EP0161421B1 - Internal rotor gear oil pump for internal-combustion engines of motor vehicles - Google Patents

Internal rotor gear oil pump for internal-combustion engines of motor vehicles Download PDF

Info

Publication number
EP0161421B1
EP0161421B1 EP19850103161 EP85103161A EP0161421B1 EP 0161421 B1 EP0161421 B1 EP 0161421B1 EP 19850103161 EP19850103161 EP 19850103161 EP 85103161 A EP85103161 A EP 85103161A EP 0161421 B1 EP0161421 B1 EP 0161421B1
Authority
EP
European Patent Office
Prior art keywords
pump
suction pocket
suction
working chamber
pocket
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
Application number
EP19850103161
Other languages
German (de)
French (fr)
Other versions
EP0161421A2 (en
EP0161421A3 (en
Inventor
Kurt Sickinger
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.)
Schwaebische Huettenwerke Automotive GmbH
Original Assignee
Schwaebische Huettenwerke Automotive GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=6230939&utm_source=***_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0161421(B1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Schwaebische Huettenwerke Automotive GmbH filed Critical Schwaebische Huettenwerke Automotive GmbH
Publication of EP0161421A2 publication Critical patent/EP0161421A2/en
Publication of EP0161421A3 publication Critical patent/EP0161421A3/en
Application granted granted Critical
Publication of EP0161421B1 publication Critical patent/EP0161421B1/en
Expired legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/02—Pressure lubrication using lubricating pumps

