EP0661454A1 - Internal gear pump - Google Patents

Internal gear pump Download PDF

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Publication number
EP0661454A1
EP0661454A1 EP94118669A EP94118669A EP0661454A1 EP 0661454 A1 EP0661454 A1 EP 0661454A1 EP 94118669 A EP94118669 A EP 94118669A EP 94118669 A EP94118669 A EP 94118669A EP 0661454 A1 EP0661454 A1 EP 0661454A1
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EP
European Patent Office
Prior art keywords
pinion
ring gear
tooth
internal gear
sealing element
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
EP94118669A
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German (de)
French (fr)
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EP0661454B1 (en
Inventor
Franz Arbogast
Peter Peiz
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.)
JM Voith SE and Co KG
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JM Voith GmbH
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Publication of EP0661454A1 publication Critical patent/EP0661454A1/en
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    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0007—Radial sealings for working fluid
    • F04C15/0019—Radial sealing elements specially adapted for intermeshing-engagement type machines or pumps, e.g. gear machines or pumps
    • 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 invention relates to a sickle-free internal gear pump for generating high pressure with the features specified in the preamble of claim 1.
  • a pump of this type is known as a special embodiment from DE 41 04 397 A1.
  • Internal gear pumps of this known type generally have an internally toothed ring gear with which an externally toothed pinion meshes, that is to say is in driving engagement.
  • This pinion has one tooth less than the ring gear.
  • the pinion is so eccentric to the ring gear that the outside of a tooth head on the pinion comes into contact with the inside of a tooth head on the ring gear.
  • the generic gear pumps also have a suction connection in the area in which the teeth disengage when the pinion rotates. Accordingly, they show a pressure connection on the side opposite the suction connection, where the teeth come back into engagement.
  • the delivery of the pressure medium into or out of the interior of the ring gear is ensured by essentially radial openings.
  • the circumference of the ring gear thus divides into a suction chamber, in which the pressure medium from the suction connection via the Breakthroughs is sucked in, and a pressure chamber in which the pressure medium from the inner region of the ring gear is pressed outwards through the openings. These two areas are separated in the tooth mesh by the so-called dead center of the toothing.
  • the present invention is based on the problem of specifying a sickle-free internal gear pump with involute toothing (i.e. with a large operating pressure angle) in which the theoretical, specific delivery volume is conveyed without the volumetric efficiency losses being recorded.
  • the sealing element is designed with respect to its head shape so that it cooperates sealingly with the foot shape of the tooth space of the ring gear or the pinion.
  • This sealing effect is due to the sealing element in connection with the base of the tooth space given in the area of the dead space.
  • This expansion of the sealing action range creates an improvement in the pump efficiency, since according to the invention now more pressure medium with a good sealing action comes from the pressure chamber into the pressure connection.
  • the pressure medium is guided to the rear of the sealing elements via axial grooves.
  • These axial grooves are arranged in the housing part in which the pinion is rotatably mounted or in the pump version with axial compensation in the axial disks.
  • Figures 1, 2 and 3 show the sickle-free internal gear pump in a longitudinal section and the arrangement and mode of operation of the gears in a cross section.
