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EP1279834A2 - Vane pump - Google Patents

Vane pump Download PDF

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Publication number
EP1279834A2
EP1279834A2 EP02090283A EP02090283A EP1279834A2 EP 1279834 A2 EP1279834 A2 EP 1279834A2 EP 02090283 A EP02090283 A EP 02090283A EP 02090283 A EP02090283 A EP 02090283A EP 1279834 A2 EP1279834 A2 EP 1279834A2
Authority
EP
European Patent Office
Prior art keywords
rotary vane
pump
rotary
drive shaft
centering
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
EP02090283A
Other languages
German (de)
French (fr)
Other versions
EP1279834B1 (en
EP1279834A3 (en
Inventor
Hermann Lidlgruber
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
LIDLGRUBER, HERMANN
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE20112695U external-priority patent/DE20112695U1/en
Priority claimed from DE2001137415 external-priority patent/DE10137415A1/en
Application filed by Individual filed Critical Individual
Publication of EP1279834A2 publication Critical patent/EP1279834A2/en
Publication of EP1279834A3 publication Critical patent/EP1279834A3/en
Application granted granted Critical
Publication of EP1279834B1 publication Critical patent/EP1279834B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C2/3441—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • F04C2/3442—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0827—Vane tracking; control therefor by mechanical means
    • F01C21/0836—Vane tracking; control therefor by mechanical means comprising guiding means, e.g. cams, rollers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0854—Vane tracking; control therefor by fluid means
    • F01C21/0863—Vane tracking; control therefor by fluid means the fluid being the working fluid
    • 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
    • F04C2230/00—Manufacture
    • F04C2230/60—Assembly methods
    • F04C2230/603—Centering; Aligning

Definitions

  • the invention relates to a rotary vane pump with the features mentioned in the preamble of claims 1 and 12 and a method with the features mentioned in the preamble of claim 19.
  • Circulation pumps including so-called rotary vane pumps or rotary vane cell pumps, are known.
  • Rotary vane pumps have a rotor that has essentially radially movable sealing slides.
  • the sealing slides are usually stored individually and are guided independently in the rotor.
  • the sealing slides are supported either by centrifugal forces or by springs, whereby they are pressed against a peripheral wall of a pump housing.
  • the control ring can be arranged within a rotary vane pump rotor. The pressure and volume flow is caused by the fact that the chamber volume that forms between the sealing slides is used to increase the pressure in the delivery area between the inlet and outlet.
  • a rotary vane pump which has a rotor arranged eccentrically in the cylinder, the pivoting vanes of which are accommodated in axially parallel recesses in the rotor and are placed against the cylinder wall under the action of centrifugal force and, if appropriate, of springs.
  • the rotor also has a number of channels between the rotor and the fully swiveled-in swivel blades.
  • a circulation pump of the type mentioned is furthermore apparent from the published patent application DE 40 12 789 A1.
  • the pump has a rotor with radially displaceable coupled sealing slides, which are guided in a hub.
  • the hub body and the sealing surfaces of the sealing slides in the sealing part between the outlet and inlet and in the delivery area only seal the sealing slides.
  • a suitable pumping method can be achieved by suitable design of radii and curves as well as the sealing slide.
  • the rotary vane pump according to the invention with the features mentioned in claim 1 offers the advantage that at least on one side of the rotary vane rotor a force is input by a centering shaft part, in that the centering shaft part is connected to the rotary vane rotor as a component of a second cover element via fastening elements, thereby extending the drive shaft a drive shaft reinforced in a second diameter is formed. This makes it possible in a simple manner to implement a higher force input on the drive shaft while maintaining the small size.
  • the rotary vane pump according to the invention with the features mentioned in claim 11 offers the advantage that a space formed between the drive shaft and an inner wall of the rotary vane rotor is connected to the pump chamber between two rotary valves in each case via at least one connecting channel, so that force peaks acting on the drive shaft are balanced and one-sided forces acting on the drive shaft are distributed over the entire circumference of the drive shaft.
  • a method with the features mentioned in claim 19 is particularly advantageous in that a partial flow is branched off from a main delivery flow and this partial flow effects the actuation of the rotary valves in the direction of a running surface of a cylinder of the pump.
  • the force input of the rotary valve rotor takes place on both sides via a centering shaft part as a component of the second cover element via fastening elements with the rotary valve rotor, as a result of which a reinforced drive shaft is formed on both sides.
  • the centering shaft part has a centering bolt, which corresponds to a centering hole in the assembled state.
  • the centering shaft part has at least one through hole.
  • the rotary vane rotor has tapped holes that correspond to the through holes.
  • the centering shaft part is connected to the rotary vane rotor via at least one fastening element which engages in the at least one threaded bore hole of the rotary vane rotor via the through bore of the centering shaft part.
  • the centering shaft part engages with its centering bolt in the centering hole of a pump rotor axis part of the drive shaft. It is further preferred that the centering shaft part has a reinforced drive shaft with a second diameter which is larger than the first diameter of the non-reinforced drive shaft.
  • the connecting channels between the space formed by the drive shaft and a rotary vane rotor inner wall and a pumping space are arranged essentially radially to the axis of rotation of the rotary vane rotor. Between this space and the pumping space, the connecting channels effect that from the method according to the invention a partial flow is branched off from a main flow and this partial flow actuates the rotary valve in the direction of a Tread of a cylinder of the pump enables.
  • the rotary vane can be controlled by the acting centrifugal forces and a pressure difference between the space inside the rotary vane rotor and the pump chamber.
  • control rings for the forced control of the rotary slide valve can alternatively be dispensed with in a preferred embodiment of the invention.
  • a rotary vane pump 10 is shown in an upper representation and a lower representation.
  • the upper illustration shows the rotary vane pump 10 in an older version with a first cover element 8A and the lower illustration shows the new solution with a new second cover element 8B.
  • the housing of the rotary vane pump 10 in different variants.
  • the first variant is to close the cylinder 1 on both sides with the first cover element 8A.
  • the second variant corresponding to FIG. 1, consists in closing the rotary vane pump 10 on one side with the first cover element 8A and on the other side with the second cover element 8B and a centering shaft part 13 according to the invention, which is part of the second cover element.
  • Figure 1 shows both of these possible variants.
  • a rotary vane rotor 3 is arranged in the rotary vane pump 10 and can be rotated in both directions about an eccentric axis of rotation 20.
  • the rotary vane rotor 3 has a pump rotor axis part 15 which merges into a drive shaft 7.
  • the drive shaft 7 has a first diameter d1.
  • FIG. 1 further shows that the rotary vane rotor 3 is arranged centered on the one hand in the first cover element 8A and on the other hand via a centering hole 16 on a centering pin 14 via its pump rotor axis part 15.
  • the centering hole 16 and the centering pin 14 correspond to one another and are preferably connected to one another in a fitting connection.
  • the centering pin 14 belongs to the centering shaft part 13, which forms an extended, reinforced drive shaft 7 ′ with a second diameter d2 in the extension of the drive shaft 7.
  • the power transmission of the rotary vane rotor 3 takes place through the centering shaft part 13 in that through holes 23 for fastening elements 24, preferably threaded screws, are located in the centering shaft part 13.
  • Correspondingly tapped holes 6 are arranged in the rotary vane rotor 3.
  • the rotary vane rotor 3 is connected to the centering shaft part 13 by screw connections. A power flow can thus be realized via this connection.
  • the centering shaft part 13 thus forms the reinforced drive shaft 7 '.
  • the drive shaft 7 ' which, as already mentioned above, can be implemented via the centering shaft part 13 and the second cover element 8B on both sides of the rotary vane rotor 3, has a larger second diameter d2.
  • This second diameter d2 is, for example, 18 mm.
  • the drive shaft 7 ' can also be designed in the second diameter d2 with 20 mm or 25 mm and more.
  • the first diameter d1 is, for example, only 12 mm. With a first diameter d1 and high pressures, for example 20 bar, a simple reinforcement by increasing the diameter d1 of the drive shaft 7 is no longer sufficiently stable without the centering shaft part 13. The solution according to the invention is therefore used particularly for higher pressures.
  • the rotary vane pump 10 can be manufactured variably. It is variable with regard to the combination of the first cover element 8A and the combination of the centering shaft part 13 and the second cover element 8B and also in the design of different diameters d1 and d2 of the drive shaft 7 or drive shaft 7 '.
  • the centering shaft part 13 is covered with respect to the cylinder 1 with the second cover element 8B and forms a guide 25 for the reinforced drive shaft 7 '.
  • the solution according to the invention also includes the arrangement of connecting channels 5 in the rotary vane rotor 3.
  • a pressure distribution in the housing of the rotary vane pump 10 can be achieved through the connecting channels 5.
  • the forces acting on the drive shaft 7 or 7 ' are equalized and force peaks are compensated for. There is no one-sided force input into the drive shaft 7 or 7 '. This prevents fatigue breaks and high wear on one side.
  • connection channels 5 are of further importance, which emerges in particular from FIG. 2 and will be discussed later.
  • FIG. 1 first shows a first space 4A and a second space 4B between the drive shaft 7 and the rotary vane rotor inner wall 21.
  • a first control ring 9A and a second control ring 9B can be arranged in the first or second space 4A or 4B.
  • the first control ring 9A and the second control ring 9B force control of rotary valves 18, which are not shown in Figure 1.
  • FIG. 1 also shows the pump chamber 19 between a rotary vane rotor outer wall 17 and a running surface 2 of the cylinder 1.
  • the pump chamber 19 and the first chamber 4A and a second chamber 4B are connected to one another via the connecting channels 5. Therefore, pressure equalization takes place here via the connecting channels 5.
  • Figure 2 shows a section A-A through the rotary vane pump 10.
  • the same reference numerals designate the same parts as in Figure 1.
  • FIG. 2 shows an inlet 11 and an outlet 12 on both sides, since the rotary vane pump 10 can optionally be operated in both directions about the axis of rotation 20.
  • the cylinder 1 can also be seen, in which the inlet 11 and the outlet 12 are arranged offset by 90 ° to the drive shaft 7.
  • the centering pin 14 can also be seen in the centering hole 16 of the drive shaft 7.
  • the second control ring 9B can be seen.
  • the control ring 9A lies behind the control ring 9B and is not visible in FIG. 2.
  • the second control ring 9B runs on the eccentric axis of rotation 20 on the drive shaft 7 in space 4B.
  • the space 4B is connected to the pump space 19 and the inlet area 11 and the outlet area 12 via the connection channels 5.
  • the rotary slide valves 18 are movably guided in hubs 22 in the rotary slide rotor 3.
  • the pump chamber 19 is formed between two rotary slide valves 18 between the rotary slide rotor outer wall 17 and the running surface 2 of the cylinder 1.
  • the mode of operation of the rotary vane pump 10 is explained in accordance with FIG. 2 as follows.
  • the rotary valves 18 are mechanically pushed out of the rotary valve rotor 3, so that the pump chamber 19 is created.
  • the rotary valve 18 is pressed into the rotary valve rotor 3 by the eccentric axis of rotation 20 on the running surface 2 of the cylinder 1.
  • the connection channels 5 are arranged, there is also pressure equalization between the first and second spaces 4A and 4B.
  • a partial flow TS of a main flow HS is pressed into the first and second spaces 4A and 4B.
  • This mode of operation relieves the drive shaft 7, on the one hand, and, on the other hand, gives the possibility of actuating the rotary slide valve 18 in the direction of the running surface 2 of the cylinder 1.
  • the mode of operation can be implemented without the first and second control rings 9A and 9B if connecting channels 5 are arranged.
  • first and second control rings 9A and 9B are alternatively dispensed with, the connecting channels 5 alone enable the rotary slide valves 18 to be actuated.
  • the rotary slide valves 18 are pressed outward from the direction of the first and second chamber 4A and 4B in addition to the centrifugal forces acting.
  • the partial flow TS will flow into the interior of the rotary vane rotor 3 in the first and second spaces 4A and 4b.
  • a partial flow TS will flow from the first and second spaces 4A and 4B into the area between the rotary vane rotor outer wall 17 and cylinder 1 as a function of a pressure difference.
  • the volume flow of the partial flow TS is also dependent on a diameter of the connecting channels 5.
  • the rotary vane pump can be used for the following industries. It is used in the chemical industry for alkalis, gases and viscous liquids. In the food industry, for example, it can be used as a honey, mustard, jam and syrup pump. There is also a field of application in the field of medical technology as a metering pump and in the fire service as a spray pump. For disaster relief, the rotary vane pump can be used to pump out used oils at sea or to pump out floods in the event of flooding. There are further possible uses in agriculture and environmental technology for irrigating fields or as a pressure booster for a photovoltaic system. These areas of application are only examples and can be expanded for other areas.

