EP3214310A1 - Système de rotor pour une pompe et groupe pompe - Google Patents

Système de rotor pour une pompe et groupe pompe Download PDF

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Publication number
EP3214310A1
EP3214310A1 EP17158319.8A EP17158319A EP3214310A1 EP 3214310 A1 EP3214310 A1 EP 3214310A1 EP 17158319 A EP17158319 A EP 17158319A EP 3214310 A1 EP3214310 A1 EP 3214310A1
Authority
EP
European Patent Office
Prior art keywords
axial
drive shaft
rotor
section
pump
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.)
Withdrawn
Application number
EP17158319.8A
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German (de)
English (en)
Inventor
Andreas Blechschmidt
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.)
Nidec GPM GmbH
Original Assignee
Nidec GPM GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Nidec GPM GmbH filed Critical Nidec GPM GmbH
Publication of EP3214310A1 publication Critical patent/EP3214310A1/fr
Withdrawn legal-status Critical Current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
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
    • F04C15/0076—Fixing rotors on shafts, e.g. by clamping together hub and shaft
    • 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
    • F04C2230/00—Manufacture
    • F04C2230/60—Assembly methods
    • F04C2230/602—Gap; Clearance
    • 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
    • F04C2230/00—Manufacture
    • F04C2230/60—Assembly methods
    • F04C2230/603—Centering; Aligning
    • 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
    • F04C2240/20—Rotors
    • 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
    • F04C2240/60—Shafts

