EP0294399A1 - Swivelling vane pump. - Google Patents

Swivelling vane pump.

Info

Publication number
EP0294399A1
EP0294399A1 EP87906386A EP87906386A EP0294399A1 EP 0294399 A1 EP0294399 A1 EP 0294399A1 EP 87906386 A EP87906386 A EP 87906386A EP 87906386 A EP87906386 A EP 87906386A EP 0294399 A1 EP0294399 A1 EP 0294399A1
Authority
EP
European Patent Office
Prior art keywords
rotor
cage
vane pump
pump
slide
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
EP87906386A
Other languages
German (de)
French (fr)
Other versions
EP0294399B1 (en
Inventor
Gerhard Winiger
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.)
NOTRON ENGINEERING AG
Original Assignee
NOTRON ENGINEERING AG
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
Application filed by NOTRON ENGINEERING AG filed Critical NOTRON ENGINEERING AG
Priority to AT87906386T priority Critical patent/ATE59438T1/en
Publication of EP0294399A1 publication Critical patent/EP0294399A1/en
Application granted granted Critical
Publication of EP0294399B1 publication Critical patent/EP0294399B1/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
    • 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
    • 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
    • F04C2/32—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 both the movement defined in groups F04C2/02 and relative reciprocation between co-operating members
    • F04C2/332—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 both the movement defined in groups F04C2/02 and relative reciprocation between co-operating members with vanes hinged to the outer member and reciprocating with respect to the inner member
    • F04C2/336—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 both the movement defined in groups F04C2/02 and relative reciprocation between co-operating members with vanes hinged to the outer member and reciprocating with respect to the inner member and hinged to the inner member

Definitions

  • the invention relates to a rotary vane pump for conveying liquid or gaseous media according to the preamble of the first claim.
  • a pump known only from the literature according to German patent 942314 shows the following structure.
  • the inner cylinder jacket of a cylinder revolving in a housing has semi-cylindrical bearings for receiving vanes with double arms.
  • a loosely rotating rotary piston rotates on a bolt which is eccentric to the cylinder, in which the second arms of the wings engage by means of sliding jaws which have recesses.
  • the disadvantage of the double-arm design of the wings is that the number of sealing edges doubles. In addition, they make it impossible to completely empty the work area, so that the suction capacity of the pump is reduced.
  • the rectangular design of the wings engaging in the sliding jaws means that the sliding jaws must each consist of two parts, which therefore jam during operation.
  • Another pump known only from the patent literature according to British patent 109186 provides for a rotatable driver provided with side plates to be arranged between the housing and the rotor. Wings are articulated to the rotatable driver, which act in the rotor through articulated, slotted tips.
  • the synchronous rotation of the rotor with the rotatable carriers and the side plates is brought about by the pins arranged on the plates and engaging in bores in the rotor.
  • the rotatable driver is connected by one of the plates and rotates with it, so that the rotor rotates about an eccentrically arranged bearing which can be adapted to the shaft by rotation.
  • Such a pump in turn has the disadvantage of a double number of sealing edges, resulting from the articulation in the driver, which in turn has to be sealed off from the housing. It is also unfavorable that this articulation of the wings is exposed to the medium and thus to wear without protection.
  • the proposed rotation of the rotor by means of pins engaging in the provided bores leads to high friction and wear of the touching parts. The tips are flat slotted ⁇ if only two parts possible, thereby jamming occurs here.
  • the radial adjustment of the rotor bearing inevitably changes the timing, so that continuous flow control is impossible. Its construction is complicated, prone to failure and difficult to assemble.
  • the invention seeks to remedy this.
  • the invention as characterized in the claims, solves the problem of making available a low-wear, structurally simple, universally applicable pump for a wide pressure range with particularly smooth running and variable flow rate at constant speed.
  • the particularly simple construction of the invention provides for one-arm slides rotatably mounted on rotor cage bolts, which seal directly on the housing. This eliminates the sealing edges in the driver, which has a favorable effect on the internal leakage and on the wear.
  • the slide receptacles are formed in one piece to prevent jamming. According to the invention, this is achieved in such a way that the slide guided by the driver has a rectangular pinnacle which engages in the corresponding recess in the driver, which earlier similar pump designers apparently had not recognized and therefore this type of slide guide could not be implemented in practice.
  • One of the main features of the invention is the support of the rotor and its characterizedn ⁇ loose radial adjustment.
  • According to the invention solved the radial, continuous adjustment of the rotor core in such a way by this sitting 'rwelle on a hollow Sekundä which unilaterally and aus ⁇ half of the pump space stored and designed to be continuously radially displaceable.
  • the drive shaft is located inside this secondary shaft f at a sufficient distance for its radial displacement.
  • the drive shaft is connected on one side to the rotor cage and thus drives the rotor core, which is firmly connected to the secondary shaft, via the rotor cage bolts and the slide.