  • the internal gear pump shows a housing which consists of the housing middle part 1 and the housing side parts 2, 3.
  • the two housing side parts 2, 3 sealingly comprise the housing middle part 1, in the interior of which the internally toothed ring gear 6 with an externally toothed pinion 5 is arranged.
  • the pinion 5 is fastened to a drive shaft 4 and drives it via its toothing 12, which engages in the toothing 12 of the ring gear.
  • the pinion 5 and the ring gear 6 are not arranged coaxially, but eccentrically to one another; furthermore, the pinion 5 has one tooth less than the ring gear 6, so that in each case the outside of a tooth head 13 on the pinion 5 comes into contact with the inside of a tooth head 14 on the ring gear.
  • a suction connection 7 can also be seen in the middle part 1 of the housing in the region in which the teeth of the pinion 5 and the ring gear 6 disengage when rotated in the direction of the arrow X.
  • the inflow of the pump medium from the suction connection 7 to the interior of the pump and from there to the pressure connection 10 takes place through openings 17. These openings 17 start from the outer surface of the ring gear 6 and open into the tooth base of a tooth space of the ring gear 6.
  • the flow of the pump medium is indicated by the arrows Y shown.
  • the housing parts 2, 3 have axial grooves 40 in the area of the interlocking teeth 13, 14.
  • FIG. 3 shows the dead center (TP) of the toothing (12, 12), which describes the end of the penetration of the pinion toothing into the hollow toothing. Due to the small number of teeth, here 11 teeth of pinion 5, compared to 12 teeth of ring gear 12, there is an operating pressure angle of the involute toothing of over 50 °, which is indicated by the so-called engagement line E.
  • FIG. 4 shows a section of FIG. 3, in which the tooth heads 13, 14 engage in the tooth gaps of the pinion 5 or the ring gear 6.
  • the tooth heads 14 of the ring gear 6 have a mushroom-shaped sealing element, which is matched with respect to its cross-sectional shape to the foot shape of the tooth space of the pinion 5.
  • the mushroom-shaped sealing element 30 is arranged in a radial profile groove 34 so that it can be moved radially displaceably over a certain margin.
  • the head of the sealing element 30 is convex and, in conjunction with the slightly concave foot shape of the tooth gap, ensures a good sealing effect.
  • This sealing effect of the sealing element 30 with the foot of the tooth gap occurs in addition to the flank seal of the teeth 13 of the pinion 5 with respect to the teeth 14 of the ring gear 6 during the advance.
  • the area in which the flank seal is effective ends before the dead center TP, ie within the pressure area. In this part of the pressure range in which the flank seal is not effective only the sealing effect through the sealing element 30 in connection with the foot of the tooth gap is effective. Since this area can now be used according to the invention, the delivery volume of the pump medium and thus the efficiency of the pump is increased.
  • An axial groove 40 in the housing part 2 or 3, which is acted upon by pump medium, is also schematically indicated in FIG. 4, via which a defined pressing of the sealing element 30 against the base of the tooth space of the pinion 5 can be achieved.
  • This axial groove 40, 40 ' is also indicated in Figure 1, 2.
  • the dead center TP of the toothing is shown in FIG. 4 with the operating pressure angle defined by the line of engagement E of over 50 °.
  • sealing element 30 in the tooth head 14 of the ring gear 6 with the foot of the tooth space of the pinion 5 was disclosed in the foregoing with reference to FIG. 4, correspondingly equivalent combinations are also via sealing elements in the tooth heads 13 of the pinion 5 in connection with the foot the tooth gap of the ring gear 6 possible.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Abstract

