EP0607497A1 - Internal gear pump with sealings incorporated in the teeth - Google Patents

Internal gear pump with sealings incorporated in the teeth Download PDF

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Publication number
EP0607497A1
EP0607497A1 EP93114117A EP93114117A EP0607497A1 EP 0607497 A1 EP0607497 A1 EP 0607497A1 EP 93114117 A EP93114117 A EP 93114117A EP 93114117 A EP93114117 A EP 93114117A EP 0607497 A1 EP0607497 A1 EP 0607497A1
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EP
European Patent Office
Prior art keywords
sealing element
ring gear
pinion
internal gear
gear pump
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
EP93114117A
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German (de)
French (fr)
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EP0607497B1 (en
Inventor
Franz Arbogast
Peter Peiz
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JM Voith GmbH
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JM Voith GmbH
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Publication of EP0607497A1 publication Critical patent/EP0607497A1/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

  • Document (2) describes a radially movable sealing element, which - without requiring excessive manufacturing effort - significantly improves the sealing effect when pressure builds up between the opposing tooth tips of the gearwheels due to the shape.
  • the contour of the sealing element on the one hand and the complementary design of the sealing element and the profile groove in the tooth head on the other hand bring with it some problems.
  • the disadvantage here is that when the dead center is exceeded, the entire system pressure, ie the working pressure generated by the pump, rests on the sealing element. This would be for the purpose of sealing a much lower pressure will suffice.
  • the high system pressure leads to excessive wear of the sealing element.
  • the invention has for its object to design a pump according to the preamble of claim 1 such that not the entire system pressure is used for sealing, but a much lower pressure, which is sufficient for the purpose of sealing.
  • the special design of the sealing element ensures that there is a minimal gap between the pinion head and the ring gear head.
  • the volumetric efficiency can be improved, which in turn means that the internal gear pump can also be used for higher pressures.
  • the elaborate and complicated profile grinding of the hollow head shape is eliminated when producing the ring gear, because the sealing elements can be produced separately therefrom.
  • FIG. 1 shows in a cross section a sickle-free, head-sealing and backlash-type internal gear pump, each sealing with a flank, in the area of a central housing part, which - viewed in the axial direction - is followed by further housing parts.
  • An externally toothed pinion 5 fastened on a pinion shaft 4 is in engagement with an internally toothed ring gear 6.
  • the toothing 12 of the pinion 5 and the ring gear 6 has an axial width which is greater than the pitch circle diameter of the pinion.
  • the pinion 5 and the ring gear 6 are not mounted 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 6.
  • a suction connection 7 can also be seen in the zone in which the teeth on the pinion 5 or ring gear 6 disengage when rotated in the direction of the arrow X.
  • the suction connection 7 in the middle part of the housing, in which the ring gear 6 and the pinion 5 are mounted, is followed in the axial direction by a suction pocket, which extends over part of the outer surface 20 of the ring gear 6, to the adjacent housing parts.
  • a pressure connection 10 is located, also starting from one over a peripheral area Ring gear 6 extending pressure pocket on the opposite side of the pump.
  • FIG. 2 shows a section of the ring gear 6 in the region of a tooth head 14.
  • the openings (radial bores) 17 provided for the inflow of the pressure medium to the interior of the internal gear pump are machined in the tooth gaps. While in the construction according to the main patent these openings 17 each cut the profile groove 34 for the sealing elements 30 and thus always act on the back of the sealing element 30 with the pressure prevailing in the leading tooth gap, the openings 17 no longer cut the profile grooves 34.
  • the design change also has functional advantages. While in the construction according to the main patent, the (contact) pressure effective on the back of the sealing element 30 is always as great as the pressure in the leading tooth gap (which means that the sealing element with the force corresponding to the system pressure in the area of reversal from the suction side to the pressure side the pump is pressed outwards), the pressure acting on the sealing element 30 is only a partial pressure due to the design change. In a particularly advantageous manner, this partial pressure effective on the back of the sealing element can be achieved by means of - cf. 3 - along the sealing elements 30 provided bores 30 'or by means of - see. Fig.
  • the partial pressure mentioned - in conjunction with the present improvement invention - also ensures that the sealing element 30 in the area of the pressure build-up (after the so-called dead center TP at the transition from the suction to the pressure space - see also reference symbol "A" / FIG. 1) is moved against the pinion head and comes to rest here.
  • the bores 30 '(and also the grooves 30'') connect the free space (groove space) of the profile groove 34 at the foot of the sealing element 30 in each case - viewed in the direction of rotation X before the dead center TP between the Suction chamber and pressure chamber - with the leading tooth gap; as soon as the dead center TP is exceeded, the bores 30 '(and the grooves 30'') connect the mentioned groove space with the (lagging) tooth gap lying behind it.
  • the sealing element 30 is provided with an allowance E in terms of construction or production technology in order to be able to compensate for any manufacturing tolerances.
  • the sealing element 30 can slide radially out of or into the profile groove 34 (arrow Y) by the allowance E mentioned compared to the theoretical tip circle diameter K of the tooth tip 14 of the ring gear 6, the two end positions by the inner collar of the mushroom cap of the sealing element 30 on the one hand and by a positive connection (fixed stop) between the foot of the sealing element 30 and a wall of the profile groove 34 on the other hand.
  • the sealing element 30 is always by means of a corrugated spring up to the abovementioned stop between the foot part of the sealing element 30 and the corresponding wall of the profile groove 34 pressed outwards.
  • the sealing element 30 is ultimately always in its position opposite the profile groove 34.
  • this now means that the theoretical tip circle diameter on the ring gear 6 necessary for a trouble-free operation is reduced by the aforementioned inlet allowance E on the sealing element 30. This reduction can now lead to faults at the moment of the first contact between the ring gear 6 and the pinion 5 (cf. "A" in FIG. 1).
  • the above-mentioned corrugated spring is dispensed with, so that after the sealing element 30, due to the centrifugal force, always in the profile groove 34, i.e. is pressed into the tooth tip 14, the tip circle diameter K is larger than the theoretical tip circle diameter. Since the theoretical beginning of the tooth tip seal is still in the suction space (cf. "A" in FIG. 1), but the sealing element 30 is pressed outwards as a result of the centrifugal force, there can be no contact between the two gear wheels. As already mentioned, the tooth tip seal is therefore only built up when the partial pressure acts on the sealing element 30.
  • the fixed stop for the sealing element 30 is realized in connection with the non-load-bearing flank F 2, and this new geometry thus ensures sufficient strength for the forces that occur.
  • the tooth cross section on the side of the load-bearing flank F 1 in the area of the profile groove 34 for receiving the sealing element 30 thus corresponds to a bending beam with the same bending stress.