  • a particularly expedient embodiment of the invention provides for the diameter of the cage bolts to be dimensioned such that the compressive force acts centrally on the cage bolts in the area of the maximum eccentricity of the rotor core and thus the sliding friction in the slide sensor is minimized. It is also provided that, depending on the intended use and size, between three and twelve slides are evenly distributed between the rotor core and cage; however, preferably five to nine slides if high pressures are to be achieved (space reasons due to the massive design of the bolts, slides and transducers).
  • the suction or. Pressure channels are preferably to be designed to extend radially in the housing over almost the entire width of the slide valve, care being taken to ensure that the inlet and outlet are as tangential as possible so that favorable inflow and outflow conditions prevail. In order to ensure optimal filling of the pump at high speeds, provision is made to prevent backflow by means of beam deflectors which are arranged radially directly to the rotor cage in the suction area.
  • two rotors can be provided axially one behind the other, the bearing of the secondary shaft remaining unchanged, so that a symmetrical double pump is created. Possibly. you can drive entire swing vane pumps from a common shaft and provide them with individual inlets and outlets or combined inlets and outlets.
  • the proposed invention is characterized in that the construction enables a speed-independent, infinitely variable flow rate change with high forces and that the design of the swivel slide results in minimal wear due to sliding friction and that the cleaning of the pump or the replacement of wear parts is quick and easy is to be carried out.
  • the pump is therefore simple, versatile and low-wear.
  • the subject matter of the invention is explained in more detail below with reference to the drawings, for example. 1 shows the longitudinal section through the rotary vane pump, FIG. 2 shows the section AA through the rotor, FIG. 3 shows the partial section of the suction area with beam deflector, FIG. 4 shows the section BB through the housing and rotor, FIG. 5 shows the section CC through the 6 the section DD through the adjusting mechanism, FIG.
  • FIGS. 1 to 6 stands on a rectangular base plate 1, which serves as additional stiffening against rotation.
  • the front 2 and rear 3 supports are on this.
  • On the inside of these supports 2, 3, the horizontally displaceable slide rings 5, 6 and the bearing support 4 located between them are inserted in a form-fitting manner.
  • the pump housing 19 is fixed on the front side of the carrier 2 by means of screws.
  • the pump housing 19 is closed with the bearing cover 18, which contains the slide bearing 26 of the primary shaft 12.
  • the bearing flange 10 which contains the rear bearing by means of slide bearings 26 of the primary shaft 12 and is thus part of the rear wall, is screwed to the rear of the rear carrier 3.
  • a pump channel e with inlet a, the sealing area f and the outlet b with outlet space g are formed in the pump housing 19.
  • a hollow cylindrical rotor 13 runs in it, which has axial bores which are offset at equal intervals on the circumference and which break through the outer cylinder jacket. These bores contain the one-piece slide receptacles 16, which in turn receive the single-arm slide 15.
  • the one-armed slides 15 are rotatably mounted at the upper end on cage bolts 14 and, with their round upper side, seal the rotor cage h against the pump housing 19 with a minimal gap in the sealing area f.
  • the rotor cage h consisting of the rotor wall 17 and the circumferentially equally spaced six cage bolts 14 fixed on one side, sits on the primary shaft 12 and is driven by it.
  • This secondary shaft 7 can now be shifted in the horizontal plane, so that the eccentricity of the rotor 13, which is seated on this shaft, can be varied.
  • This, displaceably guided secondary shaft bearing 4, 5, 6, 8, 9 arranged between the supports 2, 3 is set in play with six clamping screws 25.
  • the seal to the rotor 13 is provided by a mechanical seal 23 mounted on the secondary shaft 7, which comes to rest in a sufficiently large bore for the horizontal displacement in the carrier 2.
  • the bearing 9 is sealed by the shaft sealing ring 28, the rear of the pump with the shaft sealing ring 24.
  • the intermediate ring 20 and the guide pin 22 serve for the axial guidance of the primary shaft 12.
  • the cover 21 seals the pump from the
  • FIG. 1 shows the slider 15 engage with a pinnacle in the correspondingly designed counterpart, the slider sensor 16. With the one-piece slide sensor 16, jamming is therefore excluded.
  • This lock / key principle is reversible in that the slide 15 is formed with two or more pinnacles which engage in the correspondingly designed slide receiver 16 (cf. FIG. 9). However, it is important that the battlements are rectangular to prevent leakage.
  • 3 shows the jet deflector 29 which is provided for high speeds in the inlet a and which consists of individual tangentially arranged guide plates or groove-shaped cutouts in the housing 19 which is closed on the inlet side. The geometry of the individual baffles or the cutouts must be matched to the prevailing conditions.
  • FIG. 7 and 8 show the embodiment variant of the rotor cage h with the rotor rear wall 35.
  • the rotor core 13, rotor wall 17 ', driving screws 41, slide 15', slide receiver 16 'and the rotor rear wall form an assembly.
  • the rotor core again supported on the secondary shaft 7 and secured with a spring key 36 against rotation.
  • the clamping screw 39 clamps the entire assembly 13, 17 ', 41, 15', 16 ', 35 axially onto the secondary shaft 7' by means of the clamping bush 38.
  • FIG. 9 shows the variant of a double rotor pump which, apart from the shaft passage on one side, represents a mirror image symmetry of FIG. 7 with a central bearing 8 '.