Definitions

  • the invention relates to an internal rotor gear oil pump with the features of the preamble of claim 1.
  • Such pumps have recently become increasingly popular for supplying oil to motor vehicle internal combustion engines, in particular piston engines of this type. They have the essential advantage that a separate drive for the oil pump is not necessary, since the extension of the crankshaft, which, as is preferred and usually the case, is formed by the free end of the crankshaft, but can in principle also be a separate part , can directly drive the pinion.
  • the pinion can sit directly on the crankshaft. However, it is preferably seated on a separate bearing collar formed in the housing of the pump and is driven by the crankshaft passing through this collar via drivers.
  • the flow direction in the feed channel is approximately tangential to the central circumferential direction of the pump gearwheels in the suction kidney region.
  • the projection of the direction of flow in the feed channel in the area in which it merges into the suction kidney area should have a direction on a normal plane of the axis of rotation of the pump which approximately coincides with the direction of movement of the teeth of the pinion and the ring gear in this area.
  • the channel can also e.g. B. open parallel to the pump axis in the suction kidney. This can be the case in particular when the pump is used in an automatic motor vehicle transmission.
  • the feed channel which at the end of the oil suction pipe has the same circular cross section as the oil suction pipe, extends with a tapering circular cross section to the suction kidney.
  • the oil supply channel runs partly on the working chamber side of the end wall of the working chamber containing the suction cups and partly on the side of this end wall facing away from the working chamber.
  • the course of the feed channel is such that the oil flow not only flows around the end face of the ring gear on the suction side, but also part of the circumferential surface of the ring gear.
  • the pump according to an older application published on May 24, 1984 as DE-A-32 43 067.1 eliminates this disadvantage.
  • the delivery capacity of the pump can be increased further, at least to a great extent proportional to the speed, without increasing its dimensions, even in the higher speed range, where this power otherwise drops sharply; one avoids the foaming that often occurs with other pumps even at higher speeds.
  • the oil flow occurs approximately tangentially to the direction of rotation of the toothing in a suction kidney arranged on the side of the end wall of the working chamber facing away from the working chamber and running in the direction of rotation, reducing its cross section in the direction of rotation, which ends considerably in front of the plane containing the gearwheel axes.
  • the invention solves the problem, both in the known pump and - and in particular - in the pump according to the above-mentioned earlier application to improve the performance, that is to say the delivery rate in the unit of time, by means of a favorable design of the oil inflow.
  • the pump which is sealed in a known manner by a sickle-shaped filler arranged in the working chamber, is provided with a suction kidney which, as before, does not end well before the symmetry level of the pump, but, in contrast, extends almost to or preferably beyond the plane of symmetry (the plane containing the two gearwheel axes) of the pump.
  • a suction kidney which, as before, does not end well before the symmetry level of the pump, but, in contrast, extends almost to or preferably beyond the plane of symmetry (the plane containing the two gearwheel axes) of the pump.
  • the suction kidney extends beyond the plane of symmetry by 20 to 30 °, based on the axis of rotation of the pinion, preferably 25 °. Since the filler with its cylindrical surfaces limits the delivery spaces formed by the interdental spaces of the ring gear or pinion, which constantly move from the suction side to the pressure side, these delivery spaces are open to the suction kidney over a considerable length of their movement path, so that a longer one The period for filling the mentioned funding areas is available than was previously the case. Therefore, even at a high speed, the time during which the said delivery spaces are filled with liquid is sufficient to ensure that these delivery spaces always fill well.
  • the invention has the effect that, up to an unusually high speed, the already high delivery rate of the pump is approximately proportional to the speed.
  • the suction kidney not only extends radially outside the filler beyond the plane of symmetry, but is at its end pointing in the direction of rotation divided into two branches that run on both sides of the filler.
  • the delivery rate is particularly high when the start of the pressure kidney is at a distance of only about two gear wheel divisions from the two ends of the suction kidney branches in the circumferential direction. This means that the distance between the ends of the inner and outer suction kidney branch and the pressure kidney beginning approximately in the region of the end of the filler piece is measured in the circumferential direction at half the tooth height of the pinion or the ring gear. If the ends of the suction kidney branches now lie, for example, on a radial jet of the pinion or ring gear, then the beginnings of the pressure kidneys do not lie on a radial jet.
  • the cross section of the feed channel should only be slightly reduced to avoid losses up to the transition into the suction kidney. However, a small reduction is considered to be expedient in order to ensure a good transition of the channel cross section into the suction kidney.
  • the particularly long suction kidney according to the invention could be kept relatively flat and then still ensure a particularly good filling level of the pump. According to the embodiment of claim 5, however, their depth decreases steadily to the end, so that only relatively small changes in speed and direction of the oil flow occur in the region of the suction kidney.
  • a recess is provided on the front side of the pump opposite the suction grille, then this brings about a very substantial further increase in the delivery rate. Surprisingly, a considerable improvement already occurs when the recess is only connected to the suction kidney via the above-mentioned delivery spaces.
  • the suction kidney and the recess can also be connected to one another by a channel provided in the housing, which, however, should not touch the peripheral wall of the gear chamber in order not to weaken the bearing of the ring gear.
  • the configuration according to claim 7 is preferred.
  • the end of the filler piece opposite the direction of rotation of the pump is chamfered in such a way that the current is deflected more towards the branch of the suction kidney running radially inside the filler piece in order to compensate for the effect of the centrifugal force.
  • This configuration simultaneously leads to a shortening of the filling piece, which in turn leads to the fact that in the region of this shortening a cavity is formed which is connected to the suction kidney and extends transversely to the tooth flanks of the gears and which in turn further improves the filling of the delivery spaces.
  • the filler is also not tapered at its other end, but shortened slightly for reasons of strength.
  • a preferred embodiment of the invention is that the cover of the pump has a recess which preferably corresponds to the shape of the suction kidney.
  • This recess extends like the pressure kidney in two branches on both sides of the filler.
  • the cover is thus weakened precisely in the area in which it would have to bring about the reliable sealing between the pressure and suction side by means of a particularly saturated system.
  • the seal or the like used when flanging the pump on a motor has webs in that area which the lid has said recesses extending on both sides of the filler. As a result, the lid is supported in such a way that it maintains its full contact even in this critical area.
  • the pump shown has a housing 1 which - with the exception of the special design of the working chamber and the pressure and suction kidneys - does not differ from that housing which has already been described in the earlier application mentioned.
  • the pump has a housing 1, a working chamber cover 2 shown in detail in FIG. 5, a ring gear 4 (FIGS. 2 to 4) with its circumferential surface mounted on the circumferential wall of the working chamber 3, for example with sixteen teeth and a with its bore on a bearing collar 5 integrally formed with the housing 1 rotatably mounted pinion 6 (Fig. 2 to 4) which meshes with the ring gear 4 and z. B. has thirteen teeth.
  • the pump also has a safety valve, not shown in the drawings, the receptacle of which is shown at 7 and whose function will be discussed further below.
  • the housing 1 is flanged to the motor with its side facing the viewer in FIG. 1.
  • the oil is supplied from below through a suction channel, not shown, which is connected to a supply channel 9 in the interior of the housing 1.
  • the pump housing 1 also has a further flange surface 10 with which it is flanged to the oil pan.
  • the working chamber cover 2 sits on the surface 16 (FIG. 1) of the cast pump housing 1 which is set back somewhat more than the thickness of the working chamber cover 2 and thus forms the second end wall of the working chamber 3.
  • the two gearwheels run in the cylindrical working chamber 4 and 6 ⁇ m.
  • the drive takes place by means of the end of the crankshaft 60 of the internal combustion engine, which projects through the bore of the bearing collar 5 and carries the pinion 6, which drives the ring gear 4, by means of a drive ring 61.
  • the driver ring 61 has projections which engage in corresponding recesses in a collar 6a of the pinion.
  • the axis of rotation of the pinion 6 is offset eccentrically with respect to the axis of rotation of the ring gear 4.
  • 0 denotes the axis of the pinion 6 (not shown in FIG. 1)
  • 0 ′ denotes the axis of the ring gear 4.
  • This straight line 51 in FIG. 1 contains the point of the deepest tooth engagement on the underside of the housing and the point of the greatest distance between the teeth on the top.
  • the pump shown in the drawing is a filler pump, in which the two gears 4, 6 are far apart at the point of their greatest distance and enclose a crescent-shaped or crescent-shaped cavity between them, which is formed by an appropriately designed, over the entire depth of the working chamber 3rd extending solid filler 50 is filled.
  • the plane of symmetry 51 is at an angle of 10 ° in the sense of the clockwise rotation in FIG. 1 and opposite to the normal plane pointing vertically downward on the flange surface 10 in FIG. 1 through the axis of rotation 0 of the pinion 6 the direction of rotation of the pump indicated by arrow 25; this allows an advantageous guidance of the feed channel 9, which starts from the flange surface 10.
  • Fig. 1 can also be seen an outlet kidney 26 which is recessed in the end wall of the working chamber 3 belonging to the housing 1 and also has an extension 27 in the peripheral wall of the working chamber. From the extension 27, an outlet channel 28 extends to an annular groove 29 which rotates around part of the pump and connects to a further pressure oil channel of the pump housing at its right end in FIG. 6.
  • the groove 29 becomes a closed channel by flanging onto a suitable surface of the internal combustion engine.
  • the feed channel 9 has the cross section of an elongated hole which extends parallel to the plane of the drawing in FIG. 1, is offset somewhat below the working chamber 3 below the working chamber and opens tangentially into the suction grille 33. It is stepless and continuous according to the principles of FIG Fluid mechanics in the suction kidney 33 over.
  • the suction grille 33 covers approximately 180 ° of the working chamber 3 and thus not only extends to the plane of symmetry 51, but also extends by approximately 25 ° beyond it, that is to say also beyond the normal plane shown in FIG. 1.
  • the suction kidney 33 encompasses the filler 50 over more than half of its extent with a radially outer branch 33a and a radially inner branch 33b.
  • the filler 50 has a bevel 52 at its end opposite to the direction of rotation 25, which widens the inlet into the inner branch 33b of the suction grille 33 and ensures that the liquid flowing in approximately tangentially from the feed channel 9 is already in the area of the filler 50 is deflected and thus also exposed to the influence of centrifugal force, is skimmed off in such a way that the two branches 33a and 33b are supplied with liquid more uniformly.
  • the two branches 33a, b of the suction kidney 33 have a depth that decreases in the direction of rotation 25 to zero, as shown in FIG. 7 (section VII-VII in FIG. 1).
  • the ring channel 29 opens into a pressure relief valve (not shown) which overflows into an overflow chamber 54 which is arranged radially outside the working chamber 3 in the vicinity of the bevel 52.
  • the valve relieves the annular channel 29 to the overflow chamber 54.
  • This is connected to the suction kidney 33 and is also connected by an overflow 55, which can best be seen in FIGS. 4 and 6, to the recess 53 of the cover 2, which corresponds in shape to the suction kidney and is opposite it.
  • This working chamber cover 2 can be seen from FIG. 2 and has no special features apart from recesses for fastening screws.
  • Fig. 5 shows the inner surface.
  • the cover 2 has a series of cutouts, namely a first cutout 53, which corresponds approximately in shape and depth to the suction grille 33, and a second cutout 56.
  • the cutout 53 ends in two branches which, when the cover is mounted, lie above the two branches 33a, b and by one which has stopped Material web are separated from each other, which sits on the filler 50 and has exactly its contour.
  • the second recess 56 is arranged above the pressure kidney 26 and covers it and its extension 27.
  • the two cutouts 53 and 56 each form a space adjacent to the working chamber or the gear wheels 4, 6.
  • the space formed by the recess 56 communicates with the pressure kidney 26 via the extension 27, which extends radially outside the working chamber over its height, and ensures that the supplied pressure oil can escape on both sides of the gear wheels 4, 6 and then be collected flows through the outlet channel 28.
  • the cover 2 is cut out in the peripheral region of the recess 53 corresponding to the suction kidney 33. This cutout is delimited by a cutting edge which, starting from the circumference of the cover 2, runs approximately tangentially against the outer flank of the web supported on the filler 50, at a location which is approximately one third behind that end of the web, that lies above the bevel 52. From there, the recess branch 53a corresponding to the outer suction kidney branch 33a is delimited transversely to its extent by a cutting edge, and a third cutting edge then extends from here in a direction approximately perpendicular to the plane of symmetry 51 to the edge of the cover 2.
  • This cutout 55 can be seen in FIGS. 2 and 4 and produces the overflow between the recess 53 and the overflow chamber 54, into which the pressure generating valve of the pump, which lies between the channel 29 and the chamber 54, feeds.
  • the overflow could also be designed in the form of a depression in the peripheral wall of the working chamber, which connects the suction kidney 33 with the recess 53.
  • this is less advantageous because the bearing of the ring gear suffers.
  • the depth of the recess branches 53a, 53b in the direction of rotation is reduced to zero.
  • This gasket is a flat gasket insert, comparable to a cylinder head gasket of an engine, and like this it has the main purpose of sealing liquid-filled spaces from the outside. Accordingly, a section 57a is provided which surrounds the outlet channel 28 and seals off to the outside, and a section 57b which surrounds the overflow chamber 54 and seals off to the outside.
  • a third section 57c is provided, which, together with a part of section 57b, runs in an arc and sits exactly above the web of the cover 2 and thus above the filler 50, as can be clearly seen from FIG. 3 .
  • this sealing section 57c performs a supporting function, namely that the cover 2 has the very small wall thickness shown in FIG. 6 in the area of the inlet into the recess branch 53b, while the overflow still occurs in the area of the inlet into the recess branch 53a 55 extends. Only after the end of the two inlet branches 53a, 53b, viewed in the direction of rotation, does the cover regain its full strength and thus also bending strength.
  • the cover performs an essential sealing function between the suction and pressure sides of the pump. It is precisely in this area that weak points in the cover could ensure that it gives way and thus creates a loss of flow against the conveying direction. However, this is prevented by the sealing section 57c, which on the one hand rests firmly on the cover and on the other hand on the contact surface of the motor shown in FIGS. 3 and 4 and thus prevents that critical area of the cover 2 from yielding.
  • a pressure equalization is always established between the suction cardioid 33 and the opposite cover recess 53, since in this area the teeth of the two gear wheels 4, 6 diverge and spaces are thus formed between these teeth. Only in the area of the branches 33a, b or 53a, b could different pressure conditions arise due to the decreasing depth and the special flow conditions if the branches 33a, b had a different geometric shape than the branches 53a, b. For this reason, as can be seen particularly from FIG. 3, not only the contours in the circumferential direction, but also the cross sections of the mutually opposite branches are the same. Thus, the gears 4, 6 run load-free in the axial direction, because they are under full pressure equalization both in the area of the suction kidney and in the area of the pressure kidney. Friction losses are thus avoided; the life of the pump is extended.
  • suction kidney-side limitation of the pressure kidney in FIG. 1 runs approximately along a parallel to the tangent to the two suction kidney ends, so that the sealing distances from the two suction kidney ends to the beginning of the pressure kidney are approximately the same length.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)

Description

Die Erfindung betrifft eine Innenläuferzahnradölpumpe mit den Merkmalen des Oberbegriffs des Anspruchs 1.The invention relates to an internal rotor gear oil pump with the features of the preamble of claim 1.

