EP2634430B1 - Getriebepumpenanordnung - Google Patents

Getriebepumpenanordnung Download PDF

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Publication number
EP2634430B1
EP2634430B1 EP12157371.1A EP12157371A EP2634430B1 EP 2634430 B1 EP2634430 B1 EP 2634430B1 EP 12157371 A EP12157371 A EP 12157371A EP 2634430 B1 EP2634430 B1 EP 2634430B1
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EP
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Prior art keywords
gear pump
gear
housing
pump assembly
pumps
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EP12157371.1A
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English (en)
French (fr)
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EP2634430A1 (de
Inventor
Jörg Giesler
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Maag Pump Systems AG
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Maag Pump Systems AG
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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
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • F04C11/001—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C2/18—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms
    • 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
    • F04C15/0096—Heating; Cooling
    • 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
    • F04C2240/00—Components
    • F04C2240/30—Casings or housings

Definitions

  • the present invention relates to a gear pump assembly.
  • Gear pumps are positive displacement pumps, i.e. they pump a constant amount of fluid for each rotation, and they are particularly suited for pumping high viscosity fluids such as bitumen, pitch, diesel oil, crude oil, paints, inks, resins, adhesives, chocolate, molasses, and molten thermoplastics. They typically comprise a housing comprising a cavity in which is arranged a pair of gears, one of which is known as the "drive” gear, which is driven by a driveshaft attached to an external driver such as a motor, and an “idler” gear, which meshes with the "drive” gear.
  • Both gears may be externally toothed, as in the case of an "external” gear pump, in which case the fluid is passed between the gear teeth and the wall of the cavity in the housing from the inlet to the outlet.
  • External gear pumps typically use spur, helical, or herringbone gears, depending on intended application.
  • one gear is externally-toothed, and the other gear is internally-toothed; it does not matter whether the internally or externally toothed gear is the drive or the idler gear.
  • the axes of rotation of the gears are offset, and the externally-toothed gear is of smaller diameter than the internally-toothed gear.
  • This type of gear pump is known as an "internal” gear pump, and the fluid is passed between the toothings of the two gears.
  • a crescent-shaped partition may or may not be provided in the gap between the two gears, depending on application.
  • EP 0 091 347 describes a double gear pump for a hydraulic system with two coaxial gear pumps in a single housing, pumping fluid from a single inlet to two different outlets at different flow rates and pressures.
  • the drive shafts of the drive gears are rotationally coupled and are driven in common by a single driver.
  • This system presents the disadvantages of having a fixed flow rate and/or pressure difference between the two gear pumps due to the common drive and thus common rotational velocity of both pumps.
  • the fluid pathways through the housing have a complicated shape which significantly complicates cleaning the pump, and even if one were to arrange the fluid pathways individually straight through the housing, due to the coaxial pump arrangement the distance between each inlet and outlet would still be quite significant, and would therefore not enable a significant reduction in the length of fluid channels required or the overall space requirement.
  • US 5,842,848 describes a compact high-volume gear pump consisting of three pumping sections each with its own idler gear for pumping fluid. All of the idler gears are driven by a single, common drive gear. This arrangement presents the disadvantages of fixed flow rate and/or pressure differences between each individual pump section, and again the fluid pathways follow a very complicated shape thereby presenting cleaning difficulties and indeed rendering a pump of this type entirely unsuitable for molten thermoplastics applications. Furthermore, cross contamination of fluid between the individual pumping sections is unavoidable.
  • a gear pump assembly with a single, unitary housing which has a plurality of external faces. Contained within this housing is a first cavity containing a first gear pump, and a second cavity containing a second gear pump.
  • Each gear pump comprises a drive gear with a driveshaft and at least one idler gear, also known as a driven gear, meshing with the drive gear.
  • Each gear pump is arranged such that rotation of its driveshaft causes fluid to be pumped through the housing from an inlet situated in a face of the housing to an outlet, also situated in a face of the housing.