Abstract

PCT No. PCT/CH87/00140 Sec. 371 Date Jun. 16, 1988 Sec. 102(e) Date Jun. 16, 1988 PCT Filed Oct. 13, 1987 PCT Pub. No. WO88/03229 PCT Pub. Date May 5, 1988.Variable capacity swivelling vane pump, comprising a radially displaceable rotor (13) connecting eccentrically in a rotor cage (h) with guided vanes (15), which are rotatably supported in vane recesses (16) and on cage pins (14). The vanes (15) thus convert the rotor eccentricity (d) into a pivoting-propulsion movement. Furthermore, the rotor (13) rests on a hollow secondary shaft (7), which is mounted outside the pump casing in a bearing carrier (4) arranged in a horizontally movable manner. The rotor (13) is driven by means of the primary shaft (12) located in the hollow secondary shaft (7), the primary shaft being connected with the rotor cage (h). This structure has small oscillating masses, is versatile, easy to manufacture and assemble and operates with minimum frictonal losses and is free from bearing and sealing problems.

Description

Bezeichnun : Schwenkschieberpumpe Name: Swing vane pump
Beschreibungdescription
Die Erfindung betrifft eine Schwenkschieberpumpe zum Fördern von flüs¬ sigen oder gasförmigen Medien gemäss dem Oberbegriff des 1. Patentan¬ spruches.The invention relates to a rotary vane pump for conveying liquid or gaseous media according to the preamble of the first claim.
Es ist eine grosse Anzahl von unterschiedlichen Pumpen für flüssige oder gasförmige Medien bekannt, die das breite Anwendungsfeld benötigt. Für Aufgaben, die einen nahezu stetigen Förderstrom, der fast unabhängig vom Gegendruck ist, erfordern, werden Verdrängerpumpen eingesetzt. Bei diesen Pumpen werden durch Kolben, Schieber, Membrane oder durch Formgebung der Teile ein im Pumpraum eingeschlossener Volumenteil des Fördermediums vom Einlass zum Auslass transportiert. Für inkompressible Medien darf dabei der Förderraum nach dem Absperren gegenüber dem Ein¬ lass nicht verkleinert werden; für kompressible Medien (z.B. Gase) kann dies jedoch zur Druckerhöhung erwünscht sein. Diese Verdrängungs¬ charakteristik führt bei Kolben- oder Membranpumpen zu unerwünschter Pulsation des Förderstromes, wodurch Pulsationsdämpfer und/oder mehrere Pumpen, die mit zeitlich verschobenem Takt arbeiten, erforderlich sind. Die noch vorhandene Restpulsation verhindert jedoch eine exakte Messung des Volumenstromes. Ausserdem zeigt das Aehnlichkeitsgesetz bei diesen Konstruktionen, dass mit zunehmender Baugrösse ein exponentieller An- stieg der oszillierenden Massen auftritt, was sich ungünstig auf das Leistungsgewicht sowie auf Fertigung auswirkt. Zur Förderstromregelung kommen nur aufwendige Hubsteuerungen oder Getriebe in Betracht. Gün¬ stiger liegen hier Rotationsverdrängerpumpen, weil sie praktisch pul- sationsfrei arbeiten und keine oszillierenden Massen und keine Ventile haben. Daher sind hohe Drehzahlen erreichbar, die zu raumsparenden Konstruktionen führt, die keine grossen Fundamente benötigen. Diese Pumpen haben jedoch den Nachteil, dass die innere Leckage grösser ist als bei Kolben- oder Membranpumpen und daher die erreichbaren Druck¬ differenzen nach oben hin begrenzt sind. Die meisten Bauarten sind wegen der geringen Spiele zwischen rotierenden und feststehenden Bautei- len oder die ineinander eingreifenden Verdränger sehr empfindlich gegen abrasive Beimengungen. Hohe Gleitgeschwindigkeiten von Absperrelementen lassen aus Verschleiss- und Dichtigkeitsgründen das Fördern von nicht- selbstschmierenden Medien oder Trockenlauf nicht zu. Wegen der Verdrän- gercharakteristik kann die bei Kreiselpumpen einfache Drosselregelung nicht verwendet werden. Zur Förderstromregelung bei konstanter Drehzahl kommen nur bei Kolbenpumpen übliche aufwendige Verfahren in Betracht. Eine nur aus der Literatur bekannte Pumpe nach dem deutschen Patent 942314 zeigt den folgenden Aufbau. Der innere Zylindermantel eines in einem Gehäuse umlaufenden Zylinders weist für die Aufnahme von dop- pelarmig ausgebildeten Flügel halbzylinderförmige Lagerungen auf. Im Innern des Zylinders dreht auf einem exzentrisch zum Zylinder stehenden Bolzen ein lose umlaufender Drehkolben, in welchem die zweiten Arme der Flügel mittels Gleitbacken, die Aussparungen aufweisen, eingreifen. Die doppelarmige Ausbildung der Flügel hat den Nachteil, dass sich die Zahl der Dichtkanten verdoppelt. Zudem verunmöglichen sie ein voll¬ ständiges Entleeren der Arbeitsräume, so dass das Ansaugvermögen der Pumpe vermindert ist. Ausserdem bewirkt die rechteckförmige Ausbildung der in die Gleitbacken eingreifenden Flügel, dass die Gleitbacken je aus zwei Teilen bestehen müssen, die daher im Betrieb verklemmen.A large number of different pumps for liquid or gaseous media are known which require the broad field of application. Positive displacement pumps are used for tasks that require an almost constant flow rate that is almost independent of the back pressure. In these pumps, a volume part of the pumped medium enclosed in the pump chamber is transported from the inlet to the outlet by means of pistons, slides, membranes or by shaping the parts. For incompressible media, the delivery area must not be reduced compared to the inlet after the shut-off; for compressible media (eg gases) this can be desirable to increase the pressure. In the case of piston or diaphragm pumps, this displacement characteristic leads to undesired pulsation of the delivery flow, as a result of which pulsation dampers and / or a plurality of pumps which operate with a time-shifted cycle are required. However, the remaining pulsation prevents an exact measurement of the volume flow. In addition, the similarity law for these constructions shows that with increasing size, the exponential increase in the oscillating masses occurs, which has an unfavorable effect on the power-to-weight ratio and on production. Only complex stroke controls or gears can be considered for flow rate control. Gün¬ stiger are here rotary displacement pumps because they work practically pulsation-free and have no oscillating masses and no valves. Therefore, high speeds can be achieved, which leads to space-saving constructions that do not require large foundations. However, these pumps have the disadvantage that the internal leakage is greater than in the case of piston or diaphragm pumps and therefore the achievable pressure differences are limited at the top. Most designs are due to the small play between rotating and fixed components len or the interlocking displacers are very sensitive to abrasive additives. High sliding speeds of shut-off elements do not allow the conveying of non-self-lubricating media or dry running for reasons of wear and tightness. Because of the displacement characteristic, the simple throttle control cannot be used with centrifugal pumps. For the flow rate control at constant speed, only complicated processes customary for piston pumps come into consideration. A pump known only from the literature according to German patent 942314 shows the following structure. The inner cylinder jacket of a cylinder revolving in a housing has semi-cylindrical bearings for receiving vanes with double arms. Inside the cylinder, a loosely rotating rotary piston rotates on a bolt which is eccentric to the cylinder, in which the second arms of the wings engage by means of sliding jaws which have recesses. The disadvantage of the double-arm design of the wings is that the number of sealing edges doubles. In addition, they make it impossible to completely empty the work area, so that the suction capacity of the pump is reduced. In addition, the rectangular design of the wings engaging in the sliding jaws means that the sliding jaws must each consist of two parts, which therefore jam during operation.
