US20110038746A1 - Variable-volume internal gear pump - Google Patents

Variable-volume internal gear pump Download PDF

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Publication number
US20110038746A1
US20110038746A1 US12/863,899 US86389909A US2011038746A1 US 20110038746 A1 US20110038746 A1 US 20110038746A1 US 86389909 A US86389909 A US 86389909A US 2011038746 A1 US2011038746 A1 US 2011038746A1
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United States
Prior art keywords
rotor
teeth
internal gear
gear pump
pressure chamber
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Abandoned
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US12/863,899
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English (en)
Inventor
Siegfried A. Eisenmann
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Individual
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Individual
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Publication of US20110038746A1 publication Critical patent/US20110038746A1/en
Abandoned 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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
    • 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
    • F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/185—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by varying the useful pumping length of the cooperating members in the axial direction

Definitions

  • the invention relates to an internal gear pump, in particular for use as an engine lubrication pump for automobiles, according to the precharacterizing clause of claim 1 .
  • the lubricating oil requirement curve of the engine has a digressive characteristic over the variation of the engine speed. This means that the engine does not have a lubricating oil requirement which is proportional to the speed. Thus, this is substantially smaller at high speed.
  • a known variable-volume internal gear pump controls the specific delivery by rotating the centre distance line of the gear set relative to the suction and pressure chambers in the pump housing in an oil pressure-dependent manner.
  • this has two substantial disadvantages, namely that, in the case of a controlled pump, unavoidable squeezing losses arise through this so-called differential control and the pump therefore develops considerable noises at high speed.
  • the squeezing losses reduce the mechanical efficiency of the pump in this operating range.
  • the squeezing losses give rise to considerable pressure peaks between the teeth, with the result that the components are additionally loaded and the lifetime is reduced.
  • an external gear pump is also known in which the effective tooth width of the pump is reduced with increasing pressure by axial displacement of the two gears relative to one another. Since these gears must be relatively broad, the pump housing with its spectacle-like inner contour must also have a corresponding length. This leads to high manufacturing costs for machining of the housing cavern. In addition, external gear pumps are sensitive to cavitation and hence noise owing to their high delivery pulsation and owing to their radial filling on the suction side.
  • the invention comprises a variable-volume internal gear pump.
  • the advantage of an internal gear pump over other engine lubricating pumps controllable in their specific delivery is in particular that firstly an internal gear pump is superior to the external gear pump with regard to the noise, owing to its low instantaneous delivery pulsation over the angle of rotation of the gears.
  • it can be designed with small numbers of teeth and simultaneously an extremely centric design. Both lead to low tooth engagement frequency and to low hydraulic pressure pulsations.
  • Possible large eccentricity of the rotor set gives rise to very large-volume delivery cells which, at the required displacement volume, lead to small radial dimensions of the pump.
  • the exact internal machining of the pump housing is very simple because in principle only circular manufacturing operations easily implementable on the lathe are required.
  • the variable-volume internal gear pump comprises a housing and a rotor set chamber which is formed in the housing and which has a low pressure chamber with an inlet opening and a high pressure chamber with an outlet opening for a fluid.
  • An inner rotor held in the rotor chamber is rotatable about an axis of rotation and can be driven by a shaft.
  • an outer rotor having an outer rotor axis of rotation arranged eccentrically relative to the axis of rotation is held in a rotatable manner.
  • the inner rotor has outer teeth and the outer rotor has inner teeth such that the outer rotor can rotate with the inner rotor by means of the outer-inner teeth in a constant rotational ratio to one another and, in the case of a rotary drive, forms delivery cells in which the fluid is transported from the low pressure chamber to the high pressure chamber.
  • an adjusting member which produces an axial movement of the inner rotor.
  • the adjusting member is guided in an axially moveable manner in the inner teeth of the outer rotor.
  • the outer rotor has radial channels in the tooth spaces between the teeth of its inner teeth in the region of the low pressure chamber and of the high pressure chamber.
  • the axial position of the inner rotor relative to the outer rotor is variable by the axial movement of the adjusting member so that the volume of the delivery cells can be adjusted thereby and an internal gear pump controllable in its specific delivery is provided.
