large cross section to a delivery channel 17 in the housing 10 is.
- the delivery chamber 8 in the lifting ring 7 is connected to the deflection chamber 16 via radial inlet and outlet cross sections 71.
- the extension angle of the radial inlet and outlet cross sections 71 in the delivery chamber 8 is smaller than the extension angle of additional radial overflow channels 72 which extend on both sides of the inlet and outlet cross sections 71. With these overflow channels 72, a further inlet or outlet angle range is ensured, but the tread in the cam ring 7 is less narrowed.
- a pressure element 19 which is mounted in the housing 10 and which can act with spring force or delivery pressure.
- a spring 19 F which is mounted in the housing 10 rests the pressure piston 19 D on the cam ring 7 in a non-positive manner. It is also conceivable for the pressure piston 19 D to be supplied with the conveying medium, preferably with the conveying pressure P F , and to engage the cam ring 7 in a force-fitting manner; however, this is not shown.
- the half of the cam ring 7 facing away from the curve 12 can be sealed off from the housing 10 and to be supplied with the conveying medium and thus to replace a separate pressure element 19, see FIG. 2. It is advantageous for the actuating device 11 if the space in the housing 10 which accommodates the cam ring 7 is depressurized, the actuating device 11 can then act on the cam ring 7 without any disturbing hydraulic action.
- the inflow and outflow to and from the delivery chambers 6 in the lifting ring 7 can take place in the usual way via axially or radially opening channels.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
Description
Die Erfindung betrifft eine mengenregelbare Flügelzellenpumpe gemäß dem Oberbegriff des Hauptanspruches. Eine solche Pumpe ist in der Schrift US 5 800 131 offenbart.The invention relates to a variable-speed vane pump according to the preamble of the main claim. Such a pump is disclosed in US 5,800,131.
Vorbekannt sind gattungsgemäße Flügelzellenpumpen durch die Schrift DE-OS 2 015 744. Bei dieser Bauart sind in radialen Schlitzen eines Rotors, der in einem Gehäuse gelagert ist, Flügel schubbeweglich geführt angeordnet, wobei deren äußere Enden in einem die Flügel umfassenden Hubring gleiten.
Der Hubring kann in einem Gehäuse schiebbar - siehe Fig. 4 - oder einseitig in einer ortsfesten Lagerstelle des Gehäuses schwenkbar - siehe Fig. 2 - gelagert sein und wird jeweils mittels Federkraft in Richtung maximaler Förderung gedrängt. Einseitig an seinem Umfang gegenüber dem Gehäuse abgedichtet bildet der Hubring eine hydraulische Wirkfläche, die ihn im mit Druck beaufschlagten Zustand in Richtung - Null - Förderung - entgegen der Federkraft drängt
Nachteilig ist, daß die das Fördervolumen bestimmende Stellung des Hubringes mittels eines gesondert geregelten Druckes entgegen Federkraft gehalten bzw. verstellt werden muß.
Vorbekannt ist es durch die Schriften US 2,318,292, Fig. 4 und DE 34 46 603, Fig. 3, daß bei Flügelzellenpumpen der vorbeschriebenen Art das Füllen und Ausschieben bzw. Fördern über radiale Öffnungen im Förderraum erfolgt. Ein Umlenken der Strömung erfolgt jeweils in einem radial am Fördergehäuse angrenzenden Raum des Hubringes aus oder hin zu axialen Öffnungen im Gehäuse, die nicht unmittelbar mit dem Förderraum in Verbindung stehen. Als axiale Öffnung kann auch eine hohlgebohrte und radial mit Öffnungen versehene Achse des Hubringes dienen.Vane pumps of the generic type are previously known from the document DE-OS 2 015 744. In this type of construction, vanes are arranged in radial slots in a rotor which is mounted in a housing and are guided so as to be capable of pushing, the outer ends of which slide in a cam ring comprising the vanes.
The cam ring can be slidably mounted in a housing - see FIG. 4 - or pivoted on one side in a fixed bearing of the housing - see FIG. 2 - and is in each case pushed by spring force in the direction of maximum conveyance. Sealed on one side at its periphery with respect to the housing, the cam ring forms a hydraulic active surface which, when pressurized, urges it in the direction - zero - delivery - against the spring force
It is disadvantageous that the position of the cam ring which determines the delivery volume has to be held or adjusted against spring force by means of a separately regulated pressure.
