EP0539673B1 - Internal gear pump with two ring gears and one common pinion - Google Patents
Internal gear pump with two ring gears and one common pinion Download PDFInfo
- Publication number
- EP0539673B1 EP0539673B1 EP92113789A EP92113789A EP0539673B1 EP 0539673 B1 EP0539673 B1 EP 0539673B1 EP 92113789 A EP92113789 A EP 92113789A EP 92113789 A EP92113789 A EP 92113789A EP 0539673 B1 EP0539673 B1 EP 0539673B1
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- European Patent Office
- Prior art keywords
- ring gears
- pinion
- internal gear
- gear pump
- annular gears
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
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- 230000002706 hydrostatic effect Effects 0.000 description 7
- 238000011161 development Methods 0.000 description 2
- 230000018109 developmental process Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 230000004323 axial length Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 239000002655 kraft paper Substances 0.000 description 1
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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
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
- F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
Definitions
- the present invention relates to an internal gear pump for generating high pressure according to the preamble of claim 1.
- a pump of this generic type is known from DE 41 04 397 A1.
- Internal gear pumps generally have an internally toothed ring gear with which an externally toothed pinion meshes with a smaller number of teeth, i.e. is drivingly engaged.
- the toothing of such pumps - based on the diameter of the pinion or the ring gear - is relatively narrow, so that - after the volume flow to be pumped is determined by the height of the teeth and the width of the toothing, this volume flow in conventional pumps constructive reasons is limited.
- this generic internal gear pump is such that the ring gears driven jointly by the pinion interact synergistically as if only a single ring gear were present.
- the ring gears are hydraulically pressed apart at their axial contact surfaces.
- a pair of forces is generated at each of the ring gears, which possibly inclines the ring gears relative to one another, i.e. canted.
- the reason for these - in particular wear-promoting - inadequacies lies in the manner in which the hydrostatic relief of the ring gear pair (s) is relieved.
- the object underlying the present invention is therefore to eliminate the inadequacies mentioned, i.e. to specify an internal gear pump of the generic type, in which the axial contact surfaces of the ring gears abutting one another are stabilized. Consequently, this means that the ring gears, which are driven together by the pinion, operate exactly like a single ring gear, i.e. behave like a one-piece ring gear.
- the above-mentioned object is achieved in that, in the area of the abovementioned bearing surfaces of the ring gears, a counter bearing (abutment) is provided, viewed from the side of the pressure connection.
- FIG. 1 and 2 show in a longitudinal section and a cross section a sickle-free, head-sealing and backlash-type internal gear pump, each with a flank sealing, in the area of a middle housing part 1, which is followed by further housing parts 2 and 3 on both sides.
- the entire internal gear pump with the housing parts 1, 2 and 3 has an overall axial length L.
- An externally toothed pinion 5 fastened to a drive shaft 4 is in engagement with an internally toothed hollow pair 6 ′, 6 ⁇ .
- the teeth 12 of the pinion 5 on the one hand and the ring gears 6 ', 6 ⁇ of the ring gear pair on the other hand, have an axial width B; the pinion 5 has a pitch circle diameter d0.
- the width of the toothing B is larger than the pitch circle diameter d0.
- the pinion 5 and the ring gears 6 ', 6 ⁇ are not mounted coaxially to each other, but eccentric; furthermore, the pinion 5 has one tooth less than the ring gears 6 ', 6 ⁇ , so that in each case the outside of a toothed head 13 on the pinion 5 comes into contact with the inside of a toothed head 14 of the ring gears 6', 6 ⁇ .
- a suction connection 7 can also be seen in the zone in which the teeth of the pinion 5 or the ring gears 6 ', 6' come out of engagement when rotating in the direction of the arrow X.
- a pressure connection 10 is located - also starting from a pressure pocket 11 extending over a circumferential area on the ring gears 6 ', 6' - on the opposite side of the internal gear pump.
- a counter bearing 25 bridging the axial contact surfaces of the ring gears 6 ', 6' from the side of the pressure connection 10 is provided.