  • the displacement volume and the specific delivery of the internal gear pump are pressure-dependent, the volume of the delivery cells and hence also the specific delivery decreasing with increasing pressure at the outlet opening and hence with increasing pressure in the high pressure chamber.
  • the outer teeth of the inner rotor have a shape such that axially effective springs, in particular coil springs, can be installed between the shaft driving the inner rotor and the tooth contour of the outer teeth and are arranged there.
  • the springs which act axially on the adjusting member are arranged in the inner rotor between the shaft driving the inner rotor and the tooth contour of the outer teeth.
  • An adjustment space which is connected to the high pressure chamber and axially bounded by the adjusting member is formed within the inner teeth of the outer rotor so that a pressure of the fluid within the adjustment space acts axially on the adjusting member against the spring force of the springs.
  • springs are supported in the axial direction on the shaft, for example via a pot-like intermediate member and a securing ring.
  • three springs, in particular coil springs, are arranged uniformly distributed on the circumference on the inner rotor.
  • the commutation of the change of oil flow from the low pressure chamber—also referred to as suction chamber—to the high pressure chamber—also referred to as pressure chamber—and back from the pressure chamber to the suction chamber is effected in a gentle manner via the outer rotor with its radial channels communicating with the housing, so that any squeezing of the fluid here, in particular of the oil, in the delivery cells is substantially avoided.
  • the adjusting member has outer teeth which fit the inner teeth of the outer rotor with sufficient but small play and are therefore axially displaceable therein while providing a seal.
  • the geometrical shape of the inner-outer teeth i.e. of the outer teeth of the inner rotor and of the inner teeth of the outer rotor which are coordinated with them, is, for example, in the form of epicycloidal or arc-like outer teeth on the inner rotor, which are produced by a self-generating milling movement of the inner teeth of the outer rotor with one tooth more.
  • the outer teeth of the inner rotor therefore have one tooth less than the inner teeth of the outer rotor.
  • This self-generating principle also referred to as self-generating milling, in which a master profile is milled in a counter-wheel, the eccentricity and the rotational ratio being retained, is known from the teaching on tooth systems and need not be explained in more detail here.
  • the outer teeth of the inner rotor have, for example, between 5 and 8 teeth, in particular 6 teeth.
  • the inner rotor is arranged in an axially displaceable and nonrotatable manner substantially runout-free on the shaft driving it.
  • the arrangement in a nonrotable and axially displaceable manner is effected, for example, by means of a feather key.
  • the delivery cells are preferably closed in the axial direction and in a position opposite to the adjusting member by a pinion plate whose inner teeth fit the outer teeth of the inner rotor with sufficient but little play in such a way that the inner rotor is axially moveable within the inner teeth of the pinion plate.
  • Blading corresponding to a centrifugal pump is preferably arranged or formed on the pinion plate.
  • This blading corresponding to a centrifugal pump is in particular axial blading.
  • the pump is so to speak pitched on the suction side so that, with increasing speed, the liquid pressure in the suction chamber increases approximately with the square of the speed. According to the invention, this pump is therefore suitable for extremely high speeds, owing to the avoidance of cavitation bubbles in the oil. This too leads to small space requirement of the pump in the engine.
  • a compensating pressure region which is subjected to high pressure, compensates the axial forces and acts as a compensating surface can be provided on the drive side between the housing and a drive wheel arranged outside the housing on the shaft.
  • this compensating pressure region subjected to high pressure and compensating the axial forces is provided on the side opposite the drive side, between the housing or a cover of the housing and the pot-like intermediate member.
  • the compensating pressure region which is connected to the high pressure region or the high pressure chamber, ensures that a hydraulic compressive force in the compensating pressure region counteracts the hydraulic compressive force in the adjustment space which is likewise subjected to high pressure.
  • FIG. 1 shows an embodiment of the internal gear pump in a longitudinal section through the middle of the shaft and the middle of the inner rotor of the pump at maximum specific delivery;
  • FIG. 2 shows an identical longitudinal section at minimum specific delivery
  • FIG. 3 shows a cross-section through the pump along the section line A-A of FIG. 1 ;
  • FIG. 4 shows a longitudinal section through the middle of the shaft and the middle of the inner rotor along the section line B-B of FIG. 3 at maximum specific delivery;
  • FIG. 5 shows an identical longitudinal section at minimum specific delivery
  • FIG. 6 shows a cross-section along the section line C-C of FIG. 1 ;
  • FIG. 7 shows a diagram of the pinion plate with the axial blading for the axial centrifugal pump, which blading is fixed on said pinion plate;
  • FIG. 8 shows a diagram of the adjusting member
  • FIG. 9 shows an alternative embodiment of the internal gear pump with an alternative compensating pressure region in a longitudinal section at maximum specific delivery