Derartige Pumpen setzen sich in letzter Zeit immer mehr für die Ölversorgung von Kraftfahrzeugverbrennungsmotoren, insbesondere von derartigen Kolbenmotoren, durch. Sie haben den wesentlichen Vorteil, daß ein gesonderter Antrieb für die Ölpumpe entfällt, da die Verlängerung der Kurbelwelle, die, wie dies vorzugsweise und meist der Fall ist, vom freien Ende der Kurbelwelle gebildet ist, aber dem Grunde nach auch ein gesondertes Teil sein kann, unmittelbar das Ritzel antreiben kann. Das Ritzel kann dabei direkt auf der Kurbelwelle sitzen. Bevorzugt sitzt es jedoch an einem gesonderten im Gehäuse der Pumpe ausgebildeten Lagerkragen und wird von der diesen Kragen durchsetzenden Kurbelwelle über Mitnehmer angetrieben. Bei der bevorzugten Ausführungsform der Erfindung verläuft die Strömungsrichtung im Zuführkanal angenähert tangential zur mittleren Umfangsrichtung der Pumpenzahnräder im Saugnierenbereich. Genauer gesagt, soll die Projektion der Strömungsrichtung im Zuführkanal in dem Bereich, in dem dieser in den Saugnierenbereich übergeht, auf eine Normalebene der Drehachse der Pumpe eine Richtung haben, die mit der Bewegungsrichtung der Zähne des Ritzels und des Hohlrades in diesem Bereich etwa zusammenfällt.Such pumps have recently become increasingly popular for supplying oil to motor vehicle internal combustion engines, in particular piston engines of this type. They have the essential advantage that a separate drive for the oil pump is not necessary, since the extension of the crankshaft, which, as is preferred and usually the case, is formed by the free end of the crankshaft, but can in principle also be a separate part , can directly drive the pinion. The pinion can sit directly on the crankshaft. However, it is preferably seated on a separate bearing collar formed in the housing of the pump and is driven by the crankshaft passing through this collar via drivers. In the preferred embodiment of the invention, the flow direction in the feed channel is approximately tangential to the central circumferential direction of the pump gearwheels in the suction kidney region. More specifically, the projection of the direction of flow in the feed channel in the area in which it merges into the suction kidney area should have a direction on a normal plane of the axis of rotation of the pump which approximately coincides with the direction of movement of the teeth of the pinion and the ring gear in this area.

Der Kanal kann jedoch auch z. B. parallel zur Pumpenachse in die Saugniere münden. Das kann insbesondere bei Verwendung der Pumpe in einem automatischen Kraftfahrzeuggetriebe der Fall sein.However, the channel can also e.g. B. open parallel to the pump axis in the suction kidney. This can be the case in particular when the pump is used in an automatic motor vehicle transmission.

Bei den bekannten Ölpumpen nach dem Oberbegriff des Anspruchs 1 (siehe z. B. die US-A-3 855 987) erstreckt sich der Zuführkanal, der am Abschluß des Ölsaugrohrs den gleichen Kreisquerschnitt wie das Ölsaugrohr aufweist, mit sich verjüngendem Kreisquerschnitt zur Saugniere. Der Ölzuführkanal verläuft dabei zum Teil auf der Arbeitskammerseite der die Saugniere enthaltenden Stirnwand der Arbeitskammer und zum Teil auf der der Arbeitskammer abgewandten Seite dieser Stirnwand. Der Verlauf des Zuführkanals ist dabei derart, daß der Ölstrom nicht nur die saugnierenseitige Stirnfläche des Hohlrades umströmt, sondern auch einen Teil der Umfangsfläche des Hohlrades.In the known oil pumps according to the preamble of claim 1 (see, for example, US-A-3 855 987), the feed channel, which at the end of the oil suction pipe has the same circular cross section as the oil suction pipe, extends with a tapering circular cross section to the suction kidney. The oil supply channel runs partly on the working chamber side of the end wall of the working chamber containing the suction cups and partly on the side of this end wall facing away from the working chamber. The course of the feed channel is such that the oil flow not only flows around the end face of the ring gear on the suction side, but also part of the circumferential surface of the ring gear.

Die bekannten Ölpumpen haben sich bewährt. Bei ihnen tritt jedoch insofern eine gewisse Problematik auf, als sie beim Überschreiten einer bestimmten Drehzahl in ihrer Förderleistung (Fördermenge/Minute) abfallen.The well-known oil pumps have proven themselves. However, there is a certain problem with them in that their output (delivery rate / minute) drops when a certain speed is exceeded.

Die Pumpe nach einer älteren Anmeldung veröffentlicht am 24.05.84 als DE-A-32 43 067.1 beseitigt diesen dargelegten Nachteil. Insbesondere läßt sich die Förderleistung der Pumpe ohne Erhöhung von deren Abmessungen auch in höherem Drehzahlbereich, wo diese Leistung sonst stark abfällt, weiter, wenigstens stark angenähert proportional der Drehzahl, steigern ; man vermeidet die bei anderen Pumpen oft auftretende Schaumbildung auch bei höheren Drehzahlen. Nach der älteren Anmeldung tritt der Ölstrom etwa tangential zur Umlaufrichtung der Verzahnung in eine auf der der Arbeitskammer abgewandten Seite der einen Stirnwand der Arbeitskammer angeordnete in Umlaufrichtung verlaufende, ihren Querschnitt in Umlaufrichtung verringernde Saugniere ein, die erheblich vor der die Zahnradachsen enthaltenden Ebene endet.The pump according to an older application published on May 24, 1984 as DE-A-32 43 067.1 eliminates this disadvantage. In particular, the delivery capacity of the pump can be increased further, at least to a great extent proportional to the speed, without increasing its dimensions, even in the higher speed range, where this power otherwise drops sharply; one avoids the foaming that often occurs with other pumps even at higher speeds. According to the older application, the oil flow occurs approximately tangentially to the direction of rotation of the toothing in a suction kidney arranged on the side of the end wall of the working chamber facing away from the working chamber and running in the direction of rotation, reducing its cross section in the direction of rotation, which ends considerably in front of the plane containing the gearwheel axes.

Die Erfindung löst die Aufgabe, sowohl bei der bekannten Pumpe als auch - und das insbesondere - bei der Pumpe nach der obenerwähnten älteren Anmeldung die Leistung, also die Fördermenge in der Zeiteinheit, durch günstige Ausbildung des Ölzuflusses zu verbessern.The invention solves the problem, both in the known pump and - and in particular - in the pump according to the above-mentioned earlier application to improve the performance, that is to say the delivery rate in the unit of time, by means of a favorable design of the oil inflow.

Die Erfindung erreicht das durch die Hinzufügung der Merkmale des Anspruchs 1. Hierbei ist die durch ein sichelförmiges, in der Arbeitskammer angeordnetes Füllstück in bekannter Weise abgedichtete Pumpe mit einer Saugniere versehen, die nicht, wie bisher, schon weit vor der Symmetrieebene der Pumpe endet, sondern sich im Gegensatz hierzu bis nahezu an oder vorzugsweise über die Symmetrieebene (die die beiden Zahnradachsen enthaltende Ebene) der Pumpe hinaus erstreckt. Hierdurch tritt überraschenderweise eine deutliche Verbesserung der Förderleistung auf.The invention achieves this by adding the features of claim 1. Here, the pump, which is sealed in a known manner by a sickle-shaped filler arranged in the working chamber, is provided with a suction kidney which, as before, does not end well before the symmetry level of the pump, but, in contrast, extends almost to or preferably beyond the plane of symmetry (the plane containing the two gearwheel axes) of the pump. This surprisingly results in a significant improvement in the delivery rate.

Hierbei ist es besonders von Vorteil, wenn gemäß Anspruch 2 die Saugniere sich um 20 bis 30°, bezogen auf die Drehachse des Ritzels, vorzugsweise 25°, über die Symmetrieebene hinaus erstreckt. Da das Füllstück mit seinen zylindrischen Oberflächen die von den Zahnzwischenräumen des Hohlrades bzw. Ritzels gebildeten, sich ständig von der Saugseite zur Druckseite bewegenden Förderräume begrenzt, sind durch die Erfindung diese Förderräume über eine erhebliche Länge ihrer Bewegungsstrecke hinweg zur Saugniere offen, so daß ein längerer Zeitraum zur Füllung der genannten Förderräume zur Verfügung steht, als dies bisher der Fall war. Deshalb reicht auch bei einer hohen Drehzahl die Zeit, während welcher die genannten Förderräume mit Flüssigkeit gefüllt werden, aus, um sicherzustellen, daß diese Förderräume sich stets gut füllen. Die Erfindung bewirkt, daß bis zu einer ungewöhnlich hohen Drehzahl die an sich schon hohe Förderleistung der Pumpe etwa proportional zur Drehzahl ist.It is particularly advantageous here if the suction kidney extends beyond the plane of symmetry by 20 to 30 °, based on the axis of rotation of the pinion, preferably 25 °. Since the filler with its cylindrical surfaces limits the delivery spaces formed by the interdental spaces of the ring gear or pinion, which constantly move from the suction side to the pressure side, these delivery spaces are open to the suction kidney over a considerable length of their movement path, so that a longer one The period for filling the mentioned funding areas is available than was previously the case. Therefore, even at a high speed, the time during which the said delivery spaces are filled with liquid is sufficient to ensure that these delivery spaces always fill well. The invention has the effect that, up to an unusually high speed, the already high delivery rate of the pump is approximately proportional to the speed.