  • the exact shape of the gears, the proportions of the sizes of the gears, and the shape of the cavities is well-known to the skilled person and need not be discussed further.
  • the two gear pumps are disposed collaterally in the housing, that is to say side-by-side, with respect to the axis of rotation of each drive gear, as opposed to coaxially (i.e. end-to-end) as is the case in EP 0 091 347 as discussed above.
  • each driveshaft is arranged to be driven independently, enabling each individual pump to have its rotational velocity independently determined according to the requirements of the user, which increases flexibility in design of the overall pumping system.
  • the claim does not exclude the possibility of one or more of the gear pumps comprising multiple idler gears, such as in the case of three-gear or planetary pumps, such as described in GB 1,214,723 , EP 1 267 077 , and JP 64-77778 .
  • At least one further gear pump is provided in its own cavity in the housing, which enables many gear pumps (i.e. three or more) to be situated close together as the user demands.
  • the first gear pump and the at least one second gear pump are substantially identical, which reduces the number of different parts required for the gear pump assembly.
  • the first gear pump and the at least one second gear pump differ by the width of the gears, and/or by the number of teeth on the drive and/or idler gears, and/or the diameter of the drive and/or diameter of the idler gears and/or by clearances in the pumps and/or by differing cooling arrangements of the gears.
  • This enables the two or more pumps to be tailored to a specific application which requires different pumping geometry and/or parameters, for instance one pump be optimised for pressure and the other for flow velocity or flow rate, or in the case of cooling arrangements of the gears, when one pump requires cooling and the other not.
  • each driveshaft is arranged to be driven independently with the same or different rotational velocities, enabling the pumping rate and/or pumping pressure in each pump to be tailored to the user's requirements.
  • the drive shafts are arranged on the same or different faces of the housing. This enables a large degree of design flexibility and space optimisation for the entire pumping system, since the driving means (such as electrical or hydraulic motors) can be situated as is convenient for the user, either on the same side or on different sides.
  • the driving means such as electrical or hydraulic motors
  • At least one inlet and at least one outlet are provided in the housing according to one of the following arrangements:
  • the gear pump housing is provided with at least one heating zone.
  • This heating zone is constituted in well-known fashion, e.g. by integration of channels for heating fluid or integration of electrical heating elements, and has the purpose of maintaining the temperature of the gear pump assembly for the desired application, e.g. sufficiently warm to maintain the temperature of a thermoplastic melt.
  • This at least one heating zone may be arranged variously according to one of the following arrangements:
  • the housing comprises a heat insulating zone between two adjacent gear pumps so as to thermally isolate two adjacent gear pumps from each other, which is desirable in the case when the two pumping fluids have significantly different temperature requirements.
  • a first plane defined by the longitudinal axes of the drive gear and idler gear of the first gear pump intersects with a second plane defined by the axes of the drive gear and idly gear of the second gear pump at an angle of less than or equal to 180°, i.e. the two gear pumps are arranged either in the same plane, with the liquid flows parallel to each other, or are arranged angled toward/away from each other. In a further embodiment, this angle is between 90° and 150°, giving angles of fluid flow of between 90° and 30° to each other, which enables positioning of the pumps for optimal use of the available space in the application in question.
  • the gear pump assembly is adapted to be connected to a single-screw or double-screw extruder, enabling use of the gear pump assembly as part of the manufacturing process for extruded thermoplastics, and in the case of the double-screw extruder, being able to arrange the complete system such that one screw feeds one pump, and the other screw feeds the other pump.
  • the housing is provided with at least one cover plate, with the driveshaft of each gear pump penetrating the same cover plate, and in an alternative embodiment, a first cover plate and the second cover plate are provided on opposite faces of the housing with at least one driveshaft passing through the first cover plate and at least one other driveshaft passing through the second cover plate.
  • gear pump assembly 1 comprising a single housing 2 provided with a drive-side cover 3 and a non-drive-side cover 4. It is conceivable that one of these covers could be omitted, the omitted cover then being constructed integral with housing 2.
