EP2672119A1 - Machine à roue dentée dotée d'un tourillon logé de façon hydrodynamique et hydrostatique - Google Patents

Machine à roue dentée dotée d'un tourillon logé de façon hydrodynamique et hydrostatique Download PDF

Info

Publication number
EP2672119A1
EP2672119A1 EP13166946.7A EP13166946A EP2672119A1 EP 2672119 A1 EP2672119 A1 EP 2672119A1 EP 13166946 A EP13166946 A EP 13166946A EP 2672119 A1 EP2672119 A1 EP 2672119A1
Authority
EP
European Patent Office
Prior art keywords
bearing
groove
feed channel
gear machine
machine according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP13166946.7A
Other languages
German (de)
English (en)
Other versions
EP2672119B1 (fr
Inventor
Kai Sutter
Marc Laetzel
Stefan Cerny
Markus Stahl
Guido Bredenfeld
Dietmar Schwuchow
Sebastian Birk
Ruediger Weiss
Christoph Kessler
Andreas Leinberger
Michael Wilhelm
Heinz Martin
Andreas Klaiber
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
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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2672119A1 publication Critical patent/EP2672119A1/fr
Application granted granted Critical
Publication of EP2672119B1 publication Critical patent/EP2672119B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • F04C2/12—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
    • 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
    • F04C15/0088—Lubrication
    • 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
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/086—Carter
    • 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
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/008—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids for other than working fluid, i.e. the sealing arrangements are not between working chambers of the machine
    • F04C27/009—Shaft sealings specially adapted for pumps
    • 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
    • F04C2240/50—Bearings
    • F04C2240/54—Hydrostatic or hydrodynamic bearing assemblies specially adapted for rotary positive displacement pumps or compressors