Damit bei hohen Drehzahlen und damit großer Fliehkraft auch die von den Zähnen des Ritzels zusammen mit dem Füllstück gebildeten Förderräume zur Förderung der Pumpe voll beitragen, erstreckt sich vorzugsweise gemäß Anspruch 3 die Saugniere nicht nur radial außerhalb des Füllstücks bis über die Symmetrieebene hinaus, sondern ist an ihrem in Drehrichtung weisenden Ende in zwei Zweige aufgeteilt, die beiderseits des Füllstücks verlaufen.So that at high speeds and thus high centrifugal force, the delivery spaces formed by the teeth of the pinion together with the filler also contribute to the pump, preferably according to claim 3, the suction kidney not only extends radially outside the filler beyond the plane of symmetry, but is at its end pointing in the direction of rotation divided into two branches that run on both sides of the filler.

Gemäß Anspruch 4 wird die Förderleistung dann besonders hoch, wenn der Beginn der Druckniere von den beiden Enden der Saugnierenzweige in Umfangsrichtung einen Abstand von nur etwa zwei Zahnradteilungen hat. Dies bedeutet, daß der Abstand zwischen den Enden des inneren und des äußeren Saugnierenzweiges und der etwa im Bereich des Endes des Füllstücks beginnenden Druckniere in Umfangsrichtung auf halber Zahnhöhe des Ritzels bzw. des Hohlrades gemessen gleich ist. Wenn nun die Enden der Saugnierenzweige etwa auf einem Radialstrahl des Ritzels oder Hohlrades liegen, dann liegen demzufolge die Anfänge der Druckniere nicht auf einem Radialstrahl.According to claim 4, the delivery rate is particularly high when the start of the pressure kidney is at a distance of only about two gear wheel divisions from the two ends of the suction kidney branches in the circumferential direction. This means that the distance between the ends of the inner and outer suction kidney branch and the pressure kidney beginning approximately in the region of the end of the filler piece is measured in the circumferential direction at half the tooth height of the pinion or the ring gear. If the ends of the suction kidney branches now lie, for example, on a radial jet of the pinion or ring gear, then the beginnings of the pressure kidneys do not lie on a radial jet.

Der Querschnitt des Zuführkanals sollte sich zum Vermeiden von Verlusten bis zum Übergang in die Saugniere nur wenig verringern. Eine geringe Verringerung wird allerdings als zweckmäßig angesehen, um einen guten Übergang des Kanalquerschnittes in die Saugniere zu gewährleisten.The cross section of the feed channel should only be slightly reduced to avoid losses up to the transition into the suction kidney. However, a small reduction is considered to be expedient in order to ensure a good transition of the channel cross section into the suction kidney.

Die erfindungsgemäße besonders lange Saugniere könnte verhältnismäßig flach gehalten werden und dann immer noch einen besonders guten Füllungsgrad der Pumpe sicherstellen. Gemäß der Ausgestaltung des Anspruchs 5 aber nimmt ihre Tiefe bis zum Ende hin stetig ab, so daß nur relativ geringe Geschwindigkeits- und Richtungsänderungen der Ölströmung im Bereich der Saugniere auftreten.The particularly long suction kidney according to the invention could be kept relatively flat and then still ensure a particularly good filling level of the pump. According to the embodiment of claim 5, however, their depth decreases steadily to the end, so that only relatively small changes in speed and direction of the oil flow occur in the region of the suction kidney.

Wenn man gemäß Anspruch 6 auf der der Saugniere gegenüberliegenden Stirnseite der Pumpe eine Aussparung vorsieht, dann erbringt dies eine ganz wesentliche weitere Erhöhung der Förderleistung. Überraschenderweise tritt eine beachtliche Verbesserung bereits dann ein, wenn die Aussparung mit der Saugniere lediglich über die genannten Förderräume verbunden ist. Die Saugniere und die Aussparung können auch durch einen im Gehäuse vorgesehenen Kanal miteinander verunden sein, der allerdings die Umfangswand der Zahnradkammer nicht berühren sollte, um die Lagerung des Hohlrades nicht zu schwächen. Bevorzugt wird die Ausgestaltung gemäß Anspruch 7.If, according to claim 6, a recess is provided on the front side of the pump opposite the suction grille, then this brings about a very substantial further increase in the delivery rate. Surprisingly, a considerable improvement already occurs when the recess is only connected to the suction kidney via the above-mentioned delivery spaces. The suction kidney and the recess can also be connected to one another by a channel provided in the housing, which, however, should not touch the peripheral wall of the gear chamber in order not to weaken the bearing of the ring gear. The configuration according to claim 7 is preferred.

Gemäß Anspruch 8 ist es von Vorteil, daß das der Drehrichtung der Pumpe entgegenweisende Ende des Füllstücks so abgeschrägt ist, daß der Strom mehr zum radial innerhalb des Füllstücks verlaufenden Zweig der Saugniere hin abgelenkt wird, um die Wirkung der Fliehkraft auszugleichen. Diese Ausgestaltung führt gleichzeitig zu einer Verkürzung des Füllstücks, die wiederum dazu führt, daß im Bereich dieser Verkürzung ein mit der Saugniere verbundener, sich quer zu den Zahnflanken der Zahnräder erstrekkender Hohlraum gebildet wird, welcher seinerseits die Füllung der Förderräume noch weiter verbessert.According to claim 8, it is advantageous that the end of the filler piece opposite the direction of rotation of the pump is chamfered in such a way that the current is deflected more towards the branch of the suction kidney running radially inside the filler piece in order to compensate for the effect of the centrifugal force. This configuration simultaneously leads to a shortening of the filling piece, which in turn leads to the fact that in the region of this shortening a cavity is formed which is connected to the suction kidney and extends transversely to the tooth flanks of the gears and which in turn further improves the filling of the delivery spaces.

Das Füllstück ist auch an seinem anderen Ende nicht spitzauslaufend ausgeführt, sondern aus Festigkeitsgründen geringfügiger verkürzt.The filler is also not tapered at its other end, but shortened slightly for reasons of strength.

Wie bereits oben erwähnt, liegt eine bevorzugte Ausgestaltung der Erfindung darin, daß der Deckel der Pumpe eine bevorzugt in der Form der Saugniere entsprechende Aussparung aufweist. Diese Aussparung erstreckt sich wie die Druckniere in zwei Zweigen beiderseits des Füllstückes. Der Deckel ist somit gerade in jenem Bereich geschwächt, in welchem er durch besonders satte Anlage die zuverlässige Abdichtung zwischen Druck- und Saugseite herbeiführen müßte. Um nun ein Auswölben des Deckels in diesem Bereich und somit das Auftreten von Verlusten und hiermit wiederum eine Verringerung der Fördermenge zu vermeiden, wird vorgeschlagen, daß die beim Anflanschen der Pumpe an einem Motor od. dgl. verwendete Dichtung in jenem Bereich Stege aufweist, an welchem der Deckel die genannten, sich beiderseits des Füllstücks erstreckenden Aussparungen aufweist. Hierdurch wird der Deckel derart abgestützt, daß er auch in diesem kritischen Bereich seine satte Anlage beibehält.As already mentioned above, a preferred embodiment of the invention is that the cover of the pump has a recess which preferably corresponds to the shape of the suction kidney. This recess extends like the pressure kidney in two branches on both sides of the filler. The cover is thus weakened precisely in the area in which it would have to bring about the reliable sealing between the pressure and suction side by means of a particularly saturated system. In order to prevent the lid from bulging in this area and thus the occurrence of losses and thus a reduction in the delivery rate, it is proposed that the seal or the like used when flanging the pump on a motor has webs in that area which the lid has said recesses extending on both sides of the filler. As a result, the lid is supported in such a way that it maintains its full contact even in this critical area.

Der Gegenstand der Erfindung wird anhand eines bevorzugten Ausführungsbeispiels noch näher erläutert, das in der schematischen, beigefügten Zeichnung dargestellt ist. In dieser ist :

  • Fig. 1 die Ansicht auf eine erfindungsgemäße Motorölpumpe von der an den Motor anzuflanschenden Seite her mit abgenommenem Arbeitskammerdeckel ;
  • Fig. 2 eine Ansicht der Pumpe wie in Fig. 1, jedoch mit aufgesetztem Arbeitskammerdeckel und aufgelegter Dichtung ;
  • Fig. 3 ein Schnitt längs Linie A-B in Fig. 2 ;
  • Fig. 4 ein Schnitt längs Linie B-C in Fig. 2 ;
  • Fig. 5 die Draufsicht auf die der Arbeitskammer zugewandte Oberfläche des abgenommenen Arbeitskammerdeckels ;
  • Fig. 6 ein Schnitt längs Linie VI-VI in Fig. 5 und
  • Fig. 7 ein Schnitt längs Linie VII-VII in Fig. 1.
The object of the invention is explained in more detail with reference to a preferred embodiment which is shown in the schematic, attached drawing. In this is:
  • Figure 1 is a view of an engine oil pump according to the invention from the side to be flanged to the engine with the working chamber cover removed.
  • FIG. 2 is a view of the pump as in FIG. 1, but with the working chamber cover and seal in place;
  • Fig. 3 is a section along line AB in Fig. 2;
  • FIG. 4 shows a section along line BC in FIG. 2;
  • 5 shows a top view of the surface of the removed working chamber cover facing the working chamber;
  • Fig. 6 is a section along line VI-VI in Fig. 5 and
  • 7 is a section along line VII-VII in Fig. 1st

Die gezeigte Pumpe hat ein Gehäuse 1, das sich - die spezielle Ausbildung der Arbeitskammer und der Druck- sowie Saugniere ausgenommen - nicht von jenem Gehäuse unterscheidet, das bereits in der erwähnten älteren Anmeldung beschrieben ist.The pump shown has a housing 1 which - with the exception of the special design of the working chamber and the pressure and suction kidneys - does not differ from that housing which has already been described in the earlier application mentioned.