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

Abstract

The invention relates to a crescent-less internal gear pump with an internally toothed ring gear and a pinion meshing with the ring gear. Pinion and ring gear are rotatably mounted in a casing section which has a suction connection and a discharge connection; the ring gear has radial openings for the medium to be pumped; there is provided, in the tooth tips of the ring gear and in the tooth tips of the pinion, respectively, a profiled groove, into which one sealing element each is inserted which is able to slide on the opposite tooth tip of the pinion or the ring gear, respectively. The invention is characterised by the following features: the profiled groove is - as seen in a section perpendicular to the axis - free of connections; each of the individual sealing elements is provided with a duct which establishes a connection between the interior of the profiled groove and the sealing surface of the sealing element; the duct is enclosed - as seen in the direction of revolution of the pinion - by the material of the sealing element. <IMAGE>

Description

Die vorliegende Erfindung betrifft eine sichellose Innenzahnradpumpe mit in die Zahnköpfe eingesetzten, im Querschnitt pilzförmigen Dichtelementen zur Erzeugung von Hochdruck nach dem Oberbegriff des Patentanspruchs 1. Es ist der folgende Stand der Technik bekanntgeworden:

  • (1) DE-A-4 104 397
  • (2) DE-A-4 140 293
  • (3) US-A-3 429 269
  • (4) US-A-2 866 417
Die Druckschriften (1) und (2) zeigen und beschreiben Pumpen gemäß dem Oberbegriff von Anspruch 1.The present invention relates to a sickle-free internal gear pump with sealing elements that are mushroom-shaped in cross-section and used to generate high pressure according to the preamble of patent claim 1. The following prior art has become known:
  • (1) DE-A-4 104 397
  • (2) DE-A-4 140 293
  • (3) US-A-3,429,269
  • (4) US-A-2 866 417
The documents (1) and (2) show and describe pumps according to the preamble of claim 1.

Bei der aus (1) bekannten sichellosen Innenzahnradpumpe entsteht im Bereich des Druckaufbaus an den Zahnköpfen der geometrischen Form der Dichtelemente entsprechend nur eine Liniendichtung. Dies hat bei ungünstigen Verhältnissen aufgrund von Toleranzabweichungen, von Abstandsveränderungen oder von Änderungen der Kopfkreisdurchmesser gegebenenfalls zur Folge, daß die Dichtheit der Innenzahnradpumpe mangelhaft ist.In the case of the crescent-free internal gear pump known from (1), only a line seal is produced in the area of the pressure build-up on the tooth heads in accordance with the geometric shape of the sealing elements. In unfavorable conditions due to tolerance deviations, changes in spacing or changes in the tip diameter, this may have the consequence that the tightness of the internal gear pump is poor.

Druckschrift (2) beschreibt ein radial bewegliches Dichtelement, das - ohne einen übermäßigen Fertigungsaufwand zu bedingen- aufgrund der Formgebung die Dichtwirkung beim Druckaufbau zwischen den sich gegenüberliegenden Zahnköpfen der Zahnräder ganz wesentlich verbessert. Die Kontur des Dichtelements einerseits und die komplementäre Ausbildung des Dichtelements und der Profilnut im Zahnkopf andererseits bringen jedoch einige Probleme mit sich. Hierbei ist nämlich nachteilig, daß bei Überschreiten des Totpunktes der gesamte Systemdruck, d.h. der von der Pumpe erzeugte Arbeitsdruck, auf dem Dichtelement lastet. Dabei würde zum Zwecke des Abdichtens ein viel geringerer Druck ausreichen. Der hohe Systemdruck führt zu einem übermäßigen Verschleiß des Dichtelements.Document (2) describes a radially movable sealing element, which - without requiring excessive manufacturing effort - significantly improves the sealing effect when pressure builds up between the opposing tooth tips of the gearwheels due to the shape. However, the contour of the sealing element on the one hand and the complementary design of the sealing element and the profile groove in the tooth head on the other hand bring with it some problems. The disadvantage here is that when the dead center is exceeded, the entire system pressure, ie the working pressure generated by the pump, rests on the sealing element. This would be for the purpose of sealing a much lower pressure will suffice. The high system pressure leads to excessive wear of the sealing element.

Der Erfindung liegt die Aufgabe zugrunde, eine Pumpe gemäß dem Oberbegriff von Anspruch 1 derart zu gestalten, daß nicht der gesamte Systemdruck zum Abdichten herangezogen wird, sondern ein wesentlich niedrigerer Druck, der aber zum Zwecke des Dichtens ausreicht.The invention has for its object to design a pump according to the preamble of claim 1 such that not the entire system pressure is used for sealing, but a much lower pressure, which is sufficient for the purpose of sealing.

Diese Aufgabe wird durch die kennzeichnenden Merkmale von Anspruch 1 gelöst.This object is solved by the characterizing features of claim 1.