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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)

Abstract

The pump has a housing of cylinder (1) and cover (8A), and a rotor (3) with rotary slides. There is power introduction on at least one side of the rotor via a centering shaft section (13). The section forms part of a further cover element (8B) and is connected to the rotor via fastener elements, so that in extension of the drive shaft (7), a drive shaft (7') with second increased diameter (d2) is formed. A chamber (4) formed between drive shaft and internal rotor wall (21) is connected via channels (5) to the pump chamber (19) between two rotary slides.

Description

Die Erfindung betrifft eine Drehschieberpumpe mit den im Oberbegriff der Ansprüche 1 und 12 sowie ein Verfahren mit den im Oberbegriff des Anspruchs 19 genannten Merkmalen.The invention relates to a rotary vane pump with the features mentioned in the preamble of claims 1 and 12 and a method with the features mentioned in the preamble of claim 19.

Umlaufpumpen, darunter so genannte Drehschieberpumpen oder auch Drehflügelzellenpumpen, sind bekannt.Circulation pumps, including so-called rotary vane pumps or rotary vane cell pumps, are known.

Drehschieberpumpen besitzen einen Rotor, der im Wesentlichen radial bewegbare Dichtschieber aufweist. Die Dichtschieber werden in der Regel einzeln gelagert und sind voneinander unabhängig im Rotor geführt. Die Dichtschieber werden entweder durch Fliehkräfte oder durch Federn unterstützt, wodurch sie an einer Umfangswand eines Pumpengehäuses gedrückt werden. Bekannt ist zudem, so genannte Innenkurven oder Steuerringe vorzusehen, so dass die Dichtschieber am äußeren Umfang des mindestens eines Steuerrings an der Innenwand des Pumpengehäuses zwangsgeführt werden. Dabei kann der Steuerring innerhalb eines Drehschieberpumpenrotors angeordnet sein. Der Druckund Volumenstrom wird dadurch bewirkt, dass das sich zwischen den Dichtschiebern bildende Kammervolumen im Förderbereich zwischen Einlass und Auslass zur Druckerhöhung verwendet wird.Rotary vane pumps have a rotor that has essentially radially movable sealing slides. The sealing slides are usually stored individually and are guided independently in the rotor. The sealing slides are supported either by centrifugal forces or by springs, whereby they are pressed against a peripheral wall of a pump housing. It is also known to provide so-called inner curves or control rings, so that the sealing slides on the outer circumference of the at least one control ring are positively guided on the inner wall of the pump housing. The control ring can be arranged within a rotary vane pump rotor. The pressure and volume flow is caused by the fact that the chamber volume that forms between the sealing slides is used to increase the pressure in the delivery area between the inlet and outlet.

Aus dem Gebrauchsmuster 85 011 40 U1 ist beispielsweise eine Drehflügelpumpe bekannt, die einen exzentrisch im Zylinder angeordneten Rotor aufweist, dessen Schwenkflügel in achsparallele Ausnehmungen des Rotors aufgenommen und unter Wirkung der Fliehkraft und gegebenenfalls von Federn gegen die Zylinderwand angelegt sind. Der Rotor weist zudem bei voll eingeschwenkten Schwenkflügeln zwischen Rotor und den voll eingeschwenkten Schwenkflügeln eine Anzahl von Kanälen auf.From utility model 85 011 40 U1, for example, a rotary vane pump is known which has a rotor arranged eccentrically in the cylinder, the pivoting vanes of which are accommodated in axially parallel recesses in the rotor and are placed against the cylinder wall under the action of centrifugal force and, if appropriate, of springs. The rotor also has a number of channels between the rotor and the fully swiveled-in swivel blades.