  • FIG. 10 shows an identical longitudinal section at minimum specific delivery
  • FIG. 11 shows a diagram of the outer rotor of the alternative embodiment, in the form of a crown gear.
  • FIGS. 1 to 8 show a common embodiment of the invention in different views, sections and degrees of detail, FIGS. 1 to 8 are described substantially together.
  • FIG. 1 shows the variable-volume internal gear pump in a longitudinal section through the middle of the shaft and the middle of the inner rotor of the pump at maximum specific delivery.
  • the internal gear pump has a two-part housing which is composed of the actual housing 7 and a cover 10 of the housing which are connected to one another by means of screws 19 .
  • a rotor set chamber 40 which has a low pressure chamber 17 with an inlet opening 15 and a high pressure chamber 18 with an outlet opening 16 for a fluid is formed in the housing 7 .
  • the rotor set chamber 40 holds an inner rotor 2 which is rotatable about an axis of rotation Di within the rotor set chamber of the housing 7 and can be driven by a shaft 1 which is passed through the housing 7 and the cover 10 .
  • the inner rotor 2 is axially moveable on the shaft 1 driving it but is arranged in a nonrotatable manner only by means of a feather key 11 , substantially runout-free.
  • the rotor set chamber 40 also holds a rotatable outer rotor 3 having an outer rotor axis of rotation Da arranged eccentrically relative to the axis of rotation Di, as shown in FIGS. 3 , 4 and 6 .
  • the inner rotor 2 has outer teeth 33 —namely comprising six teeth—and the outer rotor 3 has inner teeth 34 , namely comprising seven teeth (FIGS.
  • the outer rotor 3 has radial channels 41 arranged in the seven tooth spaces between the teeth of the inner teeth 34 in the region of the low pressure chamber 17 and of the high pressure chamber 18 ( FIGS. 2 , 3 and 5 ).
  • FIGS. 1 , 2 and 5 show an adjusting member 5 according to the invention which produces an axial movement of the inner rotor 2 .
  • the adjusting member 5 is guided in an axially moveable manner in the inner teeth 34 of the outer rotor 3 , the adjusting member 5 having outer teeth 34 a which fit the inner teeth 34 of the outer rotor 3 with sufficient but little play and are therefore axially moveable therein while providing a seal.
  • FIG. 8 shows the adjusting member 5 with its outer teeth 34 a in a detailed view.
  • the axial position of the inner rotor 2 relative to the outer rotor 3 is adjustable by the axial movement of the adjusting member 5 , with the result that the volume of the delivery cells 30 , 31 is variable.
  • three axially acting coil springs 8 are installed between the shaft 1 driving the inner rotor 2 and the tooth contour of the outer teeth 33 , as shown in FIGS. 1 , 3 and 6 .
  • the outer teeth 33 of the inner rotor 2 have a corresponding shape.
  • the three coil springs 8 are supported via a pot-like intermediate member 6 ( FIGS. 1 and 5 ) and a securing ring 12 ( FIG. 1 ) in the axial direction on the shaft 1 .
  • the delivery cells 30 , 31 are closed in the axial direction and in a position opposite to the adjusting member 5 by a pinion plate 4 and 46 , which is evident in FIG. 1 and shown in detail in FIG. 7 .
  • the inner teeth 32 of the pinion plate 4 and 46 fit the outer teeth 33 of the inner rotor 2 with sufficient but little play, in such a way that the inner rotor 2 is axially moveable within the inner teeth 32 of the pinion plate 4 and 46 .
  • Blading 42 ( FIGS. 5 and 7 ) corresponding to a centrifugal pump 21 ( FIG. 1 ) is arranged on the pinion plate 4 and 46 .
  • the direction of rotation of the rotor set of the pump may be in the given direction of the arrows 43 ( FIG. 3 ), 44 ( FIG. 6) and 45 ( FIGS. 5 and 7 ), so that the respective suction side and pressure side corresponding to the expanding and compressing delivery cells of the teeth are clearly shown.
  • the intake connection on the inlet opening 15 which forms the suction opening is arranged in the cover 10 .
  • a suction space 20 surrounds the pot-like intermediate member 6 and is at the same time the suction side of the blading 42 of the axial centrifugal pump 21 .
  • the pressure side of this axial centrifugal pump 21 is at the same time the low pressure chamber 17 of the internal gear pump, which low pressure chamber acts as a suction chamber.
  • the oil is sucked into the expanding delivery cells 30 against the centrifugal force via the radial channels 41 of the outer rotor 3 .
  • the axial impeller of the centrifugal pump 21 runs in relation to the number of teeth of the rotor set by a factor of 7:6 faster than the outer rotor 3 , so that the centrifugal pressure in the radial channels 41 of the outer rotor 3 is more than compensated by the pump pressure of the impeller of the centrifugal pump 21 .
  • the compressing delivery cells 31 (cf. FIG. 3 ) displace the oil into the high pressure chamber 18 towards the outlet opening 16 .
  • the rotor set has the maximum tooth width when the coil springs 8 are able to push the inner rotor 2 and hence the adjusting member 5 completely to the left, almost up to impact on the housing 7 .
  • This is the case when a very low pressure prevails in the adjustment space 25 , clearly shown in FIG. 2 .
  • the coil springs 8 are prevented by a snap ring 13 from pressing the adjusting member 5 axially onto the housing 7 , so that no unnecessary frictional loss occurs at zero pressure, i.e. when idling.
