EP0342346A2 - Gear pump - Google Patents

Gear pump Download PDF

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Publication number
EP0342346A2
EP0342346A2 EP19890106034 EP89106034A EP0342346A2 EP 0342346 A2 EP0342346 A2 EP 0342346A2 EP 19890106034 EP19890106034 EP 19890106034 EP 89106034 A EP89106034 A EP 89106034A EP 0342346 A2 EP0342346 A2 EP 0342346A2
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EP
European Patent Office
Prior art keywords
pressure
gear
sealing plate
gear pump
fields
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
EP19890106034
Other languages
German (de)
French (fr)
Other versions
EP0342346A3 (en
EP0342346B1 (en
Inventor
Hayno Dipl.-Ing. Rustige
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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Filing date
Publication date
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Publication of EP0342346A2 publication Critical patent/EP0342346A2/en
Publication of EP0342346A3 publication Critical patent/EP0342346A3/en
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Publication of EP0342346B1 publication Critical patent/EP0342346B1/en
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Expired - Lifetime legal-status Critical Current

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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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C14/26—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
    • F04C14/265—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels being obtained by displacing a lateral sealing face
    • 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
    • F04C15/0023—Axial sealings for working fluid
    • F04C15/0026—Elements specially adapted for sealing of the lateral faces of intermeshing-engagement type machines or pumps, e.g. gear machines or pumps

Definitions

  • the invention relates to a gear pump according to the preamble of the main claim.
  • the sealing plate is brought into sealing contact with the gear side surfaces by means of stepped hydraulic loading of pressure fields, in order thereby to keep the leakage loss between high pressure and low pressure side low. It is often disadvantageous that the delivery rate increases with increasing speed.
  • the gear pump according to the invention with the characterizing features of the main claim has the advantage that the sealing plate has, in addition to the sealing function, that of a current regulator, which is effective from a certain delivery volume of the gear pump by targeted leakage oil flow from the high pressure side along the underside of the sealing plate to the low pressure side, so that the delivery volume of the pump is limited to a certain value. So this is possible without a special flow control valve, as was previously necessary. This results in significant savings.
  • FIG. 1 shows a longitudinal section through a gear pump
  • FIG. 2 shows a section along II-II according to FIG. 1
  • FIG. 3 shows a section along III-III according to FIG. 2
  • FIG. 4 shows a schematic diagram
  • FIG. 5 shows a diagram, FIGS. 6 and 7 schematic diagrams.
  • the gear pump has a housing 10, the interior 11 of which has approximately the cross-sectional shape of an eight, which is closed on both sides by covers 12, 13.
  • two gears 14, 15 mesh with one another in external engagement, the shafts 16, 17 of which are mounted in spectacle-shaped bearing bodies 18, 19.
  • Bearing bodies of this type are generally known and are therefore not described further.
  • a passage 20 is formed in the cover 13, through which an extension 23 of the shaft 17 penetrates to the outside; it is sealed there by a sealing ring 24.
  • a sealing plate 26 is arranged between the bearing body 18 and the adjacent side surfaces of the gear wheels 14, 15, which also has the contour of the housing interior, covers the entire surface of the gear wheels and has little axial freedom of movement. Two pressure fields are effective on the back, as described below.
  • FIG. 2 shows, inter alia, a top view of the bearing body 18, specifically from its end face facing the sealing plate 26.
  • a first use 27 running near the outer contour of the bearing body, which runs partially concentrically to the gear shaft and extends from the high-pressure side HD to the low-pressure side ND, but does not extend as far as this.
  • Usage 27 ends in two groove ends 27A, 27B, which penetrate to the edge of the bearing body.
  • a seal 28 made of rubber-elastic material is arranged in this use.
  • a second usable part 29 which also extends from the high pressure side to the low pressure side, its ends 29A, 29B projecting further to the low pressure side than the groove ends of the usable part 27 29 also has an indentation 29C in its central region, which leads approximately to an imaginary straight line connecting the shaft centers.
  • the high-pressure side HD is characterized by a recess 31, into which the high-pressure bore 32 penetrates from the outside of the housing, namely at the level of the gearwheels 14, 15.
  • the low-pressure side ND is characterized by a recess 33, in which an axially coextensive with the high-pressure bore 32 Low pressure bore 34 penetrates, which also extends from the exterior of the housing.
  • FIG. 2 there is an intermediate space between the usages 27, 29, which forms a somewhat enlarged field 35 in the area 29C.
  • This is acted upon via a channel 36, 37, which is partially formed in the bearing body 18, partially in the housing 10.
  • the channel 36, 37 is connected to a bore 38 formed in the housing, which opens into the outlet bore 32, in which an aperture 39 is arranged.
  • the bore 38 opens downstream of the orifice 39 into the outlet bore 32.
  • the orifice 39 is fastened in the outlet bore 39 by means of a locking ring 39A. From this it can be seen that the sealing field B is always subjected to a pressure which prevails downstream of the orifice 39.
  • FIG. 4 shows the operation of the pump in a schematic representation. The same parts as in Figures 1, 2 and 3 are denoted by the same numbers.
  • the gear pump delivers pressure medium, it passes from the container 40 through the low pressure line into the high pressure bore 32. Pressure medium reaches the pressure field A via the recess 31 in which the high pressure prevails. This is therefore always acted upon by the delivery pressure.
  • the pressure field B is applied via the channels 36, 37, 38, specifically from the bore 32, which is located downstream of the orifice 39.
  • the sealing plate 26 is now brought into sealing contact with the gear side surfaces. If the delivery rate of the gear pump continues to increase, the pressure difference at the orifice 39 increases in proportion to the speed n of the gear pump. If the so-called regulating point Z - see diagram according to FIG.
  • the gear pump sucks pressure medium from the container through line 34 40 on and displaces it in line 41.
  • the pressure fields A and B are connected in series.
  • the cut-off pressure Z is reached, the sealing plate is raised, causing pressure medium to flow from the high-pressure side to the low-pressure side. It is functionally represented by a valve function 26.
  • the line 50 with throttle 51 symbolically means the gap losses in the gear pump, which always occur, but are very low.