Hiermit wird im einzelnen folgendes erreicht: Es wird damit sichergestellt, daß das einzelne Dichtelement vor Erreichen des Totpunktes den zum Andrücken gegen den konjugierten Zahnkopf erforderlichen Druck erhält. Nach Durchlaufen des Totpunktes steht jedoch nicht der gesamte Systemdruck, d.h. der von der Pumpe erzeugte Arbeitsdruck, auf dem Dichtelement, sondern nur ein Teildruck.The following is achieved in detail: This ensures that the individual sealing element receives the pressure required for pressing against the conjugated tooth head before reaching the dead center. After passing through the dead center, however, the entire system pressure is not available, i.e. the working pressure generated by the pump on the sealing element, but only a partial pressure.

Gleichzeitig wird durch die besondere Gestaltung des Dichtelementes dafür gesorgt, daß ein minimaler Spalt zwischen Ritzelkopf und Hohlradkopf entsteht. Hierdurch läßt sich der volumetrische Wirkungsgrad verbessern, was wiederum zur Folge hat, daß die Innenzahnradpumpe auch für höhere Drücke einsetzbar ist. Ferner entfällt beim Herstellen des Hohlrades das aufwendige und komplizierte Profilschleifen der Hohlkopfform, weil die Dichtelemente jeweils getrennt hiervon hergestellt werden können.At the same time, the special design of the sealing element ensures that there is a minimal gap between the pinion head and the ring gear head. As a result, the volumetric efficiency can be improved, which in turn means that the internal gear pump can also be used for higher pressures. Furthermore, the elaborate and complicated profile grinding of the hollow head shape is eliminated when producing the ring gear, because the sealing elements can be produced separately therefrom.

Die Erfindung ist anhand der Zeichnung näher erläutert. Diese zeigt in

Figur 1
einen Querschnitt durch eine sichellose Innenzahnradpumpe im Bereich der beiden Zahnräder;
Figur 2
ein Ausführungsbeispiel eines radial beweglichen, im Querschnitt pilzförmigen Dichtelements in Verbindung mit seinem Einbau im Zahnkopf eines Hohlrads;
Figur 3
eine Aufsichtdarstellung auf ein Dichtelement nach Fig. 2, wobei der an der Rückseite des Dichtelements wirksame Teildruck über längs des Dichtelements vorgesehene Bohrungen gesteuert wird;
Figur 4
eine Aufsichtdarstellung auf ein Dichtelement nach Fig. 2, wobei der an der Rückseite des Dichtelements wirksame Teildruck über (eine) axial an der Stirnseite angearbeitete Nut(en) gesteuert wird.
The invention is explained in more detail with reference to the drawing. This shows in
Figure 1
a cross section through a sickle-free internal gear pump in the region of the two gears;
Figure 2
an embodiment of a radially movable, mushroom-shaped sealing element in cross section in Connection with its installation in the tooth head of a ring gear;
Figure 3
2 shows a top view of a sealing element according to FIG. 2, the partial pressure effective at the rear of the sealing element being controlled via bores provided along the sealing element;
Figure 4
a top view of a sealing element according to FIG. 2, wherein the partial pressure effective on the back of the sealing element is controlled via (one) axially machined groove (s) on the end face.

Die Figur 1 zeigt in einem Querschnitt eine sichellose, kopfdichtende und spielbehaftete, jeweils mit einer Flanke dichtende Innenzahnradpumpe und zwar im Bereich eines Gehäusemittelteils, dem sich - in Axialrichtung betrachtet - weitere Gehäuseteile anschließen. Ein auf einer Ritzelwelle 4 befestigtes außenverzahntes Ritzel 5 steht im Eingriff mit einem innenverzahnten Hohlrad 6. Die Verzahnung 12 des Ritzels 5 und des Hohlrads 6 hat eine axiale Breite, die größer ist als der Wälzkreisdurchmesser des Ritzels. Das Ritzel 5 und das Hohlrad 6 sind nicht koaxial, sondern exzentrisch zueinander gelagert; 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 6 in Berührung kommt. Zu erkennen ist ferner ein Sauganschluß 7 in der Zone, bei der unter Drehung in Pfeilrichtung X die Zähne am Ritzel 5 bzw. Hohlrad 6 außer Eingriff geraten. Dem Sauganschluß 7 im Gehäusemittelteil, in dem das Hohlrad 6 und das Ritzel 5 gelagert sind, schließt sich in axialer Richtung jeweils zu den benachbarten Gehäuseteilen eine Saugtasche an, die sich über einen Teil der Mantelfläche 20 des Hohlrads 6 erstreckt. Ein Druckanschluß 10 befindet sich, ebenfalls ausgehend von einer sich über einen Umfangsbereich am Hohlrad 6 erstreckenden Drucktasche auf der gegenüberliegenden Seite der Pumpe. Die Zuströmung von Druckmedium zum Innenraum der Pumpe, also zu den Zahnlücken im Ritzel 5 und im Hohlrad 6, welche die Förderung des Druckmediums bewirken, erfolgt über - vgl. Fig. 2 - radiale Durchbrüche (radiale Bohrungen) 17 im Hohlrad 6. Diese Durchbrüche 17 gehen von der Mantelfläche 20 aus und münden im Zahngrund des Hohlrades 6.1 shows in a cross section a sickle-free, head-sealing and backlash-type internal gear pump, each sealing with a flank, in the area of a central housing part, which - viewed in the axial direction - is followed by further housing parts. An externally toothed pinion 5 fastened on a pinion shaft 4 is in engagement with an internally toothed ring gear 6. The toothing 12 of the pinion 5 and the ring gear 6 has an axial width which is greater than the pitch circle diameter of the pinion. The pinion 5 and the ring gear 6 are not mounted 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 6. A suction connection 7 can also be seen in the zone in which the teeth on the pinion 5 or ring gear 6 disengage when rotated in the direction of the arrow X. The suction connection 7 in the middle part of the housing, in which the ring gear 6 and the pinion 5 are mounted, is followed in the axial direction by a suction pocket, which extends over part of the outer surface 20 of the ring gear 6, to the adjacent housing parts. A pressure connection 10 is located, also starting from one over a peripheral area Ring gear 6 extending pressure pocket on the opposite side of the pump. The inflow of pressure medium to the interior of the pump, that is, to the tooth gaps in the pinion 5 and in the ring gear 6, which effect the delivery of the pressure medium, takes place via - cf. Fig. 2 - radial openings (radial bores) 17 in the ring gear 6. These openings 17 start from the outer surface 20 and open into the tooth base of the ring gear 6.

