EP0661454B1 - Internal gear pump - Google Patents

Internal gear pump Download PDF

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Publication number
EP0661454B1
EP0661454B1 EP94118669A EP94118669A EP0661454B1 EP 0661454 B1 EP0661454 B1 EP 0661454B1 EP 94118669 A EP94118669 A EP 94118669A EP 94118669 A EP94118669 A EP 94118669A EP 0661454 B1 EP0661454 B1 EP 0661454B1
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EP
European Patent Office
Prior art keywords
internal gear
pinion
tooth
sealing element
ring gear
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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EP94118669A
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German (de)
French (fr)
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EP0661454A1 (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 and Co Beteiligungen KG
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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 is based on a sickle-free internal gear pump for generating high pressure with those in the preamble of claim 1 specified features.
  • a pump this genus is a special embodiment known from DE 41 04 397 A1.
  • Internal gear pumps of this known type generally have an internally toothed ring gear with which a externally toothed pinion meshes, that is, drivingly engaged stands.
  • This sprocket has one tooth less than the ring gear.
  • the pinion is so eccentric to the ring gear arranged that in each case the outside of a tooth head on the pinion with the inside of a tooth head on the ring gear in Touch comes.
  • the generic gear pumps show continue to have a suction port in the area where Rotation of the pinion disengage the teeth.
  • Corresponding show a pressure port on the suction port opposite side where the teeth come back in Interfered.
  • the promotion of the print medium in or out of the interior of the ring gear by in essential radial breakthroughs guaranteed. This Breakthroughs start from the outer surface of the ring gear and flow into its tooth base.
  • the circumference of the ring gear thus divides into a suction space, in which the pressure medium from the suction port on the Breakthroughs is sucked in, and a pressure chamber in which the Pressure medium from the inside of the ring gear on the Breakthroughs is pressed outwards. These are separate two areas in tooth mesh through the so-called dead center the gearing.
  • GB-A-793 089 shows and describes a sickle-free gear pump in which the teeth of the pinion always rest on the ring gear. This makes numerous Single chambers created. This makes the control complex and laborious. There are also in the sealing area between the suction side and pressure side the heads of the pinion in the gaps of the ring gear. There are Movable sealing elements are provided, which are also used for the transfer of Serve torque. That is why this pump is only for very low pressures suitable.
  • EP-A-0 545 424 describes an internal gear pump in which the head of the sealing element does not rest on the foot of the pinion. Rather there is Free space between the head of the sealing element and the foot of the pinion. When pressure builds up, the pinion head and ring gear head face each other. This internal gear pump has no involute toothing.
  • the problem underlying the present invention is a sickle-free internal gear pump with involute toothing (i.e. with a large operating pressure angle) where the theoretical, specific funding volume is promoted without the volumetric efficiency losses are recorded.
  • the sealing element is used to achieve the object in terms of its head shape so that it with the foot shape of the tooth gap of the ring gear or the Ritzels works together sealingly.
  • This sealing effect is through the sealing element in connection with the foot of the tooth gap given in the area of the dead space.
  • Sealing effect due to the abutting flanks see above that the pump of the invention has an enlarged Area of the pressure chamber with good sealing effect.
  • This expansion of the sealing action area creates one Improvement of the pump efficiency, since now according to the invention more pressure medium with a good sealing effect from the Pressure chamber gets into the pressure connection.
  • the pressure medium to the rear via axial grooves of the sealing elements.
  • axial grooves are arranged in the housing part, in which the pinion is rotatably mounted or at Pump version with axial compensation in the axial washers.
  • Figures 1, 2 and 3 show in a longitudinal section sickle-free internal gear pump or in a cross section Arrangement and mode of operation of the gears.
  • the internal gear pump shows a housing that consists of the Housing middle part 1 and the housing side parts 2,3.
  • the two housing side parts 2, 3 seal the middle housing part 1, inside of which the internally toothed Ring gear 6 is arranged with an externally toothed pinion 5 is.
  • the pinion 5 is fixed on a drive shaft 4 and drives over its gearing 12, which in the Interlocking teeth 12 of the ring gear engages this.
  • the Pinion 5 and the ring gear 6 are not coaxial, but arranged eccentrically to each other; also has the pinion 5 one tooth less than the ring gear 6, so that each the outside of a tooth head 13 on the pinion 5 with the Inside of a tooth head 14 in contact with the ring gear is coming.
  • the flow of the pump medium is shown by the arrows Y indicated.
  • the housing parts 2, 3 show in the area of interlocking teeth 13, 14 axial grooves 40.
  • 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 root 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 does not work, 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.
  • a pumped medium is also shown schematically in FIG axial groove 40 indicated in the housing part 2 or 3, via which a defined pressure of the sealing element 30 reached the foot of the tooth gap of the pinion 5 can be.
  • This axial groove 40, 40 ' is also indicated in Figure 1, 2.