Aus dem Stand der Technik geht weiterhin aus der Offenlegungsschrift DE 40 12 789 A1 eine Umlaufpumpe der genannten Art hervor. Die Pumpe besitzt einen Läufer mit radial verschiebbaren gekoppelten Dichtschiebern, die in einer Nabe verschiebbar geführt sind. Dabei dichten der Nabenkörper und die Dichtflächen der Dichtschieber im Dichtteil zwischen Auslass und Einlass und im Förderbereich nur die Dichtschieber ab. Durch geeignete Gestaltung von Radien und Kurven sowie der Dichtschieber kann eine schonende Pumpweise erzielt werden.From the prior art, a circulation pump of the type mentioned is furthermore apparent from the published patent application DE 40 12 789 A1. The pump has a rotor with radially displaceable coupled sealing slides, which are guided in a hub. The hub body and the sealing surfaces of the sealing slides in the sealing part between the outlet and inlet and in the delivery area only seal the sealing slides. A suitable pumping method can be achieved by suitable design of radii and curves as well as the sealing slide.

Für die Drehschieberpumpen gilt, dass die Kräfte, die die Drehschieber auf den Drehschieberrotor und damit auf die Antriebswelle übertragen, dadurch begrenzt sind, dass die mögliche Kraftaufnahme der Antriebswelle nicht überschritten wird. Insbesondere zur Realisierung kleiner Baugrößen von Drehschieberpumpen mit hohen Leistungen und Fördervolumen, die durch Anordnung der Schieber mit möglichst großer wirksamer Schieberfläche im Förderbereich der Drehschieberpumpe und hohen Drehzahlen erreicht werden, sind die Kräfte, die die Antriebswelle aufnehmen kann, schnell erreicht. Nachteilig bei den bekannten Lösungen ist es, dass die wirksamen Schieberflächen zum einen nicht weiter erhöht werden können und dadurch kleinere Drehzahlen zu Gunsten einer schonenden Förderung eines Fördermediums nicht eingestellt werden können, um bestimmte Drücke und Fördervolumina zu erreichen. Besonders bei Ausführungen von Drehschieberpumpen mit exzentrisch angeordneter Antriebswelle sind die Kräfte, die auf den Drehschieberrotor und damit auf die Drehschieberpumpe wirken, ungünstig verteilt. Wünschenswert sind geringe Drehzahlen mit gleichzeitig hohen Förderleistungen und Förderdrücken, wodurch eine energiesparende Förderung der Drehschieberpumpe gewährleistet wäre. Diese Merkmale, gepaart mit einer besonders platzsparenden Bauweise, können die aus dem Stand der Technik bekannten Umlaufpumpen nicht offenbaren.For rotary vane pumps, the force that the rotary vane transmits to the rotary vane rotor and thus to the drive shaft is limited by the fact that the possible force absorption of the drive shaft is not exceeded. In particular for realizing small sizes of rotary vane pumps with high outputs and delivery volumes, which are achieved by arranging the slide with the largest possible effective slide area in the delivery area of the rotary vane pump and high speeds, the forces that the drive shaft can absorb are quickly reached. A disadvantage of the known solutions is that, on the one hand, the effective slide areas cannot be increased further, and therefore lower speeds cannot be set in favor of gentle conveying of a conveying medium in order to achieve certain pressures and conveying volumes. Particularly in the case of designs of rotary vane pumps with an eccentrically arranged drive shaft, the forces acting on the rotary vane rotor and thus on the rotary vane pump are unfavorably distributed. Low speeds with high delivery rates and delivery pressures are desirable, which would ensure energy-saving delivery of the rotary vane pump. These features, coupled with a particularly space-saving design, cannot be disclosed by the circulating pumps known from the prior art.

Es ist deshalb die Aufgabe der vorliegenden Erfindung, eine Drehschieberpumpe anzubieten, die es mit ihren erfindungsgemäße Merkmalen gestattet, bei schonender Pumpweise und minimaler Baugröße sehr hohe Förderdrücke und Fördervolumina zu realisieren.It is therefore the object of the present invention to offer a rotary vane pump which, with its features according to the invention, allows very high delivery pressures and delivery volumes to be achieved with a gentle pumping method and minimal size.

Die erfindungsgemäße Drehschieberpumpe mit den im Anspruch 1 genannten Merkmalen bietet demgegenüber den Vorteil, dass mindestens auf einer Seite des Drehschieberrotors ein Krafteintrag durch ein Zentrierwellenteil erfolgt, indem das Zentrierwellenteil als Bestandteil eines zweiten Abdeckelementes über Befestigungselemente mit dem Drehschieberrotor verbunden ist, wodurch in Verlängerung der Antriebswelle eine, in einem zweiten Durchmesser verstärkte Antriebswelle, ausgebildet ist. Dadurch ist es in einfacher Weise möglich, unter Beibehaltung der geringen Baugröße einen höheren Krafteintrag auf die Antriebswelle zu realisieren.The rotary vane pump according to the invention with the features mentioned in claim 1 offers the advantage that at least on one side of the rotary vane rotor a force is input by a centering shaft part, in that the centering shaft part is connected to the rotary vane rotor as a component of a second cover element via fastening elements, thereby extending the drive shaft a drive shaft reinforced in a second diameter is formed. This makes it possible in a simple manner to implement a higher force input on the drive shaft while maintaining the small size.

Die erfindungsgemäße Drehschieberpumpe mit den im Anspruch 11 genannten Merkmalen bietet den Vorteil, dass ein zwischen der Antriebswelle und einer Drehschieberrotor-Innenwand gebildeter Raum über mindestens einen Verbindungskanal mit dem Pumpraum zwischen jeweils zwei Drehschiebern verbunden ist, so dass auf die Antriebswelle wirkende Kraftspitzen ausgeglichen und einseitig auf die Antriebswelle wirkende Kräfte auf den gesamten Umfang der Antriebswelle verteilt werden.The rotary vane pump according to the invention with the features mentioned in claim 11 offers the advantage that a space formed between the drive shaft and an inner wall of the rotary vane rotor is connected to the pump chamber between two rotary valves in each case via at least one connecting channel, so that force peaks acting on the drive shaft are balanced and one-sided forces acting on the drive shaft are distributed over the entire circumference of the drive shaft.

Zudem ist in Verbindung mit Anspruch 11 ein Verfahren mit den im Anspruch 19 genannten Merkmalen von besonderem Vorteil, dass aus einem Hauptförderstrom ein Teilstrom abgezweigt wird und dieser Teilstrom die Betätigung der Drehschieber in Richtung einer Lauffläche eines Zylinders der Pumpe bewirkt.In addition, in connection with claim 11, a method with the features mentioned in claim 19 is particularly advantageous in that a partial flow is branched off from a main delivery flow and this partial flow effects the actuation of the rotary valves in the direction of a running surface of a cylinder of the pump.