Definitions

  • the invention relates to a gear machine according to the preamble of claim 1 or claim 11.
  • the gear machine includes two gears that mesh with each other in external engagement.
  • the tooth edges are surrounded by a housing, which consists of a main body and two bearing bodies.
  • the gears lie with their tip diameter sealingly against the main body and with its two side surfaces sealingly against the associated bearing body.
  • a rotation of the gears is thus accompanied by a fluid flow between a first and a second fluid port in the housing.
  • Both toothed edges are provided on both sides with a circular cylindrical bearing journal.
  • the bearing journal is rotatably received in an associated bearing bore with respect to a rotational axis, wherein the bearing bore in the bearing bodies, ie in the housing, is arranged.
  • the bearing bore is provided with a groove which is covered by the journal.
  • the groove is connected to a feed channel, via which it can be filled with pressurized pressurized fluid, in particular hydraulic oil.
  • pressurized pressurized fluid in particular hydraulic oil.
  • the disadvantage of the known gear machine is that it is designed for operation at a certain speed of the gears. If a deviation from this design speed occurs during operation, then excessive wear occurs Bearing or the bearing bore, so that the life of the gear machine decreases.
  • the object of the invention is to provide a gear machine that can be operated at different speeds of the gears, without excessive wear on the bearing pin or the bearing bore occurs.
  • this object is achieved in that the groove is formed endlessly circumferentially around the bearing pin around, wherein on one side next to the groove in the bearing bore at least a first recess is provided, which is connected to a closed feed channel for supplying pressurized fluid.
  • the groove is preferably not connected to pressurized fluid under pressure. It is rather thought that the pressurized fluid, which flows from the bearing gap between the bearing pin and the bearing bore into the groove, is discharged from the groove substantially without pressure. This is preferably done by the pressure fluid from the groove flows back into the bearing gap and indeed in a zone in which a low pressure prevails. This is facilitated by the fact that the groove runs endlessly around the bearing journal.
  • the groove may be additionally connected to a separate discharge channel for discharging pressurized fluid.
  • This discharge channel leads, for example, to the low-pressure connection of the housing or to a pressure chamber in the housing in which the pressure fluid has a low pressure.
  • the groove divides the journal into two areas.
  • a hydrodynamic lubricant film forms between the bearing journal and the bearing bore, which completely separates the bearing journal from the bearing bore, so that they do not touch each other directly. This happens especially when the gears rotate at a high speed.
  • pressure fluid under pressure is introduced into the bearing gap via the supply channel and the first recess. This can form a lubricating film at a very low speed of the gears, the journal completely separated from the bearing bore. Consequently, at both low and high speeds of the gears, there is a bearing lubricating film between the journal and the associated bearing bore so that excessive wear does not occur.
  • the feed channel is preferably connected directly to the first recess. It is designed to be closed, so that the pressure fluid, which is located in the feed channel, does not interfere with the formation of the lubricating film.
  • the lubricating film is thus influenced primarily by the position and the shape of the first recess. In this case, preferably, a single first recess is provided so that the gear machine can be made particularly simple.
  • the bearing bore may be arranged in a separate bearing body, which bears against a side surface of the associated gear, wherein the feed channel is arranged exclusively in the bearing body.
  • the bearing body is a comparatively small component, so that the supply channel can be made there particularly easily.
  • the feed channel may lead into the area of teeth of the gear, so that there is a fluid exchange connection between the interdental spaces and the feed channel. This can flow under pressure from the interdental spaces in the feed channel and thus over the first recess in the bearing gap between the bearing pin and bearing bore under pressure.
  • the position of the mouth opening of the feed channel on the circumference of the associated gear, the pressure of the pressurized fluid can be controlled in the feed, so that there is an optimal lubricating film.
  • the mouth opening of the feed channel may be wider on the associated gear in the circumferential direction with respect to the axis of rotation than a tooth of the gear. This ensures that said mouth opening can not be completely covered by a tooth of the gear.
  • a fluid exchange connection between at least one tooth space and the feed channel in each rotational position of the gear a fluid exchange connection between at least one tooth space and the feed channel.
  • the pressure in the feed channel is accordingly constant. A pressure pulsation which disturbs the lubricating film does not occur.
  • the housing may have a pressure port, wherein the feed channel is connected to the pressure port.
  • the pressure port may be the high-pressure port of the housing to which the pressurized fluid flowing through the gear machine is supplied at high pressure. But it can also be provided a separate pressure port, is supplied to the pressurized fluid with a specially set pressure from a separate fluid source.
  • the groove may extend in a plane which is oriented perpendicular to the axis of rotation of the associated journal, preferably having a constant cross-sectional shape.
  • the groove extends in the direction of the associated axis of rotation over the smallest possible length. In this area, no bearing lubricating film can form. Thus, the lowest possible bearing width is lost at the journal by the proposed groove.
  • a groove with a constant cross-sectional shape can be produced particularly easily, for example on a lathe.
  • the bearing bore can be formed by a separate bearing bush, wherein the first recess is formed by a radial opening in the bearing bush, wherein the feed channel is arranged in the remaining housing.
  • the first recess can therefore be produced particularly easily, for example by means of a milling process.
  • the milling can be made in particular from radially outward on the bearing bush, so that even very filigree shapes of the first recess are easy to produce.
  • the feed channel in the remaining housing is preferably designed to be open at least in sections, wherein it is covered by the bearing bush, so that in the result is a closed feed channel. As a result, the production of the feed channel is simplified.
  • the breakthrough may be formed in the form of a slot which is aligned parallel to the axis of rotation of the associated journal.
  • a slot can be made very easily with an end mill.
  • the slot preferably extends over substantially the entire width between the groove and the edge of the bearing bush. This forms at low speeds over the entire area between the groove and the edge of the bearing bush a bearing lubricating film. This can support large forces due to its large area.
  • the bushing may be integrally formed, wherein the groove is limited exclusively by the bearing bush.