Die soweit beschriebene sichellose Innenzahnradpumpe ist Stand der Technik. Gemäß der Darstellung nach Fig. 1 sind nun - in an sich bekannter, aber keineswegs einschränkender Art und Weise - an den Zahnköpfen des Hohlrads 6 jeweils radial bewegliche (Pfeil Y), im querschnitt pilzförmige Dichtelemente 30 eingesetzt, die gemäß der vorliegenden Erfindung besonders ausgebildet und in einer komplementären Profilnut 34 gelagert bzw. gehalten sind. Diese erfindungsgemäß gestalteten Dichtelemente 30 und die entsprechende Profilnut 34 sind in Fig. 2 vergrößert dargestellt.The sickle-free internal gear pump described so far is state of the art. According to the illustration in FIG. 1, radially movable (arrow Y), mushroom-shaped sealing elements 30 are used on the tooth heads of the ring gear 6 in a manner known per se, but in no way restrictive, which are specially designed according to the present invention and are stored or held in a complementary profile groove 34. These sealing elements 30 designed according to the invention and the corresponding profile groove 34 are shown enlarged in FIG. 2.

Fig. 2 zeigt einen Ausschnitt des Hohlrads 6 im Bereich eines Zahnkopfes 14. Über den Umfang des Hohlrads 6 betrachtet sind jeweils in den Zahnlücken die zur Zuströmung des Druckmediums zum Innenraum der Innenzahnradpumpe vorgesehenen Durchbrüche (radiale Bohrungen) 17 eingearbeitet. Während nun bei der Konstruktion gemäß dem Hauptpatent diese Durchbrüche 17 jeweils die Profilnut 34 für die Dichtelemente 30 anschneiden und so die Rückseite des Dichtelements 30 stets mit dem in der voreilenden Zahnlücke herrschenden Druck beaufschlagen, schneiden die Durchbrüche 17 die Profilnuten 34 nunmehr nicht mehr an.2 shows a section of the ring gear 6 in the region of a tooth head 14. When viewed over the circumference of the ring gear 6, the openings (radial bores) 17 provided for the inflow of the pressure medium to the interior of the internal gear pump are machined in the tooth gaps. While in the construction according to the main patent these openings 17 each cut the profile groove 34 for the sealing elements 30 and thus always act on the back of the sealing element 30 with the pressure prevailing in the leading tooth gap, the openings 17 no longer cut the profile grooves 34.

Aufgrund dieser konstruktiven Änderung ist es somit - fertigungstechnisch betrachtet - nicht mehr erforderlich, daß die Verschneidungsstelle zwischen den Durchbrüchen 17 und den Profilnuten 34 entgratet werden müssen; dies war angesichts der etwas komplizierten Raumverhältnisse relativ kompliziert, d.h. aufwendig.Because of this design change, it is no longer necessary - from a manufacturing point of view - that the intersection between the openings 17 and the profile grooves 34 must be deburred; In view of the somewhat complicated spatial conditions, this was relatively complicated, ie complex.

Die konstruktive Änderung hat darüberhinaus auch funktionale Vorteile. Während bei der Konstruktion entsprechend dem Hauptpatent der auf der Rückseite des Dichtelements 30 wirksame (Anpreß-)Druck stets so groß ist wie der Druck in der voreilenden Zahnlücke (wodurch das Dichtelement mit der dem Systemdruck entsprechenden Kraft im Bereich der Umsteuerung von der Saugseite zur Druckseite der Pumpe nach außen gedrückt wird), ist der am Dichtelement 30 wirksame Druck aufgrund der konstruktiven Änderung nur noch ein Teildruck. In besonders vorteilhafter Weise kann dieser an der Rückseite des Dichtelements wirksame Teildruck mittels - vgl. Fig. 3 - längs der Dichtelemente 30 vorgesehenen Bohrungen 30' oder mittels - vgl. Fig. 4 - an der oder den Stirnseiten eingearbeiteten Nuten 30'' aufgebaut und gesteuert werden, so daß letztlich die Kraft, mit der das Dichtelement 30 nach außen gedrückt wird, reduziert wird. Damit wird letztendlich die zwischen dem Dichtelement 30 und dem Ritzelkopf wirksame Herz'sche Pressung und damit auch der Verschleiß reduziert.The design change also has functional advantages. While in the construction according to the main patent, the (contact) pressure effective on the back of the sealing element 30 is always as great as the pressure in the leading tooth gap (which means that the sealing element with the force corresponding to the system pressure in the area of reversal from the suction side to the pressure side the pump is pressed outwards), the pressure acting on the sealing element 30 is only a partial pressure due to the design change. In a particularly advantageous manner, this partial pressure effective on the back of the sealing element can be achieved by means of - cf. 3 - along the sealing elements 30 provided bores 30 'or by means of - see. Fig. 4 - are built and controlled on the or the incorporated end grooves 30 '', so that ultimately the force with which the sealing element 30 is pressed outwards is reduced. Ultimately, the Herz's pressure between the sealing element 30 and the pinion head and thus also the wear are reduced.

Der genannte Teildruck sorgt - in Verbindung mit der vorliegenden Verbesserungserfindung - im Bereich des Druckaufbaus (nach dem sogenannten Totpunkt TP am Übergang vom Saug- zum Druckraum - vgl. auch Bezugszeichen "A" / Fig. 1) - auch dafür, daß das Dichtelement 30 gegen den Ritzelkopf bewegt wird und hier zur Anlage kommt.The partial pressure mentioned - in conjunction with the present improvement invention - also ensures that the sealing element 30 in the area of the pressure build-up (after the so-called dead center TP at the transition from the suction to the pressure space - see also reference symbol "A" / FIG. 1) is moved against the pinion head and comes to rest here.