- This counter bearing 25 is formed as an integral part of the housing middle part 1 and serves as an abutment for the area of the ring gears 6 ', 6' adjacent to the axial contact surfaces of the ring gears 6 ', 6'. In this respect, it is readily apparent that the ring gears 6 ', 6 ⁇ are fixed exactly in their mounting position.
- a further development of the counter bearing 25 and possibly the ring gears 6 ', 6' in the area of their axial contact surfaces consists in the fact that in the counter bearing 25 and possibly in the mentioned area of the ring gears 6 ', 6' a relief groove conjugated to the contact surface of the axial contact surfaces 26 and 27 is provided is. These communicating relief grooves 26, 27 are open to the suction port 7.
- Fig. 3 a section of the internal gear pump according to FIG. 1 is shown, correspondingly, ie along the section line CD of FIG. 2, and this in the area of the abutting axial contact surfaces of the ring gears 6 ', 6 ⁇ .
- the counter bearing 25 is part of the middle housing part 1.
- the recesses adjoining on both sides of the counter bearing 25 are part of the pressure pocket 11.
- FIGS. 4, 5 and 6 The operation of the counter bearing provided according to the invention will be explained in more detail with reference to FIGS. 4, 5 and 6.
- a pair of ring gears 6 ', 6 ⁇ is shown, on which - indicated by force arrows - act on certain forces.
- FIG. 4 shows an enlarged section from FIG. 1, but without a counter bearing.
- the two ring gears 6 ', 6 ⁇ are used in the housing parts 2, 3 and are supported on the support shoulders of the middle housing part 1.
- radial openings 17 are provided, through which the pressure or delivery medium from the inside of the internal gear pump (from the pressure chamber between the pinion and the ring gears) is conveyed to the pressure connection 10.
- the hydrostatic relief on the ring gears means that the axial forces acting on the axial contact surfaces are greater than those acting on the outer sides; this results in a resulting axial force that tries to push the ring gears apart.
- the structural design is such that the forces acting on the ring gears in the conveying direction and the forces resulting from the hydrostatic relief are not exactly opposite; this creates offset attacking forces Md, which in turn results in a pair of forces that exerts a torque on the ring gears 6 ', 6 ⁇ .
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Arrangement And Driving Of Transmission Devices (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
Abstract
Description
Die vorliegende Erfindung betrifft eine Innenzahnradpumpe zur Erzeugung von Hochdruck nach dem Oberbegriff des Patentanspruchs 1. Eine Pumpe dieser gattungsgemäßen Bauart ist aus der DE 41 04 397 A1 bekannt.The present invention relates to an internal gear pump for generating high pressure according to the preamble of
Innenzahnradpumpen weisen im allgemeinen ein innenverzahntes Hohlrad auf, mit dem ein außenverzahntes Ritzel mit geringerer Zähnezahl kämmt, d.h. treibend im Eingriff steht. In der Regel ist die Verzahnung derartiger Pumpen - bezogen auf den Durchmesser der Ritzel beziehungsweise des Hohlrades - relativ schmal, so daß - nachdem der zu fördernde Volumenstrom durch die Höhe der Zähne und die Breite der Verzahnung bestimmt ist, dieser Volumenstrom bei den gängigen Pumpen aus konstruktiven Gründen begrenzt ist.Internal gear pumps generally have an internally toothed ring gear with which an externally toothed pinion meshes with a smaller number of teeth, i.e. is drivingly engaged. As a rule, the toothing of such pumps - based on the diameter of the pinion or the ring gear - is relatively narrow, so that - after the volume flow to be pumped is determined by the height of the teeth and the width of the toothing, this volume flow in conventional pumps constructive reasons is limited.