  • the groove can be made by machining the comparatively small bushing alone. This is particularly simple and therefore inexpensive.
  • the bearing bush may have a first and a separate second socket part, which delimit the groove laterally. A special chip-removing machining for the production of the groove is therefore no longer necessary.
  • the width of the groove can also be arbitrarily set during assembly of the gear machine. Further, the width of the bearing gap between the first sleeve part and the journal and the second sleeve part and the journal can be formed differently to improve the formation of the lubricating film.
  • the groove for the defined delimitation of the first and the second area can also be dispensed with.
  • said first recess is arranged completely next to a plane which is arranged perpendicular to the associated axis of rotation in the middle of the contact region between the bearing bore and bearing journal.
  • Fig. 1 shows a longitudinal section of a first embodiment of a gear machine 10 according to the invention, wherein the cutting plane passes through the axes of rotation of the gears 11.
  • the gear machine 10 comprises a housing 30, which consists of a main body 31, a first and a second cover 33; 34 and a total of four separate bearing bodies 40 is composed.
  • the tubular main body 31 has on the inner peripheral surface a constant in the direction of the rotation axes 14 cross-sectional shape, which is adapted to the gears 11, so that they rest with their tip diameter sealingly against the main body 31.
  • the toothed edges 11 are set in rotary motion with the drive pin 15, whereby the pressure fluid, in particular hydraulic oil, flows from the low-pressure connection to the high-pressure connection.
  • the gear machine is operated as a motor, the pressure fluid flows from the high-pressure port to the low-pressure port, wherein the drive pin 15 is set in rotational motion.
  • Both gears 11 have on both sides each one with respect to the associated axis of rotation 14 circular cylindrical bearing pin 13, which is received in a bearing bore 51 in the associated bearing body 40.
  • the bearing bore 51 is formed on a separate bearing bush 50, which is pressed into the remaining bearing body 40.
  • the two bearing bodies 40 on one side of the toothed wheel rest against one another on a flat contact surface 44.
  • the four bearing bodies 40 are each formed symmetrically to a plane perpendicular to the axes of rotation 14 and beyond mirror symmetry to the flat contact surface 44.
  • On its outer peripheral surface they are sealingly adapted to the inner peripheral surface of the main body 31, wherein they are in the direction of the axes of rotation 14th are received in the main body 31 minimally movable.
  • the drive pin 15 protrudes through the first cover 33 out of the housing 30, wherein the passage point is sealed with a (not shown) radial shaft sealing ring against leakage of the pressurized fluid.
  • Fig. 2 shows a longitudinal section of a bearing body 40 of the gear machine 10 after Fig. 1 ,
  • the bearing bush 50 is received in a receiving bore 41 in the bearing body 40, which is formed circular cylindrical with respect to the axis of rotation 14 of the associated gear.
  • the bushing 50 includes a first and a second Bushing 54, 55, which are each designed as a circular cylindrical tube with a constant wall thickness.
  • the inner peripheral surfaces of the bushing parts 54; 55 form the bearing bore 51, wherein both inner peripheral surfaces have the same diameter.
  • the two end faces of the first and the second sleeve part 54; 55 are each formed flat and perpendicular to the axis of rotation 14 of the associated gear.
  • the first and second sleeve parts 54; 55 are spaced apart so that there is a groove 52 therebetween.
  • the side walls of the groove 52 are defined by the associated end faces of the first and second sleeve parts 54; 55 formed.
  • the bottom wall of the groove 52 is formed by the bearing body 40, namely the receiving bore 41.
  • first recess 53 is arranged, which is in the form of an opening in the bearing bush 50, namely the first female part 54, is formed.
  • the first recess 53 is formed in the form of a slot which extends parallel to the axis of rotation 14 of the associated gear.
  • the first recess 53 may also have other shapes, as far as it is suitable for forming a lubricating film between the bearing bore 51 and the associated bearing pin.
  • a plurality of first recesses 53 may be provided.
  • the first recess is directly connected to a feed channel 42, which has a closed channel cross-sectional shape. Via the feed channel 42, pressurized fluid under pressure can be supplied to the first recess 53 so that it flows into the bearing gap between the bearing bore 51 and the bearing journal.
  • the width of the first and second regions 20; 21 and thus the width of the first and the second sleeve part 54, 55 is selected so that the respective lubricating films have approximately the same capacity.
  • a smaller width is sufficient than in the second region 21 in order to achieve the same load-bearing capacity.
  • Fig. 3 shows a cross section of the bearing body 40 after Fig. 2 , where the position of the cutting plane in Fig. 2 marked with AA.
  • the feed channel 42 is formed by a circular cylindrical bore, which intersects the receiving bore 41 in the bearing body 40. There, the feed channel 42 is covered by the bearing bush 50, namely the first socket part, so that the pressure fluid from the feed channel 42 can flow exclusively through the first recess 53 into the bearing gap. Due to the large diameter of the feed channel 42, this is associated with low pressure losses.
  • a third recess 45 is provided on the radial outer surface of the bearing body 40, which extends over the entire width of the bearing body 40. Via the third recess 45, a fluid exchange connection between the high pressure port on the housing of the gear machine and the feed channel 42 is established. Accordingly, the pressure at which the pressurized fluid flows into the bearing gap is equal to the pressure at the high pressure port of the gear machine.
  • Fig. 4 shows a longitudinal section of a bearing body 40 according to a second embodiment of the invention.
  • the second embodiment differs from the first embodiment exclusively in that instead of a first and a separate second socket part, a one-piece bearing bushing 50 is provided.
  • the bushing 50 is formed in the form of a circular cylindrical tube with a constant wall thickness.
  • the groove 52 is limited only by the bushing 50. It runs around the bearing pin in a plane that is vertical is formed to the axis of rotation 14 of the associated gear.
  • the cross-sectional shape of the groove 52 is constant and may be formed, for example, rectangular, square or semicircular.
  • Fig. 5 shows a longitudinal section of a bearing body 40 according to a third embodiment of the invention.
  • the third embodiment differs from the first and second embodiments exclusively in that the groove which delimits the first from the second region has been completely omitted.
  • the fact that the first recess 53 is arranged eccentrically results in approximately the effect according to the invention as in the first and the second embodiment of the invention.
  • An off-center arrangement should be understood to mean that the first recess 53 is arranged on one side next to a plane 23 which is perpendicular to the associated axis of rotation 14 in the middle of the contact region (No. 22 in FIG Fig. 1 ) is arranged between the bearing bore 51 and bearing journals