Definitions

  • the present invention initially relates to a rotor assembly for a pump, for example for a ring gear machine in a pump unit. Furthermore, the invention relates to a pump unit, which comprises the rotor assembly according to the invention.
  • gear pumps are known in which a gear pump is designed for conveying a medium.
  • Such gear pumps are designed for example as a toothed ring machine, which is also referred to as a gerotor.
  • An inner toothed ring forms a rotor of the pump, on which acts as a result of the generated pressure, a transverse force, which must be counteracted by a corresponding storage. If this lateral force can not be compensated sufficiently, there will be a displacement of the rotor, which in particular can negatively affect the running properties.
  • the JP 2012-026294 A shows a fluid pump with a ring gear machine whose inner ring is mounted on a drive shaft and on a housing formed on a stub axle.
  • the JP 2015-048784 A teaches an electric oil pump with a ring gear machine.
  • a drive shaft of the oil pump is supported at an axial end of the drive shaft in a housing.
  • an electric oil pump in which a housing has a bearing portion for supporting a tip end portion of a shaft to supplementally support the shaft.
  • the EP 1 580 431 A1 , the JP 2015-108306 A and the EP 2 570 672 A2 show gear pumps in which an outer ring gear is supported by a sliding bearing.
  • the object of the present invention is to minimize the undesirable influence of a transverse force on the rotor of a pump with little effort.
  • the rotor assembly according to the invention is provided for a pump for conveying a medium.
  • the pump preferably forms a pump unit together with an electric motor.
  • the rotor assembly comprises a rotor which serves by rotation for the direct delivery of the medium and thus forms a pump rotor.
  • the design of the rotor is to be selected according to the applied principle of the pump. If the pump is formed, for example, by a gear pump, then the rotor is a gear or a toothed ring.
  • the medium is preferably a liquid, more preferably an oil.
  • the rotor has an opening with which it sits non-rotatably on a drive shaft, so that a rotation of the drive shaft leads to a rotation of the rotor.
  • a torque from the drive shaft to the rotor is transferable.
  • the drive shaft protrudes at least into the opening or preferably through it.
  • the opening forms an axis of rotation of the rotor.
  • the opening constitutes a hub of the rotor and is preferably continuous.
  • the drive shaft forms a component of the rotor assembly.
  • the rotor in an operating state at an axial position of the drive shaft relative to the drive shaft about any axis perpendicular to the drive shaft tiltable, d. H. tiltable.
  • the said axis of tiltability intersects the drive shaft in said axial position of the drive shaft.
  • the said axis of tiltability has an arbitrary angle of rotation with respect to the drive shaft, so that the tiltability of the rotor is independent of the rotational angle of the drive shaft.
  • the operating condition is a condition in which the rotor is fully mounted on the drive shaft so that the rotor is non-rotatably mounted on the drive shaft and the rotor assembly is usable for its function in the pump.
  • the rotor can be tilted at said axial position about each axis perpendicular to the drive shaft yielding the lateral force, the rotor can follow an occurring lateral force without tilting with respect to the axis of rotation.
  • the lateral force yielding drive shaft is then no longer exactly in the axis of rotation.
  • the rotor due to its tiltability relative to the drive shaft can remain in the axis of rotation, its function in the pump is not limited. In particular, it does not happen that the rotor rotates in the event of tilting with respect to the axis of rotation with increased friction compared to other stationary or rotating components of the pump. Rather, the rotor shifts parallel to its main extension plane.
  • a particular advantage of the rotor assembly according to the invention is that by a low-cost warranty of said tiltability storage of the drive shaft and the rotor is not necessary on both sides of the rotor. It only requires a bearing on one side of the rotor, since it is the rotor according to the invention allows to tilt against the lateral force yielding drive shaft.
  • the tiltability of the rotor relative to the drive shaft is limited, so that the rotor can be tilted up to a maximum tilt angle relative to the drive shaft.
  • the maximum tilt angle is preferably so large that a maximum occurring during operation of the rotor assembly bending of the drive shaft can be compensated so that the rotor does not tilt with respect to the axis of rotation.
  • the maximum tilt angle is preferably at most 5 ° and more preferably at most 1 °.
  • the maximum tilt angle is preferably at least 0.1 ° and more preferably at least 0.5 °.
  • the opening preferably has a first axial section, which also forms a first axial section of the drive shaft.
  • a gap extending around the drive shaft is formed in the opening of the rotor between the rotor and the drive shaft, which constitutes a play in the radial direction between the rotor and the drive shaft.
  • the circumferential gap is increasingly formed in the axial direction.
  • the radially extending size of the gap i. H. the gap width in the axial direction too.
  • Said radial direction is related to the axis of rotation; ie that the radial direction perpendicular to Is rotational axis, namely in the direction of the radii, starting from the axis of rotation.