Zur Steigerung des Fördervolumens einer Innenzahnradpumpe ist es jedoch bereits bekannt, die Pumpe mit zwei (und gegebenenfalls mehr) Hohlrädern auszurüsten. Der Hintergrund dieser Konzeption ist darin zu sehen, daß einer einfachen Verbreiterung eines Hohlrades fertigungstechnische Grenzen gesetzt sind, mit der Konsequenz, daß eine Steigerung des Volumenstroms allenfalls dadurch erreichbar ist, daß zwei (und gegebenenfalls mehr) Hohlräder koaxial angeordnet werden, die dann gemeinsam mit einem einteiligen Ritzel in Eingriff stehen. Eine Innenzahnradpumpe dieser Art ist als Ausführungsvariante in der genannten DE 41 04 397 A1 offenbart.To increase the delivery volume of an internal gear pump, however, it is already known to equip the pump with two (and possibly more) ring gears. The background to this concept is the fact that a simple widening of a ring gear has production-technical limits, with the consequence that an increase in the volume flow can only be achieved by arranging two (and possibly more) ring gears coaxially, which are then together with engage a one-piece sprocket. An internal gear pump of this type is disclosed as a variant in the aforementioned DE 41 04 397 A1.
Die Funktionsweise dieser gattungsgemäßen Innenzahnradpumpe ist so, daß die vom Ritzel gemeinsam angetriebenen Hohlräder synergistisch so zusammenwirken, als wäre nur ein einziges Hohlrad vorhanden. In der Praxis hat sich dabei nun gezeigt, daß beim Einsatz eines Hohlradpaares in einer Innenzahnradpumpe die Hohlräder an ihren axialen Berührungsflächen hydraulisch auseinandergedrückt werden. Darüberhinaus ist auch zu beobachten, daß an den Hohlrädern je ein Kräftepaar entsteht, welches die Hohlräder gegebenenfalls relativ zueinander schrägstellt, d.h. verkantet. Die Ursache für diese - insbesondere verschleißfördernden - Unzulänglichkeiten liegt in der Art und Weise der hydrostatischen Entlastung der (des) Hohlradpaare(s).The operation of this generic internal gear pump is such that the ring gears driven jointly by the pinion interact synergistically as if only a single ring gear were present. In practice, it has now been shown that when a pair of ring gears is used in an internal gear pump, the ring gears are hydraulically pressed apart at their axial contact surfaces. In addition, it can also be observed that a pair of forces is generated at each of the ring gears, which possibly inclines the ring gears relative to one another, i.e. canted. The reason for these - in particular wear-promoting - inadequacies lies in the manner in which the hydrostatic relief of the ring gear pair (s) is relieved.
Die der vorliegenden Erfindung zugrunde liegende Aufgabe besteht somit darin, die genannten Unzulänglichkeiten zu eliminieren, d.h. eine Innenzahnradpumpe der gattungsgemäßen Art anzugeben, bei der die axialen Berührungsflächen der aneinander anliegenden Hohlräder stabilisiert sind. Konsequenterweise bedeutet dies, daß die gemeinsam vom Ritzel angetriebenen Hohlräder sich während des Betriebs exakt wie ein Einzel-Hohlrad, d.h. wie ein einstückiges Hohlrad verhalten.The object underlying the present invention is therefore to eliminate the inadequacies mentioned, i.e. to specify an internal gear pump of the generic type, in which the axial contact surfaces of the ring gears abutting one another are stabilized. Consequently, this means that the ring gears, which are driven together by the pinion, operate exactly like a single ring gear, i.e. behave like a one-piece ring gear.
Die vorgenannte Aufgabe wird dadurch gelöst, daß im Bereich der genannten Anlageflächen der Hohlräder von der Seite des Druckanschlusses her betrachtet ein Gegenlager (Wiederlager) vorgesehen ist.The above-mentioned object is achieved in that, in the area of the abovementioned bearing surfaces of the ring gears, a counter bearing (abutment) is provided, viewed from the side of the pressure connection.