Eine weitere nur aus der Patentliteratur bekannte Pumpe nach dem bri¬ tischen Patent 109186 sieht vor, zwischen dem Gehäuse und dem Rotor ein mit Seitenplatten versehener, drehbarer Mitnehmer anzuorden. An dem drehbaren Mitnehmer sind Flügel angelenkt, die im Rotor durch gelen- kige, mit Schlitzen versehene Spitzen wirken. Die synchrone Drehung des Rotors mit den drehbaren Mitnehmern und den Seitenplatten wird durch die an den Platten angeordenten und in die im Rotor in Bohrungen eingreifenden Zapfen bewirkt. Durch eine der Platten ist der drehbare Mitnehmer verbunden und dreht mit dieser mit, so dass der Rotor um ein exzentrisch angeordnetes Lager, welches an die Welle durch Drehung angepasst werden kann, dreht. Eine derartige Pumpe hat wiederum den Nachteil einer doppelten Anzahl von Dichtkanten, herrührend durch die Anlenkung im Mitnehmer, der seinerseits gegenüber dem Gehäuse abgedich¬ tet werden muss. Ungünstig ist zudem, dass diese Anlenkung der Flügel ungeschützt dem Medium und somit dem Verschleiss ausgesetzt ist. Ausser¬ dem führt die vorgeschlagene Drehung des Rotors mittels in vorgesehenen Bohrungen eingreifenden Zapfen zu hoher Reibung und Verschleiss der sich berührenden Teile. Die mit Schlitzen versehenen Spitzen sind eben¬ falls nur zweiteilig möglich, wodurch auch hier ein Verklemmen auftritt. Die radiale Verstellmöglichkeit der Rotorlagerung verändert zwangsläufig die Steuerzeiten, so dass eine kontinuierliche Förderstromregelung ausgeschlossen ist. Seine Konstruktion ist kompliziert, störanfällig und schlecht zu montieren.Another pump known only from the patent literature according to British patent 109186 provides for a rotatable driver provided with side plates to be arranged between the housing and the rotor. Wings are articulated to the rotatable driver, which act in the rotor through articulated, slotted tips. The synchronous rotation of the rotor with the rotatable carriers and the side plates is brought about by the pins arranged on the plates and engaging in bores in the rotor. The rotatable driver is connected by one of the plates and rotates with it, so that the rotor rotates about an eccentrically arranged bearing which can be adapted to the shaft by rotation. Such a pump in turn has the disadvantage of a double number of sealing edges, resulting from the articulation in the driver, which in turn has to be sealed off from the housing. It is also unfavorable that this articulation of the wings is exposed to the medium and thus to wear without protection. In addition, the proposed rotation of the rotor by means of pins engaging in the provided bores leads to high friction and wear of the touching parts. The tips are flat slotted ¬ if only two parts possible, thereby jamming occurs here. The radial adjustment of the rotor bearing inevitably changes the timing, so that continuous flow control is impossible. Its construction is complicated, prone to failure and difficult to assemble.
Hier will die Erfindung Abhilfe schaffen. Die Erfindung, wie sie in den Ansprüchen gekennzeichnet ist, löst die Aufgabe, eine verschleiss- arme, im Aufbau einfache, universell einsetzbare Pumpe für einen breiten Druckbereich mit besonders ruhigem Lauf und bei konstanter Drehzahl veränderbaren Förderstrom verfügbar zu machen.The invention seeks to remedy this. The invention, as characterized in the claims, solves the problem of making available a low-wear, structurally simple, universally applicable pump for a wide pressure range with particularly smooth running and variable flow rate at constant speed.
In Abweichnung von der bisher vorgeschlagenen Art, die Dichtelemente zweiarmig auszubilden oder in einem drehbaren Mitnehmer anzulenken, sieht die besonders einfache Konstruktion der Erfindung vor, einarmige an Rotorkäfigbolzen drehbar gelagerte Schieber anzubringen, die direkt am Gehäuse abdichten. Somit entfallen die Dichtkanten im Mitnehmer, was sich günstig auf die innere Leckage sowie auf den Verschleiss aus¬ wirkt. Erfindungsgemäss ist zudem vorgesehen, dass die Schieberaufnehmer einteilig ausgebildet sind um ein Verklemmen zu verhindern. Dies ist erfindungsgemäss derart gelöst, dass der vom Mitnehmer geführten Schie¬ ber eine rechteckige Zinne aufweist, die in die entsprechende Aussparung des Mitnehmers eingreift, was frühere ähnliche Pumpenkonstrukteure offenbar nicht erkannt hatten und deshalb diese Art der Schieberführung praktisch nicht realisiert werden konnte. Eines der wesentlichsten Merkmale der Erfindung stellt die Lagerung des Rotors und dessen stufen¬ lose radiale Verstellmöglichkeit dar. Erfindungsgemäss wird die radiale, stufenlose Verstellmöglichkeit des Rotorkerns derart gelöst, indem dieser auf einer hohlen Sekundä'rwelle sitzt, welche einseitig und aus¬ halb des Pumpraumes gelagert und stufenlos radial verschiebbar ausge- geführt ist. Im Innern dieser Sekundärwelle fin genügendem Abstand für die radiale Verschiebung derselben, befindet sich die Antriebswelle. Die Antriebswelle ist einseitig mit dem Rotorkäfig verbunden und treibt somit über die Rotorkäfigbolzen und der Schieber den fest mit der Sekun¬ därwelle verbundenen Rotorkern an. Die durch diese Konstruktion sich ergebenden Vorteile sind im wesentlichen darin zu sehen, dass nun hohe Kräfte infolge Druckaufbaus im Pumpraum lagermässig und dichtmässig viel besser zu beherrschen sind. Auch ist die Pumpe nun geeignet nicht- schmierende Medien zu fördern, die auch abrasive Beimengungen aufweisen dürfen, ohne dass bei höheren Drücken Lagerverschleiss auftritt. Die vorgeschlagene Lösung der stufenlosen Fördermengenregelung über die radiale Verschiebung der Sekundärwelle bringt den entscheidenden Vor- teil, dass mit einer einfachen Konstruktion praktisch unabhängig vom herrschenden Druck in der Pumpe die Exzentrizität variiert werden kann. Ausserdem ergibt sich eine sehr kompakte Bauweise, die nicht störanfäl¬ lig und gut zu montieren ist. Eine besonders zweckmässige Gestaltung der Erfindung sieht vor, die Käfigbolzen im Durchmesser derart zu dimensionieren, dass im Bereich der Maximalexzentrizität des Rotorkerns die Druckkraft zentrisch auf den Käfigbolzen wirkt und somit die Gleitreibung im Schieberaufnehmer minimiert ist. Auch ist vorgesehen, dass je nach Verwendungszweck und Baugrösse zwischen drei und zwölf Schieber gleichmässig verteilt zwi¬ schen Rotorkern und -käfig