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
EP13166946.7A 2012-06-08 2013-05-08 Machine à roue dentée dotée d'un tourillon logé de façon hydrodynamique et hydrostatique Active EP2672119B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102012209622A DE102012209622A1 (de) 2012-06-08 2012-06-08 Zahnradmaschine mit hydrodynamisch und hydrostatisch gelagertem Lagerzapfen

Publications (2)

Publication Number Publication Date
EP2672119A1 true EP2672119A1 (fr) 2013-12-11
EP2672119B1 EP2672119B1 (fr) 2016-07-13

Family

ID=48236780

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13166946.7A Active EP2672119B1 (fr) 2012-06-08 2013-05-08 Machine à roue dentée dotée d'un tourillon logé de façon hydrodynamique et hydrostatique

Country Status (2)

Country Link
EP (1) EP2672119B1 (fr)
DE (1) DE102012209622A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2980353A1 (fr) * 2014-07-31 2016-02-03 Hamilton Sundstrand Corporation Palier stationnaire d'engrenage d'entraînement d'une pompe à engrenages
US9726221B2 (en) 2014-07-31 2017-08-08 Hamilton Sundstrand Corporation Gear pump bearings with hybrid pads
US9890813B2 (en) 2014-11-03 2018-02-13 Hamilton Sundstrand Corporation Gear pump bearings with hybrid pads
US9980947B2 (en) 2014-12-18 2018-05-29 Genentech, Inc. Tetrahydro-pyrido[3,4-b]indole estrogen receptor modulators and uses thereof
EP3324048A4 (fr) * 2015-07-16 2019-03-27 IHI Corporation Pompe à engrenages triples et dispositif d'alimentation en fluide