In connection with an internal gear pump with internal gear (6) and a pinion (5) meshing with the internal gear (6), the internal gear (6) having radial apertures (17) for the medium to be pumped, and one sealing element (30) each, radially movable in a profiled groove (34) of corresponding design, being inserted into the tooth tips (14) of the internal gear (6) or into the tooth tips (13) of the pinion (5), which sealing element (30) can slide on the opposite tooth tip of the pinion (5) or the internal gear (6), it is proposed to adapt the head shape of the sealing element (30) and the base shape of the tooth gaps of the internal gear (6) or the pinion (5) to one another in such a way that the sealing between the pressure and suction space is verified by the sealing element (30) in the area of the dead centre. <IMAGE>

Description

Die Erfindung geht aus von einer sichellosen Innenzahnradpumpe zur Erzeugung von Hochdruck mit den im Oberbegriff des Patentanspruchs 1 angegebenen Merkmalen. Eine Pumpe dieser Gattung ist als besonderes Ausführungsbeispiel aus der DE 41 04 397 A1 bekannt.The invention relates to a sickle-free internal gear pump for generating high pressure with the features specified in the preamble of claim 1. A pump of this type is known as a special embodiment from DE 41 04 397 A1.

Innenzahnradpumpen dieser bekannten Art weisen im allgemeinen ein innenverzahntes Hohlrad auf, mit dem ein außenverzahntes Ritzel kämmt, das heißt treibend im Eingriff steht. Dieses Ritzel besitzt einen Zahn weniger als das Hohlrad. Dabei ist das Ritzel so exzentrisch zum Hohlrad angeordnet, daß jeweils die Außenseite eines Zahnkopfes am Ritzel mit der Innenseite eines Zahnkopfes am Hohlrad in Berührung kommt. Die gattungsgemäßen Zahnradpumpen zeigen weiterhin einen Sauganschluß in dem Bereich, in dem bei Drehung des Ritzels die Zähne außer Eingriff gelangen. Entsprechend zeigen sie einen Druckanschluß auf der dem Sauganschluß gegenüberliegenden Seite, wo die Zähne wieder in Eingriff geraten. Dabei wird die Förderung des Druckmediums in den oder aus dem Innenraum des Hohlrades durch im wesentlichen radiale Durchbrüche gewährleistet. Diese Durchbrüche gehen von der Mantelfläche des Hohlrades aus und münden in dessen Zahngrund.Internal gear pumps of this known type generally have an internally toothed ring gear with which an externally toothed pinion meshes, that is to say is in driving engagement. This pinion has one tooth less than the ring gear. The pinion is so eccentric to the ring gear that the outside of a tooth head on the pinion comes into contact with the inside of a tooth head on the ring gear. The generic gear pumps also have a suction connection in the area in which the teeth disengage when the pinion rotates. Accordingly, they show a pressure connection on the side opposite the suction connection, where the teeth come back into engagement. The delivery of the pressure medium into or out of the interior of the ring gear is ensured by essentially radial openings. These breakthroughs start from the outer surface of the ring gear and open into the tooth base.

Der Umfang des Hohlrades teilt sich somit in einen Saugraum, in dem das Druckmedium vom Sauganschluß über die Durchbrüche angesaugt wird, und einen Druckraum, in dem das Druckmedium aus dem Innenbereich des Hohlrades über die Durchbrüche nach außen gepreßt wird. Getrennt sind diese beiden Bereiche im Zahneingriff durch den sogenannten Totpunkt der Verzahnung.The circumference of the ring gear thus divides into a suction chamber, in which the pressure medium from the suction connection via the Breakthroughs is sucked in, and a pressure chamber in which the pressure medium from the inner region of the ring gear is pressed outwards through the openings. These two areas are separated in the tooth mesh by the so-called dead center of the toothing.

Bei der aus der DE 41 04 397 A1 bekannten sichellosen Innenzahnradpumpe endet die Flankendichtung eines Ritzelzahnes mit dem jeweiligen Hohlradzahn aufgrund der niederen Zähnezahl weit vor dem Totpunkt der Verzahnung. Der Bereich vom Endpunkt der Flankendichtung bis zum Totpunkt ist Teil des Druckraumes, in dem also Druckmittel gefördert wird. Diese Restfördermenge sollte auch in den Druckraum gefördert werden, da sonst das spezifische Fördervolumen erheblich kleiner wird (Verglichen mit dem theoretischen q).In the sickle-free internal gear pump known from DE 41 04 397 A1, the flank seal of a pinion tooth with the respective ring gear tooth ends well before the tooth dead center due to the low number of teeth. The area from the end point of the flank seal to the dead center is part of the pressure chamber, in which pressure medium is conveyed. This remaining delivery rate should also be delivered to the pressure chamber, otherwise the specific delivery volume will be considerably smaller (compared to the theoretical q).

Die dann fehlende Dichtung an der Verzahnungsflanke bewirkt eine Verschlechterung des volumetrischen Wirkungsgrades.The then missing seal on the tooth flank causes a deterioration in the volumetric efficiency.

Der vorliegenden Erfindung liegt die Problemstellung zugrunde, eine sichellose Innenzahnradpumpe mit Evolventenverzahnung (d.h. mit großem Betriebseingriffswinkel) anzugeben, bei der das theoretische, spezifische Fördervolumen gefördert wird, ohne das volumetrische Wirkungsgradverluste zu verzeichnen sind.The present invention is based on the problem of specifying a sickle-free internal gear pump with involute toothing (i.e. with a large operating pressure angle) in which the theoretical, specific delivery volume is conveyed without the volumetric efficiency losses being recorded.