Damit steht nunmehr eine Innenzahnradpumpe zur Verfügung, bei der während des Pumpbetriebs die Hohlräder an ihren axialen Berührungsflächen aneinander gepreßt werden; darüberhinaus wird auch erreicht, daß keine aus der hydrostatischen Entlastung der Hohlradpaare resultierenden Kräftepaare wirksam werden und die Hohlräder relativ zueinander verdrehen können. Die erfindungsgemäß konzipierte Maßnahme gewährleistet, daß bezüglich der hydrostatischen Belastung jedes der gemeinsam angetriebenen Hohlräder einzeln für sich betrachtet werden kann und daß die Kräfte dadurch symmetrisch angreifen.An internal gear pump is thus now available, in which the ring gears are pressed against one another at their axial contact surfaces during pump operation; moreover, it is also achieved that no force pairs resulting from the hydrostatic relief of the ring gear pairs become effective and can rotate the ring gears relative to one another. The measure designed according to the invention ensures that, with regard to the hydrostatic load, each of the jointly driven ring gears can be considered individually and that the forces thereby act symmetrically.
Weiterbildungen und besondere Ausgestaltungen der erfindungsgemäßen Innenzahnradpumpe sind Gegenstand der Unteransprüche.Developments and special configurations of the internal gear pump according to the invention are the subject of the dependent claims.
Die Erfindung wird im folgenden anhand der Zeichnung näher erläutert. Diese zeigt in
- Fig. 1
- einen Teil-Längsschnitt (längs der Schnittlinie A-B nach Fig. 2) durch eine Innenzahnradpumpe mit einem Hohlradpaar;
- Fig. 2
- einen Querschnitt durch die Innenzahnradpumpe gemäß Fig. 1 im Bereich der Zahnkämmung zwischen dem Ritzel und den Hohlrädern;
- Fig. 3
- einen Teil-Längsschnitt durch die Innenzahnradpumpe mit einem Hohlradpaar und zwar analog Fig. 1 längs der Schnittlinie C-D nach Fig. 2 und im Bereich der aneinander angrenzenden axialen Berührungsflächen der Hohlräder;
- Fig. 4
- einen Ausschnitt des Teil-Längsschnitts gemäß Fig. 1, jedoch ohne Gegenlager, zur Darstellung der am Hohlradpaar wirkenden Kräfte und zwar längs der Schnittlinie A-B nach Fig. 2;
- Fig. 5
- einen Ausschnitt gemäß Fig. 4 - mit Gegenlager - zur Demonstration der Wirkung dieses Gegenlagers;
- Fig. 6
- einen Ausschnitt analog Fig. 4 und 5 zur Demonstration der auf das Hohlradpaar wirkenden "axialen Kraft".
- Fig. 1
- a partial longitudinal section (along the section line AB of FIG. 2) through an internal gear pump with a pair of ring gears;
- Fig. 2
- a cross section through the internal gear pump of Figure 1 in the region of the tooth comb between the pinion and the ring gears.
- Fig. 3
- a partial longitudinal section through the internal gear pump with a pair of ring gears, analogously to FIG. 1 along the section line CD according to FIG. 2 and in the region of the adjoining axial contact surfaces of the ring gears;
- Fig. 4
- a section of the partial longitudinal section of FIG 1, but without a counter bearing, to show the forces acting on the ring gear pair, namely along the section line AB of FIG. 2.
- Fig. 5
- a section of Figure 4 - with counter bearing - to demonstrate the effect of this counter bearing.
- Fig. 6
- a section analogous to FIGS. 4 and 5 to demonstrate the "axial force" acting on the ring gear pair.