  • Said axial direction is the direction of the axis of rotation.
  • the first axial section preferably comprises at least half of the axial length of the opening, but may also comprise the entire axial length of the opening.
  • the drive shaft has a convex longitudinal section in an axial region carrying the rotor, in particular in the first axial section.
  • the longitudinal section lies in a plane in which the axis of rotation is located.
  • the convexity is formed with respect to the shaft bearing surface in the opening of the rotor and allows the tilting of the rotor relative to the drive shaft.
  • the rotor has a convex longitudinal section in the region of its opening, in particular in the first axial section of its opening.
  • the longitudinal section lies in a plane in which the axis of rotation is located.
  • the convexity is formed with respect to the drive shaft and allows the tilting of the rotor relative to the drive shaft.
  • the opening preferably further has a second axial section, which also forms a second axial section of the drive shaft.
  • the opening has a non-circular cross-section, to which the drive shaft has a corresponding cross-section, so that the rotor sits in the second axial section in a form-fitting manner on the drive shaft and torque can be transmitted from the drive shaft to the rotor.
  • the cross section is in one Plane which is perpendicular to the drive shaft or perpendicular to the opening.
  • the non-circular cross section of the opening or the corresponding cross section of the drive shaft is preferably formed by a polygonal or by a single or multiple flat.
  • the polygon is preferably formed by a square.
  • the multiple flat is preferably formed by a two-flat.
  • a game is present, which is preferably between 0.05 mm and 0.5 mm.
  • the drive shaft preferably further comprises an axial motor portion, in which the drive shaft forms a component of an electric motor for driving the pump; in particular a motor shaft of a motor rotor.
  • the axial motor portion is axially spaced from the first axial portion and the second axial portion.
  • the axial motor portion is axially spaced from the rotor of the pump and the opening thereof.
  • a torque is generated and transmitted to the drive shaft.
  • the torque is transmitted further from the drive shaft to the rotor of the pump.
  • the first axial section of the drive shaft is preferably arranged axially between the second axial section and the axial motor section.
  • the second axial section of the drive shaft is preferably formed on one of the two axial ends of the drive shaft.
  • the drive shaft protrudes with its axial end preferably completely into the opening of the rotor. It can protrude with an axial clearance through the opening of the rotor.
  • the opening and the drive shaft preferably each have a circular cross section.
  • the cross section lies in a plane which is perpendicular to the drive shaft or perpendicular to the opening.
  • the first axial section is preferably divided into a first axial section and into a second axial section.
  • the gap width is constant in the two axial sections in the axial direction, but differs between the two axial sections, so that the circumferential gap in the axial direction is increasingly formed.
  • a step of the gap is formed between the two axial sections.
  • the stepped gap can be given by the fact that the opening in the rotor has different diameters in the two axial sections and / or that the drive shaft has different diameters in the two axial sections.
  • the circumferential gap preferably has the shape of a hollow cylinder in the two axial sections.
  • the opening in the rotor preferably has the shape of a cylinder in the first axial section.
  • the opening in the two axial sections preferably has the shape of a cylinder.
  • the drive shaft preferably has the shape of a cylinder in the first axial section.
  • the drive shaft in the two axial sections has different diameters, so has the drive shaft in the two Axial sections preferably each have the shape of a cylinder.
  • the second axial section is preferably arranged between the first axial section and the second axial section.
  • the second axial section is located in a central axial region of the opening.
  • the second axial portion is located in an axial center of the opening.
  • the circumferential gap in the second axial section has a smaller size extending in the radial direction, i. H. a smaller gap width, as in the first axial section on.
  • the play in the radial direction between the drive shaft and the rotor in the second axial portion is smallest.
  • the play in the radial direction between the drive shaft and the rotor in the second axial section is preferably minimal.
  • the circumferential gap has in the second axial portion of a radially extending size, d. H. a gap width, which is preferably between one-thousandth and one-hundredth of the diameter of the drive shaft in the second axial section.
  • the circumferential gap has in the second axial portion of a radially extending size, d. H. a gap width which is preferably between 0.01 mm and 0.07 mm, more preferably between 0.03 mm and 0.05 mm.
  • the circumferential gap has in the first axial section a radially extending size, ie, a gap width, preferably between one hundredth and one tenth of the diameter of the drive shaft in the first axial section is.
  • the circumferential gap has, in the second axial section, a size which extends in the radial direction, ie a gap width which is preferably between 0.08 mm and 0.3 mm, particularly preferably between 0.1 mm and 0.2 mm.