Diese Aufgabe wird durch eine sichellose Innenzahnradpumpe mit den in Anspruch 1 angegebenen Merkmalen gelöst. Vorteilhafte Weiterbildungen der Erfindung sind in den Unteransprüchen dargestellt.This object is achieved by a sickle-free internal gear pump with the features specified in claim 1. Advantageous developments of the invention are presented in the subclaims.

Erfindungsgemäß wird zur Lösung der Aufgabe das Dichtelement bezüglich seiner Kopfform so ausgebildet, daß es mit der Fußform der Zahnlücke des Hohlrades bzw. des Ritzels dichtend zusammenwirkt. Diese Dichtwirkung ist durch das Dichtelement in Verbindung mit dem Fuß der Zahnlücke in dem Bereich des Totraums gegeben. Zusätzlich zu dieser Dichtwirkung existiert noch die gattungsgemäße Dichtwirkung durch die aneinander anliegenden Flanken, so daß die erfindungsgemäße Pumpe über einen vergrößerten Bereich des Druckraumes mit guter Dichtwirkung verfügt. Diese Erweiterung des Dichtwirkungsbereichs schafft eine Verbesserung des Pumpenwirkungsgrades, da nun erfindungsgemäß mehr Druckmedium bei guter Dichtwirkung aus dem Druckraum in den Druckanschluß gelangt.According to the invention, the sealing element is designed with respect to its head shape so that it cooperates sealingly with the foot shape of the tooth space of the ring gear or the pinion. This sealing effect is due to the sealing element in connection with the base of the tooth space given in the area of the dead space. In addition to this sealing effect, there is also the generic sealing effect due to the flanks lying against one another, so that the pump according to the invention has an enlarged area of the pressure chamber with a good sealing effect. This expansion of the sealing action range creates an improvement in the pump efficiency, since according to the invention now more pressure medium with a good sealing action comes from the pressure chamber into the pressure connection.

Die Verbesserung des Wirkungsgrades wird ohne zusätzliche Erhöhung des Fertigungsaufwandes erreicht, da jedes der in Verbindung mit der Gesamtkonstruktion verwendete Element in ähnlicher Weise schon im Stand der Technik Verwendung fand.The improvement in efficiency is achieved without an additional increase in production costs, since each of the elements used in connection with the overall construction has already been used in a similar manner in the prior art.

Gemäß einer weiteren Ausgestaltung der Erfindung ist vorgesehen, über axiale Nuten das Druckmedium auf die Rückseite der Dichtelemente zu führen.According to a further embodiment of the invention, the pressure medium is guided to the rear of the sealing elements via axial grooves.

Diese axialen Nuten sind in dem Gehäuseteil angeordnet, in welchem das Ritzel drehbar gelagert ist oder bei der Pumpenausführung mit Axialkompensation in den Axialscheiben.These axial grooves are arranged in the housing part in which the pinion is rotatably mounted or in the pump version with axial compensation in the axial disks.

Durch diese axialen Nuten ist gewährleistet, daß die radialen Dichtelemente an den Zahnfuß der jeweiligen Zahnlücke angepreßt werden.These axial grooves ensure that the radial sealing elements are pressed against the tooth base of the respective tooth gap.

Ein Ausführungsbeispiel ist in den Zeichnungen dargestellt und wird im folgenden näher beschrieben.

Fig. 1
zeigt in teilweise geschnittener Längsansicht ein Ausführungsbeispiel der Innenzahnradpumpe;
Fig. 2
zeigt in teilweise geschnittener Längsansicht ein Ausführungsbeispiel der Innenzahnradpumpe mit einer Axialscheibe zum Ausgleich des Axialspiels;
Fig. 3
zeigt in einem Querschnitt durch die Innenzahnradpumpe den Bereich des Ritzels und des Hohlrades;
Fig. 4
zeigt in einer Detailansicht die Verzahnung in dem Bereich des Totpunktes.
An embodiment is shown in the drawings and will be described in more detail below.
Fig. 1
shows a partially sectioned longitudinal view of an embodiment of the internal gear pump;
Fig. 2
shows a partially sectioned longitudinal view of an embodiment of the internal gear pump with an axial disk to compensate for the axial play;
Fig. 3
shows in a cross section through the internal gear pump the area of the pinion and the ring gear;
Fig. 4
shows in a detailed view the teeth in the area of the dead center.