Die Pumpe besitzt, wie aus den Zeichnungen ersichtlich, ein Gehäuse 1, einen in Fig. 5 detailliert gezeigten Arbeitskammerdeckel 2, ein mit seiner Umfangsfläche an der Umfangswand der Arbeitskammer 3 gelagertes Hohlrad 4 (Fig. 2 bis 4) mit beispielsweise sechzehn Zähnen und ein mit seiner Bohrung auf einem einstückig mit dem Gehäuse 1 ausgebildeten Lagerkragen 5 drehbar gelagertes Ritzel 6 (Fig. 2 bis 4), das mit dem Hohlrad 4 kämmt und z. B. dreizehn Zähne hat. Ferner besitzt die Pumpe noch ein in den Zeichnungen nicht dargestelltes Sicherheitsventil, dessen Aufnahme bei 7 gezeigt ist und dessen Funktion weiter unten noch erörtert wird.As can be seen from the drawings, the pump has a housing 1, a working chamber cover 2 shown in detail in FIG. 5, a ring gear 4 (FIGS. 2 to 4) with its circumferential surface mounted on the circumferential wall of the working chamber 3, for example with sixteen teeth and a with its bore on a bearing collar 5 integrally formed with the housing 1 rotatably mounted pinion 6 (Fig. 2 to 4) which meshes with the ring gear 4 and z. B. has thirteen teeth. Furthermore, the pump also has a safety valve, not shown in the drawings, the receptacle of which is shown at 7 and whose function will be discussed further below.

Das Gehäuse 1 wird mit seiner in Fig. 1 dem Beschauer zugekehrten Seite an den Motor angeflanscht. Die Ölzufuhr erfolgt durch einen nicht gezeigten Ansaugkanal von unten her, der an einen Zuführkanal 9 im Inneren des Gehäuses 1 angeschlossen ist. Nach unten besitzt das Pumpengehäuse 1 ebenfalls eine weitere Flanschfläche 10, mit der es an die Ölwanne angeflanscht ist.The housing 1 is flanged to the motor with its side facing the viewer in FIG. 1. The oil is supplied from below through a suction channel, not shown, which is connected to a supply channel 9 in the interior of the housing 1. At the bottom, the pump housing 1 also has a further flange surface 10 with which it is flanged to the oil pan.

Der Arbeitskammerdeckel 2 sitzt auf der gegenüber der Flanschfläche 1 um etwas mehr als die Dicke des Arbeitskammerdeckels 2 zurückgesetzten Fläche 16 (Fig. 1) des gegossenen Pumpengehäuses 1 auf und bildet somit die zweite Stirnwand der Arbeitskammer 3. In der zylinderförmigen Arbeitskammer laufen die beiden Zahnräder 4 und 6 um. Der Antrieb erfolgt mittels des Endes der Kurbelwelle 60 des Verbrennungsmotors, welches durch die Bohrung des Lagerkragens 5 ragt und mittels eines Mitnehmerrings 61 das Ritzel 6 mitnimmt, welches das Hohlrad 4 antreibt. Zu diesem Zweck hat der Mitnehmerring 61 Vorsprünge, welche in korrespondierende Aussparungen eines Kragens 6a des Ritzels eingreifen. Gemäß dem Prinzip der Innenzahnradpumpe ist die Drehachse des Ritzels 6 gegenüber der Drehachse des Hohlrades 4 exzentrisch versetzt. Hierbei bezeichnet in Fig. 1 0 die Achse des (in Fig. 1 nicht gezeigten) Ritzels 6, während 0' die Achse des Hohlrades 4 bezeichnet.The working chamber cover 2 sits on the surface 16 (FIG. 1) of the cast pump housing 1 which is set back somewhat more than the thickness of the working chamber cover 2 and thus forms the second end wall of the working chamber 3. The two gearwheels run in the cylindrical working chamber 4 and 6 µm. The drive takes place by means of the end of the crankshaft 60 of the internal combustion engine, which projects through the bore of the bearing collar 5 and carries the pinion 6, which drives the ring gear 4, by means of a drive ring 61. For this purpose, the driver ring 61 has projections which engage in corresponding recesses in a collar 6a of the pinion. According to the principle of the internal gear pump, the axis of rotation of the pinion 6 is offset eccentrically with respect to the axis of rotation of the ring gear 4. In this case, in FIG. 1 0 denotes the axis of the pinion 6 (not shown in FIG. 1), while 0 ′ denotes the axis of the ring gear 4.

Die beiden Achsen 0, 0' verlaufen parallel zueinander und definieren eine Symmetrieebene, deren Spur die Gerade 51 in Fig.1 bildet.The two axes 0, 0 'run parallel to one another and define a plane of symmetry, the track of which forms the straight line 51 in FIG.

Diese Gerade 51 enthält in Fig. 1 an der Unterseite des Gehäuses den Punkt des tiefsten Zahneingriffes und an der Oberseite den Punkt der größten Entfernung der Zähne voneinander.This straight line 51 in FIG. 1 contains the point of the deepest tooth engagement on the underside of the housing and the point of the greatest distance between the teeth on the top.

Die in der Zeichnung gezeigte Pumpe ist eine Füllstückpumpe, bei welcher die beiden Zahnräder 4, 6 an der Stelle ihrer größten Entfernung weit auseinanderliegen und zwischeneinander einen sichel- oder halbmondförmigen Hohlraum einschließen, der durch ein entsprechend ausgebildetes, sich über die gesamte Tiefe der Arbeitskammer 3 erstreckendes, massives Füllstück 50 ausgefüllt ist.The pump shown in the drawing is a filler pump, in which the two gears 4, 6 are far apart at the point of their greatest distance and enclose a crescent-shaped or crescent-shaped cavity between them, which is formed by an appropriately designed, over the entire depth of the working chamber 3rd extending solid filler 50 is filled.

Wie aus Fig. 1 ferner erkennbar, ist die Symmetrieebene 51 gegenüber der in Fig. 1 senkrecht nach unten auf die Flanschfläche 10 weisenden Normalebene durch die Drehachse 0 des Ritzels 6 um einen Winkel von 10° im Sinne der Uhrzeigerdrehung in Fig. 1 und entgegen der durch den Pfeil 25 bezeichneten Drehrichtung der Pumpe versetzt ; das erlaubt eine vorteilhafte Führung des Zuführkanals 9, der ja von der Flanschfläche 10 ausgeht.As can also be seen from FIG. 1, the plane of symmetry 51 is at an angle of 10 ° in the sense of the clockwise rotation in FIG. 1 and opposite to the normal plane pointing vertically downward on the flange surface 10 in FIG. 1 through the axis of rotation 0 of the pinion 6 the direction of rotation of the pump indicated by arrow 25; this allows an advantageous guidance of the feed channel 9, which starts from the flange surface 10.

In Fig. 1 erkennt man ferner eine Auslaßniere 26, die in der dem Gehäuse 1 angehörenden Stirnwand der Arbeitskammer 3 ausgespart ist und ferner über eine Erweiterung 27 in der Umfangswand der Arbeitskammer verfügt. Von der Erweiterung 27 erstreckt sich ein Auslaßkanal 28 zu einer Ringnut 29, die einen Teil der Pumpe umläuft und an ihrem in Fig. 6 rechten Ende an einen weiterführenden Druckölkanal des Pumpengehäuses anschließt. Die Nut 29 wird durch das Anflanschen an eine geeignete Fläche des Verbrennungsmotors zu einem geschlossenen Kanal.In Fig. 1 can also be seen an outlet kidney 26 which is recessed in the end wall of the working chamber 3 belonging to the housing 1 and also has an extension 27 in the peripheral wall of the working chamber. From the extension 27, an outlet channel 28 extends to an annular groove 29 which rotates around part of the pump and connects to a further pressure oil channel of the pump housing at its right end in FIG. 6. The groove 29 becomes a closed channel by flanging onto a suitable surface of the internal combustion engine.