Abstract

The gear pump has two gears (14, 15) which mesh in external engagement with each other and against the side faces of which a sealing plate (26) is pressed with the aid of two approximately concentrically extending pressure fields (A, B). The two pressure fields are not connected to each other. The pressure of one pressure field (B) can be relieved with the aid of an orifice plate (39) arranged in the delivery line, in particular in such a way that the sealing plate (16) is lifted off from the gear side faces, as a result of which a horizontal delivery rate characteristic is produced, i.e. from a certain point limiting the delivery rate no longer increases with the rotational speed. As a result, the sealing plate has the function of a flow control valve. …<IMAGE>…

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Zahnradpumpe nach der Gattung des Hauptanspruchs. Bei einer derartigen bekannten Zahnradpumpe wird die Dichtplatte durch abgestufte hydraulische Belastung von Druckfeldern her in dichtende Berührung mit den Zahnradseitenflächen gebracht, um dadurch den Leckverlust zwischen Hochdruck- und Niederdruckseite gering zu halten. Nachteilig ist dabei häufig, daß die Fördermenge mit steigender Drehzahl ansteigt.The invention relates to a gear pump according to the preamble of the main claim. In such a known gear pump, the sealing plate is brought into sealing contact with the gear side surfaces by means of stepped hydraulic loading of pressure fields, in order thereby to keep the leakage loss between high pressure and low pressure side low. It is often disadvantageous that the delivery rate increases with increasing speed.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Zahnradpumpe mit den kennzeichnenden Merkmalen des Hauptanspruchs hat demgegenüber den Vorteil, daß die Dichtplatte außer der Dichtfunktion noch die eines Stromreglers hat, der ab einem bestimmten Fördervolumen der Zahnradpumpe wirksam wird durch gezielte Leckölströmung von der Hochdruckseite entlang der Unter­seite der Dichtplatte zur Niederdruckseite, so daß das Fördervolumen der Pumpe auf einen bestimmten Wert begrenzt wird. Dies ist also möglich ohne ein spezielles Stromregelventil, wie es bisher not­wendig war. Dadurch ergibt sich eine bedeutende Ersparnis.The gear pump according to the invention with the characterizing features of the main claim has the advantage that the sealing plate has, in addition to the sealing function, that of a current regulator, which is effective from a certain delivery volume of the gear pump by targeted leakage oil flow from the high pressure side along the underside of the sealing plate to the low pressure side, so that the delivery volume of the pump is limited to a certain value. So this is possible without a special flow control valve, as was previously necessary. This results in significant savings.