  • gear pumps 8a, 8b within the housing 2 are provided two gear pumps 8a, 8b, although more could be present, each consisting of a drive gear 5a, 5b, and an idler gear 6a, 6b, situated in respective cavities 7a, 7b.
  • Each gear 5a, 5b, 6a, 6b is provided with a shaft 9a, 9b, 10a, 10b, which penetrates at least the drive-side cover 3, and is held in a bearing therein, as is conventional.
  • Shafts 9a, 9b are driveshafts, and are adapted to be coupled with a source of rotation such as a motor (not illustrated).
  • the driveshafts 9a, 9b are provided with splines, however any other convenient geometric shape such as a square or hexagonal cross-section is also conceivable.
  • the driveshafts and the shafts of the idler gears may be provided with cooling means (not illustrated) such as a water-based cooling system, as is known to the skilled person. It is possible that neither pump is provided with such a cooling system, only one of the pumps is provided with such a cooling system, or both pumps are provided with such a cooling system.
  • Openings 11a, 11b, 12a, 12b are provided in the housing 2 for the passage of fluid through wider inlet channels 13a, 13b leading to the gear pumps 8a, 8b, and narrower outlet channels 14a, 14b leading from the gear pumps 8a, 8b respectively.
  • Each individual gear pump is of completely conventional design and need not be described further. It is of course self-evident to the skilled person that the direction of flow can be reversed through one or both of the gear pumps, and the modifications to permit this are well within the scope of normal design modifications - for instance, to permit gear pump 8a to pump in the opposite direction, channel 13a would be made narrower and channel 14a would be made wider, and the shape of the cavity 7a would be mirrored. It is entirely conceivable that each pump could be arranged to allow flow in either direction, in which case the cavity 7 would be made symmetric and the channels 13 and 14 would be made of equal cross-sectional area.
  • openings 11a, 11b are illustrated here as being separate, a further design option is that channels 14a, 14b merge on the inside of housing 2 thus resulting in a single opening 11.
  • the illustrated arrangement is particularly advantageous since it has great flexibility in that it can be used with a variety of different types of flow guiding means so that an essentially standard gear pump assembly can be modified for various applications by means of external, bolt-on flow-guiding attachments.
  • the inlet channels 13a, 13b are coaxial with the outlet channels 14a, 14b, although this does not have to be the case: the channels may be at an angle, curved, or bent as desired by the user, however coaxial inlet and outlet channels present a significant advantage during cleaning, since solidified matter such as plastic or rubber can be withdrawn as a single piece, and/or a cleaning device can be passed easily through the straight channels.
  • the two gear pumps 8a, 8b are situated at an angle to each other. Defining a first plane by the axis of rotation of drive gear 5a and idler gear 6a, and defining a second plane by the axis of rotation of the other drive gear 5b and the other idler gear 6b, these planes intersect at an angle in the illustration of 140°, that is to say that in the illustrated case the angle between the channel 14a and the channel 14b is 40°.
  • the channels 13a, 14a are perpendicular to the above-mentioned first plane
  • the channels 13b, 14b are perpendicular to the above-mentioned second plane, although this does not necessarily have to be the case.
  • the housing 2 comprises channels 15 for heating fluid so as to create a heated zone, in this case encompassing the whole gear pump assembly.
  • a heated zone in this case encompassing the whole gear pump assembly.
  • the arrangement could be made more complex, dividing the gear pump into separate heated zones, each associated with at least one gear pump 8a, 8b.
  • FIG. 5 shows schematically a possible use of the gear pump according to the invention.
  • Extruder 16 supplies a flow of molten plastic to a flow divider 17, attached to the inlets of double gear pump assembly 1.
  • Gear pump 1 in this example is in the opposite configuration to that of figures 1-4 , i.e. the inlets are closer together than the outlets. If a single inlet is present in the housing of the gear pump assembly 1, flow divider 17 may be dispensed with.
  • Motors 18a, 18b drive the driveshafts of each respective gear pump via universal driveshafts 19a, 19b, pumping molten plastic out of the outlets 20.
  • Pressure sensors 21 monitor the pressure at the inlets and outlet of the gear pumps, and temperature sensors 22 monitor the melt temperature at the outlets 20.
  • thermoplastics are not to be construed as limiting: many uses are foreseeable including, but not limited to, food products, pharmaceutical products, chemical products, lubricants, greases, oils, inks, and so on.