  • the first axial section preferably has an axial length that is between one tenth and five tenths of the axial length of the opening. This axial length is particularly preferably between two tenths and four tenths of the axial length of the opening.
  • the second axial section preferably has an axial length that is between one tenth and five tenths of the axial length of the opening. This axial length is particularly preferably between two tenths and four tenths of the axial length of the opening.
  • the second axial section preferably has a technically minimum axial length such that it forms a peripheral edge against which the drive shaft and the rotor abut in the radial direction with minimal play. This edge forms the fulcrum for tilting the rotor.
  • the second axial portion preferably has an axial length that is between one tenth and five tenths of the axial length of the opening. This axial length is particularly preferably between two tenths and four tenths of the axial length of the opening.
  • the opening further preferably has an axial insertion portion, in which it is widened with respect to the circumferential gap.
  • the opening is widened in a cone shape with respect to the circumferential gap.
  • the Drive shaft protrudes into the opening of the rotor starting at the introduction section.
  • the drive shaft preferably has a smaller extent in the radial direction than in the first axial section.
  • the drive shaft preferably has an outer diameter of the non-circular cross-sectional shape which is smaller than the diameter in the first axial section, in particular smaller than the diameter in the second axial section section.
  • the drive shaft preferably has a circumferential phase between the first axial section and the second axial section, which is preferably formed at the transition from the greater extent in the radial direction in the first axial section to the smaller extent in the radial direction in the second axial section.
  • This phase is a circumferential slope of the described transition. Due to the phase sufficient tiltability is ensured without the need for a larger gap width in the second axial section.
  • a free space extending in the axial direction is preferably formed between the drive shaft and the rotor. This clearance leads to a play in the axial direction between the drive shaft and the rotor, which prevents a striking lateral abutment when tilting the rotor.
  • the drive shaft is formed by a motor shaft of an electric motor.
  • the electric motor is to drive of the rotor and thus designed to drive the pump.
  • the motor shaft has the above-mentioned axial motor portion and an axial pump portion, wherein the axial pump portion is seated in the opening of the rotor.
  • the motor shaft preferably has exactly two axial bearing sections in which it can be stored rotatably; in which it is designed in particular for inclusion in a plain bearing or in a rolling bearing.
  • One of the exactly two bearing sections is arranged at an axial end of the motor shaft opposite the pump section, so that it is located in the axial motor section.
  • the other of the exactly two bearing sections is arranged between the axial motor section and the axial pump section.
  • the drive shaft is preferably located at that axial end of the drive shaft, which is located in the axial pump section, no bearing section, d. H. the drive shaft is not formed there for rotary bearing. It is namely a particular advantage of the rotor assembly according to the invention that can be dispensed with a rotary bearing of the drive shaft at this axial end, since the drive shaft can bend slightly under load, without the rotor is tilted relative to the axis of rotation.
  • the rotor is designed according to the realized operating principle of the pump, which may be any working principle with rotating components.
  • the pump is preferably a gear pump, in particular a ring gear machine, which is also referred to as a gerotor.
  • the rotor is preferably formed by a gear, in particular by an inner toothed ring.
  • the rotor in particular the inner toothed ring, is designed to have an axial play in the pump of preferably less than 0.1 mm, particularly preferably less than 0.02 mm.
  • the pump is preferably a pump for conveying a working fluid in a motor vehicle; for example, an oil pump.
  • the pump unit according to the invention serves to convey a medium.
  • the pump unit comprises a pump formed in an axial pump section of the pump unit for direct delivery of a medium.
  • the pump unit further comprises an electric motor formed in an axial motor section of the pump unit for driving the pump.
  • the pump unit comprises the rotor arrangement according to the invention.
  • the drive shaft of the rotor assembly forms a motor shaft of the electric motor and is non-rotatably connected to the rotor arranged in the pump.
  • the electric motor preferably has a motor rotor comprising the motor shaft and a motor stator.
  • the rotor of the pump is preferably formed by an inner ring, wherein the pump preferably further comprises an outer ring, wherein the inner ring and the outer ring form a toothed ring machine.
  • the pump unit preferably comprises one of the preferred embodiments of the rotor arrangement according to the invention. Moreover, the pump unit preferably also has those features which are specified in connection with the rotor arrangement according to the invention and its preferred embodiments.
  • the pump unit is preferably an electric oil pump for a motor vehicle.
  • Fig. 1 shows a side view of a preferred embodiment of a pump assembly according to the invention, which is designed to convey oil in a motor vehicle.