angeordnet sind; vorzugsweise jedoch fünf bis neun Schieber, wenn hohe Drücke erzielt werden sollen (Platzgründe wegen massiver Ausführung der Bolzen, Schieber und Aufnehmer). Der Ansaug- resp. Druckkanal sind vorzugsweise radial im Gehäuse über nahezu die gesamte Breite der Schieber erstreckend zu gestalten, wobei auf eine möglichst tangentiale Zu- und Abführung zu achten ist, damit gün¬ stige Ein- und Ausströmverhältnisse herrschen. Um eine optimale Befül- lung der Pumpe bei hohen Drehzahlen zu gewährleisten, ist vorgesehen, mittels Strahlablenker, welche radial unmittelbar zum Rotorkäfig im Ansaugbereich angeordnet sind, ein Zurückströmen zu verhindern.In a departure from the previously proposed way of designing the sealing elements with two arms or articulating them in a rotatable driver, the particularly simple construction of the invention provides for one-arm slides rotatably mounted on rotor cage bolts, which seal directly on the housing. This eliminates the sealing edges in the driver, which has a favorable effect on the internal leakage and on the wear. According to the invention it is also provided that the slide receptacles are formed in one piece to prevent jamming. According to the invention, this is achieved in such a way that the slide guided by the driver has a rectangular pinnacle which engages in the corresponding recess in the driver, which earlier similar pump designers apparently had not recognized and therefore this type of slide guide could not be implemented in practice. One of the main features of the invention is the support of the rotor and its stufen¬ loose radial adjustment. According to the invention solved the radial, continuous adjustment of the rotor core in such a way by this sitting 'rwelle on a hollow Sekundä which unilaterally and aus¬ half of the pump space stored and designed to be continuously radially displaceable. The drive shaft is located inside this secondary shaft f at a sufficient distance for its radial displacement. The drive shaft is connected on one side to the rotor cage and thus drives the rotor core, which is firmly connected to the secondary shaft, via the rotor cage bolts and the slide. The advantages resulting from this construction can essentially be seen in the fact that high forces due to pressure build-up in the pump chamber can now be controlled much better in terms of storage and sealing. Also the pump is now not suitable to convey lubricating media, which may also have abrasive additives, without bearing wear occurring at higher pressures. The proposed solution of the infinitely variable delivery rate control via the radial displacement of the secondary shaft brings the decisive advantage that the eccentricity can be varied with a simple construction practically independent of the prevailing pressure in the pump. In addition, there is a very compact design which is not susceptible to faults and is easy to assemble. A particularly expedient embodiment of the invention provides for the diameter of the cage bolts to be dimensioned such that the compressive force acts centrally on the cage bolts in the area of the maximum eccentricity of the rotor core and thus the sliding friction in the slide sensor is minimized. It is also provided that, depending on the intended use and size, between three and twelve slides are evenly distributed between the rotor core and cage; however, preferably five to nine slides if high pressures are to be achieved (space reasons due to the massive design of the bolts, slides and transducers). The suction or. Pressure channels are preferably to be designed to extend radially in the housing over almost the entire width of the slide valve, care being taken to ensure that the inlet and outlet are as tangential as possible so that favorable inflow and outflow conditions prevail. In order to ensure optimal filling of the pump at high speeds, provision is made to prevent backflow by means of beam deflectors which are arranged radially directly to the rotor cage in the suction area.
Zur Vergrösserung der Pumpleistung bei gleicher Rotorgeometrie können zwei Rotoren axial hintereinander vorgesehen sein, wobei die Lagerung der Sekundärwelle unverändert bleibt, so dass eine symmetrisch Doppel¬ pumpe entsteht. Ggf. kann man ganze Schwenkschieberpumpen von einer gemeinsamen Welle antreiben und diese mit einzelnen Ein- und Auslässen oder vereinigten Ein- und Auslässen versehen.To increase the pump power with the same rotor geometry, two rotors can be provided axially one behind the other, the bearing of the secondary shaft remaining unchanged, so that a symmetrical double pump is created. Possibly. you can drive entire swing vane pumps from a common shaft and provide them with individual inlets and outlets or combined inlets and outlets.
Insgesamt zeichnet sich die vorgeschlagene Erfindung darin aus, dass die Konstruktion eine drehzahlunabhängige stufenlose Förderstromänderung bei hohen Kräften möglich macht und dass durch die Konstruktion der Schwenkschieber ein minimaler Verschleiss durch Gleitreibung resultiert und dass die Reinigung der Pumpe oder das Auswechseln von Verschleiss- teilen schnell und einfach auszuführen ist. Die Pumpe ist somit einfach, vielseitig und verschleissarm. Der Erfindungsgegenständ ist nachstehend mit Bezugnahme auf die Zeich¬ nungen beispielsweise näher erläutert. Es zeigen Fig. 1 den Längsschnitt durch die Schwenkschieberpumpe, Fig. 2 den Schnitt A-A durch den Rotor, Fig. 3 den Teilauschnitt des Ansaugbereichs mit Strahlablenker, Fig. 4 den Schnitt B-B durch Gehäuse und Rotor, Fig. 5 den Schnitt C-C durch den radial verschobenen Gleitring, Fig. 6 den Schnitt D-D durch den Verstellmechanismus, Fig. 7 den Längsschnitt durch den Rotor mit Gegenwand als Alternative, Fig. 8 den Längsschnitt der Primärwellenlagerung als Ergänzung zu Fig.7, Fig. 9 den Längsschnitt der Variante Doppelrotorpumpe, wobei nur wesent¬ liche Teile dargestellt sind. Das in den Fig. 1 bis 6 dargestellte Ausführungsbeispiel der erfindungs- gemässen Schwenkschieberpumpe steht auf einer rechteckigen Grundplatte 1, die als zusätzliche Versteifung gegen Verdrehung dient. Auf dieser stehen der vordere 2 und der hintere 3 Träger. An der Innenseite dieser Träger 2,3 sind die horizontal verschiebbar geführten Gleitringe 5,6 sowie der dazwischen liegende Lagerträger 4 formschlüssig eingesetzt. An der vorderen Seite des Trägers 2 ist das Pumpengehäuse 19 mittels Schrauben fixiert. Das Pumpengehäuse 19 wird mit dem Lagerdeckel 18, der das Gleitlager 26 der Primärwelle 12 enthält, abgeschlossen. Rück¬ seitig an den hinteren Träger 3 ist der Lagerflansch 10 angeschraubt, der die hintere Lagerung mittels Gleitlager 26 der Primärwelle 12 ent- hält und somit ein Teil der Rückwand darstellt. Im Pumpengehäuse 19 ist ein Pumpkanal e mit Einlass a, der Dichtbereich f und der Auslass b mit Auslassraum g ausgebildet. In ihr läuft ein hohlzylinderförmiger Rotor 13, der am Umfang zu gleichen Abständen versetzt axiale Bohrungen aufweist, die den äusseren Zylindermantel durchbrechen. Diese