It is previously known from the documents US 2,318,292, FIG. 4 and DE 34 46 603, FIG. 3 that vane cell pumps of the type described above are filled and pushed out or conveyed via radial openings in the conveying space. The flow is deflected in a space of the cam ring which is radially adjacent to the delivery housing or towards axial openings in the housing which are not directly connected to the delivery space. A hollow bore and radially apertured axis of the cam ring can also serve as the axial opening.
Vorbekannt ist es durch die Schrift DE 40 11 671 C2 bei Flügelzellenpumpen, daß das Füllen und Ausschieben bzw. Fördern über radiale Öffnungen im Förderraum erfolgt, wobei jedoch die radialen Flächen des Hubringes um den Bereich der radialen Öffnungen geringe Spaltquerschnitte bildend und damit ohne Berührung dichtend, gegenüber einer komplementären Innenkontur des Gehäuses geführt sind. Hierzu sind die Außenkontur des Hubringes und die komplementäre Innenkontur des Gehäuses um den Bereich der Öffnungen in ihrer Form durch einen Radius um die Schwenkachse des Hubringes definiert. Bei dieser Ausführung erfolgt ein Umlenken der Strömung in einem radial am Hubring angrenzenden Raum des Fördergehäuses.It is previously known from DE 40 11 671 C2 for vane pumps that the filling and pushing out or conveying takes place via radial openings in the delivery chamber, but the radial surfaces of the cam ring around the area of the radial openings form small gap cross sections and thus seal without contact , are guided against a complementary inner contour of the housing. For this purpose, the shape of the outer contour of the cam ring and the complementary inner contour of the housing around the area of the openings are defined by a radius around the pivot axis of the cam ring. In this embodiment, the flow is deflected in a space of the delivery housing that adjoins the lifting ring radially.
Nachteilig ist bei dieser Ausführung, daß der Bereich des Überströmens von unter Förderdruck stehendem Öl vom Hubring zum Gehäuse nur über Spaltquerschnitte abgedichtet ist.
Der Erfindung liegt die Aufgabe zugrunde, für eine mengenregelbare Flügelzellenpumpe eine Stellanordnung für den Hubring zu schaffen, die mechanisch kompakt und reibungsarm ausgeführt ist und bei der die Fördermenge betriebszustandsgerecht, z. B. für die Schmierung eines Verbrennungsmotors, einstellbar ist.
Erfindungsgemäß wird diese Aufgabe durch die im kennzeichnenden Teil des Hauptanspruches genannten Mittel gelöst.
In Folge dessen, daß der Hubring erfindungsgemäß auf einer im Gehäuse gegengelagerten, schieb- und / oder drehbaren Kurve abgestützt ist, deren Stellung für maximale Förderung ausschließlich beim Start, im abgestellten Zustand oder bei Ausfall der Regeleinrichtung von der Federkraft bestimmt ist, können von der Stellgröße unproportionale Stellwege für den Hubring und damit für das notwendige Fördervolumen erreicht werden.
Im Rahmen der Beschreibung werden die Merkmale der Unteransprüche zusammen mit ihren Wirkungen und Vorteilen erläutert.A disadvantage of this embodiment is that the area of overflow of oil under delivery pressure from the cam ring to the housing is sealed only by means of gap cross sections.
The invention has for its object to provide an actuating arrangement for the cam ring for a variable-speed vane pump, which is mechanically compact and low-friction and in which the flow rate according to the operating state, for. B. for the lubrication of an internal combustion engine, is adjustable.
According to the invention, this object is achieved by the means mentioned in the characterizing part of the main claim.
As a result of the fact that the cam ring is supported according to the invention on a counter-sliding, and / or rotatable curve in the housing, the position of which is determined by the spring force for maximum conveyance only at the start, in the switched-off state or in the event of failure of the control device Control variable disproportionate travel ranges for the cam ring and thus for the necessary delivery volume can be achieved.
In the context of the description, the features of the subclaims are explained together with their effects and advantages.
Anhand einer Zeichnung werden nachfolgend Ausführungsbeispiele der Erfindung erläutert.Exemplary embodiments of the invention are explained below with the aid of a drawing.