  • the pump unit comprises a pump 01 and an electric motor 02 for driving the pump 01.
  • the pump 01 comprises an inlet 03 and an outlet 04 for the oil to be pumped.
  • Fig. 2 shows that in Fig. 1 shown pump unit in a longitudinal sectional view.
  • the electric motor 02 comprises a motor stator 06 and a motor rotor 07.
  • the motor rotor 07 comprises a motor shaft 08, which simultaneously forms a drive shaft of the pump 01.
  • the pump 01 comprises an inner ring 09 and an outer ring 11, which form a toothed ring machine.
  • Of the Inner ring 09 is non-rotatably mounted on the drive shaft 08 and forms a rotor of the pump 01st
  • the drive shaft 08 is rotatably mounted at exactly two axial positions, each with a rolling bearing 12; namely on both sides of the motor rotor 07, so that one of the two rolling bearings 12 is arranged axially between the motor motor 07 and the inner ring 09. Consequently, the drive shaft 08 is supported only on one of the two sides of the inner ring 09, so that an arranged in the pump 01 axial end 13 of the drive shaft 08 is not stored.
  • a pressure acting on the oil to be delivered between 3 bar and 25 bar can be generated. Due to the principle of action of the ring gear formed by the inner ring 09 and the outer ring 11 acts on the inner ring 09, a transverse force on the drive shaft 08 from the direction of the inlet 03. Since the drive shaft 08 is not supported at its axial end 13, there is a bending of Drive shaft 08 in the region of the axial end 13, so that the drive shaft 08 is tilted in this area relative to a rotational axis 14. However, this tilting does not mean that the inner ring 09 is tilted relative to the rotational axis 14, since according to the invention the inner ring 09 is tiltable relative to the drive shaft 08.
  • This tiltability is independent of the angle of rotation of the drive shaft 08, so that the inner ring 09 is tiltable at any angle of rotation of the drive shaft 08 relative to the drive shaft 08.
  • This tiltability is made possible by a special design of the drive shaft 08 in its inner ring 09 supporting axial region.
  • This axial region initially comprises a first axial section 16 and a second axial section 17.
  • the second axial section 17 is used for transmission a torque from the drive shaft 08 on the inner ring 09, for which the drive shaft 08 in the second axial section 17 has a square as a cross section, which sits with a radial clearance of a few tenths of a millimeter in the inner ring 09.
  • a drive shaft 08 receiving opening 18 in the inner ring 09 has in the second axial section 17 has a four-sided cross section, so that a rotationally fixed connection between the drive shaft 08 and the inner ring 09 is formed.
  • the first axial section 16 is divided into a first axial section 19 and a first axial section 21.
  • the drive shaft 08 and the opening 18 each have a circular cross-section.
  • a circumferential gap 22 (shown in FIG Fig. 3 ) exists, so that a clearance in the radial direction between the drive shaft 08 and the inner ring 09 is given.
  • the circumferential gap 22 in the first axial portion 19 is about 0.15 mm and in the second axial portion 21 only about 0.04 mm wide. Consequently, the gap 22 in the first axial section 19 in the radial direction is greater than in the second axial section 21.
  • the circumferential gap 22 can also be described as a cutout in the drive shaft 08.
  • the drive shaft 08 and a rotor of the pump 01 performing inner ring 09 form a rotor assembly according to the invention, which is characterized by the Verkipples of the rotor 09 relative to the drive shaft 08 regardless of the rotation angle of the drive shaft 08.
  • Fig. 3 shows the formed from the drive shaft 08 and the one rotor representing inner ring 09 rotor assembly of the Fig. 1 and Fig. 2 shown pump unit in detail.
  • the circumferential gap 22 is only about 0.04 mm wide. Consequently, the circumferential gap 22 is very small, so that the play in the radial direction between the drive shaft 08 and the inner ring 09 in the second axial section 21 is very small.
  • the second axial section 21 forms the fulcrum for the tilting of the inner ring 09 relative to the drive shaft 08.
  • the second axial section 21 has an axial length a which is approximately one third of an axial length b of the opening 18.
  • the opening 18 On the electric motor 02 (shown in Fig. 2 ) facing side, the opening 18 has a cone-shaped extension 24 in the form of a phase.
  • the drive shaft 08 has at the end of the first axial portion 16, which faces the second axial portion 17, a phase 26, which also contributes to the tiltability.
  • a phase 26 which also contributes to the tiltability.
  • an axially extending clearance 27 is present, so that between the drive shaft 08 and the inner ring 09 is also a game in the axial direction, which also contributes to Verkipp sadness.
  • Fig. 4 shows that in Fig. 1 and Fig. 2 shown pump unit in a perspective detail view, in which the pump 01 is shown in an open state.
  • the toothed ring machine formed by the inner ring 09 and the outer ring 11 and the drive shaft 08 can be seen.
  • the drive shaft 08 has in the second axial portion 17 (shown in FIG Fig. 3 ) has a square-shaped cross section.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Rotary Pumps (AREA)
EP17158319.8A 2016-03-04 2017-02-28 Système de rotor pour une pompe et groupe pompe Withdrawn EP3214310A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102016103902.0A DE102016103902B4 (de) 2016-03-04 2016-03-04 Rotoranordnung für eine Pumpe sowie Pumpenaggregat