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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 is based on a sickle-free internal gear pump for generating high pressure with those in the preamble of claim 1 specified features. A pump this genus is a special embodiment known 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 a externally toothed pinion meshes, that is, drivingly engaged stands. This sprocket has one tooth less than the ring gear. The pinion is so eccentric to the ring gear arranged that in each case the outside of a tooth head on the pinion with the inside of a tooth head on the ring gear in Touch comes. The generic gear pumps show continue to have a suction port in the area where Rotation of the pinion disengage the teeth. Corresponding show a pressure port on the suction port opposite side where the teeth come back in Interfered. The promotion of the print medium in or out of the interior of the ring gear by in essential radial breakthroughs guaranteed. This Breakthroughs start from the outer surface of the ring gear and flow into its 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 space, in which the pressure medium from the suction port on the Breakthroughs is sucked in, and a pressure chamber in which the Pressure medium from the inside of the ring gear on the Breakthroughs is pressed outwards. These are separate two areas in tooth mesh through the so-called dead center the gearing.

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 known from DE 41 04 397 A1 Internal gear pump ends the flank seal of a pinion tooth with the respective ring gear tooth due to the lower Number of teeth far before the tooth dead center. The area from the end point of the flank seal to the dead center is part the pressure chamber, in which pressure medium is conveyed. This residual flow rate should also be pumped into the pressure chamber otherwise the specific funding volume will be considerable becomes 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 volumetric efficiency.

GB-A-793 089 zeigt und beschreibt eine sichel lose Zahnradpumpe, bei der die Zähne des Ritzels stets am Hohlrad anliegen. Dadurch werden zahlreiche Einzelkammern geschaffen. Dies macht die Steuerung aufwendig und umständlich. Ferner liegen dort im Abdichtungsbereich zwischen Saugseite und Druckseite die Köpfe des Ritzels in den Lücken des Hohlrades. Es sind bewegliche Dichtelemente vorgesehen, die gleichzeitig zum Übertragen von Drehmoment dienen. Deshalb ist diese Pumpe nur für ganz geringe Drücke geeignet.GB-A-793 089 shows and describes a sickle-free gear pump in which the teeth of the pinion always rest on the ring gear. This makes numerous Single chambers created. This makes the control complex and laborious. There are also in the sealing area between the suction side and pressure side the heads of the pinion in the gaps of the ring gear. There are Movable sealing elements are provided, which are also used for the transfer of Serve torque. That is why this pump is only for very low pressures suitable.

EP-A-0 545 424 beschreibt eine Innenzahnradpumpe, bei welcher der Kopf des Dichtelementes nicht am Fuß des Ritzels anliegt. Vielmehr besteht ein Freiraum zwischen dem Kopf des Dichtelementes und dem Fuß des Ritzels. Beim Druckaufbau liegen Ritzel kopf und Hohlradkopf einander gegenüber. Diese Innenzahnradpumpe weist keine Evolventenverzahnung auf. EP-A-0 545 424 describes an internal gear pump in which the head of the sealing element does not rest on the foot of the pinion. Rather there is Free space between the head of the sealing element and the foot of the pinion. When pressure builds up, the pinion head and ring gear head face each other. This internal gear pump has no involute toothing.

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 problem underlying the present invention is a sickle-free internal gear pump with involute toothing (i.e. with a large operating pressure angle) where the theoretical, specific funding volume is promoted without the volumetric efficiency losses are 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 task is accomplished by a crescentless internal gear pump solved with the features specified in claim 1. Beneficial Further developments of the invention are in the subclaims shown.

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 used to achieve the object in terms of its head shape so that it with the foot shape of the tooth gap of the ring gear or the Ritzels works together sealingly. This sealing effect is through the sealing element in connection with the foot of the tooth gap given in the area of the dead space. In addition to this sealing effect still exists Sealing effect due to the abutting flanks, see above that the pump of the invention has an enlarged Area of the pressure chamber with good sealing effect. This expansion of the sealing action area creates one Improvement of the pump efficiency, since now according to the invention more pressure medium with a good sealing effect from the Pressure chamber gets 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 without additional Increase in manufacturing costs achieved because each of the in Element used in connection with the overall construction similarly has already been used 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 to the rear via axial grooves of the sealing elements.

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 at Pump version with axial compensation in the axial washers.

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 on the tooth base of the respective tooth gap be pressed.

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 sichel lose Innenzahnradpumpe bzw. in einem Querschnitt die Anordnung und Wirkungsweise der Zahnräder.Figures 1, 2 and 3 show in a longitudinal section sickle-free internal gear pump or in a cross section Arrangement and mode of operation of the gears.