Die Figuren 1, 2 und 3 zeigen in einem Längsschnitt die sichellose Innenzahnradpumpe bzw. in einem Querschnitt die Anordnung und Wirkungsweise der Zahnräder.Figures 1, 2 and 3 show the sickle-free internal gear pump in a longitudinal section and the arrangement and mode of operation of the gears in a cross section.

Die Innenzahnradpumpe zeigt ein Gehäuse, das aus dem Gehäusemittelteil 1 und den Gehäuseseitenteilen 2,3 besteht. Die beiden Gehäuseseitenteile 2,3 umfassen dichtend das Gehäusemittelteil 1, in dessen Innerem das innenverzahnte Hohlrad 6 mit einem außenverzahnten Ritzel 5 angeordnet ist. Das Ritzel 5 ist auf einer Antriebswelle 4 befestigt und treibt über seine Verzahnung 12, die in die Verzahnung 12 des Hohlrades eingreift, dieses an. Das Ritzel 5 und das Hohlrad 6 sind nicht koaxial, sondern exzentrisch zueinander angeordnet; ferner weist das Ritzel 5 einen Zahn weniger auf als das Hohlrad 6, so daß jeweils die Außenseite eines Zahnkopfes 13 am Ritzel 5 mit der Innenseite eines Zahnkopfes 14 am Hohlrad in Berührung kommt. Zu erkennen ist ferner im Gehäusemittelteil 1 ein Sauganschluß 7 in dem Bereich, in dem unter Drehung in Pfeilrichtung X die Zähne des Ritzel 5 und des Hohlrades 6 außer Eingriff geraten. Auf der dem Sauganschluß 7 gegenüberliegenden Seite des Gehäusemittelteils 1 befindet sich ein Druckanschluß 10, der in dem Bereich angeordnet ist, in dem die Zähne des Ritzels 5 und des Hohlrades 6 wieder in Eingriff geraten. Der Zufluß des Pumpmediums von dem Sauganschluß 7 zum Innenraum der Pumpe und von dort zum Druckanschluß 10 erfolgt über Durchbrüche 17. Diese Durchbrüche 17 gehen von der Mantelfläche des Hohlrades 6 aus und münden in den Zahngrund einer Zahnlücke des Hohlrades 6.The internal gear pump shows a housing which consists of the housing middle part 1 and the housing side parts 2, 3. The two housing side parts 2, 3 sealingly comprise the housing middle part 1, in the interior of which the internally toothed ring gear 6 with an externally toothed pinion 5 is arranged. The pinion 5 is fastened to a drive shaft 4 and drives it via its toothing 12, which engages in the toothing 12 of the ring gear. The pinion 5 and the ring gear 6 are not arranged coaxially, but eccentrically to one another; furthermore, the pinion 5 has one tooth less than the ring gear 6, so that in each case the outside of a tooth head 13 on the pinion 5 comes into contact with the inside of a tooth head 14 on the ring gear. A suction connection 7 can also be seen in the middle part 1 of the housing in the region in which the teeth of the pinion 5 and the ring gear 6 disengage when rotated in the direction of the arrow X. On the side of the housing middle part 1 opposite the suction connection 7 there is a pressure connection 10 which is arranged in the region in which the teeth of the pinion 5 and the ring gear 6 come into engagement again. The inflow of the pump medium from the suction connection 7 to the interior of the pump and from there to the pressure connection 10 takes place through openings 17. These openings 17 start from the outer surface of the ring gear 6 and open into the tooth base of a tooth space of the ring gear 6.

Der Fluß des Pumpmediums ist durch die dargestellten Pfeile Y angedeutet. Die Gehäuseteile 2,3 zeigen im Bereich der ineinandergreifenden Zähne 13,14 axiale Nuten 40.The flow of the pump medium is indicated by the arrows Y shown. The housing parts 2, 3 have axial grooves 40 in the area of the interlocking teeth 13, 14.