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

Claims (15)

  1. Getriebepumpenanordnung (1), umfassend ein einziges Gehäuse (2), das eine Vielzahl von Seiten aufweist, wobei sich eine erste Getriebepumpe (8a) im Inneren eines ersten Hohlraums (7a) in dem Gehäuse (2) befindet und sich wenigstens eine zweite Getriebepumpe (8b) im Inneren eines zweiten Hohlraums (7b) in dem Gehäuse (2) befindet, wobei jede Getriebepumpe (8a, 8b) Folgendes umfasst: ein Antriebszahnrad (5a, 5b), das mit einer Antriebswelle (9a, 9b) versehen ist, und wenigstens ein Leerlaufzahnrad (6a, 6b) das in das jeweilige Antriebszahnrad (5a, 5b) eingreift, wobei jede Getriebepumpe (8a, 8b) derart angeordnet ist, dass die Drehung ihrer jeweiligen Antriebswelle (9a, 9b) bewirkt, dass Fluid durch das Gehäuse (2) von wenigstens einem Einlass (11a, 11b, 12a, 12b), der sich in einer Seite des Gehäuses (2) befindet, zu wenigstens einem Auslass (12a, 12b, 11a, 11b) verdrängt wird, der sich in einer Seite des Gehäuses (2) befindet, dadurch gekennzeichnet, dass die erste Getriebepumpe (8a) und die zweite Getriebepumpe (8b) kollateral in Bezug auf die Drehachse jedes Antriebszahnzahnrads (5a, 5b) in dem Gehäuse (2) angeordnet sind, dass jede Antriebswelle (9a, 9b) angeordnet ist, um durch eine jeweilige Drehungsquelle (18a, 18b), die sich außerhalb des Gehäuses (2) befindet, unabhängig angetrieben zu werden, und dass jede Getriebepumpe (8a, 8b) angeordnet ist, um einen unabhängigen Fluidstrom oder unterschiedliche Fluide zu pumpen.
  2. Getriebepumpenanordnung (1) nach dem vorhergehenden Anspruch, wobei wenigstens eine weitere Getriebepumpe im Inneren eines entsprechenden Hohlraums in dem Gehäuse (2) enthalten ist, wobei die/jede weitere Getriebepumpe Folgendes umfasst: ein weiteres Antriebszahnrad, das mit einer weiteren Antriebswelle versehen ist, und wenigstens ein weiteres Leerlaufzahnrad, das in das weitere Antriebszahnrad eingreift, wobei jede weitere Getriebepumpe derart angeordnet ist, dass die Drehung der weiteren Antriebswelle bewirkt, dass Fluid durch das Gehäuse (2) von wenigstens einem Einlass, der sich in einer Seite des Gehäuses (2) befindet, zu wenigstens einem Auslass verdrängt wird, der sich in einer Seite des Gehäuses (2) befindet.
  3. Getriebepumpenanordnung (1) nach einem der vorhergehenden Ansprüche, wobei die erste Getriebepumpe (8a) und die wenigstens eine zweite Getriebepumpe (8b) im Wesentlichen identisch sind.
  4. Getriebepumpenanordnung (1) nach Anspruch 1 oder 2, wobei sich die erste Getriebepumpe (8a) und die wenigstens eine zweite Getriebepumpe (8b) durch wenigstens eines aus der Breite der Zahnräder (5a, 6a, 5b, 6b), der Anzahl der Zähne an den Antriebs- und Leerlaufzahnrädern (5a, 6a, 5b, 6b), dem Durchmesser der Antriebszahnräder (5a, 5b), dem Durchmesser der Leerlaufzahnräder (6a, 6b), Freiräumen in den Pumpen und unterschiedlichen Kühlanordnungen der Zahnräder (5a, 6a, 5b, 6b) voneinander unterscheiden.
  5. Getriebepumpenanordnung (1) nach einem der vorhergehenden Ansprüche, wobei jede Antriebswelle (9a, 9b) derart angeordnet ist, dass sie unabhängig mit der gleichen Drehgeschwindigkeit oder mit unterschiedlichen Drehgeschwindigkeiten angetrieben wird.
  6. Getriebepumpenanordnung (1) nach einem der vorhergehenden Ansprüche, wobei die Antriebswellen (9a, 9b) an der gleichen Seite oder an unterschiedlichen Seiten des Gehäuses angeordnet sind.
  7. Getriebepumpenanordnung (1) nach einem der vorhergehenden Ansprüche, wobei wenigstens ein Einlass (11a, 11b, 12a, 12b) und wenigstens ein Auslass (12a, 12b, 11a, 11b) in dem Gehäuse (2) und gemäß einer oder mehreren der folgenden Anordnungen vorgesehen sind:
    - ein einziger Einlass, der wenigstens für zwei Getriebepumpen (8a, 8b) gemeinsam ist, und ein jeder einzelnen Getriebepumpe (8a, 8b) zugeordneter separater Auslass; oder
    - ein jeder einzelnen Getriebepumpe (8a, 8b) zugeordneter separater Einlass und ein wenigstens zwei Getriebepumpen (8a, 8b) zugeordneter gemeinsamer Auslass; oder
    - im Fall von drei oder mehr Getriebepumpen wenigstens eine Getriebepumpe, die einem eigenen Einlass und einem eigenen Auslass zugeordnet ist, in Kombination mit einer der oben erwähnten Kombinationen für zwei oder mehr weitere Getriebepumpen; oder
    - ein Einlass (11a, 11b, 12a, 12b) und ein Auslass (12a, 12b, 11a, 11b), die jeder Getriebepumpe (8a, 8b) zugeordnet sind, wobei jede Getriebepumpe (8a, 8b) dafür angeordnet ist, in der gleichen Richtung oder in einer Richtung zu pumpen, die sich von jener der wenigstens einen anderen Getriebepumpe (8b, 8a) unterscheidet.
  8. Getriebepumpenanordnung (1) nach einem der vorhergehenden Ansprüche, umfassend wenigstens einen Heizbereich, der gemäß einer der folgenden Anordnungen angeordnet ist:
    - das Gehäuse umfasst einen einzigen Heizbereich, der einer oder mehreren Getriebepumpen (8a, 8b) zugeordnet ist; oder
    - das Gehäuse umfasst eine Vielzahl von separaten Heizbereichen, die jeweils einer einzigen Getriebepumpe (8a, 8b) zugeordnet sind; oder
    - im Fall von drei oder mehr Getriebepumpen umfasst das Gehäuse wenigstens zwei separate Heizbereiche, die jeweils wenigstens einer Getriebepumpe zugeordnet sind.
  9. Getriebepumpenanordnung (1) nach einem der vorhergehenden Ansprüche, wobei das Gehäuse (2) einen wärmeisolierenden Bereich zwischen zwei benachbarten Getriebepumpen (8a, 8b) umfasst.
  10. Getriebepumpenanordnung (1) nach einem der vorhergehenden Ansprüche, wobei eine erste Ebene, die durch die Längsachse des Antriebszahnrads (5a) und die Längsachse des Leerlaufzahnrads (6a) der ersten Getriebepumpe (8a) definiert wird, und eine zweite Ebene, die durch die Längsachse des Antriebszahnrads (5b) und die Längsachse des Leerlaufzahnrads (6b) der zweiten Getriebepumpe (8b) definiert wird, einander mit einem Winkel von weniger als oder gleich 180° schneiden.
  11. Getriebepumpenanordnung (1) nach dem vorhergehenden Anspruch, wobei der Winkel zwischen 90° und 150° beträgt.
  12. Getriebepumpenanordnung (1) nach einem der vorhergehenden Ansprüche, wobei die Getriebepumpenanordnung (1) dafür eingerichtet ist, mit einem Einschnecken- oder Doppelschneckenextruder (16) verbunden zu werden.
  13. Getriebepumpenanordnung (1) nach einem der vorhergehenden Ansprüche, wobei das Gehäuse (2) mit wenigstens einer Abdeckplatte (3, 4) versehen ist, wobei die Antriebswelle (9a, 9b) jeder Getriebepumpe durch die gleiche wenigstens eine Abdeckplatte (3, 4) verläuft.
  14. Getriebepumpenanordnung (1) nach einem der Ansprüche 1 bis 12, wobei das Gehäuse mit einer ersten Abdeckplatte (3) und einer zweiten Abdeckplatte (4) versehen ist, die an gegenüberliegenden Seiten des Gehäuses (2) angeordnet sind, wobei wenigstens eine Antriebswelle (9a, 9b) durch die erste Abdeckplatte (3) verläuft und wenigstens eine andere Antriebswelle durch die zweite Abdeckplatte (4) verläuft.
  15. Getriebepumpenanordnung (1) nach einem der vorhergehenden Ansprüche, wobei die Strömungsrichtung des Fluids durch jede Getriebepumpe (8a, 8b) derart angeordnet ist, dass sie in einer Richtung senkrecht zu einer Ebene verläuft, die durch die Längsachse des Antriebszahnrads (5a, 5b) und die Längsachse des Leerlaufzahnrads (6a, 6b) der jeweiligen Getriebepumpe (8a, 8b) definiert wird.
EP12157371.1A 2012-02-28 2012-02-28 Getriebepumpenanordnung Active EP2634430B1 (de)