Bevorzugt ist, dass der Krafteintrag des Drehschieberrotors auf beiden Seiten über ein Zentrierwellenteil als Bestandteil des zweiten Abdeckelementes über Befestigungselemente mit dem Drehschieberrotor erfolgt, wodurch beidseitig eine verstärkte Antriebswelle ausgebildet ist. Dazu weist das Zentrierwellenteil einen Zentrierbolzen auf, welcher im montierten Zustand mit einem Zentrierloch korrespondiert. Zudem weist das Zentrierwellenteil mindestens eine Durchgangsbohrung auf. Der Drehschieberrotor weist Gewindebohrlöcher auf, die mit den Durchgangsbohrungen korrespondieren. Das Zentrierwellenteil ist mit dem Drehschieberrotor über mindestens ein Befestigungselement, welches über die Durchgangsbohrung des Zentrierwellenteils in das mindestens eine Gewindebohrloch des Drehschieberrotors eingreift, verbunden.It is preferred that the force input of the rotary valve rotor takes place on both sides via a centering shaft part as a component of the second cover element via fastening elements with the rotary valve rotor, as a result of which a reinforced drive shaft is formed on both sides. For this purpose, the centering shaft part has a centering bolt, which corresponds to a centering hole in the assembled state. In addition, the centering shaft part has at least one through hole. The rotary vane rotor has tapped holes that correspond to the through holes. The centering shaft part is connected to the rotary vane rotor via at least one fastening element which engages in the at least one threaded bore hole of the rotary vane rotor via the through bore of the centering shaft part.

In einer bevorzugten Ausgestaltung der Erfindung greift das Zentrierwellenteil mit seinem Zentrierbolzen in das Zentrierloch eines Pumpenrotorachsenteiles der Antriebswelle ein.
Bevorzugt ist ferner, dass das Zentrierwellenteil eine verstärkte Antriebswelle mit einem zweiten Durchmesser aufweist, welcher größer als der erste Durchmesser der nicht verstärkten Antriebswelle ist.In a preferred embodiment of the invention, the centering shaft part engages with its centering bolt in the centering hole of a pump rotor axis part of the drive shaft.
It is further preferred that the centering shaft part has a reinforced drive shaft with a second diameter which is larger than the first diameter of the non-reinforced drive shaft.

In bevorzugter Ausführung der Erfindung sind die Verbindungskanäle zwischen dem von der Antriebswelle und einer Drehschieberrotor-Innenwand gebildeten Raum und einem Pumpraum im Wesentlichen radial zu der Drehachse des Drehschieberrotors angeordnet.. Zwischen diesem Raum und dem Pumpraum bewirken die Verbindungskanäle nach dem erfindungsgemäßen Verfahren, dass aus einem Hauptförderstrom ein Teilstrom abgezweigt wird und dieser Teilstrom die Betätigung der Drehschieber in Richtung einer Lauffläche eines Zylinders der Pumpe ermöglicht. Die Drehschieber sind durch die wirkenden Fliehkräfte und einer Druckdifferenz zwischen dem Raum im Innern des Drehschieberrotors und dem Pumpraum steuerbar.In a preferred embodiment of the invention, the connecting channels between the space formed by the drive shaft and a rotary vane rotor inner wall and a pumping space are arranged essentially radially to the axis of rotation of the rotary vane rotor. Between this space and the pumping space, the connecting channels effect that from the method according to the invention a partial flow is branched off from a main flow and this partial flow actuates the rotary valve in the direction of a Tread of a cylinder of the pump enables. The rotary vane can be controlled by the acting centrifugal forces and a pressure difference between the space inside the rotary vane rotor and the pump chamber.

Durch diese erfindungsgemäße Lösung kann in bevorzugter Ausgestaltung der Erfindung alternativ auf angeordnete Steuerringe zur Zwangssteuerung der Drehschieber verzichtet werden.By means of this solution according to the invention, arranged control rings for the forced control of the rotary slide valve can alternatively be dispensed with in a preferred embodiment of the invention.

Weitere bevorzugte Ausgestaltungen der Erfindung ergeben sich aus den übrigen, in den Unteransprüchen genannten Merkmalen.Further preferred embodiments of the invention result from the other features mentioned in the subclaims.

Die Erfindung wird nachfolgend in einem Ausführungsbeispiel anhand der zugehörigen Zeichnungen näher erläutert. Es zeigen:

  • Figur 1 einen Schnitt in einer Draufsicht auf eine Drehschieberpumpe in bisheriger und neuer Ausführung und
  • Figur 2 einen Schnitt A-A in einer Seitenansicht.
The invention is explained in more detail in an exemplary embodiment with reference to the accompanying drawings. Show it:
  • 1 shows a section in a plan view of a rotary vane pump in the previous and new design and
  • Figure 2 shows a section AA in a side view.

In Figur 1 ist eine Drehschieberpumpe 10 in einer oberen Darstellung und einer unteren Darstellung gezeigt. Die obere Darstellung zeigt die Drehschieberpumpe 10 in einer älteren Version mit einem ersten Abdeckelement 8A und die untere Darstellung die neue Lösung mit einem neuen zweiten Abdeckelement 8B.In Figure 1, a rotary vane pump 10 is shown in an upper representation and a lower representation. The upper illustration shows the rotary vane pump 10 in an older version with a first cover element 8A and the lower illustration shows the new solution with a new second cover element 8B.

Grundsätzlich besteht die Möglichkeit, das Gehäuse der Drehschieberpumpe 10 in verschiedenen Varianten auszuführen. Die erste Variante ist wie bisher, den Zylinder 1 auf beiden Seiten mit dem ersten Abdeckelement 8A zu verschließen. Die zweite Variante, entsprechend Figur 1, besteht darin, die Drehschieberpumpe 10 auf einer Seite mit dem ersten Abdeckelement 8A und auf der anderen Seite mit dem zweiten Abdeckelement 8B und einem erfindungsgemäßen Zentrierwellenteil 13, welches Bestandteil des zweites Abdeckelementes ist, zu verschließen. Zur Verdeutlichung zeigt Figur 1 beide dieser möglichen Varianten.Basically, there is the possibility of designing the housing of the rotary vane pump 10 in different variants. As before, the first variant is to close the cylinder 1 on both sides with the first cover element 8A. The second variant, corresponding to FIG. 1, consists in closing the rotary vane pump 10 on one side with the first cover element 8A and on the other side with the second cover element 8B and a centering shaft part 13 according to the invention, which is part of the second cover element. For clarification, Figure 1 shows both of these possible variants.

In der Drehschieberpumpe 10 ist ein Drehschieberrotor 3 angeordnet, der um eine exzentrische Drehachse 20 in beide Richtungen drehbar ist. Der Drehschieberrotor 3 besitzt ein Pumpenrotorachsenteil 15, welches in eine Antriebswelle 7 übergeht. Die Antriebswelle 7 besitzt einen ersten Durchmesser d1. Figur 1 zeigt ferner, dass der Drehschieberrotor 3 über sein Pumpenrotorachsenteil 15 zum einen in dem ersten Abdeckelement 8A und zum anderen über ein Zentrierloch 16 an einem Zentrierbolzen 14 zentriert angeordnet ist. Das Zentrierloch 16 und der Zentrierbolzen 14 korrespondieren miteinander und sind vorzugsweise in einer Passverbindung miteinander verbunden.
Der Zentrierbolzen 14 gehört zu dem Zentrierwellenteil 13, welches in Verlängerung der Antriebswelle 7 eine verlängerte, verstärkte Antriebswelle 7' mit einem zweiten Durchmesser d2 ausbildet. Die Kraftübertragung des Drehschieberrotors 3 erfolgt durch das Zentrierwellenteil 13 dadurch, dass sich im Zentrierwellenteil 13 Durchgangsbohrungen 23 für Befestigungselemente 24, vorzugsweise Gewindeschrauben, befinden. Im Drehschieberrotor 3 sind korrespondierend Gewindebohrlöcher 6 angeordnet. Durch Schraubverbindungen ist der Drehschieberrotor 3 mit dem Zentrierwellenteil 13 verbunden. Somit ist ein Kraftfluss über diese Verbindung realisierbar. Das Zentrierwellenteil 13 bildet somit die verstärkte Antriebswelle 7' aus.A rotary vane rotor 3 is arranged in the rotary vane pump 10 and can be rotated in both directions about an eccentric axis of rotation 20. The rotary vane rotor 3 has a pump rotor axis part 15 which merges into a drive shaft 7. The drive shaft 7 has a first diameter d1. FIG. 1 further shows that the rotary vane rotor 3 is arranged centered on the one hand in the first cover element 8A and on the other hand via a centering hole 16 on a centering pin 14 via its pump rotor axis part 15. The centering hole 16 and the centering pin 14 correspond to one another and are preferably connected to one another in a fitting connection.
The centering pin 14 belongs to the centering shaft part 13, which forms an extended, reinforced drive shaft 7 ′ with a second diameter d2 in the extension of the drive shaft 7. The power transmission of the rotary vane rotor 3 takes place through the centering shaft part 13 in that through holes 23 for fastening elements 24, preferably threaded screws, are located in the centering shaft part 13. Correspondingly tapped holes 6 are arranged in the rotary vane rotor 3. The rotary vane rotor 3 is connected to the centering shaft part 13 by screw connections. A power flow can thus be realized via this connection. The centering shaft part 13 thus forms the reinforced drive shaft 7 '.