  • This snap ring 13 and the securing ring 12 in the form of a Seeger circlip ring, both fixed on the shaft 1 should be chosen so that, between the packet consisting of, in particular, the adjusting member 5 , the inner rotor 2 , the coil springs 8 , the pot-like intermediate member 6 and the pinion 4 , 46 , there is still sufficient axial play between the adjusting member 5 and the housing 7 .
  • this internal gear pump is now connected on the high pressure side at the outlet opening 16 to the lubricating oil circulation, for example of an internal combustion engine
  • the oil pressure in the high pressure chamber 18 increases according to the absorption curve of the motor with increasing motor speed and hence (in the case of a rigid drive) pump speed.
  • this high pressure also prevails in the adjustment space 25 and, depending on the speed level and hence the high pressure level, pushes the adjusting member 5 and with it the inner rotor 2 to the right against the spring force.
  • the outer rotor 3 maintains its axial position, owing to the small axial play between the housing 7 and the pinion plate 4 and 46 .
  • the effective tooth width of the rotor set is reduced thereby and the specific delivery is reduced, as illustrated in FIG. 2 .
  • a compensating pressure region 22 which is subjected to high pressure via the channel 23 ( FIG. 2 ) is provided on the drive side between a drive wheel 9 ( FIG. 1 ), arranged outside the housing 7 on the shaft 1 , and the housing 7 .
  • This compensating pressure region 22 is dimensioned so that the axial force it exerts on the shaft 1 via a central screw 14 to the left in FIG. 1 is somewhat smaller than the total hydrostatic axial force of the rotor system to the right.
  • the lubrication and the cooling of an annular sealing surface 47 between the drive wheel 9 and the housing 7 , which sealing surface seals the compensating pressure region 22 from the outside, can be optimized.
  • FIGS. 9 to 11 corresponds in substantial parts to the embodiments of the internal gear pump which are illustrated in FIGS. 1 to 8 , and it is for this reason that in some cases only the substantial differences are discussed below.
  • the alternative embodiment of the internal gear pump has the housing 7 with the cover 10 belonging to the housing.
  • the housing is provided with the rotor set chamber 40 , which has the low pressure chamber 17 with the inlet opening 15 and the high pressure chamber 18 with the outlet opening 16 for a fluid.
  • the rotor set chamber 40 holds the inner rotor 2 which is rotatable about the axis of rotation D i and can be driven by the shaft 1 .
  • the outer rotor 3 a rotatably held in the rotor set chamber 40 has an outer rotor axis of rotation arranged eccentrically relative to the axis of rotation D i .
  • the inner rotor 2 has outer teeth 33
  • the outer rotor 3 a has inner teeth 34 , such that the outer rotor 3 a rotates with the inner rotor 2 by the outer-inner teeth 33 , 34 in a constant rotational ratio and, in the case of a rotary drive, forms the delivery cells 30 , 31 in which the fluid is transported from the low pressure chamber 17 to the high pressure chamber 18 .
  • the adjusting member 5 guided in an axially moveable manner in the inner teeth 34 of the outer rotor 3 , an axial movement of the inner rotor 2 can be produced.
  • FIG. 9 shows the internal gear pump at maximum specific delivery
  • FIG. 10 shows said pump at minimum specific delivery.
  • the outer teeth 33 of the inner rotor 2 have a shape such that the axially effective springs 8 are located between the shaft 1 driving the inner rotor 2 and the tooth contour of the outer teeth 33 .
  • the alternative embodiment of the internal gear pump of FIGS. 9 and 10 corresponds to the embodiment of FIGS. 1 to 8 .
  • the outer rotor 3 a likewise has radial channels 41 a in the tooth spaces between its inner teeth 34 in the region of the low pressure chamber 17 and of the high pressure chamber 18 , but these radial channels 41 a are not formed as radial bores in the middle of the outer rotor 3 a , as can be seen in the first embodiment and as can be seen in FIG. 1 , but the radial channels 41 a are present as slot-like radial recesses at the edge of the outer rotor 3 a .
  • the outer rotor 3 a is in the form of a crown gear, as shown in FIG. 11 in an individual front view and an individual side view. An advantage of this arrangement consists in the easier producability of the radial channels 41 a.
  • annular intermediate plate 50 is provided between the cover 10 and the remaining housing 7 , which intermediate plate has passages for the channels, the pattern of holes corresponding substantially to the pattern of holes of the housing 7 .
  • the springs 8 are likewise supported via a pot-like intermediate member 6 a and a securing ring 12 in the axial direction on the shaft 1 , but the pot-like intermediate member 6 a has an outer shape—in particular cylindrical outer shape—such that the intermediate member 6 a touches the cover 10 of the housing 7 while providing a radial seal.
  • a piston ring 48 is provided for sealing.
  • a channel 49 which connects the compensating pressure region 22 a to the high pressure chamber 18 is provided.
  • This compensating pressure region 22 a is dimensioned so that hydraulic pressure in the compensating pressure region 22 a counteracts the hydraulic pressure in the adjustment space 25 likewise subjected to high pressure.
  • the compensating pressure region 22 a was moved from the side of the drive wheel 9 , FIG. 1 , to the opposite side. This has in particular the advantage that the drive wheel 9 in the embodiment of FIGS. 9 to 11 no longer has a sealing function and can be easily replaced by another drive wheel 9 on the shaft 1 .