Es zeigt:
- Fig. 1
- eine erfindungsgemäß ausgestaltete Flügelzellenpumpe mit Stelleinrichtung und schiebbarem Hubring
- Fig. 2
- eine Flügelzellenpumpe mit hydraulischer Stelleinrichtung und schwenkbarem Hubring
- Fig. 3
- eine Flügelzellenpumpe entsprechend Fig. 2 jedoch mit einer Lagermulde im Gehäuse und einem Lagersegment am Hubring.
- Fig. 1
- a vane pump designed according to the invention with an adjusting device and a sliding cam ring
- Fig. 2
- a vane pump with hydraulic actuator and swiveling cam ring
- Fig. 3
- a vane pump according to FIG. 2 but with a bearing recess in the housing and a bearing segment on the cam ring.
In Fig. 1 ist eine erfindungsgemäß ausgestaltete Flügelzellenpumpe 1 gezeigt. In radialen Schlitzen 3 eines in einem Gehäuse 10 gelagerten Rotors 4 sind Flügel 5 schubbeweglich geführt angeordnet.
Die äußeren Enden der Flügel 5 gleiten in der Innenkontur 6 eines Hubringes 7, der den Förderraum 8 mit veränderlichen Förderkammern 9 bildet.
Der Hubring 7 kann im Gehäuse 10 schiebbar - siehe Fig. 1 - oder einseitig in einer ortsfesten Lagerstelle 15 des Gehäuses 10 schwenkbar - siehe Fig. 2 - gelagert sein.1 shows a vane pump 1 designed according to the invention. In radial slots 3 of a rotor 4 mounted in a housing 10, vanes 5 are arranged so that they can be pushed.
The outer ends of the wings 5 slide in the inner contour 6 of a cam ring 7, which forms the delivery chamber 8 with variable delivery chambers 9.
The cam ring 7 can be slidably mounted in the housing 10 - see FIG. 1 - or pivoted on one side in a fixed bearing 15 of the housing 10 - see FIG. 2.
Die veränderlichen Förderkammern 9 stehen in allgemein bekannter Weise beim Saug- und Fördervorgang mit axialen Saug- oder Druckschlitzen bzw. -taschen im Gehäuse 10 in Verbindung, nicht dargestellt.
An seinem Umfang ist der Hubring 7 einseitig gegenüber dem Gehäuse 10 abgedichtet. Dabei bildet er eine hydraulische Wirkfläche 7P, die ihn im druckbeaufschlagten Zustand auf eine Stelleinrichtung 11 mit im Gehäuse 10 gegengelagerter schieb- und / oder drehbaren Kurve12 drückt. Der Innenbereich des Gehäuses 10 mit der Stelleinrichtung 11 ist druckentlastet.The variable delivery chambers 9 are connected in a generally known manner during the suction and delivery process with axial suction or pressure slots or pockets in the housing 10, not shown.
On its circumference, the cam ring 7 is sealed on one side with respect to the housing 10. In doing so, it forms a hydraulic active surface 7P which, in the pressurized state, presses it onto an actuating device 11 with a sliding and / or rotatable curve 12 counter-mounted in the housing 10. The interior of the housing 10 with the actuating device 11 is relieved of pressure.
Die im Gehäuse 10 gegengelagerte dreh- und / oder schiebbare Kurve 12 ist mit einem Stellglied 13 zum Einleiten einer Dreh- und / oder Schubbewegung verbunden. An ihr greift direkt - Fig.2 - oder indirekt - Fig.1 - eine in Stellung maximaler Förderung wirkende Federkraft F an, die bei nicht wirksamem Stellglied 13 den Hubring 7 über die Kurve 12 in eine Stellung maximaler Förderung drängt und, wie in beiden Figuren dargestellt, hält.
Das Stellglied 13 verlagert die Kurve 12 gegenüber dem Abstützpunkt A7 des Hubringes 7 entgegen oder in Richtung der wirkenden Federkraft F in Abhängigkeit von Stellsignalen S13 eines Druckregelkreises 30, in Fig. 1 nicht dargestellt.