Bohrungen enthalten die einteilig ausgebildeten Schieberaufnehmer 16, die ihrer¬ seits die einarmigen Schieber 15 aufnehmen. Die einarmigen Schieber 15 sind am oberen Ende an Käfigbolzen 14 drehbar gelagert und dichten mit ihrer runden Oberseite den Rotorkäfig h gegen das Pumpengehäuse 19 mit Minimalspalt im Dichtbereich f ab. Der Rotorkäfig h, bestehend aus Rotorwand 17 und den umfangmässig zu gleichen Anständen angeordneten einseitig in dieser fixierten sechs Käfigbolzen 14, sitzt auf der Pri¬ märwelle 12 und wird von dieser angetrieben. Der Rotor 13, der mittels Schieberaufnehmer 16 und Schieber 15 mit dem Rotorkäfig verbunden ist, sitzt fest verbunden' auf der Sekundärwelle 7, die ausserhalb des Pumpen¬ gehäuses 19 im Lagerträger 4 mit einem Rollenlager 8 und einem Kugel¬ lager 9 drehbar gelagert ist. Diese Sekundärwelle 7 lässt sich nun in der Horizontalebene verschieben, so dass sich die Exzentrizität des Rotors 13, der auf dieser Welle sitzt, variieren lässt. Dies wird ermöglicht durch den Verstellmechanismus, der aus vier Stützbolzen mit darüber geschobenen Auflagestücken 31, dem Halter 32, der Verstell¬ welle 33 und dem Verstellrad 34 besteht. Wird das Verstellrad 34 nun gedreht, so verschiebt sich nun der Lagerträger 4, zusammen mit den an beiden Seiten formschlüssig angebrachten Gleitringen 5,6 in der horizontalen Ebene. Diese, zwischen den Trägern 2,3 angeordneten, ver¬ schiebbar geführten Sekundärwellelagerung 4,5,6,8,9 wird mit sechs Spannschrauben 25 im Spiel eingestellt. Die Abdichtung zum Rotor 13 übernimmt eine auf der Sekundärwelle 7 montierte Gleitringdichtung 23, die in einer genügend grossen Bohrung für die horizontale Verschie¬ bung im Träger 2 zu liegen kommt. Das Lager 9 wird durch den Wellen- dichtring 28, die Rückseite der Pumpe mit dem Wellendichtring 24, abge¬ dichtet. Der Zwischenring 20 und der Führungsbolzen 22 dienen zur axia¬ len Führung der Primärwelle 12. Der Deckel 21 dichtet die Pumpe gegen aussen ab.Overall, the proposed invention is characterized in that the construction enables a speed-independent, infinitely variable flow rate change with high forces and that the design of the swivel slide results in minimal wear due to sliding friction and that the cleaning of the pump or the replacement of wear parts is quick and easy is to be carried out. The pump is therefore simple, versatile and low-wear. The subject matter of the invention is explained in more detail below with reference to the drawings, for example. 1 shows the longitudinal section through the rotary vane pump, FIG. 2 shows the section AA through the rotor, FIG. 3 shows the partial section of the suction area with beam deflector, FIG. 4 shows the section BB through the housing and rotor, FIG. 5 shows the section CC through the 6 the section DD through the adjusting mechanism, FIG. 7 the longitudinal section through the rotor with counter wall as an alternative, FIG. 8 the longitudinal section of the primary shaft bearing as a supplement to FIG. 7, FIG. 9 the longitudinal section of the double rotor pump variant, only essential parts are shown. The exemplary embodiment of the swivel vane pump according to the invention shown in FIGS. 1 to 6 stands on a rectangular base plate 1, which serves as additional stiffening against rotation. The front 2 and rear 3 supports are on this. On the inside of these supports 2, 3, the horizontally displaceable slide rings 5, 6 and the bearing support 4 located between them are inserted in a form-fitting manner. The pump housing 19 is fixed on the front side of the carrier 2 by means of screws. The pump housing 19 is closed with the bearing cover 18, which contains the slide bearing 26 of the primary shaft 12. The bearing flange 10, which contains the rear bearing by means of slide bearings 26 of the primary shaft 12 and is thus part of the rear wall, is screwed to the rear of the rear carrier 3. A pump channel e with inlet a, the sealing area f and the outlet b with outlet space g are formed in the pump housing 19. A hollow cylindrical rotor 13 runs in it, which has axial bores which are offset at equal intervals on the circumference and which break through the outer cylinder jacket. These bores contain the one-piece slide receptacles 16, which in turn receive the single-arm slide 15. The one-armed slides 15 are rotatably mounted at the upper end on cage bolts 14 and, with their round upper side, seal the rotor cage h against the pump housing 19 with a minimal gap in the sealing area f. The rotor cage h, consisting of the rotor wall 17 and the circumferentially equally spaced six cage bolts 14 fixed on one side, sits on the primary shaft 12 and is driven by it. The rotor 13, which is connected to the rotor cage by means of slide sensor 16 and slide 15, sits firmly connected 'on the secondary shaft 7, which is rotatably mounted outside the pump housing 19 in the bearing bracket 4 with a roller bearing 8 and a ball bearing 9. This secondary shaft 7 can now be shifted in the horizontal plane, so that the eccentricity of the rotor 13, which is seated on this shaft, can be varied. This is made possible by the adjustment mechanism, which consists of four support bolts with support pieces 31 pushed over them, the holder 32, the adjustment shaft 33 and the adjustment wheel 34. If the adjusting wheel 34 is now rotated, the bearing bracket 4 is now displaced in the horizontal plane together with the sliding rings 5, 6 which are positively attached on both sides. This, displaceably guided secondary shaft bearing 4, 5, 6, 8, 9 arranged between the supports 2, 3 is set in play with six clamping screws 25. The seal to the rotor 13 is provided by a mechanical seal 23 mounted on the secondary shaft 7, which comes to rest in a sufficiently large bore for the horizontal displacement in the carrier 2. The bearing 9 is sealed by the shaft sealing ring 28, the rear of the pump with the shaft sealing ring 24. The intermediate ring 20 and the guide pin 22 serve for the axial guidance of the primary shaft 12. The cover 21 seals the pump from the outside.