Funktional betrachtet sei bezüglich der Realisierung der Kanäle zur Steuerung des auf das Dichtelement 30 wirkenden Teildrucks noch folgendes angemerkt: Die Bohrungen 30' (und auch die Nuten 30'') verbinden den Freiraum (Nutraum) der Profilnut 34 am Fuß des Dichtelemtns 30 jeweils - in Drehrichtung X betrachtet vor dem Totpunkt TP zwischen dem Saugraum und dem Druckraum - mit der voreilenden Zahnlücke; sobald der Totpunkt TP überschritten ist, verbinden die Bohrungen 30' (und die Nuten 30'') den genannten Nutraum mit der jeweils dahinter liegenden (nacheilenden) Zahnlücke. Dies hat die vorteilhafte Wirkung, daß vor Erreichen des Totpunktes TP das Dichtelement den zum Andrücken gegen den konjugierten Zahnkopf erforderlichen Druck erhält. Stünde nur der Druck aus der nacheilenden Zahnlücke zur Verfügung, so käme es gar nicht zum Andrücken des Dichtelements, da der Nutraum drucklos wäre. Bezüglich der Wirkung der Bohrungen 30' (bzw. der Nuten 30'') sei ergänzend und erläuternd angemerkt, daß nach dem Überwinden des Totpunkts TP eben nicht der gesamte Systemdruck, d.h. der von der Pumpe erzeugte Arbeitsdruck, am Dichtelement 30 ansteht, sondern nur der über die Bohrungen 30' (bzw. die Nuten 30'') vermittelte Teildruck (Druckaufbau-Druck).From a functional point of view, the following should also be noted with regard to the implementation of the channels for controlling the partial pressure acting on the sealing element 30: the bores 30 '(and also the grooves 30'') connect the free space (groove space) of the profile groove 34 at the foot of the sealing element 30 in each case - viewed in the direction of rotation X before the dead center TP between the Suction chamber and pressure chamber - with the leading tooth gap; as soon as the dead center TP is exceeded, the bores 30 '(and the grooves 30'') connect the mentioned groove space with the (lagging) tooth gap lying behind it. This has the advantageous effect that before the dead center TP is reached, the sealing element receives the pressure required for pressing against the conjugated tooth head. If only the pressure from the lagging tooth gap were available, the sealing element would not be pressed at all, since the groove space would be depressurized. With regard to the effect of the bores 30 '(or the grooves 30''), it should be added and explained that after the dead center TP has been overcome, not all the system pressure, ie the working pressure generated by the pump, is present at the sealing element 30, but only the partial pressure (pressure build-up pressure) conveyed via the bores 30 '(or the grooves 30'').

Konstruktiv betrachtet ist im Vergleich zwischen dem Hauptpatent und der vorliegenden weiteren Ausgestaltung noch folgendes anzumerken: Das Dichtelement 30 ist konstruktiv bzw. fertigungstechnisch betrachtet mit einem Aufmaß E versehen, um so etwaige Fertigungstoleranzen kompensieren zu können. Wie der Darstellung nach Fig. 2 zu entnehmen ist, kann das Dichtelement 30 um das genannte Aufmaß E gegenüber dem theoretischen Kopfkreisdurchmesser K des Zahnkopfes 14 des Hohlrads 6 radial aus der bzw. in die Profilnut 34 gleiten (Pfeil Y), wobei die beiden Endpositionen durch den Innenkragen der Pilzkappe des Dichtelements 30 einerseits und durch einen Formschluß (Festanschlag) zwischen dem Fuß des Dichtelements 30 und einer Wandung der Profilnut 34 andererseits bestimmt sind. Diese Randbedingungen gelten gleichermaßen für das Hauptpatent und die erfindungsgemäße Weiterbildung.From a constructional point of view, the following should also be noted in the comparison between the main patent and the present further embodiment: The sealing element 30 is provided with an allowance E in terms of construction or production technology in order to be able to compensate for any manufacturing tolerances. As can be seen in the illustration according to FIG. 2, the sealing element 30 can slide radially out of or into the profile groove 34 (arrow Y) by the allowance E mentioned compared to the theoretical tip circle diameter K of the tooth tip 14 of the ring gear 6, the two end positions by the inner collar of the mushroom cap of the sealing element 30 on the one hand and by a positive connection (fixed stop) between the foot of the sealing element 30 and a wall of the profile groove 34 on the other hand. These boundary conditions apply equally to the main patent and the further development according to the invention.

Beim Ausführungsbeispiel gemäß dem Hauptpatent wird das Dichtelement 30 mittels einer Wellfeder stets bis zum genannten Anschlag zwischen dem Fußteil des Dichtelements 30 und der entsprechenden Wandung der Profilnut 34 nach außen gedrückt. Das Dichtelement 30 befindet sich letztlich immer in seiner der Profilnut 34 gegenüber vorstehenden Position. Dies bedeutet nun aber, daß der für einen störungsfreien Ablauf notwendige theoretische Kopfkreisdurchmesser am Hohlrad 6 um das genannte EInlauf-Aufmaß E am Dichtelement 30 verkleinert wird. Diese Verkleinerung kann nun im Moment der ersten Berührung zwischen dem Hohlrad 6 und dem Ritzel 5 (vgl. "A" in Fig. 1) zu Störungen führen.In the embodiment according to the main patent, the sealing element 30 is always by means of a corrugated spring up to the abovementioned stop between the foot part of the sealing element 30 and the corresponding wall of the profile groove 34 pressed outwards. The sealing element 30 is ultimately always in its position opposite the profile groove 34. However, this now means that the theoretical tip circle diameter on the ring gear 6 necessary for a trouble-free operation is reduced by the aforementioned inlet allowance E on the sealing element 30. This reduction can now lead to faults at the moment of the first contact between the ring gear 6 and the pinion 5 (cf. "A" in FIG. 1).