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
US12/863,899 2008-01-21 2009-01-21 Variable-volume internal gear pump Abandoned US20110038746A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP08100673.6 2008-01-21
EP08100673 2008-01-21
PCT/EP2009/050630 WO2009092719A2 (de) 2008-01-21 2009-01-21 Volumenveränderbare innenzahnradpumpe

Publications (1)

Publication Number Publication Date
US20110038746A1 true US20110038746A1 (en) 2011-02-17

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ID=39523755

Family Applications (1)

Application Number Title Priority Date Filing Date
US12/863,899 Abandoned US20110038746A1 (en) 2008-01-21 2009-01-21 Variable-volume internal gear pump

Country Status (5)

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US (1) US20110038746A1 (de)
EP (1) EP2235374B1 (de)
AT (1) ATE517262T1 (de)
CA (1) CA2712550A1 (de)
WO (1) WO2009092719A2 (de)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20110125332A1 (en) * 2009-11-20 2011-05-26 Halliburton Energy Services, Inc. Systems and Methods for Specifying an Operational Parameter for a Pumping System
CN102135096A (zh) * 2011-03-13 2011-07-27 深圳乐满商务服务有限公司 偏心式双转子泵的外驱动传动结构
US20130315770A1 (en) * 2012-05-24 2013-11-28 Gm Global Technology Operation Llc Pump assembly for a vehicle
US11319811B2 (en) * 2019-09-27 2022-05-03 Subaru Corporation Internal gear pump