Zeichnungdrawing

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung darge­stellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 einen Längsschnitt durch eine Zahnradpumpe, Figur 2 einen Schnitt längs II-II nach Figur 1, Figur 3 einen Schnitt längs III-III nach Figur 2, Figur 4 eine Prinzipskizze und Figur 5 ein Diagramm, Figuren 6 und 7 Prinzipskizzen.An embodiment of the invention is shown in the drawing and explained in more detail in the following description. 1 shows a longitudinal section through a gear pump, FIG. 2 shows a section along II-II according to FIG. 1, FIG. 3 shows a section along III-III according to FIG. 2, FIG. 4 shows a schematic diagram, and FIG. 5 shows a diagram, FIGS. 6 and 7 schematic diagrams.

Beschreibung des ErfindungsbeispielesDescription of the invention example

Die Zahnradpumpe weist ein Gehäuse 10 auf, dessen Innenraum 11 etwa die Querschnittsform einer Acht hat, das beidseitig durch Deckel 12, 13 verschlossen ist. Im Innenraum kämmen zwei Zahnräder 14, 15 im Außeneingriff miteinander, deren Wellen 16, 17 in brillenförmigen Lagerkörpern 18, 19 gelagert sind. Derartige Lagerkörper sind all­gemein bekannt und deshalb nicht weiter beschrieben. Im Deckel 13 ist ein Durchgang 20 ausgebildet, durch welche eine Verlängerung 23 der Welle 17 nach außen dringt; sie ist dort durch einen Dichtring 24 abgedichtet.The gear pump has a housing 10, the interior 11 of which has approximately the cross-sectional shape of an eight, which is closed on both sides by covers 12, 13. In the interior, two gears 14, 15 mesh with one another in external engagement, the shafts 16, 17 of which are mounted in spectacle-shaped bearing bodies 18, 19. Bearing bodies of this type are generally known and are therefore not described further. A passage 20 is formed in the cover 13, through which an extension 23 of the shaft 17 penetrates to the outside; it is sealed there by a sealing ring 24.

Zwischen dem Lagerkörper 18 und den benachbarten Seitenflächen der Zahnräder 14, 15 ist eine Dichtplatte 26 angeordnet, die ebenfalls die Kontur des Gehäuseinnenraums hat, die gesamte Fläche der Zahn­räder überdeckt und eine geringe axiale Bewegungsfreiheit hat. An ihrer Rückseite sind zwei Druckfelder wirksam, wie sie nachfolgend beschrieben sind.A sealing plate 26 is arranged between the bearing body 18 and the adjacent side surfaces of the gear wheels 14, 15, which also has the contour of the housing interior, covers the entire surface of the gear wheels and has little axial freedom of movement. Two pressure fields are effective on the back, as described below.