Wie aus Figur 1 weiter hervorgeht, besitzt die Antriebswelle 7', die, wie bereits oben erwähnt, über das Zentrierwellenteil 13 und das zweite Abdeckelement 8B auf beiden Seiten des Drehschieberrotors 3 ausführbar ist, einen größeren zweiten Durchmesser d2. Dieser zweite Durchmesser d2 beträgt beispielsweise 18 mm. Die Antriebswelle 7' kann aber auch in dem zweiten Durchmesser d2 mit 20 mm oder 25 mm und mehr ausgeführt werden. Der erste Durchmesser d1 beträgt beispielsweise nur 12 mm. Bei einem ersten Durchmesser d1 und hohen Drücken, beispielsweise 20 bar, ist eine einfache Verstärkung über Erhöhung des Durchmessers d1 der Antriebswelle 7 ohne Zentrierwellenteil 13 nicht mehr ausreichend stabil genug. Die erfindungsgemäße Lösung kommt also besonders für höhere Drücke zum Einsatz.As can further be seen from FIG. 1, the drive shaft 7 ', which, as already mentioned above, can be implemented via the centering shaft part 13 and the second cover element 8B on both sides of the rotary vane rotor 3, has a larger second diameter d2. This second diameter d2 is, for example, 18 mm. The drive shaft 7 'can also be designed in the second diameter d2 with 20 mm or 25 mm and more. The first diameter d1 is, for example, only 12 mm. With a first diameter d1 and high pressures, for example 20 bar, a simple reinforcement by increasing the diameter d1 of the drive shaft 7 is no longer sufficiently stable without the centering shaft part 13. The solution according to the invention is therefore used particularly for higher pressures.

Je nach Bedarf und Arbeitsweise ist die Drehschieberpumpe 10 variabel herstellbar. Sie ist variabel bezüglich der Kombination aus erstem Abdeckelement 8A und der Kombination Zentrierwellenteil 13 und zweites Abdeckelement 8B und zudem in der Ausführung unterschiedlicher Durchmesser d1 und d2 der Antriebswelle 7 beziehungsweise Antriebswelle 7'.Depending on the need and working method, the rotary vane pump 10 can be manufactured variably. It is variable with regard to the combination of the first cover element 8A and the combination of the centering shaft part 13 and the second cover element 8B and also in the design of different diameters d1 and d2 of the drive shaft 7 or drive shaft 7 '.

Das Zentrierwellenteil 13 ist gegenüber dem Zylinder 1 mit dem zweiten Abdeckelement 8B abgedeckt und bildet eine Führung 25 für die verstärkte Antriebswelle 7'.The centering shaft part 13 is covered with respect to the cylinder 1 with the second cover element 8B and forms a guide 25 for the reinforced drive shaft 7 '.

Die erfindungsgemäße Lösung beinhaltet zudem die Anordnung von Verbindungskanälen 5 im Drehschieberrotor 3. Durch die Verbindungskanäle 5 ist eine Druckverteilung im Gehäuse der Drehschieberpumpe 10 bewirkbar. Die Kräfte, die auf die Antriebswelle 7 beziehungsweise 7' wirken, werden vergleichmäßigt und Kraftspitzen werden ausgeglichen. Es kommt nicht zu einem einseitigen Krafteintrag in die Antriebswelle 7 beziehungsweise 7'. Ermüdungsbrüche und einseitiger hoher Verschleiß werden dadurch vermieden.The solution according to the invention also includes the arrangement of connecting channels 5 in the rotary vane rotor 3. A pressure distribution in the housing of the rotary vane pump 10 can be achieved through the connecting channels 5. The forces acting on the drive shaft 7 or 7 'are equalized and force peaks are compensated for. There is no one-sided force input into the drive shaft 7 or 7 '. This prevents fatigue breaks and high wear on one side.

Ferner kommt den Verbindungskanälen 5 eine weitere Bedeutung zu, die insbesondere aus Figur 2 hervorgeht und auf die später eingegangen wird.Furthermore, the connection channels 5 are of further importance, which emerges in particular from FIG. 2 and will be discussed later.

Figur 1 zeigt zunächst zwischen Antriebswelle 7 und Drehschieberrotor-Innenwand 21 einen ersten Raum 4A und einen zweiten Raum 4B. In dem ersten beziehungsweise zweiten Raum 4A beziehungsweise 4B kann alternativ ein erster Steuerring 9A und ein zweiter Steuerring 9B angeordnet sein. Durch den ersten Steuerring 9A und den zweiten Steuerring 9B erfolgt eine Zwangssteuerung von Drehschiebern 18, die in Figur 1 nicht dargestellt sind.FIG. 1 first shows a first space 4A and a second space 4B between the drive shaft 7 and the rotary vane rotor inner wall 21. Alternatively, a first control ring 9A and a second control ring 9B can be arranged in the first or second space 4A or 4B. The first control ring 9A and the second control ring 9B force control of rotary valves 18, which are not shown in Figure 1.

Figur 1 zeigt weiterhin den Pumpraum 19 zwischen einer Drehschieberrotor-Außenwand 17 und einer Lauffläche 2 des Zylinders 1.FIG. 1 also shows the pump chamber 19 between a rotary vane rotor outer wall 17 and a running surface 2 of the cylinder 1.

Der Pumpraum 19 und der erste Raum 4A und ein zweiter Raum 4B sind über die Verbindungskanäle 5 miteinander verbunden. Deshalb findet hier über die Verbindungskanäle 5 ein Druckausgleich statt.The pump chamber 19 and the first chamber 4A and a second chamber 4B are connected to one another via the connecting channels 5. Therefore, pressure equalization takes place here via the connecting channels 5.

Figur 2 zeigt einen Schnitt A-A durch die Drehschieberpumpe 10. Gleiche Bezugszeichen bezeichnen gleiche Teile wie in Figur 1.Figure 2 shows a section A-A through the rotary vane pump 10. The same reference numerals designate the same parts as in Figure 1.

Figur 2 zeigt einen Einlass 11 und einen Auslass 12 auf beiden Seiten, da die Drehschieberpumpe 10 wahlweise in beide Richtungen um die Drehachse 20 betreibbar ist.FIG. 2 shows an inlet 11 and an outlet 12 on both sides, since the rotary vane pump 10 can optionally be operated in both directions about the axis of rotation 20.

Ersichtlich ist weiterhin der Zylinder 1, in dem um 90° zur Antriebswelle 7 versetzt der Einlass 11 und der Auslass 12 angeordnet sind. Ferner ersichtlich ist der Zentrierbolzen 14 im Zentrierloch 16 der Antriebswelle 7. Auf der Antriebswelle 7 ist der zweite Steuerring 9B ersichtlich. Der Steuerring 9A liegt hinter dem Steuerring 9B und ist in Figur 2 nicht sichtbar. Der zweite Steuerring 9B läuft auf der exzentrischen Drehachse 20 auf der Antriebswelle 7 im Raum 4B. Der Raum 4B ist über die Verbindungskanäle 5 mit dem Pumpraum 19 und dem Einlassbereich 11 und dem Auslassbereich 12 verbunden. Die Drehschieber 18 sind in Naben 22 im Drehschieberrotor 3 beweglich geführt.The cylinder 1 can also be seen, in which the inlet 11 and the outlet 12 are arranged offset by 90 ° to the drive shaft 7. The centering pin 14 can also be seen in the centering hole 16 of the drive shaft 7. On the Drive shaft 7, the second control ring 9B can be seen. The control ring 9A lies behind the control ring 9B and is not visible in FIG. 2. The second control ring 9B runs on the eccentric axis of rotation 20 on the drive shaft 7 in space 4B. The space 4B is connected to the pump space 19 and the inlet area 11 and the outlet area 12 via the connection channels 5. The rotary slide valves 18 are movably guided in hubs 22 in the rotary slide rotor 3.