Das Stellglied 13 kann ein Elektromagnet, ein elektrischer, hydraulischer oder pneumatischer Stellmotor sein, dessen Ansteuerung direkt oder indirekt vom Druckregelkreis 30 erfolgt. In Fig. 2 und 3 wird ein hydraulischer Stellmotor gezeigt.The rotatable and / or pushable curve 12, which is mounted in the housing 10, is connected to an actuator 13 for initiating a rotating and / or pushing movement. It acts directly - FIG. 2 - or indirectly - FIG. 1 - on a spring force F acting in the maximum delivery position, which, when the actuator 13 is not effective, urges the cam ring 7 via the curve 12 into a position of maximum delivery and, as in both Figures shown, holds.
The actuator 13 shifts the curve 12 with respect to the support point A7 of the lifting ring 7 counter to or in the direction of the acting spring force F as a function of control signals S13 of a pressure control circuit 30, not shown in FIG. 1.
The actuator 13 can be an electromagnet, an electric, hydraulic or pneumatic servomotor, which is controlled directly or indirectly by the pressure control circuit 30. 2 and 3, a hydraulic servomotor is shown.
Bei der in Fig.1 gezeigten Ausführung weist die Stellvorrichtung 11 eine drehbare Kurve 12 auf, die über ein Zahnrad und eine vom Stellglied 13 oder der angreifenden Federkraft bewegte Zahnstange verdreht wird.In the embodiment shown in FIG. 1, the adjusting device 11 has a rotatable curve 12 which is rotated via a toothed wheel and a toothed rack moved by the actuator 13 or by the spring force applied.
Die im Gehäuse 10 gegengelagerte Kurve 12 kann eine gegen die Reaktionskraft des Hubringes 7 gerichtete hydrostatische Abstützanordnung 20, z. B. eine in Fig.2 gezeigte, mittel- oder unmittelbar vom Förderdruck beaufschlagte, segmentförmige Tasche 21, aufweisen. Vorteihaft kann der Hubring 7 über eine Rollen- oder Kugelanordnung 23 auf der im Gehäuse 10 gegengelagerten schieb- und / oder drehbaren Kurve 12 abgestützt sein.The counter-bearing curve 12 in the housing 10 can be a hydrostatic support arrangement 20 directed against the reaction force of the cam ring 7, e.g. B. have a segment-shaped pocket 21 shown in FIG. 2, acted upon directly or indirectly by the delivery pressure. Advantageously, the cam ring 7 can be supported by means of a roller or ball arrangement 23 on the sliding and / or rotatable curve 12 mounted in the housing 10.
Beide Gestaltungsmerkmale erzielen eine Leichtgängigkeit von dreh- oder schiebbaren Kurven 12, mit der Folge, daß durch die vom Stellglied 13 aufzubringende Stellkraft zum Inbewegungbringen der Kurve 12 gering gehalten werden kann.Both design features achieve smooth movement of rotatable or slidable curves 12, with the result that the actuating force to be applied by the actuator 13 to bring the curve 12 into motion can be kept low.
In Fig.3 ist die Lagerstelle 15 als halbrunde Lagermulde 18 ausgebildet, dabei weist der Hubring 7 ein komplementäres Lagersegment 73 auf, das durch die wirkenden Kräfte am Hubring 7 in die Lagermulde 18 gedrückt wird.In Figure 3, the bearing point 15 is formed as a semicircular bearing recess 18, the cam ring 7 has a complementary bearing segment 73 which is pressed into the bearing recess 18 by the forces acting on the cam ring 7.
Vorteilhaft kann sein, daß sich bei solcher Ausführung der Hubring (7) im Bereich seiner Schwenkachse (SA) in einem radial am Förderraum (6) angrenzenden Umlenkraum (16) befindet, der axial mit einem großen Querschnitt zu einem Förderkanal 17 im Gehäuse 10 verbunden ist. Der Förderraum 8 im Hubring 7 ist über radiale Ein- bzw. Auslaßquerschnitte 71 mit dem Umlenkraum 16 verbunden. Der Erstreckungswinkel der radialen Ein- bzw. Auslaßquerschnitte 71 im Förderraum 8 ist geringer als der Erstreckungswinkel von zusätzlichen radialen Überströmrinnen 72, die sich beidseits der Ein- bzw. Auslaßquerschnitte 71 erstrecken. Mit diesen Überströmrinnen 72 wird ein weiterer Ein- bzw. Auslaßwinkelbereich gewährleistet, jedoch die Lauffläche im Hubring 7 weniger geschmälert.It can be advantageous that, in such an embodiment, the cam ring (7) is located in the region of its pivot axis (SA) in a deflection space (16) radially adjacent to the delivery space (6), which is connected axially with a large cross section to a delivery channel 17 in the housing 10 is. The delivery chamber 8 in the lifting ring 7 is connected to the deflection chamber 16 via radial inlet and outlet cross sections 71. The extension angle of the radial inlet and outlet cross sections 71 in the delivery chamber 8 is smaller than the extension angle of additional radial overflow channels 72 which extend on both sides of the inlet and outlet cross sections 71. With these overflow channels 72, a further inlet or outlet angle range is ensured, but the tread in the cam ring 7 is less narrowed.