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2571377A (en) * 1947-05-15 1951-10-16 Prec Developments Co Ltd Rotary displacement pump
DE1006722B (de) 1953-08-06 1957-04-18 Otto Eckerle Zahnradpumpe
US3008426A (en) * 1957-01-28 1961-11-14 Thompson Ramo Wooldridge Inc Gear fuel pump
GB883356A (en) * 1959-04-24 1961-11-29 Thompson Ramo Wooldridge Inc Improvements in or relating to pumps
DE1528965A1 (de) * 1965-08-10 1969-10-30 Bosch Gmbh Robert Verdraengungsmaschine
DE2005740A1 (de) * 1969-02-26 1970-09-10 Hydroperfect International, Saint-Maur (Frankre i ch) Gleitlager mit hydrodynamischer Schmierung
DE102006021815A1 (de) * 2006-05-10 2007-11-15 Robert Bosch Gmbh Hydraulische Zahnradmaschine

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1293022B (de) * 1955-10-24 1969-04-17 Plessey Company U K Ltd Lagerschmierung und -kuehlung bei einer Zahnradpumpe oder einem Zahnradmotor
DE1226420B (de) * 1958-11-15 1966-10-06 Hans Molly Dipl Ing Zahnradpumpe oder-motor
DE19804132C1 (de) * 1998-02-03 1999-09-09 Hasse Abdichtungssystem für Zahnradpumpen für hochviskosen Kautschuk, polymere Stoffe und sonstige zu fördernde Produkte
DE102007051779A1 (de) * 2007-07-11 2009-01-15 Audi Ag Zahnradschmiermittelpumpe, insbesondere Außenzahnradpumpe
DE102009019418B4 (de) * 2009-04-29 2013-05-16 Schwäbische Hüttenwerke Automotive GmbH Umlaufverdrängerpumpe mit verbesserter Lagerschmierung
DE102009019419B4 (de) * 2009-04-29 2016-01-14 Schwäbische Hüttenwerke Automotive GmbH Umlaufverdrängermaschine mit vereinfachter Lagerachse oder -welle

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2571377A (en) * 1947-05-15 1951-10-16 Prec Developments Co Ltd Rotary displacement pump
DE1006722B (de) 1953-08-06 1957-04-18 Otto Eckerle Zahnradpumpe
US3008426A (en) * 1957-01-28 1961-11-14 Thompson Ramo Wooldridge Inc Gear fuel pump
GB883356A (en) * 1959-04-24 1961-11-29 Thompson Ramo Wooldridge Inc Improvements in or relating to pumps
DE1528965A1 (de) * 1965-08-10 1969-10-30 Bosch Gmbh Robert Verdraengungsmaschine
DE2005740A1 (de) * 1969-02-26 1970-09-10 Hydroperfect International, Saint-Maur (Frankre i ch) Gleitlager mit hydrodynamischer Schmierung
DE102006021815A1 (de) * 2006-05-10 2007-11-15 Robert Bosch Gmbh Hydraulische Zahnradmaschine

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2980353A1 (fr) * 2014-07-31 2016-02-03 Hamilton Sundstrand Corporation Palier stationnaire d'engrenage d'entraînement d'une pompe à engrenages
US9488173B2 (en) 2014-07-31 2016-11-08 Hamilton Sundstrand Corporation Gear pump drive gear stationary bearing
US9726221B2 (en) 2014-07-31 2017-08-08 Hamilton Sundstrand Corporation Gear pump bearings with hybrid pads
US9890813B2 (en) 2014-11-03 2018-02-13 Hamilton Sundstrand Corporation Gear pump bearings with hybrid pads
US9980947B2 (en) 2014-12-18 2018-05-29 Genentech, Inc. Tetrahydro-pyrido[3,4-b]indole estrogen receptor modulators and uses thereof
EP3324048A4 (fr) * 2015-07-16 2019-03-27 IHI Corporation Pompe à engrenages triples et dispositif d'alimentation en fluide
US10648467B2 (en) 2015-07-16 2020-05-12 Ihi Corporation Triple gear pump and fluid supplying device