Die Figur 2 zeigt u.a. eine Draufsicht auf den Lagerkörper 18, und zwar von seiner der Dichtplatte 26 zugewandten Stirnseite her. In dieser Stirnseite ist ein nahe der Außenkontur des Lagerkörpers ver­laufender erster Nutzug 27 ausgebildet, welcher teilweise konzen­trisch zu den Zahnradwellen verläuft, und sich von der Hochdruck­seite HD zur Niederdruckseite ND hinzieht, jedoch nicht bis zu dieser verläuft. Der Nutzug 27 endet jeweils in zwei Nutenden 27A, 27B, die bis an den Rand des Lagerkörpers vordringen. In diesem Nutzug ist eine Dichtung 28 aus gummielastischem Werkstoff ange­ordnet.FIG. 2 shows, inter alia, a top view of the bearing body 18, specifically from its end face facing the sealing plate 26. In this end face is formed a first use 27 running near the outer contour of the bearing body, which runs partially concentrically to the gear shaft and extends from the high-pressure side HD to the low-pressure side ND, but does not extend as far as this. Usage 27 ends in two groove ends 27A, 27B, which penetrate to the edge of the bearing body. A seal 28 made of rubber-elastic material is arranged in this use.

Ebenfalls konzentrisch zu den Zahnradwellen, aber radial innerhalb des Nutzugs 27 ist ein zweiter Nutzug 29 ausgebildet, der sich eben­falls von der Hochdruckseite zur Niederdruckseite hin erstreckt, wobei seine Enden 29A, 29B noch weiter zur Niederdruckseite vor­dringen als die Nutenden des Nutzuges 27. Der Nutzug 29 hat außerdem in seinem mittleren Bereich eine Einbuchtung 29C, die etwa bis zu einer die Wellenmitten verbindenden gedachten Geraden führt. Im Nutzug 29 ist passend eine Dichtung 30 angeordnet, die ebenfalls aus einem gummielastischen Werkstoff besteht.Also concentric to the gear shaft, but radially inside the usable part 27 is a second usable part 29, which also extends from the high pressure side to the low pressure side, its ends 29A, 29B projecting further to the low pressure side than the groove ends of the usable part 27 29 also has an indentation 29C in its central region, which leads approximately to an imaginary straight line connecting the shaft centers. A seal 30, which also consists of a rubber-elastic material, is suitably arranged in the utilization 29.

Die Hochdruckseite HD ist gekennzeichnet durch eine Ausnehmung 31, in welche die Hochdruckbohrung 32 vom Äußeren des Gehäuses ausgehend eindringt, und zwar in Höhe der Zahnräder 14, 15. Die Niederdruck­seite ND ist gekennzeichnet durch eine Ausnehmung 33, in welche eine achsgleich zur Hochdruckbohrung 32 verlaufende Niederdruckbohrung 34 eindringt, die ebenfalls vom Äußeren des Gehäuses ausgeht.The high-pressure side HD is characterized by a recess 31, into which the high-pressure bore 32 penetrates from the outside of the housing, namely at the level of the gearwheels 14, 15. The low-pressure side ND is characterized by a recess 33, in which an axially coextensive with the high-pressure bore 32 Low pressure bore 34 penetrates, which also extends from the exterior of the housing.

Wie aus Figur 2 ersichtlich ist, besteht zwischen den Nutzügen 27, 29 ein Zwischenraum, welcher im Bereich 29C ein etwas vergrößertes Feld 35 bildet. Dieses ist über einen Kanal 36, 37, welcher teil­weise im Lagerkörper 18, teilweise im Gehäuse 10 ausgebildet ist, beaufschlagt. Der Kanal 36, 37 steht mit einer im Gehäuse ausge­bildeten Bohrung 38 in Verbindung, welche in die Auslaßbohrung 32 mündet, in der eine Blende 39 angeordnet ist. Die Bohrung 38 mündet stromabwärts der Blende 39 in die Auslaßbohrung 32. Die Blende 39 ist mit Hilfe eines Sicherungsringes 39A in der Auslaßbohrung 39 befestigt. Daraus ist zu erkennen, daß das Dichtfeld B stets mit einem Druck beaufschlagt ist, welcher stromabwärts der Blende 39 herrscht.As can be seen from FIG. 2, there is an intermediate space between the usages 27, 29, which forms a somewhat enlarged field 35 in the area 29C. This is acted upon via a channel 36, 37, which is partially formed in the bearing body 18, partially in the housing 10. The channel 36, 37 is connected to a bore 38 formed in the housing, which opens into the outlet bore 32, in which an aperture 39 is arranged. The bore 38 opens downstream of the orifice 39 into the outlet bore 32. The orifice 39 is fastened in the outlet bore 39 by means of a locking ring 39A. From this it can be seen that the sealing field B is always subjected to a pressure which prevails downstream of the orifice 39.