Der Zuführkanal 9 weist den Querschnitt eines Langloches auf, welches sich parallel zur Zeichenebene der Fig. 1 erstreckt, ist gegenüber der Arbeitskammer 3 etwas nach unten unter die Arbeitskammer versetzt und mündet tangential in die Saugniere 33. Er geht stufenlos und stetig nach den Grundsätzen der Strömungsmechanik in die Saugniere 33 über.The feed channel 9 has the cross section of an elongated hole which extends parallel to the plane of the drawing in FIG. 1, is offset somewhat below the working chamber 3 below the working chamber and opens tangentially into the suction grille 33. It is stepless and continuous according to the principles of FIG Fluid mechanics in the suction kidney 33 over.

Die Ansaugniere 33 überdeckt etwa 180° der Arbeitskammer 3 und reicht somit nicht nur bis an die Symmetrieebene 51 heran, sondern erstreckt sich noch um etwa 25° über diese hinaus, also auch noch über die in Fig. 1 eingezeichnete Normalebene hinaus. Hierbei umgreift die Saugniere 33 mit einem radial äußeren Zweig 33a und einem radial innenliegenden Zweig 33b das Füllstück 50 über mehr als die Hälfte seiner Erstreckung.The suction grille 33 covers approximately 180 ° of the working chamber 3 and thus not only extends to the plane of symmetry 51, but also extends by approximately 25 ° beyond it, that is to say also beyond the normal plane shown in FIG. 1. In this case, the suction kidney 33 encompasses the filler 50 over more than half of its extent with a radially outer branch 33a and a radially inner branch 33b.

Das Füllstück 50 weist an seinem der Drehrichtung 25 entgegengewandten Ende eine Abschrägung 52 auf, die den Einlauf in den Innenzweig 33b der Saugniere 33 trichterartig erweitert und dafür sorgt, daß die aus dem Zuführkanal 9 etwa tangential einströmende Flüssigkeit, die im Bereich des Füllstücks 50 bereits umgelenkt wird und somit auch dem Einfluß der Fliehkraft ausgesetzt ist, derart abgeschöpft wird, daß die beiden Zweige 33a und 33b gleichmäßiger mit Flüssigkeit versorgt werden.The filler 50 has a bevel 52 at its end opposite to the direction of rotation 25, which widens the inlet into the inner branch 33b of the suction grille 33 and ensures that the liquid flowing in approximately tangentially from the feed channel 9 is already in the area of the filler 50 is deflected and thus also exposed to the influence of centrifugal force, is skimmed off in such a way that the two branches 33a and 33b are supplied with liquid more uniformly.

Die beiden Zweige 33a, b der Saugniere 33 weisen eine in Drehrichtung 25 bis auf Null abnehmende Tiefe auf, wie Fig. 7 zeigt (Schnitt VII-VII in Fig. 1).The two branches 33a, b of the suction kidney 33 have a depth that decreases in the direction of rotation 25 to zero, as shown in FIG. 7 (section VII-VII in FIG. 1).

Es wird allerdings darauf hingewiesen, daß die Darstellung der Fig. 7 nicht maßstäblich ist, sondern in Richtung der Erstreckung des Zweiges 33a stark verkürzt ist.It is pointed out, however, that the illustration in FIG. 7 is not to scale, but is greatly shortened in the direction of the extension of branch 33a.

Wie bereits oben erwähnt, mündet der Ringkanal 29 in ein (nicht gezeigtes) Überdruckventil, welches in eine Überlaufkammer 54 hinein überläuft, die radial außerhalb der Arbeitskammer 3 in Nähe der Abschrägung 52 angeordnet ist.As already mentioned above, the ring channel 29 opens into a pressure relief valve (not shown) which overflows into an overflow chamber 54 which is arranged radially outside the working chamber 3 in the vicinity of the bevel 52.

Wenn die Pumpe einen Druck innerhalb zulässiger Grenzen liefert, dann strömt alles durch den Ringkanal 29 geförderte Öl durch eine nicht gezeigte Ablaufleitung.If the pump delivers a pressure within permissible limits, then all of the oil conveyed through the ring channel 29 flows through a drain line, not shown.

Wird jedoch der zulässige Förderdruck überschritten, dann wird durch das Ventil der Ringkanal 29 zur Überlaufkammer 54 hin entlastet. Diese steht mit der Saugniere 33 in Verbindung und ist ferner durch einen Überlauf 55, der am besten aus Fig. 4 und 6 ersichtlich ist, mit der Aussparung 53 des Deckels 2 verbunden, die in der Form der Saugniere entspricht und dieser gegenüberliegt.However, if the permissible delivery pressure is exceeded, the valve relieves the annular channel 29 to the overflow chamber 54. This is connected to the suction kidney 33 and is also connected by an overflow 55, which can best be seen in FIGS. 4 and 6, to the recess 53 of the cover 2, which corresponds in shape to the suction kidney and is opposite it.

Um den Überlauf 55 besser beschreiben zu können, wird zunächst auf den Arbeitskammerdeckel 2 näher eingegangen.In order to be able to better describe the overflow 55, the working chamber cover 2 is first discussed in more detail.

Die Außenseite dieses Arbeitskammerdeckels 2 ist aus Fig. 2 ersichtlich und weist außer Vertiefungen für Befestigungsschrauben keinerlei Besonderheiten auf.The outside of this working chamber cover 2 can be seen from FIG. 2 and has no special features apart from recesses for fastening screws.

Fig. 5 zeigt die Innenoberfläche. Wie aus Fig. 5 ersichtlich, weist der Deckel 2 eine Reihe von Aussparungen auf, und zwar eine erste, nach Form und Tiefe etwa mit der Saugniere 33 übereinstimmende Aussparung 53, sowie eine zweite Aussparung 56.Fig. 5 shows the inner surface. As can be seen from FIG. 5, the cover 2 has a series of cutouts, namely a first cutout 53, which corresponds approximately in shape and depth to the suction grille 33, and a second cutout 56.

Die Aussparung 53 endet in zwei Zweigen, die bei montiertem Deckel über den beiden Zweigen 33a, b liegen und durch einen stehengebliebenen Materialsteg voneinander getrennt sind, der auf dem Füllstück 50 aufsitzt und genau dessen Kontur aufweist. Die zweite Aussparung 56 ist über der Druckniere 26 angeordnet und überdeckt diese sowie deren Erweiterung 27.The cutout 53 ends in two branches which, when the cover is mounted, lie above the two branches 33a, b and by one which has stopped Material web are separated from each other, which sits on the filler 50 and has exactly its contour. The second recess 56 is arranged above the pressure kidney 26 and covers it and its extension 27.

Bei montiertem Deckel 2 bilden die beiden Aussparungen 53 und 56 jeweils einen an die Arbeitskammer bzw. die Zahnräder 4, 6 angrenzenden Raum.When the cover 2 is installed, the two cutouts 53 and 56 each form a space adjacent to the working chamber or the gear wheels 4, 6.

Der von der Vertiefung 56 gebildete Raum steht überdie Erweiterung 27, die sich radial außerhalb der Arbeitskammer über deren Höhe erstreckt, mit der Druckniere 26 in Verbindung und sorgt dafür, daß das angeförderte Drucköl auf beiden Seiten der Zahnräder 4, 6 austreten kann und dann gesammelt durch den Auslaßkanal 28 strömt.The space formed by the recess 56 communicates with the pressure kidney 26 via the extension 27, which extends radially outside the working chamber over its height, and ensures that the supplied pressure oil can escape on both sides of the gear wheels 4, 6 and then be collected flows through the outlet channel 28.

Im Umfangsbereich der der Saugniere 33 entsprechenden Aussparung 53 ist der Deckel 2 ausgeschnitten. Dieser Ausschnitt wird von einer Schnittkante begrenzt, die, vom Umfang des Deckels 2 ausgehend, etwa tangential gegen die außenliegende Flanke des sich auf dem Füllstück 50 abstützenden Steges anläuft, und zwar an einer Stelle, die etwa ein Drittel hinter jenem Ende des Steges liegt, das über der Abschrägung 52 liegt. Von dort aus wird der dem äußeren Saugnierenzweig 33a entsprechende Vertiefungszweig 53a quer zu seiner Erstreckung durch eine Schnittkante begrenzt, und eine dritte Schnittkante erstreckt sich dann von hier aus in einer Richtung etwa senkrecht zur Symmetrieebene 51 bis zum Rand des Deckels 2.The cover 2 is cut out in the peripheral region of the recess 53 corresponding to the suction kidney 33. This cutout is delimited by a cutting edge which, starting from the circumference of the cover 2, runs approximately tangentially against the outer flank of the web supported on the filler 50, at a location which is approximately one third behind that end of the web, that lies above the bevel 52. From there, the recess branch 53a corresponding to the outer suction kidney branch 33a is delimited transversely to its extent by a cutting edge, and a third cutting edge then extends from here in a direction approximately perpendicular to the plane of symmetry 51 to the edge of the cover 2.