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2585719A2 (de) 2010-06-23 2013-05-01 Siegfried A. Eisenmann Stufenlos volumenveränderbare hydrostatische kreiskolbenmaschine
EP2614274A1 (de) 2010-09-06 2013-07-17 Siegfried A. Eisenmann Hydrostatischer antrieb für ein kraftfahrzeug
DE102013212002A1 (de) * 2013-06-25 2015-01-08 Bayerische Motoren Werke Aktiengesellschaft Innenzahnradpumpe für die Förderung von Fluid
CN104976112B (zh) * 2014-04-01 2018-12-18 松下知识产权经营株式会社 液体用泵和兰金循环装置
US11965509B2 (en) * 2022-02-28 2024-04-23 Genesis Advanced Technology Inc. Energy transfer machine for corrosive fluids

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US2484789A (en) * 1944-04-15 1949-10-11 Hill Lab Variable displacement pump and motor
US4740142A (en) * 1985-08-09 1988-04-26 Rohs Hans Gunther Variable capacity gear pump with pressure balance for transverse forces
US6244839B1 (en) * 1997-11-14 2001-06-12 University Of Arkansas Pressure compensated variable displacement internal gear pumps
WO2006066403A1 (en) * 2004-12-22 2006-06-29 Magna Powertrain Inc. Variable capacity gerotor pump
US7179070B2 (en) * 2004-04-09 2007-02-20 Hybra-Drive Systems, Llc Variable capacity pump/motor
US20070065327A1 (en) * 2003-09-01 2007-03-22 Mitsubishi Materials Corporation Oil pump rotor assembly
US7195467B2 (en) * 2002-06-26 2007-03-27 Vhit S.P.A. Internal gear machine with variable capacity

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JPS5647692A (en) * 1979-09-27 1981-04-30 Ishikawajima Harima Heavy Ind Co Ltd Variable displacement type internal gear pump
DE10352029A1 (de) * 2003-11-07 2005-06-16 SCHWäBISCHE HüTTENWERKE GMBH Verdrängerpumpe mit Vorladeeinrichtung

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US2484789A (en) * 1944-04-15 1949-10-11 Hill Lab Variable displacement pump and motor
US4740142A (en) * 1985-08-09 1988-04-26 Rohs Hans Gunther Variable capacity gear pump with pressure balance for transverse forces
US6244839B1 (en) * 1997-11-14 2001-06-12 University Of Arkansas Pressure compensated variable displacement internal gear pumps
US7195467B2 (en) * 2002-06-26 2007-03-27 Vhit S.P.A. Internal gear machine with variable capacity
US20070065327A1 (en) * 2003-09-01 2007-03-22 Mitsubishi Materials Corporation Oil pump rotor assembly
US7179070B2 (en) * 2004-04-09 2007-02-20 Hybra-Drive Systems, Llc Variable capacity pump/motor
WO2006066403A1 (en) * 2004-12-22 2006-06-29 Magna Powertrain Inc. Variable capacity gerotor pump
US7832997B2 (en) * 2004-12-22 2010-11-16 Magna Powertrain, Inc. Variable capacity gerotor pump

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20110125332A1 (en) * 2009-11-20 2011-05-26 Halliburton Energy Services, Inc. Systems and Methods for Specifying an Operational Parameter for a Pumping System
US8543245B2 (en) * 2009-11-20 2013-09-24 Halliburton Energy Services, Inc. Systems and methods for specifying an operational parameter for a pumping system
CN102135096A (zh) * 2011-03-13 2011-07-27 深圳乐满商务服务有限公司 偏心式双转子泵的外驱动传动结构
US20130315770A1 (en) * 2012-05-24 2013-11-28 Gm Global Technology Operation Llc Pump assembly for a vehicle
CN103423155A (zh) * 2012-05-24 2013-12-04 通用汽车环球科技运作有限责任公司 用于车辆的泵组件
US9488172B2 (en) * 2012-05-24 2016-11-08 GM Global Technology Operations LLC Pump assembly for a vehicle
US11319811B2 (en) * 2019-09-27 2022-05-03 Subaru Corporation Internal gear pump

Also Published As

Publication number Publication date
WO2009092719A2 (de) 2009-07-30
EP2235374B1 (de) 2011-07-20
ATE517262T1 (de) 2011-08-15
CA2712550A1 (en) 2009-07-30
EP2235374A2 (de) 2010-10-06
WO2009092719A3 (de) 2009-12-03

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