An die Hochdruckbohrung 32 ist eine Leitung 41 angeschlossen, die zu einem Verbraucher 42 führt und von dort zum Behälter 40. Die Figur 4 zeigt die Funktionsweise der Pumpe in schematischer Darstellung. Gleiche Teile wie in den Figuren 1, 2 und 3 sind mit denselben Ziffern bezeichnet.A line 41 is connected to the high-pressure bore 32, which leads to a consumer 42 and from there to the container 40. FIG. 4 shows the operation of the pump in a schematic representation. The same parts as in Figures 1, 2 and 3 are denoted by the same numbers.

Wenn die Zahnradpumpe Druckmittel fördert, so gelangt dieses vom Behälter 40 durch die Niederdruckleitung in die Hochdruckbohrung 32. Über die Ausnehmung 31, in welcher der Hochdruck herrscht, gelangt Druckmittel in das Druckfeld A. Dieses ist also stets vom Förder­druck beaufschlagt. Die Beaufschlagung des Druckfelds B erfolgt über die Kanäle 36, 37, 38, und zwar von der Bohrung 32 aus, welche stromabwärts der Blende 39 liegt. Die Dichtplatte 26 wird nun in dichtende Berührung mit den Zahnradseitenflächen gebracht. Steigt die Fördermenge der Zahnradpumpe weiter an, so steigt die Druck­differenz an der Blende 39 proportional zur Drehzahl n der Zahnrad­pumpe. Ist der sogenannte Abregelpunkt Z - siehe hierzu Diagramm nach Figur 4 - erreicht, dann wird die Dichtplatte 26 von den Zahnradseitenflächen abgehoben, und zwar deshalb, weil nun infolge der Druckdifferenz an der Blende 39 keine weitere Beaufschlagung des Druckfelds B mehr erfolgt. Daraus ist zu erkennen, daß die Kräfte aus den Druckfeldern A und B nicht mehr ausreichen, um die Dicht­platte 26 weiter an die Zahnräder anzudrücken. Dies bedeutet, daß nun die Fördermenge trotz steigender Drehzahl nicht weiter ansteigt. Dies ist dadurch zu erklären, daß durch das Abheben der Dichtplatte 26 eine direkte Verbindung von der Hochdruckseite zur Niederdruck­seite entlang der Zahnradseitenflächen stattfindet. Es handelt sich also um eine Fördermengenregelung ohne das bisher notwendige Strom­regelventil. Ab einer bestimmten Drehzahl bleibt die Förderung trotz weiter ansteigender Drehzahl konstant.When the gear pump delivers pressure medium, it passes from the container 40 through the low pressure line into the high pressure bore 32. Pressure medium reaches the pressure field A via the recess 31 in which the high pressure prevails. This is therefore always acted upon by the delivery pressure. The pressure field B is applied via the channels 36, 37, 38, specifically from the bore 32, which is located downstream of the orifice 39. The sealing plate 26 is now brought into sealing contact with the gear side surfaces. If the delivery rate of the gear pump continues to increase, the pressure difference at the orifice 39 increases in proportion to the speed n of the gear pump. If the so-called regulating point Z - see diagram according to FIG. 4 - has been reached, then the sealing plate 26 is lifted off the gear side surfaces, because now that the pressure field B is no longer acted on due to the pressure difference at the orifice 39. From this it can be seen that the forces from the pressure fields A and B are no longer sufficient to press the sealing plate 26 further against the gears. This means that the delivery rate does not continue to increase despite the increasing speed. This can be explained in that a direct connection from the high-pressure side to the low-pressure side takes place along the gearwheel side surfaces by lifting off the sealing plate 26. It is therefore a flow control without the flow control valve previously required. From a certain speed, the delivery remains constant despite the increasing speed.