Also Published As

Publication number Publication date
DE102012209622A1 (de) 2013-12-12
EP2672119B1 (fr) 2016-07-13

Similar Documents

Publication Publication Date Title
EP2683955B1 (fr) Coquille de coussinet lisse
EP2672119B1 (fr) Machine à roue dentée dotée d'un tourillon logé de façon hydrodynamique et hydrostatique
DE102011122642A1 (de) Reversible Gerotorpumpe
DE102011101648B4 (de) Schraubenmaschine, insbesondere Schraubenspindelpumpe
EP2140142B1 (fr) Pompe à engrenage
DE102012206699B4 (de) Zahnradmaschine mit wannenartiger Vertiefung an der Außenoberfläche des Gehäuses
EP2711552B1 (fr) Machine à roue dentée pourvue d'un raccord basse pression déviant de la forme circulaire
EP2707629B1 (fr) Dispositif d'étanchéification d'une chambre de pompage d'une pompe à piston tournant, et pompe à piston tournant dotée de ce dispositif
DE102014212255A1 (de) Außenzahnradmaschine mit Lagerkörpern, die geradlinig gleitbeweglich aneinander abgestützt sind
DE1264958B (de) Zahnradpumpe oder -motor
DE102004021216B4 (de) Hochdruck-Innenzahnradmaschine mit mehrfacher hydrostatischer Lagerung pro Hohlrad
DE102012209152A1 (de) Zahnradmaschine mit hydraulischer Verlagerung der Zahnränder
DE102012209775A1 (de) Zahnradmaschine mit Schneidzahn
DE102016207093B4 (de) Zahnradfluidmaschine
DE1653810A1 (de) Druckbelastete Pumpe
DE102017204145A1 (de) Ölmehrfachpumpe und Kraftfahrzeug mit einer solchen Ölmehrfachpumpe
DE102014208826B4 (de) Kurbelwelle für eine Innenzahnradmaschine zum Ansteuern mehrerer Durchströmebenen eines Rotors
EP0328745B1 (fr) Machine à engrenages internes
WO2011128218A2 (fr) Pompe à engrenage
DE102013202917A1 (de) Zahnradmaschine mit erhöhter Partikelrobustheit
DE102013202606A1 (de) Zahnradmaschine mit einer Lagerhülse, die mehrere Vorsprünge aufweist.
DE102014105613A1 (de) Flügelzellenpumpe mit verstellbarem Fördervolumen
DE1280056B (de) Drehkolbenmaschine mit zwei Zahnraedern im Inneneingriff
DE102012221950A1 (de) Außenzahnradmotor
DE102010005072A1 (de) Innenzahnradpumpe mit druckentlastetem Wellendichtring

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

17P Request for examination filed

Effective date: 20140611

RBV Designated contracting states (corrected)

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

RIC1 Information provided on ipc code assigned before grant

Ipc: F04C 15/00 20060101ALI20160118BHEP

Ipc: F04C 2/14 20060101ALI20160118BHEP

Ipc: F04C 27/00 20060101AFI20160118BHEP

Ipc: F04C 2/08 20060101ALI20160118BHEP

INTG Intention to grant announced

Effective date: 20160219

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 812577

Country of ref document: AT

Kind code of ref document: T

Effective date: 20160715

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502013003664

Country of ref document: DE

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20160713

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161013

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160713

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160713

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160713

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160713

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161113

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160713

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161014

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160713

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160713

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161114

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160713

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160713

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502013003664

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160713

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160713

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 5

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160713

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160713

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161013

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160713

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160713

26N No opposition filed

Effective date: 20170418

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170531

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160713

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20170508

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160713

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170531

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170531

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170508

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20170531

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170508

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170508

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 6

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170531

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160713

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160713

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20130508

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 812577

Country of ref document: AT

Kind code of ref document: T

Effective date: 20180508

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160713

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180508

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160713

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160713

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20230531

Year of fee payment: 11

Ref country code: FR

Payment date: 20230517

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20230726

Year of fee payment: 11