Bei der Ausführung nach Fig. 3 ist auf der der Kurve 12 abgewandten Hälfte des Hubringes 7 ein im Gehäuse 10 gelagertes Druckelement 19 angeordnet, welches mit Federkraft oder Förderdruck wirken kann. Eine im Gehäuse 10 gegengelagerte Feder 19 F legt den Druckkolben 19 D kraftschlüssig am Hubring 7 an. Denkbar ist es auch, daß der Druckkolben 19 D mit Fördermedium, vorzugsweise mit Förderdruck PF beaufschlagt ist und sich kraftschlüssig am Hubring 7 anlegt; dies ist jedoch nicht dargestellt.In the embodiment according to FIG. 3, on the half of the cam ring 7 facing away from the curve 12 there is arranged a pressure element 19 which is mounted in the housing 10 and which can act with spring force or delivery pressure. A spring 19 F which is mounted in the housing 10 rests the pressure piston 19 D on the cam ring 7 in a non-positive manner. It is also conceivable for the pressure piston 19 D to be supplied with the conveying medium, preferably with the conveying pressure P F , and to engage the cam ring 7 in a force-fitting manner; however, this is not shown.
Gleichfalls ist es möglich, daß die der Kurve 12 abgewandte Hälfte des Hubringes 7 gegenüber dem Gehäuse 10 abgedichtet und mit Fördermedium beaufschlagt ist und damit ein gesondertes Druckelement 19 ersetzt, siehe Fig. 2.
Vorteilhaft für die Stellvorrichtung 11 ist es, wenn der den Hubring 7 aufnehmende Raum im Gehäuse 10 drucklos ist, die Stelleinrichtung 11 kann dann ohne störende hydraulische Beaufschlagung am Hubring 7 angreifen.
Das Ein- und Ausströmen zu und aus den Förderkammern 6 im Hubring 7 kann in üblicher Weise über axial oder radial mündende Kanäle erfolgen.Likewise, it is possible for the half of the cam ring 7 facing away from the curve 12 to be sealed off from the housing 10 and to be supplied with the conveying medium and thus to replace a separate pressure element 19, see FIG. 2.
It is advantageous for the actuating device 11 if the space in the housing 10 which accommodates the cam ring 7 is depressurized, the actuating device 11 can then act on the cam ring 7 without any disturbing hydraulic action.
The inflow and outflow to and from the delivery chambers 6 in the lifting ring 7 can take place in the usual way via axially or radially opening channels.
Claims (10)
- A volume-controllable vane pump constructed as follows:- vanes (5) are guided for sliding in radial slots in a rotor 4,- the outer ends of the vanes (5) slide in a reciprocating ring (7) containing a delivery chamber,- the reciprocating ring (7) is mounted slidably in a casing (10) or so as to pivot on one side in a stationary bearing on the casing, and when the rotor is stationary a spring presses and holds the ring in a position for maximum delivery and- the ring (7) is in engagement with an actuator (13, 14), the actuating force of which acts against the force (F) of the spring, which is in the direction for maximum delivery,characterised by the following features:- a pressure element (19) engages the reciprocating ring (7) and presses it in the zero-delivery direction against a slidable and/or rotatable cam (12) abutting in the casing (10) and holds the ring in engagement with the cam, and- the slidable and/or rotatable cam (12) is movable by an actuator (13, 14) operated by a pressure-regulating circuit (30) against a spring force (F) in the direction for setting the maximum delivery rate.