In der Figur 4 sind diese Vorgänge schematisch dargestellt. Die Zahnradpumpe saugt durch die Leitung 34 Druckmittel aus dem Behälter 40 an und verdrängt es in die Leitung 41. An der Blende 39 entsteht der oben geschilderte Druckabfall. Die Druckfelder A und B sind in Serie geschaltet. Ist der Abregeldruck Z erreicht, dann wird die Dichtplatte angehoben, wodurch nun Druckmittel von der Hochdruck­seite zur Niederdruckseite fließt. Es ist funktionell durch eine Ventilfunktion 26 dargestellt. Die Leitung 50 mit Drossel 51 bedeu­tet symbolisch die Spaltverluste in der Zahnradpumpe, die immer auf­treten, aber sehr gering sind.These processes are shown schematically in FIG. The gear pump sucks pressure medium from the container through line 34 40 on and displaces it in line 41. At the orifice 39, the pressure drop described above arises. The pressure fields A and B are connected in series. When the cut-off pressure Z is reached, the sealing plate is raised, causing pressure medium to flow from the high-pressure side to the low-pressure side. It is functionally represented by a valve function 26. The line 50 with throttle 51 symbolically means the gap losses in the gear pump, which always occur, but are very low.

Es ist auch möglich, das geförderte Druckmittel axial über die Aus­nehmung 31 und eine Öffnung im Deckel abzuführen. Dieses ist in der Figur 6 schematisch angedeutet. Im Punkt P kann ein Strahlapparat angeordnet sein, um die Kennlinie nach Figur 5 zu verbessern. Dies ist skizzenhaft in Figur 7 angedeutet.It is also possible to discharge the pressure medium conveyed axially via the recess 31 and an opening in the cover. This is indicated schematically in FIG. 6. A beam apparatus can be arranged at point P in order to improve the characteristic curve according to FIG. This is indicated sketchily in FIG. 7.

Claims (3)

1. Zahnradpumpe mit zwei im Außeneingriff kämmenden Zahnrädern, wobei auf mindestens einer Seite der Zahnräder eine der Kontur des Innenraums (11) des Gehäuses (10) angepaßte, axial geringfügig bewegliche Dichtplatte (26) angeordnet ist, die durch in zwei Druck­feldern (A, B) wirkenden Flüssigkeitsdruck dichtend gegen die Zahn­radseitenflächen gedrückt wird und die Druckfelder durch auf der den Zahnrädern abgewandten Seite angeordnete Dichtungen (28, 30) abge­grenzt sind, wobei die Druckfelder als zwei zueinander mindestens über einen Teilbereich zu den Wellenbohrungen (27, 28) im wesent­lichen konzentrische Bereiche ausgebildet sind, und zwar einem radial außenliegenden ersten Vordruckfeld (A) und einem radial innenliegenden zweiten Hauptdruckfeld (B), dadurch gekennzeichnet, daß auf der Hochdruckseite (32) der Zahnradpumpe eine Verengung (39) ausgebildet ist und daß die an dieser herrschende Druckdifferenz an der Dichtplatte wirksam ist, so daß sich diese ab einer durch die Verengung festgelegten Drehzahl von den Zahnradseitenflächen abhebt.1. Gear pump with two meshing external gears, on at least one side of the gears one of the contours of the interior (11) of the housing (10), axially slightly movable sealing plate (26) is arranged, which is arranged in two pressure fields (A, B) acting liquid pressure is pressed sealingly against the gear side surfaces and the pressure fields are delimited by seals (28, 30) arranged on the side facing away from the gear wheels, the pressure fields essentially being two to one another at least over a partial area to the shaft bores (27, 28) concentric areas are formed, namely a radially outer first pre-pressure field (A) and a radially inner second main pressure field (B), characterized in that a constriction (39) is formed on the high pressure side (32) of the gear pump and that the prevailing thereon Pressure difference at the sealing plate is effective, so that it starts from a narrowing set speed from the gear side surfaces. 2. Pumpe nach Anspruch 1, dadurch gekennzeichnet, daß die Verengung in Form einer Drossel oder Blende in der Auslaßbohrung (32) der Zahnradpumpe selbst angeordnet ist.2. Pump according to claim 1, characterized in that the constriction is arranged in the form of a throttle or diaphragm in the outlet bore (32) of the gear pump itself. 3. Pumpe nach Anspruch 1 und/oder 2, dadurch gekennzeichnet, daß stromabwärts der Drossel (39) ein Strahlapparat (55) angeordnet ist, durch den einerseits der Förderstrom fließt, andererseits eine Ver­bindung (56) zum Behälter führt.3. Pump according to claim 1 and / or 2, characterized in that a jet apparatus (55) is arranged downstream of the throttle (39), through which on the one hand the flow flows, on the other hand a connection (56) leads to the container.
EP89106034A 1988-05-14 1989-04-06 Gear pump Expired - Lifetime EP0342346B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3816537 1988-05-14
DE3816537A DE3816537A1 (en) 1988-05-14 1988-05-14 GEAR PUMP