Dieser Ausschnitt 55 ist in Fig. 2 und Fig. 4 erkennbar und stellt den Überlauf zwischen der Aussparung 53 und der Überlaufkammer 54 her, in welche das Druckbezeugungsventil der Pumpe, das zwischen dem Kanal 29 und der Kammer 54 liegt, einspeist.This cutout 55 can be seen in FIGS. 2 and 4 and produces the overflow between the recess 53 and the overflow chamber 54, into which the pressure generating valve of the pump, which lies between the channel 29 and the chamber 54, feeds.

Auf diese Weise kann überschüssiges Drucköl aus der Überlaufkammer 54 durch den Überlauf 55 in die Aussparung 53 des Deckels 2 eintreten und gelangt von dort unmittelbar bzw. über die Aussparungszweige 53a und 53b wieder in den Förderbereich der Zahnräder 4, 6.In this way, excess pressure oil from the overflow chamber 54 can enter the recess 53 of the cover 2 through the overflow 55 and from there directly or via the recess branches 53a and 53b again into the delivery area of the gear wheels 4, 6.

Der Überlauf könnte auch in Form einer Vertiefung der Umfangswand der Arbeitskammer ausgebildet sein, welche die Saugniere 33 mit der Aussparung 53 verbindet. Das ist jedoch weniger vorteilhaft, da die Lagerung des Hohlrades leidet. Wie aus Fig. 6 erkennbar ist, verringert sich die Tiefe der Aussparungszweige 53a, 53b in Drehrichtung bis auf Null.The overflow could also be designed in the form of a depression in the peripheral wall of the working chamber, which connects the suction kidney 33 with the recess 53. However, this is less advantageous because the bearing of the ring gear suffers. As can be seen from FIG. 6, the depth of the recess branches 53a, 53b in the direction of rotation is reduced to zero.

Aus Fig. 2 und 3 sind Ausbildung und Anordnung der Dichtung 57 ersichtlich. Diese Dichtung ist eine ebene Dichtungseinlage, etwa vergleichbar einer Zylinderkopfdichtung eines Motors, und hat wie diese den Hauptzweck, flüssigkeitsgefüllte Räume nach außen abzudichten. Demzufolge ist ein Abschnitt 57a vorgesehen, der den Auslaßkanal 28 umgibt und nach außen abdichtet, sowie ein Abschnitt 57b, der die Überlaufkammer 54 umgibt und nach außen abdichtet.2 and 3, the design and arrangement of the seal 57 can be seen. This gasket is a flat gasket insert, comparable to a cylinder head gasket of an engine, and like this it has the main purpose of sealing liquid-filled spaces from the outside. Accordingly, a section 57a is provided which surrounds the outlet channel 28 and seals off to the outside, and a section 57b which surrounds the overflow chamber 54 and seals off to the outside.

Im Gegensatz zu einer herkömmlichen Dichtung dieser Art ist aber ein dritter Abschnitt 57c vorgesehen, der zusammen mit einem Teil des Abschnitts 57b bogenförmig verläuft und genau über dem Steg des Deckels 2 und somit über dem Füllstück 50 sitzt, wie deutlich aus Fig. 3 ersichtlich ist. Dieser Dichtungsabschnitt 57c übt neben seiner Dichtungsfunktion eine Stützfunktion aus, der Deckel 2 weist nämlich im Bereich des Einlaufs in den Aussparungszweig 53b die aus Fig. 6 ersichtliche, sehr geringe Wandstärke auf, während sich in dem Bereich des Einlaufs in den Aussparungszweig 53a noch der Überlauf 55 erstreckt. Erst nach dem Ende der beiden Einlaufzweige 53a, 53b, in Drehrichtung gesehen, gewinnt der Deckel wieder seine volle Stärke und somit auch Biegefestigkeit.In contrast to a conventional seal of this type, however, a third section 57c is provided, which, together with a part of section 57b, runs in an arc and sits exactly above the web of the cover 2 and thus above the filler 50, as can be clearly seen from FIG. 3 . In addition to its sealing function, this sealing section 57c performs a supporting function, namely that the cover 2 has the very small wall thickness shown in FIG. 6 in the area of the inlet into the recess branch 53b, while the overflow still occurs in the area of the inlet into the recess branch 53a 55 extends. Only after the end of the two inlet branches 53a, 53b, viewed in the direction of rotation, does the cover regain its full strength and thus also bending strength.

Der Deckel übt nun aber mit seiner der Arbeitskammer 3 zugewandten, in Fig. 5 dem Betrachter zugewandten Fläche eine wesentliche Abdichtfunktion zwischen Saug- und Druckseite der Pumpe aus. Genau in diesem Bereich könnten nun Schwachstellen des Deckels dafür sorgen, daß dieser nachgibt und somit eine Verlustströmung entgegen der Förderrichtung herstellt. Dies wird aber durch den Dichtungsabschnitt 57c verhindert, der dort einerseits auf dem Deckel und andererseits auf der aus Fig. 3 und 4 ersichtlichen Anlagefläche des Motors fest anliegt und somit ein Nachgeben jenes kritischen Bereiches des Deckels 2 verhindert.However, the cover, with its surface facing the working chamber 3 and facing the viewer in FIG. 5, performs an essential sealing function between the suction and pressure sides of the pump. It is precisely in this area that weak points in the cover could ensure that it gives way and thus creates a loss of flow against the conveying direction. However, this is prevented by the sealing section 57c, which on the one hand rests firmly on the cover and on the other hand on the contact surface of the motor shown in FIGS. 3 and 4 and thus prevents that critical area of the cover 2 from yielding.

Zwischen der Saugniere 33 und der gegenüberliegenden Deckelaussparung 53 stellt sich stets ein Druckausgleich ein, da in diesem Bereich die Zähne der beiden Zahnräder 4, 6 auseinanderIaufen und somit zwischen diesen Zähnen Zwischenräume gebildet sind. Nur im Bereich der Zweige 33a, b bzw. 53a, b könnten sich infolge der abnehmenden Tiefe und der speziellen Strömungsverhältnisse dann unterschiedliche Druckverhältnisse einstellen, wenn die Zweige 33a, b eine andere geometrische Form aufwiesen als die Zweige 53a, b. Aus diesem Grund sind, wie besonders aus Fig. 3 ersichtlich, nicht nur die Konturen in Umfangsrichtung, sondern auch die Querschnitte der einander gegenüberliegenden Zweige jeweils gleich. Somit laufen die Zahnräder 4, 6 in axialer Richtung lastfrei, weil sie sowohl im Bereich der Saugniere als auch im Bereich der Druckniere jeweils unter vollem Druckausgleich stehen. Somit werden Reibungsverluste vermieden ; die Lebensdauer der Pumpe ist verlängert.A pressure equalization is always established between the suction cardioid 33 and the opposite cover recess 53, since in this area the teeth of the two gear wheels 4, 6 diverge and spaces are thus formed between these teeth. Only in the area of the branches 33a, b or 53a, b could different pressure conditions arise due to the decreasing depth and the special flow conditions if the branches 33a, b had a different geometric shape than the branches 53a, b. For this reason, as can be seen particularly from FIG. 3, not only the contours in the circumferential direction, but also the cross sections of the mutually opposite branches are the same. Thus, the gears 4, 6 run load-free in the axial direction, because they are under full pressure equalization both in the area of the suction kidney and in the area of the pressure kidney. Friction losses are thus avoided; the life of the pump is extended.

Zu erwähnen ist noch, daß die saugnierenseitige Begrenzung der Druckniere in Fig. 1 etwa längs einer Parallelen zur Tangente an die beiden Saugnierenenden verläuft, so daß die Abdichtungsstrecken von den beiden Saugnierenenden zum Drucknierenbeginn etwa gleich lang sind.It should also be mentioned that the suction kidney-side limitation of the pressure kidney in FIG. 1 runs approximately along a parallel to the tangent to the two suction kidney ends, so that the sealing distances from the two suction kidney ends to the beginning of the pressure kidney are approximately the same length.