Gemäß der vorliegenden Weiterbildung der erfindungsgemäßen Innenzahnradpumpe wird auf die genannte Wellfeder verzichtet, so daß, nachdem das Dichtelement 30 infolge der Zentrifugalkraft stets in die Profilnut 34, d.h. in den Zahnkopf 14 hineingedrückt wird, der Kopfkreisdurchmesser K größer ist als der theoretische Kopfkreisdurchmesser. Da nun der theoretische Beginn der Zahnkopfdichtung noch im Saugraum (vgl. "A" in Fig. 1) liegt, das Dichtelement 30 infolge der Zentrifugalkraft jedoch nach außen gedrückt wird, kann es so zu keiner Berührung der beiden Zahnräder kommen. Die Zahnkopfdichtung wird - wie bereits erwähnt - somit erst dann aufgebaut, wenn der Teildruck auf das Dichtelement 30 wirkt.According to the present development of the internal gear pump according to the invention, the above-mentioned corrugated spring is dispensed with, so that after the sealing element 30, due to the centrifugal force, always in the profile groove 34, i.e. is pressed into the tooth tip 14, the tip circle diameter K is larger than the theoretical tip circle diameter. Since the theoretical beginning of the tooth tip seal is still in the suction space (cf. "A" in FIG. 1), but the sealing element 30 is pressed outwards as a result of the centrifugal force, there can be no contact between the two gear wheels. As already mentioned, the tooth tip seal is therefore only built up when the partial pressure acts on the sealing element 30.

Was die spezifische Kontur, d.h. die Formgebung des Dichtelements 30 angeht, so traten in Verbindung mit ersten praktischen Erprobungen folgende Problempunkte auf: Es hat sich gezeigt, daß die scharfen Kanten der Pilzkappe des Dichtelements 30 bruchgefährdet sind und dies wiederum hatte letztlich zur Folge, daß - wegen des Einlaufs E - die Dichtlänge zunehmend länger wird (vgl. "b) in Fig. 2).As for the specific contour, i.e. As far as the shape of the sealing element 30 is concerned, the following problem points arose in connection with initial practical tests: It has been shown that the sharp edges of the mushroom cap of the sealing element 30 are prone to breakage, and this in turn ultimately has the consequence that - because of the inlet E - the sealing length becomes increasingly longer (cf. "b) in Fig. 2).

Um diese bei der Ausführung entsprechend dem Hauptpatent beobachteten Probleme zu eliminieren, ist das Dichtelement 30 wie folgt konstruktiv neu gestaltet worden:

  • Dadurch, daß zu Beginn der theoretischen Kopfdichtung die Saugphase noch vorhanden ist, wird im Bereich von der Mitte bis zur Saugseite (vgl. Pfeil S) die maximale Dichtlänge am Dichtelement 30 nicht benötigt. Somit wurde die Pilzkappe des Dichtelements 30 in diesem Bereich mit einem Radius R 1 versehen;
  • im Bereich von der Mitte zur Druckseite (vgl. Pfeil D) muß die vom Dichtelement 30 zwischen dem Ritzel 5 und dem Hohlrad 6 aufgebrachte Dichtwirkung stets maximale Dichtlänge aufweisen. Dies bedeutet, daß ein Radius R 2 am Ende der Dichtung realisiert werden kann, wenn gleichzeitig die Evolventenlänge auf der entsprechenden nichttragenden Zahnflanke F 2 zurückgenommen wird (vgl. Z).
In order to eliminate these problems observed in the execution according to the main patent, the sealing element 30 has been redesigned as follows:
  • Because the suction phase is still present at the beginning of the theoretical head gasket, the maximum sealing length on the sealing element 30 is not required in the area from the middle to the suction side (cf. arrow S). Thus, the mushroom cap of the sealing element 30 was provided with a radius R 1 in this area;
  • in the area from the center to the pressure side (cf. arrow D), the sealing action applied by the sealing element 30 between the pinion 5 and the ring gear 6 must always have a maximum sealing length. This means that a radius R 2 can be realized at the end of the seal if the involute length on the corresponding non-load-bearing tooth flank F 2 is simultaneously reduced (cf. Z).

In Fig. 2 ist die neugestaltete Pilzkappe des Dichtelements 30 im Detail dargestellt, wobei nochmals anzumerken ist, daß mit den beiden Radien R 1 und R 2 am Dichtelement eine zweifache Wirkung erzielt wird, nämlich

  • einerseits wird gewährleistet, daß durch den Einlauf die Dichtlänge nicht - wie bei der Innenzahnradpumpe gemäß dem Patentanmeldung P 41 40 293.6 - kleiner, sondern größer wird (vgl. "b"), und
  • andererseits wird sichergestellt, daß die Kanten der Pilzkappe nicht scharfkantig sind und somit nicht ausbrechen können.
2, the redesigned mushroom cap of the sealing element 30 is shown in detail, it being noted once again that a double effect is achieved with the two radii R 1 and R 2 on the sealing element, namely
  • on the one hand it is ensured that the sealing length does not become smaller - as in the case of the internal gear pump according to patent application P 41 40 293.6 - but larger (cf. "b"), and
  • on the other hand, it ensures that the edges of the mushroom cap are not sharp-edged and therefore cannot break out.