Bei Pumpen - der aus der DE-OS 42 08 767.8 bekannten Art -, welche eine Axialscheibe zum Ausgleich des Axialspiels aufweisen (siehe Fig. 2) befindet sich die axiale Steuernut 40' in der Axialscheibe 41.In pumps - of the type known from DE-OS 42 08 767.8 - which have an axial disk to compensate for the axial play (see FIG. 2), the axial control groove 40 'is located in the axial disk 41.

In Figur 3 ist der Totpunkt (TP) der Verzahnung (12,12) eingezeichnet, welcher das Ende des Eindringes der Ritzelverzahnung in die Hohlverzahnung beschreibt. Aufgrund der geringen Zähnezahl, hier 11 Zähne des Ritzels 5, gegenüber 12 Zähnen des Hohlrads 12, ergibt sich ein Betriebseingriffswinkel der Evolventenverzahnung von über 50°, der über die sogenannte Eingriffslinie E angedeutet ist.FIG. 3 shows the dead center (TP) of the toothing (12, 12), which describes the end of the penetration of the pinion toothing into the hollow toothing. Due to the small number of teeth, here 11 teeth of pinion 5, compared to 12 teeth of ring gear 12, there is an operating pressure angle of the involute toothing of over 50 °, which is indicated by the so-called engagement line E.

In Figur 4 ist ein Ausschnitt der Figur 3 dargestellt, in dem die Zahnköpfe 13,14 in die Zahnlücken des Ritzels 5 bzw. des Hohlrades 6 eingreifen. Die Zahnköpfe 14 des Hohlrades 6 weisen ein pilzförmiges Dichtelement auf, das bezüglich seiner Querschnittsform auf die Fußform der Zahnlücke des Ritzels 5 abgestimmt ist. Das pilzförmige Dichtelement 30 ist in einer radialen Profilnut 34 so angeordnet, daß es über einen gewissen Spielraum radial verschieblich beweglich ist. Der Kopf des Dichtelements 30 ist konvex ausgebildet und gewährleistet dadurch in Verbindung mit der leicht konkav ausgebildeten Fußform der Zahnlücke eine gute Dichtwirkung. Diese Dichtwirkung des Dichtelementes 30 mit dem Fuß der Zahnlücke tritt zusätzlich zu der Flankendichtung der Zähne 13 des Ritzels 5 gegenüber den Zähnen 14 des Hohlrades 6 beim Vortrieb hinzu.
Der Bereich, in dem die Flankendichtung wirksam ist, endet in Drehrichtung X betrachtet bereits vor dem Totpunkt TP, also innerhalb des Druckbereichs. In diesem Teil des Druckbereichs, in dem die Flankendichtung nicht wirkt, ist allein die Dichtwirkung durch das Dichtelement 30 in Verbindung mit dem Fuß der Zahnlücke wirksam. Da dieser Bereich nun erfindungsgemäß nutzbar ist, ist die Fördermenge des Pumpmediums und damit der Wirkungsgrad der Pumpe erhöht.FIG. 4 shows a section of FIG. 3, in which the tooth heads 13, 14 engage in the tooth gaps of the pinion 5 or the ring gear 6. The tooth heads 14 of the ring gear 6 have a mushroom-shaped sealing element, which is matched with respect to its cross-sectional shape to the foot shape of the tooth space of the pinion 5. The mushroom-shaped sealing element 30 is arranged in a radial profile groove 34 so that it can be moved radially displaceably over a certain margin. The head of the sealing element 30 is convex and, in conjunction with the slightly concave foot shape of the tooth gap, ensures a good sealing effect. This sealing effect of the sealing element 30 with the foot of the tooth gap occurs in addition to the flank seal of the teeth 13 of the pinion 5 with respect to the teeth 14 of the ring gear 6 during the advance.
The area in which the flank seal is effective, viewed in the direction of rotation X, ends before the dead center TP, ie within the pressure area. In this part of the pressure range in which the flank seal is not effective only the sealing effect through the sealing element 30 in connection with the foot of the tooth gap is effective. Since this area can now be used according to the invention, the delivery volume of the pump medium and thus the efficiency of the pump is increased.

