EP0342346B1 - Gear pump - Google Patents

Gear pump Download PDF

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Publication number
EP0342346B1
EP0342346B1 EP89106034A EP89106034A EP0342346B1 EP 0342346 B1 EP0342346 B1 EP 0342346B1 EP 89106034 A EP89106034 A EP 89106034A EP 89106034 A EP89106034 A EP 89106034A EP 0342346 B1 EP0342346 B1 EP 0342346B1
Authority
EP
European Patent Office
Prior art keywords
pressure
gearwheels
gear pump
sealing plate
disposed
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP89106034A
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German (de)
French (fr)
Other versions
EP0342346A2 (en
EP0342346A3 (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
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0342346A2 publication Critical patent/EP0342346A2/en
Publication of EP0342346A3 publication Critical patent/EP0342346A3/en
Application granted granted Critical
Publication of EP0342346B1 publication Critical patent/EP0342346B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • 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.
  • a gear pump See GB-A-2048385
  • the sealing plate is brought into sealing contact with the gear side surfaces by means of graduated hydraulic loading of pressure fields, in order to thereby keep the leakage loss between the high pressure and low pressure sides 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 small.

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Zahnradpumpe nach der Gattung des Hauptanspruchs. Bei einer derartigen bekannten Zahnradpumpe Siehe GB-A-2048385 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 See GB-A-2048385, the sealing plate is brought into sealing contact with the gear side surfaces by means of graduated hydraulic loading of pressure fields, in order to thereby keep the leakage loss between the high pressure and low pressure sides 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 small.

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. Gear pump having two gearwheels which intermesh in outside engagement, there being disposed on at least one side of the gearwheels an axially slightly movable sealing plate (26), which is matched to the contour of the interior (11) of the housing (10) and which, as a result of liquid pressure acting in two pressure fields (A, B), is pressed in seal-tight manner against the side faces of the gearwheels, and the pressure fields being delimited by seals (28, 30) disposed on the side facing away from the gearwheels, the pressure fields being essentially configured as two areas essentially concentric to one another and, at least across a partial section, also to the shaft boreholes (27, 28), namely in the form of a radially outer first preliminary pressure field (A) and a radially inner second main pressure field (B),
characterised in that,
on the high pressure side (32) of the gear pump, there is configured a constriction (39), and in that the pressure difference present at the latter has an effect at the sealing plate, with the result that, from a certain speed determined by the constriction, this sealing plate is raised from the side faces of the gearwheels.
2. Pump according to Claim 1,
characterised in that
the constriction is disposed, in the form of a throttle or diaphragm, in the outlet borehole (32) of the gear pump itself.
3. Pump according to Claim 1 and/or 2,
characterised in that,
downstream from the throttle (39), there is disposed a jet apparatus (55), through which, on the one hand, the feed current flows, and on the other hand, a connection (56) runs to the reservoir.
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 EP0342346A2 (en) 1989-11-23
EP0342346A3 EP0342346A3 (en) 1990-04-18
EP0342346B1 true EP0342346B1 (en) 1992-04-15

Family

ID=6354402

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89106034A Expired - Lifetime EP0342346B1 (en) 1988-05-14 1989-04-06 Gear pump

Country Status (3)

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

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3902139A1 (en) * 1989-01-25 1990-07-26 Bosch Gmbh Robert HYDROSTATIC DRIVE
EP0620369B1 (en) * 1994-06-26 1998-10-07 Maag Pump Systems Textron AG Gear pump
US7963186B2 (en) * 2006-04-12 2011-06-21 Arvinmeritor Technology, Llc Ancillary oil pumping for gear box assembly
DE202015100277U1 (en) * 2015-01-12 2015-03-05 Ludwig Michelbach Gear pump and humidifier with such a gear pump

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2990341A (en) * 1956-08-27 1961-06-27 Pittsburgh Plate Glass Co Process for concentrating hydrogen peroxide
US2996999A (en) * 1958-01-22 1961-08-22 Hupp Corp Gear pump
US3476055A (en) * 1967-12-19 1969-11-04 Lucas Industries Ltd Gear pumps
DE2349304C3 (en) * 1973-10-01 1981-07-16 Robert Bosch Gmbh, 7000 Stuttgart Gear motor operated with hydraulic fluid
DE2846547A1 (en) * 1978-10-26 1980-04-30 Pierburg Luftfahrtgeraete SELF-SEALING GEAR PUMP
DD142741A1 (en) * 1979-04-09 1980-07-09 Hubert Stroehl DEVICE FOR CONTROLLING THE FLUID CURRENT OF ROTATION PISTON MACHINES, IN PARTICULAR GEAR PUMPS
DE3430271A1 (en) * 1984-08-17 1986-02-27 Robert Bosch Gmbh, 7000 Stuttgart Hydraulic gear motor
US4678341A (en) * 1985-05-16 1987-07-07 Stuckey William C Integrated liquid distribution apparatus
DE3605246C2 (en) * 1986-02-19 1993-11-25 Bosch Gmbh Robert Gear machine (pump or motor)
DE8806388U1 (en) * 1987-09-10 1989-01-12 Robert Bosch Gmbh, 7000 Stuttgart, De

Also Published As

Publication number Publication date
DE58901138D1 (en) 1992-05-21
EP0342346A2 (en) 1989-11-23
US4971534A (en) 1990-11-20
DE3816537A1 (en) 1989-11-23
EP0342346A3 (en) 1990-04-18

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