Zwischen zwei Drehschiebern 18 bildet sich der Pumpraum 19 zwischen der Drehschieberrotor-Außenwand 17 und der Lauffläche 2 des Zylinder 1 aus.The pump chamber 19 is formed between two rotary slide valves 18 between the rotary slide rotor outer wall 17 and the running surface 2 of the cylinder 1.

Ersichtlich sind weiterhin die Gewindebohrlöcher 6 im Drehschieberrotor 3 an dem - wie Figur 1 zeigt - mittels der Befestigungselemente 24 der Zentrierwellenteil 13 über seine Durchgangsbohrungen 23 befestigt wird und der Kraftfluss auf die verstärkte Antriebswelle 7' umgeleitet wird.Also visible are the tapped holes 6 in the rotary vane rotor 3 to which - as shown in FIG. 1 - the centering shaft part 13 is fastened by means of the fastening elements 24 via its through bores 23 and the power flow is redirected to the reinforced drive shaft 7 '.

Die Wirkungsweise der Drehschieberpumpe 10 ist entsprechend der Figur 2 erläutert Folgende. Bei Einsatz der ersten und zweiten Steuerringe 9A beziehungsweise 9B werden die Drehschieber 18 aus dem Drehschieberrotor 3 mechanisch herausgedrückt, so dass der Pumpraum 19 entsteht. Im oberen Bereich werden die Drehschieber 18 durch die exzentrische Drehachse 20 an der Lauffläche 2 des Zylinders 1 in den Drehschieberrotor 3 hineingedrückt. Bei Anordnung der Verbindungskanäle 5 findet zudem ein Druckausgleich zwischen den ersten und zweiten Räumen 4A und 4B statt. Zudem wird ein Teilstrom TS eines Hauptstromes HS in die ersten und zweiten Räumen 4A und 4B hineingedrückt.The mode of operation of the rotary vane pump 10 is explained in accordance with FIG. 2 as follows. When using the first and second control rings 9A and 9B, the rotary valves 18 are mechanically pushed out of the rotary valve rotor 3, so that the pump chamber 19 is created. In the upper region, the rotary valve 18 is pressed into the rotary valve rotor 3 by the eccentric axis of rotation 20 on the running surface 2 of the cylinder 1. When the connection channels 5 are arranged, there is also pressure equalization between the first and second spaces 4A and 4B. In addition, a partial flow TS of a main flow HS is pressed into the first and second spaces 4A and 4B.

Durch diese Wirkungsweise findet zum einen eine Entlastung der Antriebswelle 7 statt und zum anderen ist damit die Möglichkeit gegeben, die Drehschieber 18 in Richtung der Lauffläche 2 des Zylinders 1 zu betätigen. Die Wirkungsweise ist ohne den ersten und zweiten Steuerring 9A und 9B realisierbar, wenn Verbindungskanäle 5 angeordnet sind.This mode of operation relieves the drive shaft 7, on the one hand, and, on the other hand, gives the possibility of actuating the rotary slide valve 18 in the direction of the running surface 2 of the cylinder 1. The mode of operation can be implemented without the first and second control rings 9A and 9B if connecting channels 5 are arranged.

Wird alternativ auf den ersten und zweiten Steuerring 9A und 9B verzichtet, ermöglichen die Verbindungskanäle 5 allein die Betätigung der Drehschieber 18.If the first and second control rings 9A and 9B are alternatively dispensed with, the connecting channels 5 alone enable the rotary slide valves 18 to be actuated.

Durch den im Pumpraum 19 sich aufbauenden Druck werden die Drehschieber 18 aus Richtung des ersten und zweiten Raumes 4A beziehungsweise 4B zusätzlich zu den wirkenden Fliehkräften nach außen gedrückt. Der Teilstrom TS wird in das Innere des Drehschieberrotors 3 in den ersten und zweiten Raum 4A und 4b fließen. Im Bereich von niedrigeren Drücken, beispielsweise im Einlassbereich 11, wird in Abhängigkeit einer Druckdifferenz eine Teilstrom TS aus dem ersten und zweiten Raum 4A und 4B in den Bereich zwischen Drehschieberrotor-Außenwand 17 und Zylinder 1 fließen.Due to the pressure building up in the pump chamber 19, the rotary slide valves 18 are pressed outward from the direction of the first and second chamber 4A and 4B in addition to the centrifugal forces acting. The partial flow TS will flow into the interior of the rotary vane rotor 3 in the first and second spaces 4A and 4b. In the area of lower pressures, for example in the inlet area 11, a partial flow TS will flow from the first and second spaces 4A and 4B into the area between the rotary vane rotor outer wall 17 and cylinder 1 as a function of a pressure difference.

Der Volumenstrom des Teilstroms TS ist zudem abhängig von einem Durchmesser der Verbindungskanäle 5.The volume flow of the partial flow TS is also dependent on a diameter of the connecting channels 5.

Durch die erfindungsgemäße Lösung des zweites Abdeckelementes mit dem Zentrierwellenteil 13 und den Verbindungskanälen 5 sind zum einen höhere Kräfte auf die Antriebswelle 7 und den Drehschieberrotor 3 realisierbar. Zum anderen kann, wie oben erwähnt, auf die Steuerringe 9A und 9B verzichtet werden.The inventive solution of the second cover element with the centering shaft part 13 and the connecting channels 5 on the one hand enables higher forces to be achieved on the drive shaft 7 and the rotary vane rotor 3. On the other hand, as mentioned above, the control rings 9A and 9B can be dispensed with.

Die Drehschieberpumpe ist für folgende Industriezweige einsetzbar. Sie dient in der chemischen Industrie für Laugen, Gase und viskose Flüssigkeiten. In der Lebensmittelindustrie ist sie beispielsweise als Honig-, Senf-, Marmelade-, und Siruppumpe einsetzbar. Zudem ergibt sich im Bereich der Medizintechnik ein Einsatzfeld als Dosierpumpe und bei der Feuerwehr als Spritzpumpe. Für den Katastropheneinsatz ist die Drehschieberpumpe zum Abpumpen von Altölen auf dem Meer oder zum Abpumpen von Hochwasser bei Überschwemmungen einsetzbar. Weitere Einsatzmöglichkeiten ergeben sich in der Landwirtschaft und der Umwelttechnologie zum Bewässern von Feldern beziehungsweise als Druckerhöhungsanlage für eine Photovoltaikanlage. Diese Einsatzgebiete sind nur beispielhaft und sind für andere Bereiche beliebig erweiterbar.The rotary vane pump can be used for the following industries. It is used in the chemical industry for alkalis, gases and viscous liquids. In the food industry, for example, it can be used as a honey, mustard, jam and syrup pump. There is also a field of application in the field of medical technology as a metering pump and in the fire service as a spray pump. For disaster relief, the rotary vane pump can be used to pump out used oils at sea or to pump out floods in the event of flooding. There are further possible uses in agriculture and environmental technology for irrigating fields or as a pressure booster for a photovoltaic system. These areas of application are only examples and can be expanded for other areas.