Schematisch ist in Figur 4 auch eine mit Pumpmedium beaufschlagte axiale Nut 40 in dem Gehäuseteil 2 oder 3 angedeutet, über welche eine definierte Anpressung des Dichtelements 30 an den Fuß der Zahnlücke des Ritzels 5 erreicht werden kann. (Diese axiale Nut 40, 40' ist auch in Figur 1, 2 angedeutet.)An axial groove 40 in the housing part 2 or 3, which is acted upon by pump medium, is also schematically indicated in FIG. 4, via which a defined pressing of the sealing element 30 against the base of the tooth space of the pinion 5 can be achieved. (This axial groove 40, 40 'is also indicated in Figure 1, 2.)

Ebenso wie in Figur 3 ist in Figur 4 der Totpunkt TP der Verzahnung mit dem durch die Eingriffslinie E definierten Betriebseingriffswinkel von über 50° dargestellt.As in FIG. 3, the dead center TP of the toothing is shown in FIG. 4 with the operating pressure angle defined by the line of engagement E of over 50 °.

Auch wenn im vorstehenden anhand der Figur 4 die Kombination aus Dichtelement 30 im Zahnkopf 14 des Hohlrades 6 mit dem Fuß der Zahnlücke des Ritzels 5 offenbart wurde, so sind entsprechend gleichwirkende Kombinationen auch über Dichtelemente in den Zahnköpfen 13 des Ritzels 5 in Verbindung mit dem Fuß der Zahnlücke des Hohlrades 6 möglich.Even if the combination of sealing element 30 in the tooth head 14 of the ring gear 6 with the foot of the tooth space of the pinion 5 was disclosed in the foregoing with reference to FIG. 4, correspondingly equivalent combinations are also via sealing elements in the tooth heads 13 of the pinion 5 in connection with the foot the tooth gap of the ring gear 6 possible.

Claims (2)

Sichellose Innenzahnradpumpe mit innenverzahntem Hohlrad (6) und einem mit dem Hohlrad (6) kämmenden Ritzel (5), die in einem gemeinsam gelagerten Gehäuseteil (1) drehbar gelagert sind, dessen axiale Erstreckung der Breite der Verzahnung (12) des Hohlrades (6) und des Ritzels (5) entspricht und welches einen Sauganschluß (7) und einen Druckanschluß (10) aufweist, wobei das Hohlrad (6) radiale Durchbrüche (17) für das zu pumpende Medium aufweist, und wobei in den Zahnköpfen (14) des Hohlrads (6) bzw. in den Zahnköpfen (13) des Ritzels (5) je ein in einer entsprechend ausgebildeten Profilnut (34) radial bewegliches Dichtelement (30) eingesetzt ist, das am gegenüberliegenden Zahnkopf des Ritzels (5) bzw. des Hohlrades (6) gleiten kann,
dadurch gekennzeichnet,
daß die Kopfform des Dichtelementes (30) und die Fußform der Zahnlücke des Hohlrades (6) bzw. des Ritzels (5) so aufeinander abgestimmt sind, daß im Bereich des Totpunktes die Abdichtung zwischen dem Druck- und dem Saugraum vom Dichtelement (30) verifiziert wird.Sickle-free internal gear pump with internally toothed ring gear (6) and a pinion (5) meshing with the ring gear (6), which is rotatably mounted in a jointly mounted housing part (1), the axial extent of which is the width of the toothing (12) of the ring gear (6) and of the pinion (5) and which has a suction connection (7) and a pressure connection (10), the ring gear (6) having radial openings (17) for the medium to be pumped, and in the tooth tips (14) of the ring gear (6) or in the tooth heads (13) of the pinion (5) each a radially movable sealing element (30) is inserted in a correspondingly designed profile groove (34), which on the opposite tooth head of the pinion (5) or the ring gear (6 ) can slide,
characterized,
that the head shape of the sealing element (30) and the foot shape of the tooth space of the ring gear (6) or the pinion (5) are coordinated with one another in such a way that the seal between the pressure chamber and the suction chamber is verified by the sealing element (30) in the region of the dead center becomes. Sichellose Innenzahnradpumpe nach Anspruch 1,
dadurch gekennzeichnet,
daß das oder die Gehäuseteile (2,3), welche das Hohlrad (6) und das Ritzel (5) gemeinsam dichtend lagern, im Bereich des Totpunktes eine axiale Nut (40) aufweisen, durch die das Anpressen des Dichtelements (30) am Verzahnungsgrund gesteuert wird.Sickle-free internal gear pump according to claim 1,
characterized,
that the housing part or parts (2, 3), which jointly support the ring gear (6) and the pinion (5), have an axial groove (40) in the area of the dead center, through which the pressing of the sealing element (30) on the tooth base is controlled.
EP94118669A 1993-12-17 1994-11-28 Internal gear pump Expired - Lifetime EP0661454B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4343193 1993-12-17
DE4343193 1993-12-17