Letztendlich hat sich in Verbindung mit der Erprobung der dem Hauptpatent entsprechenden Innenzahnradpumpe noch ein weiterer Punkt als problematisch erwiesen. Auszugehen ist dabei von dem Umstand, daß die im Zahneingriff tragende (nacheilende) Flanke F 1 des Hohlrads 6 das dem Betriebsdruck entsprechende Drehmoment übertragen muß. Gemäß dem im Hauptpatent dargestellten Ausführungsbeispiel war der formschlüssige Festanschlag des Dichtelements 30 relativ zur Profilnut 34 dadurch verifiziert, daß das in Umlaufrichtung X des Hohlrads 6 betrachtet nacheilende Fußteil konisch verbreitert und die Wandung der Profilnut 34 komplementär ausgebildet wurde. Damit jedoch wurde die tragende Flanke F 1 des Hohlrads 6 geschwächt.Finally, in connection with the testing of the internal gear pump corresponding to the main patent, another point has proven to be problematic. The starting point here is the fact that the (trailing) flank F 1 of the ring gear 6 bearing in the tooth engagement must transmit the torque corresponding to the operating pressure. According to the embodiment shown in the main patent, the positive fixed stop of the sealing element 30 was verified relative to the profile groove 34 by the fact that the lagging viewed in the direction of rotation X of the ring gear 6 Base part widened conically and the wall of the profile groove 34 was complementary. However, this has weakened the supporting flank F 1 of the ring gear 6.

Gemäß der vorliegenden Weiterbildung ist der Festanschlag für das Dichtelement 30 in Verbindung mit der nicht tragenden Flanke F 2 realisiert, und diese neue Geometrie gewährleistet so eine für die auftretenden Kräfte ausreichende Festigkeit. Der Zahnquerschnitt auf der Seite der tragenden Flanke F 1 im Bereich der Profilnut 34 zur Aufnahme des Dichtelements 30 entspricht so einem Biegeträger gleicher Biegebeanspruchung.According to the present development, the fixed stop for the sealing element 30 is realized in connection with the non-load-bearing flank F 2, and this new geometry thus ensures sufficient strength for the forces that occur. The tooth cross section on the side of the load-bearing flank F 1 in the area of the profile groove 34 for receiving the sealing element 30 thus corresponds to a bending beam with the same bending stress.

Claims (9)

Sichellose Innenzahnradpumpe 1.1 mit einem innenverzahnten Hohlrad (6) und einem mit dem Hohlrad (6) kämmenden Ritzel (5) 1.2 Ritzel (5) und Hohlrad (6) sind in einem Gehäuseteil drehbar gelagert, das einen Sauganschluß (7) und einen Druckanschluß (10) aufweist; 1.3 das Hohlrad (6) weist radiale Durchbrüche (17) für das zu pumpende Medium auf; 1.4 in den Zahnköpfen (14) des Hohlrades (6) bzw. in den Zahnköpfen (13) des Ritzels (5) ist eine Profilnut (34) vorgesehen, in die jeweils ein Dichtelement (30) eingesetzt ist, das am gegenüberliegenden Zahnkopf des Ritzels (5) bzw. des Hohlrades (6) gleiten kann, gekennzeichnet durch die folgenden Merkmale: 1.5 die Profilnut (34) ist - in einem achssenkrechten Schnitt gesehen - frei von Anschlüssen; 1.6 das einzelne Dichtelement (30) ist jeweils mit einem Kanal (30', 30'') versehen, der eine Verbindung zwischen dem Innenraum der Profilnut (34) und der Dichtfläche des Dichtelementes (30) herstellt; 1.7 der Kanal (30', 30'') ist - in Umlaufrichtung des Ritzels (5) gesehen - vom Fleisch des Dichtelementes (30) umschlossen. Sickle-free internal gear pump 1.1 with an internally toothed ring gear (6) and a pinion (5) meshing with the ring gear (6) 1.2 pinion (5) and ring gear (6) are rotatably mounted in a housing part which has a suction connection (7) and a pressure connection (10); 1.3 the ring gear (6) has radial openings (17) for the medium to be pumped; 1.4 in the tooth heads (14) of the ring gear (6) or in the tooth heads (13) of the pinion (5) a profile groove (34) is provided, in each of which a sealing element (30) is inserted, which is on the opposite tooth head of the pinion (5) or the ring gear (6) can slide, characterized by the following features: 1.5 the profile groove (34) is - seen in a section perpendicular to the axis - free of connections; 1.6 the individual sealing element (30) is each provided with a channel (30 ', 30'') which creates a connection between the interior of the profile groove (34) and the sealing surface of the sealing element (30); 1.7 the channel (30 ', 30'') - seen in the direction of rotation of the pinion (5) - is enclosed by the meat of the sealing element (30). Innenzahnradpumpe nach Anspruch 1, dadurch gekennzeichnet, daß das Gehäuseteil, in welchem Ritzel (5) und Hohlrad (6) gelagert sind, in axialer Richtung so breit ist, wie die Verzahnung (12) des Hohlrades (6) und des Ritzels (5).Internal gear pump according to claim 1, characterized in that the housing part, in which pinion (5) and ring gear (6) are mounted, is as wide in the axial direction as the toothing (12) of the ring gear (6) and pinion (5) . Innenzahnradpumpe nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß das Dichtelement (30) - in einem achssenkrechten Schnitt gesehen - Pilzform aufweist, wobei die Dichtfläche des Dichtelementes (30) den Hut des Pilzes bildet.Internal gear pump according to claim 1 or 2, characterized in that the sealing element (30) - as seen in a section perpendicular to the axis - has a mushroom shape, the sealing surface of the sealing element (30) forming the hat of the mushroom. Innenzahnradpumpe nach einem der Ansprüche 1-3, dadurch gekennzeichnet, daß der Kanal als Bohrung (30') ausgebildet ist.Internal gear pump according to one of claims 1-3, characterized in that the channel is designed as a bore (30 '). Innenzahnradpumpe nach einem der Ansprüche 1-3, dadurch gekennzeichnet, daß der Kanal als Nut (30'') ausgebildet ist.Internal gear pump according to one of claims 1-3, characterized in that the channel is designed as a groove (30 ''). Innenzahnradpumpe nach Anspruch 5, dadurch gekennzeichnet, daß die Nut (30'') - in axialer Richtung gesehen - an einem Rand des Dichtelements (30) angeordnet und randoffen ist.Internal gear pump according to claim 5, characterized in that the groove (30 '') - viewed in the axial direction - is arranged on an edge of the sealing element (30) and is open at the edge. Innenzahnradpumpe nach einem der Ansprüche 1-6, dadurch gekennzeichnet, daß die Außenkanten der am konjugierten Zahnkopf des Ritzels (5) bzw. des Hohlrades (6) abgleitende Fläche des Dichtelements (30) abgerundet sind (Radien R1, R2).Internal gear pump according to one of claims 1-6, characterized in that the outer edges of the surface of the sealing element (30) sliding on the conjugate tooth head of the pinion (5) or of the ring gear (6) are rounded (radii R1, R2). Innenzahnradpumpe nach Anspruch 7, dadurch gekennzeichnet, daß die nicht-tragende Flanke (F2) der Zahnköpfe (14) des Hohlrades (6) bzw. der Zahnköpfe (13) des Ritzels (5) maßlich reduziert ist.Internal gear pump according to claim 7, characterized in that the non-load-bearing flank (F2) of the tooth heads (14) of the ring gear (6) or the tooth heads (13) of the pinion (5) is reduced in size. Innenzahnradpumpe nach Anspruch 7 oder 8, dadurch gekennzeichnet, daß das Dichtelement (30) und die Profilnut (34) derart zueinander komplementär ausgebildet sind, daß die radiale Beweglichkeit des Dichtelements (30) durch einen Festanschlag definiert ist, der das Ausfahren der Profilnut (34) begrenzt, und daß der Festanschlag in Verbindung mit der nichttragenden Flanke (F2) des Zahnkopfes (14) des Hohlrades (6) bzw. des Zahnkopfes (13) des Ritzels (5) ausgeführt ist.Internal gear pump according to Claim 7 or 8, characterized in that the sealing element (30) and the profile groove (34) are designed to be complementary to one another in such a way that the radial mobility of the sealing element (30) is defined by a fixed stop which defines the extension of the profile groove (34 ) limited, and that the fixed stop in connection with the non-load-bearing Flank (F2) of the tooth head (14) of the ring gear (6) or the tooth head (13) of the pinion (5).
EP93114117A 1993-01-18 1993-09-03 Internal gear pump with sealings incorporated in the teeth Expired - Lifetime EP0607497B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4301104 1993-01-18
DE4301104 1993-01-18