Fig. 1 und 2 zeigen in einem Längsschnitt und einem Querschnitt eine sichellose, kopfdichtende und spielbehaftete jeweils mit einer Flanke dichtenden Innenzahnradpumpe, und zwar im Bereich eines Gehäusemittelteils 1, dem sich auf beiden Seiten weitere Gehäuseteile 2 und 3 anschließen. Die gesamte Innenzahnradpumpe mit den Gehäuseteilen 1, 2 und 3 hat eine axiale Gesamtlänge L. Ein auf einer Antriebswelle 4 befestigtes außenverzahntes Ritzel 5 steht in Eingriff mit einem innenverzahnten Hohlpaar 6′, 6˝. Die Verzahnungen 12 des Ritzels 5 einerseits beziehungsweise der Hohlräder 6′, 6˝ des Hohlradpaars andererseits, haben eine axiale Breite B; das Ritzel 5 hat einen Wälzkreisdurchmesser d0. Die Breite der Verzahnung B ist größer als der Wälzkreisdurchmesser d0. Das Ritzel 5 und die Hohlräder 6′, 6˝ sind nicht koaxial zueinander gelagert, sondern exzentrisch; ferner weist das Ritzel 5 einen Zahn weniger auf als die Hohlräder 6′, 6˝, so daß jeweils die Außenseite eines Zahnkopfs 13 am Ritzel 5 mit der Innenseite eines Zahnkopfs 14 der Hohlräder 6′, 6˝ in Berührung kommt.1 and 2 show in a longitudinal section and a cross section a sickle-free, head-sealing and backlash-type internal gear pump, each with a flank sealing, in the area of a
Zu erkennen ist ferner ein Sauganschluß 7 in der Zone, bei der unter Drehung in Pfeilrichtung X die Zähne des Ritzels 5, beziehungsweise der Hohlräder 6′, 6˝ außer Eingriff geraten. Dem Sauganschluß 7 im Gehäusemittelteil 1, in dem die Hohlräder 6′, 6˝und das Ritzel 5 gelagert sind, schließt sich in axialer Richtung jeweils zu den benachbarten Gehäuseteilen 2 und 3 hin ein Saugtasche 8 an, die sich über einen Teil der Mantelfläche 20 der Hohlräder 6′, 6˝ erstreckt. Ein Druckanschluß 10 befindet sich - ebenfalls ausgehend von einer sich über einen Umfangsbereich an den Hohlrädern 6′, 6˝ erstreckenden Drucktasche 11 - auf der gegenüberliegenden Seite der Innenzahnradpumpe. Die Zuströmung des zu pumpenden Mediums (Druckmedium) vom Sauganschluß 7 zum Innenraum der Innenzahnradpumpe, d.h. zu den Zahnlücken zwischen dem Ritzel 5 und den Hohlrädern 6 ′, 6 ˝, wodurch die Förderung des Druckmediums bewirkt wird, erfolgt über radiale Durchbrüche 17 in den Hohlrädern 6′, 6˝. Diese Durchbrüche 17 gehen jeweils von der Mantelfläche 20 der Hohlräder 6′, 6˝ aus und münden im Zahngrund der Hohlräder 6′, 6˝.A
Die im Vorstehenden erläuterte Innenzahnradpumpe ist Stand der Technik (vergleiche DE 41 04 397 A1). Bezugnehmend auf den in Fig. 1 dargestellten Längsschnitt läßt sich prinzipiell ohne weiteres erkennen, daß aufgrund der Strömungsrichtung des Druck- beziehungsweise Fördermediums und des hydrostatischen Drucks auf die Hohlräder 6′, 6˝ diese relativ zueinander verkantet werden.The internal gear pump explained above is state of the art (compare DE 41 04 397 A1). Referring to the longitudinal section shown in Fig. 1, it can in principle be readily recognized that due to the direction of flow of the pressure or delivery medium and the hydrostatic pressure on the
Um dieser Verkantung á priori entgegen zu wirken ist ein die axialen Berührungsflächen der Hohlräder 6′, 6˝ von der Seite des Druckanschlusses 10 her überbrückendes Gegenlager 25 vorgesehen. Dieses Gegenlager 25 ist als integraler Bestandteil des Gehäusemittelteils 1 ausgebildet und dient als Widerlager für den an die axialen Berührungsflächen der Hohlräder 6′, 6˝ angrenzenden Bereich der Hohlräder 6′, 6˝. Es ist insoweit ohne weiteres ersichtlich, daß die Hohlräder 6′, 6˝ exakt in ihrer Montageposition fixiert sind.In order to counteract this tilting a priori, a counter bearing 25 bridging the axial contact surfaces of the ring gears 6 ', 6' from the side of the