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 that consists of the Housing middle part 1 and the housing side parts 2,3. The two housing side parts 2, 3 seal the middle housing part 1, inside of which the internally toothed Ring gear 6 is arranged with an externally toothed pinion 5 is. The pinion 5 is fixed on a drive shaft 4 and drives over its gearing 12, which in the Interlocking teeth 12 of the ring gear engages this. The Pinion 5 and the ring gear 6 are not coaxial, but arranged eccentrically to each other; also has the pinion 5 one tooth less than the ring gear 6, so that each the outside of a tooth head 13 on the pinion 5 with the Inside of a tooth head 14 in contact with the ring gear is coming. One can also see in the middle part 1 of the housing Suction port 7 in the area where under rotation in Arrow direction X the teeth of the pinion 5 and the ring gear 6 disengaged. On the suction port 7 opposite Side of the middle housing part 1 is located a pressure port 10 located in the area in which the teeth of the pinion 5 and the ring gear 6 back in Interfered. The inflow of the pump medium from the suction port 7 to the interior of the pump and from there to Pressure connection 10 takes place via openings 17. These openings 17 start from the outer surface of the ring gear 6 and open into the tooth base of a tooth gap 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 shown by the arrows Y indicated. The housing parts 2, 3 show in the area of interlocking teeth 13, 14 axial grooves 40.

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 disc to compensate for the axial play (see Fig. 2) is the axial control groove 40 '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.3 shows the dead center (TP) of the toothing (12, 12) which is the end of the penetration of the pinion gear describes in the hollow toothing. Due to the small number of teeth, here 11 teeth of pinion 5, opposite 12 teeth of the ring gear 12, there is an operating pressure angle the involute toothing of over 50 °, the is indicated via the so-called line of engagement 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 root 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 does not work, 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.)A pumped medium is also shown schematically in FIG axial groove 40 indicated in the housing part 2 or 3, via which a defined pressure of the sealing element 30 reached the foot of the tooth gap of the pinion 5 can be. (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.Just like in FIG. 3, the dead center TP in FIG Interlocking with that defined by the line of engagement E. Operating pressure angle of over 50 ° shown.

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 is based on FIG. 4 above from sealing element 30 in tooth head 14 of ring gear 6 with the foot of the tooth space of the pinion 5 was disclosed, so are accordingly equivalent combinations over Sealing elements in the tooth tips 13 of the pinion 5 in connection possible with the foot of the tooth space of the ring gear 6.

Claims (2)

  1. Internal gear pump with an internally toothed internal gear (6) and a pinion (5) meshing with the internal gear (6), which are mounted rotatably in a common housing element (1), the axial dimension of which corresponds to the width of the toothing (12) of the internal gear (6) and the pinion (5) and which has a suction connection (7) and a pressure connection (10), wherein the internal gear (6) has radial openings (17) for the medium to be pumped, and wherein in the tooth tips (14) of the internal gear (6) or the tooth tips (13) of the pinion (5) respectively a sealing element (30) is inserted that is movable radially in correspondingly designed shaped groove (34) which sealing element can slide on the opposite tooth tip of the pinion (5) or internal gear,
    characterised in that
    the tip shape of the sealing element (30) and the root shape of the tooth space of the pinion (5) are designed and arranged so that the pressure and extraction chamber are sealed off from one another by a sealing element (30), even in the region of the dead centre, where a side sealing of the teeth (13) of the pinion (5) from the teeth (14) of the hollow wheel (6) is not effective.
  2. Internal gear pump according to claim 1, characterised in that the housing part or parts (2, 3), which sealingly mount the internal gear (6) and the pinion (5) together, in the region of the dead centre have an axial groove (40), by means of which the pressing of the sealing element (30) on the tooth root 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 EP0661454A1 (en) 1995-07-05
EP0661454B1 true 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)

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US12006864B2 (en) 2022-02-02 2024-06-11 1159718 B.C. Ltd. Energy transfer machine

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DE19746769C1 (en) 1997-10-23 1999-02-11 Bosch Gmbh Robert Inner geared fluid pump or motor
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
US8016356B2 (en) * 2006-07-31 2011-09-13 Toyota Boshoku Kabushiki Kaisha Gears and coupling apparatus using the gears
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
US11549507B2 (en) 2021-06-11 2023-01-10 Genesis Advanced Technology Inc. Hypotrochoid positive-displacement machine
US11965509B2 (en) 2022-02-28 2024-04-23 Genesis Advanced Technology Inc. Energy transfer machine for corrosive fluids

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GB793089A (en) * 1956-06-09 1958-04-09 Hanomag Ag Improvements in rotary engines and compressors
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DE4104397C2 (en) * 1990-03-09 1993-12-16 Voith Gmbh J M Internal gear pump
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EP0563661A1 (en) * 1992-03-19 1993-10-06 J.M. Voith GmbH Internal gear pump with radially movable sealing elements for radial compensation
DK0607497T3 (en) * 1993-01-18 1996-10-21 Voith Gmbh J M Internally toothed gear pump without seal with sealing elements inserted into the tooth heads

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US12006864B2 (en) 2022-02-02 2024-06-11 1159718 B.C. Ltd. Energy transfer machine

Also Published As

Publication number Publication date
ES2129564T3 (en) 1999-06-16
US5540573A (en) 1996-07-30
ATE176301T1 (en) 1999-02-15
DK0661454T3 (en) 1999-09-13
JPH07197887A (en) 1995-08-01
DE59407738D1 (en) 1999-03-11
EP0661454A1 (en) 1995-07-05

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