Claims (8)

1. Internal rotor gear oil pump for engines of motor vehicles and automatic motor vehicle gears with the following features :
a) The pump housing (1), holding the hollow wheel (4) and pinion (6) of the pump in a working chamber (3), is able to be flanged to the front side of the engine or respectively gear and has a passage (18) for an extension of the crankshaft or respectively the pinion drive shaft, which penetrates and drives the pinion (6) which is arranged coaxially to the shaft ;
b) In the housing (1) a supply channel (9) runs to a suction pocket (33) which is hollowed out in at least one of the two end walls of the working chamber (3) of the pump ;
c) In the housing (1), in addition, a removal channel (28, 29) for the conveyed oil runs from the working chamber (3) to a corresponding connection ;
d) In the construction as engine oil pump, the supply channel (9) runs at least in its part close to the working chamber approximately in a normal plane to the rotation axis of the pump, and the direction of flow in the supply channel (9) approximately tangentially to the central circumference direction of the pump gears (4, 6) in the region of the suction pocket ;
e) An approximately crescent-shaped filler (50) fills the majority of the space lying opposite the site of deepest mesh of teeth between the crown lines of the gears (4, 6) characterized in that the suction pocket (33) in the direction of rotation of the pump extends to close to the plane (51) containing the two gear axes (0,0'), prererably beyond these.
2. Pump according to Claim 1, characterized in that the suction pocket (33) extends 20 to 30°, preferably 25°, beyond the said plane (51).
3. Pump according to Claim 1 or 2, characterized in that the suction pocket (33) has both a branch (33a, 33b) running radially outside and running radially inside the filler (50).
4. Pump according to one of Claims 1 to 3, characterized in that the beginning of the pressure pocket (26) from the two ends of the suction pocket branches (33a, 33b) in circumferential direction has a spacing of approximately two gear divisions.
5. Pump according to one of Claims 1 to 4, characterized in that the cross-section of the suction pocket (33) constantly reduces to zero from the transition of the supply channel (9) into the suction pocket (33) towards the end of the suction pocket away from the supply channel.
6. Pump according to one of Claims 1 to 5, characterized in that a further recess (53), preferably in the form and extent of the suction pocket (33), is provided in the end wall of the working chamber (3) lying opposite the suction pocket, and that preferably this recess (53) is connected with the suction pocket by a channel.
7. Pump according to one of Claims 1 to 6, characterized in that the radially outer edge of the suction pocket (33) and if applicable of the recess (53) runs over the majority of the length of this suction pocket in the region of the outer edge of the working chamber (3).
8. Pump according to one of Claims 1 to 7, characterized in that the end of the filler (50) projecting between the branches (33a, 33b) of the suction pocket is bevelled (bevel 52) such that the radially inner branch (33b) has a run-in which widens contrary to the direction of rotation.
EP19850103161 1984-03-19 1985-03-19 Internal rotor gear oil pump for internal-combustion engines of motor vehicles Expired EP0161421B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3410015 1984-03-19
DE19843410015 DE3410015C2 (en) 1984-03-19 1984-03-19 Internal rotor gear oil pump for automotive engines and automatic automotive transmissions

Publications (3)

Publication Number Publication Date
EP0161421A2 EP0161421A2 (en) 1985-11-21
EP0161421A3 EP0161421A3 (en) 1986-12-17
EP0161421B1 true EP0161421B1 (en) 1988-12-21

Family

ID=6230939

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19850103161 Expired EP0161421B1 (en) 1984-03-19 1985-03-19 Internal rotor gear oil pump for internal-combustion engines of motor vehicles

Country Status (3)

Country Link
EP (1) EP0161421B1 (en)
JP (1) JPS60259785A (en)
DE (1) DE3410015C2 (en)

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6226588U (en) * 1985-07-30 1987-02-18
FR2607867B1 (en) * 1986-12-08 1991-01-11 Peugeot DEVICE FOR THE CIRCULATION OF A LUBRICANT IN A LUBRICATION CIRCUIT OF AN INTERNAL COMBUSTION ENGINE
IT208998Z2 (en) * 1986-12-23 1988-09-02 Fiat Auto Spa CONTROL DEVICE FOR AN OIL PUMP IN AN INTERNAL COMBUSTION ENGINE
ES2025589T3 (en) * 1987-06-23 1992-04-01 Schwabische Huttenwerke Gesellschaft Mit Beschrankter Haftung INTERNAL TOOTHED WHEEL PUMP AS LUBRICATING OIL PUMP.
JPH0417833Y2 (en) * 1987-07-23 1992-04-21
DE4413515A1 (en) * 1993-05-11 1994-11-17 Barmag Luk Automobiltech Hydraulic pump
DE19514021C2 (en) * 1995-04-13 1998-02-12 Daimler Benz Ag Gear pump
DE19814545A1 (en) 1998-04-01 1999-10-07 Schwaebische Huettenwerke Gmbh Oil pump with pressure compensation hole
US6179595B1 (en) * 1998-05-27 2001-01-30 Luk Getriebe-Systeme Gmbh Hydraulic gear machine having a transmission shaft in a bearing tube
US6149415A (en) 1999-02-11 2000-11-21 Viking Pump, Inc. Internal gear pump having a feed groove aligned with the roots of the idler teeth
DE102007008265A1 (en) * 2007-02-20 2008-08-21 Siemens Ag gerotor
DE102008054474B4 (en) * 2008-12-10 2013-07-25 Zf Friedrichshafen Ag Internal gear pump with optimized noise behavior

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE719405C (en) * 1939-03-25 1942-04-07 Fritz Egersdoerfer Fast running gear pump
GB1035529A (en) * 1963-08-12 1966-07-13 Lucas Industries Ltd Gear pumps
US3291060A (en) * 1966-03-21 1966-12-13 Lucas Industries Ltd Gear pumps
DE1914444C3 (en) * 1969-03-21 1973-06-28 Zahnradfabrik Friednchshafen AG, 7990 Friednchshafen Gear pump
GB1457514A (en) * 1973-05-10 1976-12-01 Lucas Industries Ltd Gear pumps and motors
JPS5065904A (en) * 1973-10-17 1975-06-03
US3855987A (en) * 1974-01-14 1974-12-24 Gen Motors Corp Rotary engine oil lubrication system
JPS5730991A (en) * 1980-08-01 1982-02-19 Tokyo Shibaura Electric Co Failed fuel detection device
DE3243067A1 (en) * 1982-11-22 1984-05-24 Schwäbische Hüttenwerke GmbH, 7080 Aalen Internal-rotor gear-type oil pump for motor vehicle internal combustion engines

Also Published As

Publication number Publication date
EP0161421A2 (en) 1985-11-21
JPS60259785A (en) 1985-12-21
DE3410015A1 (en) 1985-09-26
EP0161421A3 (en) 1986-12-17
DE3410015C2 (en) 1995-09-28

Similar Documents

Publication Publication Date Title
DE4200883C1 (en)
EP0043899B1 (en) Annular gear pump
EP0362906B1 (en) Internal gear pump
EP0161421B1 (en) Internal rotor gear oil pump for internal-combustion engines of motor vehicles
EP0619430B1 (en) Internal gear pump for high rotary speed range
DE3400594A1 (en) FLOWING MACHINE
DE2758376C2 (en)
DE19533287A1 (en) Bearing lubrication system
EP0422617B1 (en) Suction regulated annular gear pump
DE2836094A1 (en) ARRANGEMENT OF AN OIL PUMP
DE4345273C2 (en) Hydraulic gear machine (pump or motor), in particular internal gear machine
DE2444659B2 (en)
DE3416400C2 (en) Motor vehicle oil pump
DE4303328C2 (en) Gerotor pump for conveying fluid, in particular as a fuel delivery unit for motor vehicles
DE102016207093B4 (en) Gear fluid machine
DE4421255C1 (en) Packing pieceless inner gearwheel pump
DE102013202917A1 (en) Geared machine, particularly gear pump or gear motor, has pressure chamber, in which pressure fluid having low particle concentration is present, and channel, through which pressure chamber is connected with axial force compensating groove
DE4302242C2 (en) Rotary piston compressor with horizontal axis of rotation
EP0328745B1 (en) Internal gear machine
DE3243067C2 (en)
DE4440782C5 (en) Internal gear pump with displacement projections
EP2063126A2 (en) Hydraulic cog wheel machine and method for sealing a hydraulic cog wheel machine
DE8111149U1 (en) GEAR PUMP
DE2621720A1 (en) LIQUID-COOLED MULTI-ANGLE PISTON OF A ROTARY PISTON MACHINE
DE3448253C2 (en)

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Designated state(s): FR GB IT

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): FR GB IT

17P Request for examination filed

Effective date: 19870203

17Q First examination report despatched

Effective date: 19880318

ITF It: translation for a ep patent filed

Owner name: BARZANO' E ZANARDO MILANO S.P.A.

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): FR GB IT

ET Fr: translation filed
GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)
PLBI Opposition filed

Free format text: ORIGINAL CODE: 0009260

26 Opposition filed

Opponent name: OTTO ECKERLE GMBH & CO. KG

Effective date: 19890921

ITTA It: last paid annual fee
PLBM Termination of opposition procedure: date of legal effect published

Free format text: ORIGINAL CODE: 0009276

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: OPPOSITION PROCEDURE CLOSED

27C Opposition proceedings terminated

Effective date: 19910713

REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20040303

Year of fee payment: 20

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20040310

Year of fee payment: 20

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF EXPIRATION OF PROTECTION

Effective date: 20050318

REG Reference to a national code

Ref country code: GB

Ref legal event code: PE20