Eine Weiterbildung des Gegenlagers 25 und gegebenenfalls der Hohlräder 6′, 6˝ im Bereich ihrer axialen Berührungsflächen besteht darin, daß im Gegenlager 25 und gegebenenfalls im genannten Bereich der Hohlräder 6′, 6˝ eine zur Anlagefläche der axialen Berührungsflächen konjugierte Entlastungsnut 26 beziehungsweise 27 vorgesehen ist. Diese miteinander kommunizierenden Enlastungsnuten 26, 27 sind dabei zum Sauganschluß 7 hin offen.A further development of the counter bearing 25 and possibly the ring gears 6 ', 6' in the area of their axial contact surfaces consists in the fact that in the counter bearing 25 and possibly in the mentioned area of the ring gears 6 ', 6' a relief groove conjugated to the contact surface of the
In Fig. 3 ist ein Ausschnitt der Innenzahnradpumpe gemäß Fig. 1 dargestellt, und zwar entsprechend, d.h. längs der Schnittlinie C-D nach Fig. 2, und dies im Bereich der aneinander anliegenden axialen Berührungsflächen der Hohlräder 6′, 6˝. Aus der Darstellung nach Fig. 3 ist insbesondere zu erkennen, daß das Gegenlager 25 Teil des Gehäusemittelteils 1 ist. Die zu beiden Seiten des Gegenlagers 25 anschließenden Ausnehmungen sind Teil der Drucktasche 11.In Fig. 3 a section of the internal gear pump according to FIG. 1 is shown, correspondingly, ie along the section line CD of FIG. 2, and this in the area of the abutting axial contact surfaces of the
Anhand der Fig. 4, 5 und 6 soll die Wirkungsweise des erfindungsgemäß vorgesehenen Gegenlagers näher erläutert werden. In allen drei Zeichnungen ist ein Hohlräderpaar 6′, 6˝ dargestellt, an dem - jeweils über Kraftpfeile angedeutet - bestimmte Kräfte einwirken.The operation of the counter bearing provided according to the invention will be explained in more detail with reference to FIGS. 4, 5 and 6. In all three drawings, a pair of ring gears 6 ', 6˝ is shown, on which - indicated by force arrows - act on certain forces.
Fig. 4 zeigt einen vergrößerten Abschnitt aus Fig. 1, jedoch ohne Gegenlager. Die beiden Hohlräder 6′, 6˝ sind in den Gehäuseteilen 2, 3 eingesetzt und stützen sich an Tragschultern des Gehäusemittelteils 1 ab. In den Hohlrädern 6′, 6˝ sind jeweils radiale Durchbrüche 17 vorgesehen, über die das Druck- beziehungsweise Fördermedium aus dem Inneren der Innenzahnradpumpe (aus dem Druckraum zwischen dem Ritzel und den Hohlrädern) zum Druckanschluß 10 gefördert wird.FIG. 4 shows an enlarged section from FIG. 1, but without a counter bearing. The two
Die hydrostatische Entlastung an den Hohlrädern bedingt einerseits, daß die an den axialen Berührungsflächen wirksamen axialen Kräfte größer sind als die an den Außenseiten wirkenden; damit ergibt sich eine resultierende axiale Kraft, die die Hohlräder auseinander zu drücken sucht. Anderseits ist die konstruktive Gestaltung so, daß die in Förderichtung auf die Hohlräder wirkenden Kräfte und die von der hydrostatischen Entlastung herrührenden Kräfte sich nicht genau gegenüberliegen; so entstehen versetzt angreifende Kräfte Md, aus denen wiederum ein Kräftepaar resultiert, das ein Drehmoment auf die Hohlräder 6′, 6˝ ausübt.On the one hand, the hydrostatic relief on the ring gears means that the axial forces acting on the axial contact surfaces are greater than those acting on the outer sides; this results in a resulting axial force that tries to push the ring gears apart. On the other hand, the structural design is such that the forces acting on the ring gears in the conveying direction and the forces resulting from the hydrostatic relief are not exactly opposite; this creates offset attacking forces Md, which in turn results in a pair of forces that exerts a torque on the ring gears 6 ', 6˝.