Aus Fig. 1 ist ersichtlich, dass die Schieber 15 mit einer Zinne in das entsprechend ausgebildete Gegenstück, dem Schieberaufnehmer 16 eingreifen. Beim einteiligen Schieberaufnehmer 16 ist somit ein Verklem¬ men ausgeschlossen. Dieses Schloss/Schlüssel-Prinzip ist umkehrbar, indem der Schieber 15 mit zwei oder mehr Zinnen ausgebildet wird, die in den entsprechend ausgebildeten Schieberaufnehmer 16 eingreifen (vgl. Fig. 9). Wichtig ist jedoch, dass die Zinnen rechteckförmig ausgebildet sind, um Leckverluste zu verhindern. Fig. 3 zeigt den für hohe Drehzahlen im Einlass a vorgesehenen Strahl- ablenker 29, der aus einzelnen tangential angeordneten Leitblechen oder nutenförmigen Ausfräsungen im einlasseitig geschlossenen Gehäuse 19 besteht. Die Geometrie der einzelnen Leitbleche oder der Ausfräsungen ist auf die herrschenden Bedingungen abzustimmen. Fig. 7 und 8 zeigen die Ausführungsvariante des Rotorskäfigs h mit Rotorrückwand 35. Bei dieser Ausführungsvariante bilden Rotorkern 13, Rotorwand 17', Mitnehmerschrauben 41, Schieber 15', Schieberaufnehmer 16' und die Rotorrückwand eine Baugruppe. Dabei wird der Rotorkern wieder auf der Sekundärwelle 7 abgestützt und mit einem Federkeil 36 gegen Verdrehung gesichert. Die Rotorwand 17' sitzt auf der Primärwelle, wobei der Federkeil 37 als Mitnehmer dient. Die Spannschraube 39 spannt mittels Spannbüchse 38 die gesamte Baugruppe 13,17' ,41,15' ,16' ,35 axial auf die Sekundärwelle 7'. Bei der Montage oder einer Reinigung der Pumpe kann somit die Baugruppe 13,17' ,41,15,16' ,35 nach dem Lösen der Spannschraube 39 von der Primärwelle 12' resp. Sekundärwelle 7' abgezo¬ gen werden. Fig. 8 zeigt die antriebsseitige Lagerung der Primärwelle 12' mittels Kugellager 42. Die axiale Justierung der Primärwelle 12' erfolgt durch den Justierring 43 und den Spannring 44,- welcher gleich¬ zeitig die Primärwelle 12' axial sichert. Die Sicherungsschrauben 46, 47 sichern Justierring 43 und Spannring 44 auf der Primärwelle 12'. Der Abdeckflansch 45 behält das Kugellager 42 in seinem Sitz und dient gleichzeitig als Abdeckung. Fig. 9 zeigt die Variante einer Doppelrotorpumpe, die bis auf die ein¬ seitige Wellendurchführung eine Spiegelbildsymmetrie der Fig. 7 mit mittiger Lagerung 8' darstellt.From Fig. 1 it can be seen that the slider 15 engage with a pinnacle in the correspondingly designed counterpart, the slider sensor 16. With the one-piece slide sensor 16, jamming is therefore excluded. This lock / key principle is reversible in that the slide 15 is formed with two or more pinnacles which engage in the correspondingly designed slide receiver 16 (cf. FIG. 9). However, it is important that the battlements are rectangular to prevent leakage. 3 shows the jet deflector 29 which is provided for high speeds in the inlet a and which consists of individual tangentially arranged guide plates or groove-shaped cutouts in the housing 19 which is closed on the inlet side. The geometry of the individual baffles or the cutouts must be matched to the prevailing conditions. 7 and 8 show the embodiment variant of the rotor cage h with the rotor rear wall 35. In this embodiment variant, the rotor core 13, rotor wall 17 ', driving screws 41, slide 15', slide receiver 16 'and the rotor rear wall form an assembly. The rotor core again supported on the secondary shaft 7 and secured with a spring key 36 against rotation. The rotor wall 17 'sits on the primary shaft, the spring wedge 37 serving as a driver. The clamping screw 39 clamps the entire assembly 13, 17 ', 41, 15', 16 ', 35 axially onto the secondary shaft 7' by means of the clamping bush 38. When assembling or cleaning the pump, the assembly 13, 17 ', 41, 15, 16', 35 can, respectively, after loosening the clamping screw 39 from the primary shaft 12 '. Secondary shaft 7 'are deducted. 8 shows the drive-side mounting of the primary shaft 12 'by means of ball bearings 42. The primary shaft 12' is axially adjusted by the adjusting ring 43 and the clamping ring 44, which at the same time axially secures the primary shaft 12 '. The locking screws 46, 47 secure the adjusting ring 43 and the clamping ring 44 on the primary shaft 12 '. The cover flange 45 holds the ball bearing 42 in its seat and also serves as a cover. FIG. 9 shows the variant of a double rotor pump which, apart from the shaft passage on one side, represents a mirror image symmetry of FIG. 7 with a central bearing 8 '.
Beim Antrieb der Primärwelle 12 in der angegebenen Drehrichtung saugen die grösser werdenden Zellen c zwischen den sich am Einlass a vorbeibe- wegenden schwenkbaren Schiebern 15 das zu fördernde Medium an, um es am Auslass b bei sich verkleinernden Zellengrösse c aus dem Pumpenge¬ häuse 19 herauszudrücken. Diese Wirkungsweise ist weitgehend bekannt und braucht deshalb nicht noch näher erläutert zu werden. Durch die vorgeschlagene Zwangsführung der einarmigen Schiebern 15 mittels Käfig- bolzen 14 und einteiligen Schieberaufnehmer 16 wird Reibung durch Zen¬ trifugalkräfte an das Pumpengehäuse 19 verhindert und dennoch der Ar¬ beitsraum im Dichtbereich f genügend abgedichtet. Die vorgeschlagene in der Horizontalebene verschiebbare aussenseitige Rotorlagerung 4,5,6, 8,9 ermöglicht hohe Kräfte auf den Rotor 13 und macht zudem die Pumpe unempfindlich gegenüber nichtschmierenden Fördermedien, bei gleichzei¬ tiger stufenloser Fördermengenregelung. BezugszeichenlisteWhen the primary shaft 12 is driven in the specified direction of rotation, the cells c, which are becoming larger, suck the medium to be conveyed between the pivotable slides 15 moving past the inlet a, in order to press it out of the pump housing 19 at the outlet b, with the cell size c decreasing . This mode of action is largely known and therefore does not need to be explained in more detail. The proposed positive guidance of the one-armed slides 15 by means of cage bolts 14 and one-piece slider receptacles 16 prevents friction by centrifugal forces on the pump housing 19 and nevertheless seals the working space in the sealing area f sufficiently. The proposed external rotor bearing 4, 5, 6, 8, 9, which can be displaced in the horizontal plane, enables high forces on the rotor 13 and also makes the pump insensitive to non-lubricating delivery media, with simultaneous stepless flow rate control. Reference list
Einzelteileindividual parts
1 Grundplatte 35 Rotorrückwand1 base plate 35 rotor rear wall
2 vorderer Träger 36 Federkeil2 front supports 36 spring wedge
3 hinterer Träger 37 Federkeil3 rear carrier 37 spring key
4 Lagerträger • 38 Spannbüchse4 bearing brackets • 38 clamping bush
5 vorderer Gleitring 39 Spannschraube5 front slide ring 39 clamping screw
6 hinterer Gleitring 40 Lagerbüchse6 rear slide ring 40 bearing bush
7 Sekundärwelle 41 Mitnehmerschraube7 secondary shaft 41 drive screw
8 Rollenlager 42 Kugellager8 roller bearings 42 ball bearings
9 Kugellager 43 Justierring9 ball bearings 43 adjustment ring
10 Lagerflansch 44 Spannring10 bearing flange 44 clamping ring
11 Deckel 45 Abdeckflansch11 Cover 45 cover flange
12 Primärwelle 46 Sicheruttgsschraube12 primary shaft 46 safety screw
13 Rotor 47 Sicherungsschraube13 Rotor 47 locking screw
14 Käfigbolzen14 cage bolts
15 Schieber Verschiedenes15 slider miscellaneous
16 Schieberaufnehmer a Einlass16 slide sensor a inlet
17 Rotorwand b Auslass17 Rotor wall b outlet
18 Lagerdeckel c Zelle18 bearing cap c cell
19 Pumpengehäuse d Exzentrizität der Achse19 Pump housing d eccentricity of the axis
20 Zwischenring e Pumpkanal20 intermediate ring e pump channel
21 Deckel f Dichtbereich21 cover for sealing area
22 Führungsbolzen g Auslassraum22 guide bolts g outlet space
23 Gleitringdichtung h Rotorkäfig23 Mechanical seal h rotor cage
24 Wellendichtung24 shaft seal
25 Spannschraube25 clamping screw
26 Gleitlager26 plain bearings
27 Federkeil27 spring wedge
28 Wellendichtring28 shaft seal
29 Strahlablenker29 beam deflectors
30 Stützbolzen30 support bolts
31 Auflagestück31 support piece
32 Halter32 holders
33 Verstellwelle33 adjustment shaft
34 Verstellrad 34 adjusting wheel