Publications (1)

Publication Number Publication Date
EP3214310A1 true EP3214310A1 (fr) 2017-09-06

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ID=58192159

Family Applications (1)

Application Number Title Priority Date Filing Date
EP17158319.8A Withdrawn EP3214310A1 (fr) 2016-03-04 2017-02-28 Système de rotor pour une pompe et groupe pompe

Country Status (2)

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EP (1) EP3214310A1 (fr)
DE (1) DE102016103902B4 (fr)

Citations (10)

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DE102004028127A1 (de) * 2003-06-11 2005-01-05 Denso Corp., Kariya Kraftstoffeinspritzpumpe mit einem inneren Aufbau zum Absorbieren einer Winkelverlagerung
EP1580431A1 (fr) 2002-12-24 2005-09-28 Koyo Seiko Co., Ltd. Pompe a engrenages interne electrique
JP2012026294A (ja) 2010-07-20 2012-02-09 Aisin Seiki Co Ltd 流体ポンプ
DE102011011384A1 (de) * 2011-02-17 2012-08-23 Festool Gmbh Hand-Werkzeugmaschine mit einem Lamellenmotor aus einem Nicht-Metall
DE102012204191A1 (de) 2011-03-30 2012-10-04 Hitachi Automotive Systems, Ltd. Elektrische Ölpumpe
EP2570672A2 (fr) 2011-09-17 2013-03-20 Jtekt Corporation Pompe à huile électrique
US20140178234A1 (en) * 2012-12-24 2014-06-26 Denso Corporation Internal rotor-type fluid machine
WO2015019859A1 (fr) * 2013-08-09 2015-02-12 アイシン精機株式会社 Rotor interne de pompe hydraulique
JP2015048784A (ja) 2013-09-02 2015-03-16 株式会社ジェイテクト 電動オイルポンプ装置
JP2015108306A (ja) 2013-12-03 2015-06-11 本田技研工業株式会社 オイルポンプ

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2157803B (en) 1984-04-25 1988-05-18 Facet Enterprises Vent-relief valve for a wet motor gerotor fuel pump
DE102011000533A1 (de) 2011-02-07 2012-08-09 Zf Lenksysteme Gmbh Verstellbare Verdrängerpumpe
DE102013223999A1 (de) 2013-11-25 2015-05-28 Mahle International Gmbh Flügelzellenpumpe oder Pendelschieberpumpe

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1580431A1 (fr) 2002-12-24 2005-09-28 Koyo Seiko Co., Ltd. Pompe a engrenages interne electrique
DE102004028127A1 (de) * 2003-06-11 2005-01-05 Denso Corp., Kariya Kraftstoffeinspritzpumpe mit einem inneren Aufbau zum Absorbieren einer Winkelverlagerung
JP2012026294A (ja) 2010-07-20 2012-02-09 Aisin Seiki Co Ltd 流体ポンプ
DE102011011384A1 (de) * 2011-02-17 2012-08-23 Festool Gmbh Hand-Werkzeugmaschine mit einem Lamellenmotor aus einem Nicht-Metall
DE102012204191A1 (de) 2011-03-30 2012-10-04 Hitachi Automotive Systems, Ltd. Elektrische Ölpumpe
EP2570672A2 (fr) 2011-09-17 2013-03-20 Jtekt Corporation Pompe à huile électrique
US20140178234A1 (en) * 2012-12-24 2014-06-26 Denso Corporation Internal rotor-type fluid machine
WO2015019859A1 (fr) * 2013-08-09 2015-02-12 アイシン精機株式会社 Rotor interne de pompe hydraulique
EP3032102A1 (fr) * 2013-08-09 2016-06-15 Aisin Seiki Kabushiki Kaisha Rotor interne de pompe hydraulique
JP2015048784A (ja) 2013-09-02 2015-03-16 株式会社ジェイテクト 電動オイルポンプ装置
JP2015108306A (ja) 2013-12-03 2015-06-11 本田技研工業株式会社 オイルポンプ

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