BEZUGSZEICHENLISTELIST OF REFERENCE NUMBERS

11
Zylindercylinder
22
Laufflächetread
33
DrehschieberrotorRotary vane rotor
44
Raum (für Steuerringe)Space (for control rings)
4A4A
erster Raumfirst room
4B4B
zweiter Raumsecond room
55
Verbindungskanäle (Durchflusslöcher)Connection channels (flow holes)
66
Gewindebohrlöcherthreaded bore holes
77
Antriebswelledrive shaft
7'7 '
verstärkte Antriebswellereinforced drive shaft
88th
Abdeckelementcover
8A8A
erstes Abdeckelementfirst cover element
8B8B
zweites Abdeckelementsecond cover element
99
Steuerringcontrol ring
9A9A
erster Steuerringfirst control ring
9B9B
zweiter Steuerringsecond control ring
1010
DrehschieberpumpeRotary vane pump
1111
Einlassinlet
1212
Auslassoutlet
1313
Zentrierwellenteilcentering shaft
1414
Zentrierbolzencentering
1515
PumpenrotorachsenteilPump rotor axis part
1616
Zentrierlochcentering
1717
Drehschieberrotor-AußenwandRotary vane rotor outer wall
1818
Drehschieber (Lamellenschieber)Rotary vane
1919
Pumpraumpump chamber
2020
Drehachseaxis of rotation
2121
Drehschieberrotor-InnenwandRotary vane rotor inner wall
2222
Nabehub
2323
DurchgangsbohrungThrough Hole
2424
Befestigungselementefasteners
2525
Führungguide
d1d1
erster Durchmesserfirst diameter
d2d2
zweiter Durchmessersecond diameter
HSHS
Hauptstrommain power
TSTS
Teilstrompartial flow

Claims (23)

Drehschieberpumpe (10), die ein Gehäuse aus einem Zylinder (1) und Abdeckelementen (8A) und einen Drehschieberrotor (3) aufweist, in dem steuerbare, im Wesentlichen radial zu einer Drehachse (20) verschiebbare Drehschieber (18) angeordnet sind, die zwischen einem Einlass (11) und einem Auslass (12) und einer Drehschieberrotor-Außenwand (17) und dem Gehäuse einen Pumpraum (19) ausbilden, dadurch gekennzeichnet, dass mindestens auf einer Seite des Drehschieberrotors (3) ein Krafteintrag durch ein Zentrierwellenteil (13) erfolgt, indem das Zentrierwellenteil (13) als Bestandteil eines zweiten Abdeckelementes (8B) über Befestigungselemente (24) mit dem Drehschieberrotor (3) verbunden ist, wodurch in Verlängerung der Antriebswelle (7) eine, in einem zweiten Durchmesser (d2) verstärkte Antriebswelle (7'), ausgebildet ist.Rotary vane pump (10), which has a housing consisting of a cylinder (1) and cover elements (8A) and a rotary vane rotor (3) in which controllable rotary vane (18), which can be displaced essentially radially to an axis of rotation (20), are arranged between an inlet (11) and an outlet (12) and a rotary vane rotor outer wall (17) and the housing form a pump chamber (19), characterized in that at least on one side of the rotary vane rotor (3) an input of force by a centering shaft part (13) is carried out by connecting the centering shaft part (13) as part of a second cover element (8B) to the rotary vane rotor (3) via fastening elements (24), so that in the extension of the drive shaft (7) a drive shaft (2) reinforced with a second diameter (d2) 7 '), is formed. Drehschieberpumpe (10) nach Anspruch 1, dadurch gekennzeichnet, dass der Krafteintrag des Drehschieberrotors (3) auf beiden Seiten über ein Zentrierwellenteil (13) als Bestandteil des zweiten Abdeckelementes (8B) über Befestigungselemente (24) mit dem Drehschieberrotor (3) erfolgt, wodurch beidseitig eine verstärkte Antriebswelle (7') ausgebildet ist.Rotary vane pump (10) according to claim 1, characterized in that the force input of the rotary vane rotor (3) on both sides via a centering shaft part (13) as part of the second cover element (8B) via fastening elements (24) with the rotary vane rotor (3), whereby a reinforced drive shaft (7 ') is formed on both sides. Drehschieberpumpe (10) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Zentrierwellenteil (13) einen Zentrierbolzen (14) aufweist, welcher im montierten Zustand mit einem Zentrierloch (16) korrespondiert.Rotary vane pump (10) according to one of the preceding claims, characterized in that the centering shaft part (13) has a centering pin (14) which corresponds to a centering hole (16) in the assembled state. Drehschieberpumpe (10) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Zentrierwellenteil (13) mindestens eine Durchgangsbohrung (23) aufweist.Rotary vane pump (10) according to one of the preceding claims, characterized in that the centering shaft part (13) has at least one through hole (23). Drehschieberpumpe (10) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Drehschieberrotor (3) Gewindebohrlöcher (6) aufweist.Rotary vane pump (10) according to one of the preceding claims, characterized in that the rotary vane rotor (3) has tapped holes (6). Drehschieberpumpe (10) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass mindestens ein Befestigungselement (24) über die Durchgangsbohrung (23) des Zentrierwellenteiles (13) in das mindestens eine Gewindebohrloch (6) des Drehschieberrotors (3) eingreift.Rotary vane pump (10) according to one of the preceding claims, characterized in that at least one fastening element (24) engages in the at least one threaded bore hole (6) of the rotary vane rotor (3) via the through bore (23) of the centering shaft part (13). Drehschieberpumpe (10) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Zentrierwellenteil (13) mit seinem Zentrierbolzen (14) in das Zentrierloch (16) eines Pumpenrotorachsenteiles (15) der Antriebswelle (7) eingreift.Rotary vane pump (10) according to one of the preceding claims, characterized in that the centering shaft part (13) engages with its centering bolt (14) in the centering hole (16) of a pump rotor axis part (15) of the drive shaft (7). Drehschieberpumpe (10) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Zentrierwellenteil (13) eine verstärkte Antriebswelle (7') mit einem zweiten Durchmesser (d2) aufweist, welcher größer ist als der Durchmesser (d1).Rotary vane pump (10) according to one of the preceding claims, characterized in that the centering shaft part (13) has a reinforced drive shaft (7 ') with a second diameter (d2) which is larger than the diameter (d1). Drehschieberpumpe (10) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der zweite Deckel (8B) eine Führung (25) aufweist.Rotary vane pump (10) according to one of the preceding claims, characterized in that the second cover (8B) has a guide (25). Drehschieberpumpe (10) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der zweite Deckel (8B) und das Zentrierwellenteil (13) den Zylinder (1) unter Umschließung der Antriebswelle (7') mittels der Führung (25) verschließt.Rotary vane pump (10) according to one of the preceding claims, characterized in that the second cover (8B) and the centering shaft part (13) closes the cylinder (1) by enclosing the drive shaft (7 ') by means of the guide (25). Drehschieberpumpe (10) mit einem in einem Gehäuse beidseitig über die Antriebswelle (7) gelagerten Drehschieberrotor (3), in dem steuerbare, im Wesentlichen radial zu einer Drehachse (20) verschiebbare Drehschieber (18) angeordnet sind, die zwischen einem Einlass (11) und einem Auslass (12) und einer Drehschieberrotoraußenwand (17) und dem Gehäuse einen Pumpraum (19) ausbilden, dadurch gekennzeichnet, dass ein zwischen der Antriebswelle (7) und einer Drehschieberrotor-Innenwand (21) gebildeter Raum (4) über mindestens einen Verbindungskanal (5) mit dem Pumpraum (19) zwischen jeweils zwei Drehschiebern (18) verbunden ist.Rotary vane pump (10) with a rotary vane rotor (3) mounted on both sides of the drive shaft (7) in a housing, in which controllable rotary vane (18), which can be moved essentially radially to an axis of rotation (20), are arranged, which are located between an inlet (11) and an outlet (12) and a rotary vane rotor outer wall (17) and the housing form a pump chamber (19), characterized in that a space (4) formed between the drive shaft (7) and a rotary vane rotor inner wall (21) via at least one connecting channel (5) with the pump chamber (19) between two rotary valves (18). Drehschieberpumpe (10) nach Anspruch 11, dadurch gekennzeichnet, dass der mindestens eine Verbindungskanal (5) ein Durchflussloch ist.Rotary vane pump (10) according to claim 11, characterized in that the at least one connecting channel (5) is a flow hole. Drehschieberpumpe (10) nach Anspruch 11 und 12, dadurch gekennzeichnet, dass der Verbindungskanal (5) im Wesentlichen radial zu der Drehachse (20) des Drehschieberrotors (3) angeordnet ist.Rotary vane pump (10) according to claim 11 and 12, characterized in that the connecting channel (5) is arranged substantially radially to the axis of rotation (20) of the rotary vane rotor (3). Drehschieberpumpe (10) nach Anspruch 11, dadurch gekennzeichnet, dass zwischen der Antriebswelle (7) und der Drehschieberrotor-Innenwand (21) ein erster Raum (4A) und ein zweiter Raum (4B) angeordnet sind.Rotary vane pump (10) according to claim 11, characterized in that a first space (4A) and a second space (4B) are arranged between the drive shaft (7) and the rotary vane rotor inner wall (21). Drehschieberpumpe (10) nach Anspruch 11 bis 14, dadurch gekennzeichnet, dass die Drehschieber (18) durch die auf die Drehschieber (18) wirkende Fliehkraft und eine Druckdifferenz zwischen dem Raum (4A) und/oder dem Raum (4B) und dem Pumpraum (19) steuerbar sind.Rotary vane pump (10) according to claim 11 to 14, characterized in that the rotary slide valve (18) by the centrifugal force acting on the rotary slide valve (18) and a pressure difference between the space (4A) and / or the space (4B) and the pump space ( 19) are controllable. Drehschieberpumpe (10) nach Anspruch 12, dadurch gekennzeichnet, dass zwischen der Antriebswelle (7) und der Drehschieberrotor-Innenwand (21) der erste Raum (4A) mit einem ersten Steuerring (9A) und/oder der zweite Raum (4B) mit einem zweiten Steuerring (9B) angeordnet ist.Rotary vane pump (10) according to claim 12, characterized in that between the drive shaft (7) and the rotary vane rotor inner wall (21) the first space (4A) with a first control ring (9A) and / or the second space (4B) with one second control ring (9B) is arranged. Drehschieberpumpe (10) nach Anspruch 12 und 17, dadurch gekennzeichnet, dass die Drehschieber (18) durch die auf die Drehschieber (18) wirkenden ersten und/oder zweiten Steuerringe (9A) und/oder (9B)steuerbar sind.Rotary vane pump (10) according to Claims 12 and 17, characterized in that the rotary vane (18) can be controlled by the first and / or second control rings (9A) and / or (9B) acting on the rotary vane (18). Drehschieberpumpe (10) nach Anspruch 16 und/oder 18, dadurch gekennzeichnet, dass die Drehschieber (18) im Pumpraum (19) an einer Lauffläche (2) anliegen.Rotary vane pump (10) according to claim 16 and / or 18, characterized in that the rotary vane (18) abut a running surface (2) in the pump chamber (19). Verfahren zur Betätigung eines Drehschiebers (18) einer Pumpe, dadurch gekennzeichnet, dass aus einem Hauptförderstrom (HS) ein Teilstrom (TS) abgezweigt wird und dieser Teilstrom (TS) die Betätigung der Drehschieber (18) in Richtung einer Lauffläche (2) eines Zylinders (1) der Pumpe bewirkt.Method for actuating a rotary slide valve (18) of a pump, characterized in that a partial flow (TS) is branched off from a main delivery flow (HS) and this partial flow (TS) actuates the rotary slide valves (18) in the direction of a running surface (2) of a cylinder (1) causes the pump. Verfahren nach Anspruch 19, dadurch gekennzeichnet, dass der Teilstrom (TS) von einem Pumpraum (19) über mindestens einen Verbindungskanal (5) zu einem Raum (4) im Innern eines Drehschieberrotors (3) zu den Drehschiebern (18) geführt wird.Method according to claim 19, characterized in that the partial flow (TS) is led from a pump chamber (19) via at least one connecting channel (5) to a chamber (4) inside a rotary vane rotor (3) to the rotary valves (18). Verfahren nach Anspruch 19 und 20, dadurch gekennzeichnet, dass über den mindestens einen Verbindungskanal (5) ein Druckausgleich zwischen dem mindestens einen Raum (4) und dem Pumpraum (19) durchgeführt wird.Method according to claims 19 and 20, characterized in that a pressure equalization between the at least one space (4) and the pump space (19) is carried out via the at least one connecting channel (5). Verfahren nach Anspruch 19 bis 21, dadurch gekennzeichnet, dass ein bestimmter Volumenstrom als Teilstrom (TS) in Abhängigkeit einer Druckdifferenz zwischen dem mindestens einen Raum (4) und dem Pumpraum (19) abgezweigt wird.Method according to Claims 19 to 21, characterized in that a certain volume flow is branched off as a partial flow (TS) as a function of a pressure difference between the at least one space (4) and the pump space (19). Verfahren nach Anspruch 19 bis 22, dadurch gekennzeichnet, dass ein bestimmter Volumenstrom als Teilstrom (TS) in Abhängigkeit eines Durchmessers des mindestens einen Verbindungselementes (5) abgezweigt wird.Method according to claims 19 to 22, characterized in that a certain volume flow is branched off as a partial flow (TS) depending on a diameter of the at least one connecting element (5).
EP02090283A 2001-07-27 2002-07-26 Vane pump Expired - Lifetime EP1279834B1 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE20112695U 2001-07-27
DE20112695U DE20112695U1 (en) 2001-07-27 2001-07-27 Cover with reinforced shaft for screwing on the rotary vane pump rotor and flow holes drilled from the outer wall to the clearance of the control rings
DE2001137415 DE10137415A1 (en) 2001-07-27 2001-07-27 Rotary slide pump with power introduction one side of the rotary slide rotor via centering shaft section
DE10137415 2001-07-27