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EP0607497B1 EP0607497B1 (en) 1996-06-12

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US (1) US5451150A (en)
EP (1) EP0607497B1 (en)
JP (1) JPH06241174A (en)
AT (1) ATE139305T1 (en)
DE (1) DE59302915D1 (en)
DK (1) DK0607497T3 (en)
ES (1) ES2090799T3 (en)

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EP0661454A1 (en) * 1993-12-17 1995-07-05 J.M. Voith GmbH Internal gear pump
DE4419975A1 (en) * 1994-06-08 1995-12-14 Voith Gmbh J M Sickle-free internal gear pump with sealing elements inserted into the tooth heads and controlled via pressure channels on the back
DE19746769C1 (en) * 1997-10-23 1999-02-11 Bosch Gmbh Robert Inner geared fluid pump or motor
EP0933530A1 (en) * 1998-02-03 1999-08-04 Voith Turbo GmbH & Co. KG Internal gear pump free from inner crescent space
EP0933529A3 (en) * 1998-02-03 2000-06-07 Voith Turbo GmbH & Co. KG Internal gear pump with empty crescent space

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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
DE102020001287A1 (en) 2020-02-27 2021-09-02 Hypneu Gmbh Hydraulik Und Pneumatik Arrangement for the axial sealing of a gearwheel along the tooth flank and the tooth base against a displaceable negative component

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GB793089A (en) * 1956-06-09 1958-04-09 Hanomag Ag Improvements in rotary engines and compressors
US2866417A (en) * 1956-06-11 1958-12-30 Hanomag Ag Rotary piston machine
US3429269A (en) * 1965-08-21 1969-02-25 Concentric Eng Ltd Fluid pumps and motors
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
DE4140293A1 (en) * 1991-12-06 1993-06-09 J.M. Voith Gmbh, 7920 Heidenheim, De SAFETY INTERNAL GEAR PUMP WITH SEALING ELEMENTS INSERTED IN THE GEAR HEADS

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0661454A1 (en) * 1993-12-17 1995-07-05 J.M. Voith GmbH Internal gear pump
DE4419975A1 (en) * 1994-06-08 1995-12-14 Voith Gmbh J M Sickle-free internal gear pump with sealing elements inserted into the tooth heads and controlled via pressure channels on the back
DE19746769C1 (en) * 1997-10-23 1999-02-11 Bosch Gmbh Robert Inner geared fluid pump or motor
EP0933530A1 (en) * 1998-02-03 1999-08-04 Voith Turbo GmbH & Co. KG Internal gear pump free from inner crescent space
EP0933529A3 (en) * 1998-02-03 2000-06-07 Voith Turbo GmbH & Co. KG Internal gear pump with empty crescent space
US6095782A (en) * 1998-02-03 2000-08-01 Voith Turbo Gmbh & Co Kg Crescentless internal gear pump
US6164943A (en) * 1998-02-03 2000-12-26 Voith Turbo Gmbh & Co., Kg Internal geared wheel pump without crescent-shaped [sickle] piece

Also Published As

Publication number Publication date
EP0607497B1 (en) 1996-06-12
DK0607497T3 (en) 1996-10-21
JPH06241174A (en) 1994-08-30
US5451150A (en) 1995-09-19
ES2090799T3 (en) 1996-10-16
DE59302915D1 (en) 1996-07-18
ATE139305T1 (en) 1996-06-15

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