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* Cited by examiner, † Cited by third party
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CN104235013B (zh) * 2014-08-16 2016-03-16 湖北钟洋机电科技有限公司 一种油墨抽送机组合泵
US11685095B2 (en) 2015-06-30 2023-06-27 The Goodyear Tire & Rubber Company Method and apparatus for forming tire components using a coextruded strip
EP3112144B1 (de) * 2015-06-30 2020-02-19 The Goodyear Tire & Rubber Company Verbindungsschaltvorrichtung zur herstellung von reifenbestandteilen und verfahren zur herstellung einer reifenlauffläche
GB2627004A (en) * 2023-02-13 2024-08-14 Neatjet Ltd Liquid delivery system

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE443369C (de) * 1927-04-27 Robert Bosch A G Umlaufschmierung mit je einer besonderen Pumpe fuer das Umlaufoel und fuer das Frischoel
WO1996025858A1 (en) * 1995-02-22 1996-08-29 Chris Ritter Process for reducing sterols and free fatty acids from animal fat
DE19857053A1 (de) * 1998-12-10 2000-06-15 Zahoransky Anton Gmbh & Co Verfahren und Vorrichtung zum Herstellen von Bürsten

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1214300A (en) * 1910-11-18 1917-01-30 Philippe Jules Grouvelle System of multiple pumps.
US3427985A (en) 1967-08-09 1969-02-18 Chandler Evans Inc Three-gear pump with movable elements having plurality of sealing forces
FR2524575B1 (fr) 1982-03-30 1986-02-28 Dba Pompe multiple a engrenages
JPS6477778A (en) 1987-09-16 1989-03-23 Kubota Ltd Gear pump
US5004407A (en) * 1989-09-26 1991-04-02 Sundstrand Corporation Method of scavenging air and oil and gear pump therefor
US5174725A (en) * 1991-12-02 1992-12-29 Corning Incorporated Gear pump having multiple pairs of gears
US5842848A (en) 1997-01-03 1998-12-01 Knowles; Frederick W. Compact high-volume gear pump
FR2826069B1 (fr) 2001-06-15 2004-03-12 Renault Pompe volumetrique a double engrenage
ATE499463T1 (de) * 2007-09-13 2011-03-15 Oerlikon Textile Gmbh & Co Kg Vorrichtung zum dosieren und einspeisen flüssiger stoffe

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE443369C (de) * 1927-04-27 Robert Bosch A G Umlaufschmierung mit je einer besonderen Pumpe fuer das Umlaufoel und fuer das Frischoel
WO1996025858A1 (en) * 1995-02-22 1996-08-29 Chris Ritter Process for reducing sterols and free fatty acids from animal fat
DE19857053A1 (de) * 1998-12-10 2000-06-15 Zahoransky Anton Gmbh & Co Verfahren und Vorrichtung zum Herstellen von Bürsten

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