Publications (3)

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EP1279834A2 true EP1279834A2 (en) 2003-01-29
EP1279834A3 EP1279834A3 (en) 2004-11-03
EP1279834B1 EP1279834B1 (en) 2007-02-28

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EP02090283A Expired - Lifetime EP1279834B1 (en) 2001-07-27 2002-07-26 Vane pump

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AT (1) ATE355463T1 (en)
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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1960672A1 (en) * 2005-12-12 2008-08-27 Magna Powertrain Inc. Noise reduced variable displacement vane pump
DE102012006016A1 (en) 2012-03-20 2013-09-26 Hermann Lidlgruber Rotary vane pump has rotary vane rotor transport chambers that form rotor disc space for transportation of medium from pump chamber
EP2401503A4 (en) * 2009-02-26 2016-03-30 Stt Technologies Inc A Joint Venture Of Magna Powertrain Inc And Shw Gmbh Integrated electric vane oil pump

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2353965A (en) * 1941-06-18 1944-07-18 Meador Calender Corp Rotary pump or compressor
US3361076A (en) * 1966-05-06 1968-01-02 William B Pritchett Jr Expansible chamber device

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2353965A (en) * 1941-06-18 1944-07-18 Meador Calender Corp Rotary pump or compressor
US3361076A (en) * 1966-05-06 1968-01-02 William B Pritchett Jr Expansible chamber device

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1960672A1 (en) * 2005-12-12 2008-08-27 Magna Powertrain Inc. Noise reduced variable displacement vane pump
EP1960672A4 (en) * 2005-12-12 2013-11-06 Stt Technologies Inc A Joint Venture Of Magna Powertrain Inc And Shw Gmbh Noise reduced variable displacement vane pump
EP2401503A4 (en) * 2009-02-26 2016-03-30 Stt Technologies Inc A Joint Venture Of Magna Powertrain Inc And Shw Gmbh Integrated electric vane oil pump
DE102012006016A1 (en) 2012-03-20 2013-09-26 Hermann Lidlgruber Rotary vane pump has rotary vane rotor transport chambers that form rotor disc space for transportation of medium from pump chamber

Also Published As

Publication number Publication date
EP1279834B1 (en) 2007-02-28
ATE355463T1 (en) 2006-03-15
DE50209573D1 (en) 2007-04-12
EP1279834A3 (en) 2004-11-03

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