Wird nun - wie in Fig. 5 dargestellt - das Hohlradpaar durch das Gegenlager 25 gestützt, so ergibt sich, daß die von der hydrostatischen Entlastung an den Hohlrädern 6′, 6˝ herrührenden Kräfte diametral sich genau gegenüberliegen. Damit herrscht an den Hohlrädern 6′, 6˝ näherungsweise ein Kräftegleichgewicht - die Hohlräder 6′, 6˝ können demzufolge nicht verkantet werden.Now - as shown in Fig. 5 - the ring gear pair is supported by the counter bearing 25, it follows that the resulting from the hydrostatic relief on the ring gears 6 ', 6˝ diametrically opposed forces. Thus there is approximately a balance of forces on the ring gears 6 ', 6˝ - the ring gears 6', 6˝ can therefore not be tilted.
Anhand von Fig. 6 soll gezeigt werden, daß über das Gegenlager 25 die an den axialen Berührungsflächen der Hohlräder 6′, 6˝ wirksamen Kräfte dahingehend beeinflußt werden, daß nunmehr eine resultierende Kraft wirksam wird, die die Hohlräder 6′, 6˝ aneinander preßt. Diese letztgenannte Wirkung wird durch die Wirkung der Entlastungsnuten 26, 27 zusätzlich verbessert.6 is to be shown that on the
Abschließend sei noch angemerkt, daß die im Vorstehenden offenbarte Erfindung nicht nur in Verbindung mit sichellosen Innenzahnradpumpen der in der DE 41 03 397 A1 genannten Art sinnvoll und damit effektiv anwendbar ist, sondern auch in Verbindung mit Innenzahnradpumpen mit Sichel. Auch ist die vorliegende Erfindung in Verbindung mit Innenzahnradpumpen mit axialer Förderung verwendbar.Finally, it should also be noted that the invention disclosed in the foregoing is not only useful and therefore effective in connection with sickle-free internal gear pumps of the type mentioned in DE 41 03 397 A1, but also in connection with internal gear pumps with sickle. The present invention can also be used in connection with internal gear pumps with axial delivery.
Claims (3)
- Internally geared pump with at least two substantially identical, internally toothed annular gears (6′, 6˝) and a pinion (5) meshing jointly with the annular gears, which are mounted to rotate in a jointly mounted housing part (1), whereof the axial extent corresponds to the width (B) of the toothing (12) of the annular gears (6′, 6˝) and of the pinion (5) and which comprises a suction connection (7) and a pressure connection (10), the annular gears (6′, 6˝) comprising radial openings (17) for the medium to be pumped, characterised in that a counter-bearing (25) is provided in the region of the bearing surfaces of the annular gears, seen from the side of the pressure connection.
- Internally geared pump according to Claim 1, characterised in that the counter-bearing comprises a groove (26) open towards the suction connection.