- A volume-controllable vane pump according to claim 1,
characterised in that
the cam (12) abutting the casing (10) has a hydrostatic stay arrangement (20) acted upon directly or indirectly by the delivery pressure (PF). - A volume-controllable vane pump according to claim 1,
characterised in that
the reciprocating ring (7) is mounted via a roller or ball arrangement (23) on the slidable and/or rotatable cam (12) abutting in the casing (10). - A volume-controllable vane pump according to claim 1,
characterised in that
the half of the reciprocating ring (7) remote from the cam (12) is sealed from the casing (10) and acted upon by delivery medium and thus constitutes a pressure element. - A volume-controllable vane pump according to claim 1,
characterised in that
a pressure piston (19D) constituting the pressure element (19) and guided in the casing (10) is disposed on and abuts the half of the reciprocating ring (7) remote from the cam (12), wherein the reciprocating piston (19D) is acted upon by delivery medium, preferably at the delivery pressure (pF). - A volume-controllable vane pump according to claim 1,
characterised in that
a spring (19F) abutting the casing on the half of the reciprocating ring (7) remote from the cam (12) co-operates with the pressure piston (19D) to generate the force for the pressure element (19). - A volume-controllable vane pump according to claim 1,
characterised in that
the chamber receiving the reciprocating ring (7) in the casing (10) is not under pressure. - A volume-controllable vane pump according to claim 1,
characterised in that
the reciprocating ring (7), in the region of its axis of rotation (SA), has a guide chamber (16) radially adjoining the delivery chamber (8) and opening axially into a delivery duct (17) in the casing (10). - A volume-controllable vane pump according to claim 1,
characterised in that
the delivery chamber (8) in the reciprocating ring (7) has radial open inlet and outlet cross-sections (71) which extend over a smaller angle than additional radial overflow channels (72). - A volume-controllable vane pump according to claim 1,
characterised in that
the bearing (15) is a semicircular cavity (18) and the reciprocating ring (7) has a complementary bearing segment (73) held in the cavity (18) by the forces acting on the ring (7).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19915739A DE19915739A1 (en) | 1999-04-08 | 1999-04-08 | Variable-speed vane pump |
| DE19915739 | 1999-04-08 |
Publications (3)
| Publication Number | Publication Date |
|---|---|
| EP1043504A2 EP1043504A2 (en) | 2000-10-11 |
| EP1043504A3 EP1043504A3 (en) | 2002-03-27 |
| EP1043504B1 true EP1043504B1 (en) | 2003-09-10 |
Family
ID=7903818
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP00105641A Expired - Lifetime EP1043504B1 (en) | 1999-04-08 | 2000-03-16 | Vane pump with capacity control |
Country Status (2)
| Country | Link |
|---|---|
| EP (1) | EP1043504B1 (en) |
| DE (2) | DE19915739A1 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102005006703A1 (en) * | 2005-02-15 | 2006-08-17 | Audi Ag | Apparatus and method for lubricating oil supply |
| DE102006061326A1 (en) | 2006-12-22 | 2008-07-03 | Beez, Günther, Dipl.-Ing. | Adjusting device for use in e.g. lubricating oil pump in motor vehicle, has control pressure chambers separately controlled and subjected with pump- or main channel pressure and arranged at circumference of control slide valve |
| DE102008048856A1 (en) * | 2008-09-25 | 2010-04-08 | Bayerische Motoren Werke Aktiengesellschaft | Pressure controlling unit, particularly for lubricant cycle of internal-combustion engine, has lubricant pump with changeable displacement volume flow and control piston movable in housing |
Families Citing this family (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10104851A1 (en) * | 2001-02-03 | 2002-08-22 | Zf Lenksysteme Gmbh | Pump system with a hydraulic pump, in particular for a steering system |