Claims

Ansprüche Expectations
1. Schwenkschieberpumpe mit Pumpengehäuse (19), Einlass (a), Auslass (b), Pumpkanal mit Ansaugraum (e), Dichtbereich (f) und Auslassraum (g) mit einem radial verstellbaren Rotor und mit Schiebern, die beim Umlauf des Rotors den Pumpraum abdichten, dadurch gekennzeichnet, dass der auf einer hohlen Sekundärwelle (7) sitzende Rotor (13) sich in einem Rotorkäfig (h) befindet und am Umfang einteilige, drehbar angeord¬ nete Schieberaufnehmer (16) aufweist, in welchen die an Käfigbolzen (14) drehbar gelagerten einarmigen Schieber (15) eindringen und somit bei der Drehung des Rotorkäfigs (h) resp. des Rotors (13) die variable Exzentrizität der Achse (d) durch eine Schwenk-Hub-Bewegung auffangen und somit direkt das Pumpengehäuse (19) im Dichtbereich (f) abdichten ohne dass die Rotorlagerung mit dem Fördermedium in Berührung kommt.1.Pivoting vane pump with pump housing (19), inlet (a), outlet (b), pump channel with suction chamber (e), sealing area (f) and outlet chamber (g) with a radially adjustable rotor and with slides that rotate when the rotor rotates Sealing the pump chamber, characterized in that the rotor (13) seated on a hollow secondary shaft (7) is located in a rotor cage (h) and has one-piece, rotatably arranged slide receptacles (16) in which the cage bolts (14 ) rotatably mounted single-arm slide (15) penetrate and thus when the rotor cage (h) resp. of the rotor (13) absorb the variable eccentricity of the axis (d) by means of a swivel-stroke movement and thus directly seal the pump housing (19) in the sealing area (f) without the rotor bearing coming into contact with the pumped medium.
2. Schwenkschieberpumpe nach Anspruch 1, dadurch gekennzeichnet, dass der Kraftfluss ausgehend von der Primär- welle (12) auf den Rotorkäfig (h) über die Schieber (15) auf das Medium verläuft.2. Swing vane pump according to claim 1, characterized in that the power flow starting from the primary shaft (12) on the rotor cage (h) via the slide (15) on the medium.
3. Schwenkschieberpumpe nach Anspruch 1, dadurch gekennzeichnet, dass im Ansaugraum (e), unmittelbar zum Rotor¬ käfig (h) hin, Strahlablenker (29) angeordnet sind.3. Swing vane pump according to claim 1, characterized in that in the suction chamber (e), directly to the rotor cage (h), beam deflectors (29) are arranged.
4, Schwenkschieberpumpe nach Anspruch 1, dadurch gekennzeichnet, dass an den Schiebern rechteckförmige Zinnen (15) ausgebildet sind, die in die entsprechend ausgebildeten Schieber¬ aufnehmer (16) im Schloss/Schlüssel-Prinzip eindringen, derart, dass die Schieberaufnehmer (16) einteilig vorliegen.4, swivel slide pump according to claim 1, characterized in that rectangular slats (15) are formed on the slides, which penetrate into the correspondingly designed slide receptacles (16) in the lock / key principle, such that the slide receptacles (16) are in one piece available.
5, Schwenkschieberpumpe nach Anspruch 1, dadurch gekennzeichnet, dass der Rotor (13) resp. der Rotorkäfig (h) drei bis zwölf, vorzugsweise fünf bis neun Schieber (15) aufweist.5, rotary vane pump according to claim 1, characterized in that the rotor (13) respectively. the rotor cage (h) has three to twelve, preferably five to nine slides (15).
6. Schwenkschieberpumpe nach Anspruch 1, dadurch gekennzeichnet, dass der Dichtbereich (f) mindestens das Bogen- mass 2 Pi dividiert durch Anzahl Schieber aufweist. 6. Swing vane pump according to claim 1, characterized in that the sealing area (f) has at least the radian measure 2 pi divided by the number of pusher.
7. Schwenkschieberpumpe nach Anspruch 1, dadurch gekennzeichnet, dass der Lagerträger (4) der Sekundärwelle (7) zwischen den beiden Trägern (2,3) mittels den beidseitig angeord¬ neten Gleitringen (5,6) und dem Verstellmechanismus (30,31,32,33,34) stufenlos radial in der Horizontalebene verschoben werden kann und somit direkt die Rotorexzentrizität (d) variiert werden kann.7. Swing vane pump according to claim 1, characterized in that the bearing bracket (4) of the secondary shaft (7) between the two brackets (2, 3) by means of the sliding rings (5, 6) arranged on both sides and the adjusting mechanism (30, 31, 32,33,34) can be continuously shifted radially in the horizontal plane and thus the rotor eccentricity (d) can be varied directly.
8. Schwenkschieberpumpe nach Anspruch 1, dadurch gekennzeichnet, dass die Konstruktion eine spiegelbildsymme¬ trische axiale Anordnung von zwei oder mehreren, unter Zwischenschaltung von Zwischenlagerungen und Trennwänden, Pumpelementen (13,17' ,41' ,15' , 16',35) ermöglicht.8. Swing vane pump according to claim 1, characterized in that the construction allows a mirror image symmetrical axial arrangement of two or more, with the interposition of intermediate bearings and partitions, pump elements (13, 17 ', 41', 15 ', 16', 35) .
9. Schwenkschieberpumpe nach Anspruch 1, dadurch gekennzeichnet, dass der Rotorkäfig (h) einseitig fixierte9. Swing vane pump according to claim 1, characterized in that the rotor cage (h) fixed on one side
Käfigbolzen (14) aufweist, derart, dass zum Auswechseln der Schiebern (15) nur der Lagerdeckel (18) und die Rotorwand (17) entfernt werden muss.Cage bolt (14) has such that only the bearing cover (18) and the rotor wall (17) have to be removed to replace the slides (15).
10. Schwenkschieberpumpe nach. Anspruch 1, dadurch gekennzeichnet, dass die angetriebene Primärwelle (12) innerhalb einer mit mindestens dem Maximalexzentrizitätsabstand (d) aufweisenden hohlen Sekundärwelle (7) dreht, die (7) ausserhalb des Pumpengehäuses (19) im Lagerträger (4) drehbar gelagert (8,9) ist.10. Swing vane pump after. Claim 1, characterized in that the driven primary shaft (12) rotates within a hollow secondary shaft (7) having at least the maximum eccentricity distance (d), which (7) rotatably supports (7) outside the pump housing (19) in the bearing bracket (4), 9) is.
11. Schwenkschieberpumpe nach Anspruch 1, dadurch gekennzeichnet, dass das als Baugruppe (13,17' ,41,15' ,16' ,35) bestehende kompakte Pumpelement axial, nach dem Lösen der Spannschraube (39) bei enterntem Lagerdeckel (18'), inklusiv der Spannbüchse (38) von der Primär- (12), resp. Sekundärwelle (7) abgezogen werden kann. 11. Swing vane pump according to claim 1, characterized in that the existing as an assembly (13, 17 ', 41, 15', 16 ', 35) compact pump element axially, after loosening the clamping screw (39) with the bearing cap (18') removed. , including the clamping sleeve (38) from the primary (12), respectively. Secondary shaft (7) can be removed.
EP87906386A 1986-10-27 1987-10-13 Swivelling vane pump Expired - Lifetime EP0294399B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT87906386T ATE59438T1 (en) 1986-10-27 1987-10-13 VALVE PUMP.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH4252/86A CH673509A5 (en) 1986-10-27 1986-10-27
CH4252/86 1986-10-27

Publications (2)

Publication Number Publication Date
EP0294399A1 true EP0294399A1 (en) 1988-12-14
EP0294399B1 EP0294399B1 (en) 1990-12-27

Family

ID=4272646

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87906386A Expired - Lifetime EP0294399B1 (en) 1986-10-27 1987-10-13 Swivelling vane pump

Country Status (8)

Country Link
US (1) US4958992A (en)
EP (1) EP0294399B1 (en)
JP (1) JP2587665B2 (en)
AT (1) ATE59438T1 (en)
CH (1) CH673509A5 (en)
DE (1) DE3767154D1 (en)
RU (1) RU1809864C (en)
WO (1) WO1988003229A2 (en)

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WO1999027255A1 (en) 1997-11-19 1999-06-03 Notron Engineering Ag Swivelling vane pump

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Also Published As

Publication number Publication date
DE3767154D1 (en) 1991-02-07
US4958992A (en) 1990-09-25
JP2587665B2 (en) 1997-03-05
WO1988003229A2 (en) 1988-05-05
RU1809864C (en) 1993-04-15
AU8074787A (en) 1988-05-25
ATE59438T1 (en) 1991-01-15
CH673509A5 (en) 1990-03-15
JPH01501082A (en) 1989-04-13
EP0294399B1 (en) 1990-12-27
AU625256B2 (en) 1992-07-02
WO1988003229A3 (en) 1988-06-30

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