- Internally geared pump according to Claim 2, characterised in that in the region of the bearing surfaces lying opposite the groove, the annular gears comprise recesses (groove 27) corresponding to the annular gears.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE4135725A DE4135725C2 (en) | 1991-10-30 | 1991-10-30 | Internal gear pump with two ring gears and a common pinion |
| DE4135725 | 1991-10-30 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP0539673A1 EP0539673A1 (en) | 1993-05-05 |
| EP0539673B1 true EP0539673B1 (en) | 1994-10-19 |
Family
ID=6443720
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP92113789A Expired - Lifetime EP0539673B1 (en) | 1991-10-30 | 1992-08-13 | Internal gear pump with two ring gears and one common pinion |
Country Status (8)
| Country | Link |
|---|---|
| US (1) | US5242286A (en) |
| EP (1) | EP0539673B1 (en) |
| JP (1) | JPH05215080A (en) |
| AT (1) | ATE113117T1 (en) |
| DE (2) | DE4135725C2 (en) |
| DK (1) | DK0539673T3 (en) |
| ES (1) | ES2062857T3 (en) |
| NO (1) | NO177326C (en) |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19613835A1 (en) * | 1996-04-06 | 1997-10-09 | Eckerle Rexroth Gmbh Co Kg | Inner toothed wheel machine (Pump or engine) |
| DE19651683A1 (en) * | 1996-12-12 | 1998-06-18 | Otto Eckerle | Internal gear pump without filler |
| CA2407784C (en) * | 2000-05-19 | 2014-08-26 | Bionebraska, Inc. | Treatment of acute coronary syndrome with glp-1 |
| DE102004021216B4 (en) * | 2004-04-29 | 2014-07-03 | Eckerle Industrie-Elektronik Gmbh | High-pressure internal gear machine with multiple hydrostatic bearings per ring gear |
| DE202009000690U1 (en) * | 2009-01-16 | 2009-04-09 | Gather Industrie Gmbh | Rotary displacement |
| DE102015209836B3 (en) * | 2015-05-28 | 2016-06-02 | Eckerle Industrie-Elektronik Gmbh | Internal gear pump |
| DE102022200830A1 (en) | 2022-01-26 | 2023-07-27 | Zf Friedrichshafen Ag | Gear pump with noise optimization |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1624099A (en) * | 1925-03-11 | 1927-04-12 | Hiram H Haight | Gear pump |
| US2915982A (en) * | 1955-02-14 | 1959-12-08 | Crandall Loid | Rotary pump |
| DE3141682A1 (en) * | 1981-10-21 | 1983-05-05 | Volkswagenwerk Ag, 3180 Wolfsburg | Gear pump, especially for pumping lubricating oil |
| CH682939A5 (en) * | 1990-03-09 | 1993-12-15 | Voith Gmbh J M | Internal gear pump. |
| DE4104397C2 (en) * | 1990-03-09 | 1993-12-16 | Voith Gmbh J M | Internal gear pump |
-
1991
- 1991-10-30 DE DE4135725A patent/DE4135725C2/en not_active Expired - Fee Related
-
1992
- 1992-08-13 ES ES92113789T patent/ES2062857T3/en not_active Expired - Lifetime
- 1992-08-13 AT AT92113789T patent/ATE113117T1/en not_active IP Right Cessation
- 1992-08-13 EP EP92113789A patent/EP0539673B1/en not_active Expired - Lifetime
- 1992-08-13 DK DK92113789.9T patent/DK0539673T3/en active
- 1992-08-13 DE DE59200656T patent/DE59200656D1/en not_active Expired - Fee Related
- 1992-10-28 JP JP4290254A patent/JPH05215080A/en active Pending
- 1992-10-29 NO NO924170A patent/NO177326C/en not_active IP Right Cessation
- 1992-10-30 US US07/969,800 patent/US5242286A/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| NO177326B (en) | 1995-05-15 |
| NO924170D0 (en) | 1992-10-29 |
| US5242286A (en) | 1993-09-07 |
| JPH05215080A (en) | 1993-08-24 |
| ATE113117T1 (en) | 1994-11-15 |
| NO177326C (en) | 1995-08-30 |
| ES2062857T3 (en) | 1994-12-16 |
| EP0539673A1 (en) | 1993-05-05 |
| DK0539673T3 (en) | 1995-04-18 |
| DE4135725C2 (en) | 1994-05-26 |
| DE4135725A1 (en) | 1993-05-06 |
| DE59200656D1 (en) | 1994-11-24 |
| NO924170L (en) | 1993-05-03 |
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