| US7108493B2 (en) | 2002-03-27 | 2006-09-19 | Argo-Tech Corporation | Variable displacement pump having rotating cam ring |
| DE10124564A1 (en) * | 2001-05-14 | 2002-11-28 | Joma Hydromechanic Gmbh | Control of variable-displacement lubricant pump for use in internal combustion engine, involves measurement of engine parameters and matching pump delivery to engine requirements |
| DE10292344D2 (en) * | 2001-05-31 | 2004-05-27 | Luk Automobiltech Gmbh & Co Kg | pump |
| FR2833048B1 (en) | 2001-11-30 | 2004-01-16 | Rene Snyders | ROTATING VOLUMETRIC MACHINE OPERATING WITHOUT FRICTION IN THE WORKING VOLUME AND SUPPORTING HIGH PRESSURES AND TEMPERATURES |
| US7247008B2 (en) * | 2002-07-19 | 2007-07-24 | Argo-Tech Corporation | Cam ring bearing for fuel delivery system |
| DE10239364A1 (en) | 2002-08-28 | 2004-03-18 | Dr.Ing.H.C. F. Porsche Ag | Device for controlling the pump output of a lubricant pump for an internal combustion engine |
| ITBO20030528A1 (en) * | 2003-09-12 | 2005-03-13 | Pierburg Spa | PUMPING SYSTEM USING A PALETTE PUMP |
| ITBO20050383A1 (en) * | 2005-06-01 | 2006-12-02 | Pierburg Spa | OIL PUMP CONTROL SYSTEM |
| CN105960531B (en) * | 2013-11-21 | 2018-01-02 | 皮尔伯格泵技术有限责任公司 | Variable-displacement lubricant pump |
| DE102014201572A1 (en) | 2014-01-29 | 2015-07-30 | Robert Bosch Automotive Steering Gmbh | expander |
| DE102014201575A1 (en) | 2014-01-29 | 2015-07-30 | Zf Friedrichshafen Ag | expander |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2318292A (en) | 1941-08-21 | 1943-05-04 | Chandler Evans Corp | Fluid pump |
| US3415058A (en) * | 1967-04-26 | 1968-12-10 | Borg Warner | Hydraulic pump control system |
| US4259039A (en) * | 1979-03-20 | 1981-03-31 | Integral Hydraulic & Co. | Adjustable volume vane-type pump |
| DE3333647C2 (en) * | 1982-09-21 | 1986-10-30 | Glyco-Antriebstechnik Gmbh, 6200 Wiesbaden | Lubricant pump for generating pressure in an internal combustion engine lubricated by pressure circulation |
| JPS59137673A (en) * | 1983-01-25 | 1984-08-07 | Saitama Kiki Kk | Flow-rate control valve |
| IT1167695B (en) | 1983-12-23 | 1987-05-13 | Atos Oleodinamica Spa | VARIABLE DISPLACEMENT VOLUMETRIC VANE PUMP FOR HYDRAULIC FLUID OPERATION |
| DE4011671C2 (en) | 1990-04-11 | 1994-04-28 | Glyco Metall Werke | Adjustable vane pump |
| DE4302610C2 (en) * | 1993-01-30 | 1996-08-08 | Daimler Benz Ag | Process for regulating the pump output of lubricant pumps and lubricant pump therefor |
-
1999
- 1999-04-08 DE DE19915739A patent/DE19915739A1/en not_active Withdrawn
-
2000
- 2000-03-16 DE DE50003605T patent/DE50003605D1/en not_active Expired - Lifetime
- 2000-03-16 EP EP00105641A patent/EP1043504B1/en not_active Expired - Lifetime
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102005006703A1 (en) * | 2005-02-15 | 2006-08-17 | Audi Ag | Apparatus and method for lubricating oil supply |
| DE102006061326A1 (en) | 2006-12-22 | 2008-07-03 | Beez, Günther, Dipl.-Ing. | Adjusting device for use in e.g. lubricating oil pump in motor vehicle, has control pressure chambers separately controlled and subjected with pump- or main channel pressure and arranged at circumference of control slide valve |
| DE102006061326B4 (en) * | 2006-12-22 | 2012-02-16 | Mahle International Gmbh | Positioning device for a volume-adjustable cell pump |
| DE102008048856A1 (en) * | 2008-09-25 | 2010-04-08 | Bayerische Motoren Werke Aktiengesellschaft | Pressure controlling unit, particularly for lubricant cycle of internal-combustion engine, has lubricant pump with changeable displacement volume flow and control piston movable in housing |
Also Published As
| Publication number | Publication date |
|---|---|
| DE19915739A1 (en) | 2000-10-12 |
| EP1043504A2 (en) | 2000-10-11 |
| EP1043504A3 (en) | 2002-03-27 |
| DE50003605D1 (en) | 2003-10-16 |
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