Publications (2)

Publication Number Publication Date
EP0661454A1 true EP0661454A1 (en) 1995-07-05
EP0661454B1 EP0661454B1 (en) 1999-01-27

Family

ID=6505348

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94118669A Expired - Lifetime EP0661454B1 (en) 1993-12-17 1994-11-28 Internal gear pump

Country Status (7)

Country Link
US (1) US5540573A (en)
EP (1) EP0661454B1 (en)
JP (1) JPH07197887A (en)
AT (1) ATE176301T1 (en)
DE (1) DE59407738D1 (en)
DK (1) DK0661454T3 (en)
ES (1) ES2129564T3 (en)

Cited By (4)

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DE19746769C1 (en) * 1997-10-23 1999-02-11 Bosch Gmbh Robert Inner geared fluid pump or motor
US11549507B2 (en) 2021-06-11 2023-01-10 Genesis Advanced Technology Inc. Hypotrochoid positive-displacement machine
US11761377B2 (en) 2022-02-02 2023-09-19 1159718 B.C. Ltd. Energy transfer machine
US11965509B2 (en) 2022-02-28 2024-04-23 Genesis Advanced Technology Inc. Energy transfer machine for corrosive fluids

Families Citing this family (4)

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Publication number Priority date Publication date Assignee Title
DE19804134A1 (en) * 1998-02-03 1999-08-12 Voith Turbo Kg Sickle-free internal gear pump
US6273695B1 (en) * 1999-03-26 2001-08-14 Voith Turbo Gmbh & Co. Kg Sickleless internal gear wheel pump with sealing elements inserted into the tooth tips
WO2008015845A1 (en) * 2006-07-31 2008-02-07 Toyota Boshoku Kabushiki Kaisha Gear and connection device using the gear
CN104895781A (en) * 2014-09-17 2015-09-09 襄阳博亚精工装备股份有限公司 Internal gear pump

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DE4104397A1 (en) * 1990-03-09 1991-09-12 Voith Gmbh J M Internal gear pump without sickle element - incorporates method of dimensioning teeth to give compact design
EP0545424A1 (en) * 1991-12-06 1993-06-09 J.M. Voith GmbH Internal gear pump with sealings incorporated in the teeth
EP0607497A1 (en) * 1993-01-18 1994-07-27 J.M. Voith GmbH Internal gear pump with sealings incorporated in the teeth

Cited By (6)

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Publication number Priority date Publication date Assignee Title
DE19746769C1 (en) * 1997-10-23 1999-02-11 Bosch Gmbh Robert Inner geared fluid pump or motor
EP0911524A1 (en) 1997-10-23 1999-04-28 Robert Bosch Gmbh Internal gear pump
US11549507B2 (en) 2021-06-11 2023-01-10 Genesis Advanced Technology Inc. Hypotrochoid positive-displacement machine
US11761377B2 (en) 2022-02-02 2023-09-19 1159718 B.C. Ltd. Energy transfer machine
US12006864B2 (en) 2022-02-02 2024-06-11 1159718 B.C. Ltd. Energy transfer machine
US11965509B2 (en) 2022-02-28 2024-04-23 Genesis Advanced Technology Inc. Energy transfer machine for corrosive fluids

Also Published As

Publication number Publication date
ES2129564T3 (en) 1999-06-16
EP0661454B1 (en) 1999-01-27
DK0661454T3 (en) 1999-09-13
ATE176301T1 (en) 1999-02-15
JPH07197887A (en) 1995-08-01
US5540573A (en) 1996-07-30
DE59407738D1 (en) 1999-03-11

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