Publications (3)

Publication Number Publication Date
EP0342346A2 true EP0342346A2 (en) 1989-11-23
EP0342346A3 EP0342346A3 (en) 1990-04-18
EP0342346B1 EP0342346B1 (en) 1992-04-15

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EP89106034A Expired - Lifetime EP0342346B1 (en) 1988-05-14 1989-04-06 Gear pump

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US (1) US4971534A (en)
EP (1) EP0342346B1 (en)
DE (2) DE3816537A1 (en)

Cited By (2)

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Publication number Priority date Publication date Assignee Title
EP0379697A2 (en) * 1989-01-25 1990-08-01 Robert Bosch Gmbh Hydrostatic drive
EP0620369A2 (en) * 1994-06-26 1994-10-19 Maag Pump Systems Ag Gear pump

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7963186B2 (en) * 2006-04-12 2011-06-21 Arvinmeritor Technology, Llc Ancillary oil pumping for gear box assembly
DE102015100350B3 (en) * 2015-01-12 2016-03-03 Ludwig Michelbach Gear pump and humidifier with such a gear pump

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FR2246188A5 (en) * 1973-10-01 1975-04-25 Bosch Gmbh Robert
GB2032526A (en) * 1978-10-26 1980-05-08 Pierburg Kg A Rotary positive-displacement fluid-machines
GB2048385A (en) * 1979-04-09 1980-12-10 Karl Marx Stadt Ind Werke A rotary fluid pump or motor
DE3605246A1 (en) * 1986-02-19 1987-08-20 Bosch Gmbh Robert Gear machine (pump or motor)
WO1989002515A1 (en) * 1987-09-10 1989-03-23 Robert Bosch Gmbh Gearwheel motor

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EP0379697A2 (en) * 1989-01-25 1990-08-01 Robert Bosch Gmbh Hydrostatic drive
EP0379697A3 (en) * 1989-01-25 1992-07-22 Robert Bosch Gmbh Hydrostatic drive
EP0620369A2 (en) * 1994-06-26 1994-10-19 Maag Pump Systems Ag Gear pump
EP0620369A3 (en) * 1994-06-26 1995-01-25 Maag Pump Systems Ag Gear pump.

Also Published As

Publication number Publication date
EP0342346A3 (en) 1990-04-18
DE58901138D1 (en) 1992-05-21
DE3816537A1 (en) 1989-11-23
EP0342346B1 (en) 1992-04-15
US4971534A (en) 1990-11-20

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