EP1406015A1 - Pompe à engrenage interne avec remplissage amélioré - Google Patents

Pompe à engrenage interne avec remplissage amélioré Download PDF

Info

Publication number
EP1406015A1
EP1406015A1 EP03020503A EP03020503A EP1406015A1 EP 1406015 A1 EP1406015 A1 EP 1406015A1 EP 03020503 A EP03020503 A EP 03020503A EP 03020503 A EP03020503 A EP 03020503A EP 1406015 A1 EP1406015 A1 EP 1406015A1
Authority
EP
European Patent Office
Prior art keywords
internal gear
depressions
gear pump
base
face
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
EP03020503A
Other languages
German (de)
English (en)
Other versions
EP1406015B1 (fr
Inventor
Sven Peters
Claus Welte
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.)
Schwaebische Huettenwerke Automotive GmbH
Original Assignee
SCHWAEBISCHE HUETTENWERKEGMBH
Schwaebische Huettenwerke Automotive 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 SCHWAEBISCHE HUETTENWERKEGMBH, Schwaebische Huettenwerke Automotive GmbH filed Critical SCHWAEBISCHE HUETTENWERKEGMBH
Publication of EP1406015A1 publication Critical patent/EP1406015A1/fr
Application granted granted Critical
Publication of EP1406015B1 publication Critical patent/EP1406015B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/088—Elements in the toothed wheels or the carter for relieving the pressure of fluid imprisoned in the zones of engagement
    • 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

Definitions

  • the invention relates to internal gear pumps, in particular internal gear pumps for the Use as lubricating oil pumps for combustion piston engines.
  • the invention relates to an internal gear pump, which has a housing, at least one in the Housing formed gear chamber and at least two in the gear chamber has recorded, meshing gears.
  • One of the Gears is an externally toothed, inner gear, the other is an internally toothed, outer gear.
  • the gears can be rotated about mutually offset axes of rotation.
  • In the gear chamber open on a low pressure side, which is also referred to as the suction side at least one inlet opening and at least one on a high-pressure side Outlet opening for a fluid to be pumped.
  • the fluid is preferably a hydraulic fluid.
  • the internal toothing of the outer gear has at least one more tooth than the external toothing of the inner gear, preferably it has exactly one tooth more on.
  • the gears form feed cells that are in the direction of rotation of the gears an area of deepest tooth engagement to an area of lowest tooth engagement expand the low pressure side of the gear chamber, that is, enlarge, and then from the area of least tooth mesh to the area deepest Reduce tooth engagement on the high pressure side of the gear chamber again, that is they form compressing delivery cells on the high pressure side.
  • the gears are on the low pressure side of the gear chamber from there Expanding fluid cells sucked in, over the area of minimal tooth meshing promoted and by the compressing conveyor cells on the high pressure side through the displaced at least one outlet opening.
  • the end face of the external toothing only extends into the base of the tooth base, i.e. the depressions according to the invention are to the relevant end face of the External teeth open and each end in the base of the tooth base.
  • the depression thus formed does not extend from one end face to the opposite other end face of the external toothing continuously, but it remains in a tooth on the tooth feet, which extends to the root circle of the external toothing and the Foot circle determined.
  • the wells be in one way or another Embodiment of the invention axially from one end face to the other end face extend continuously, however, they have at least one of the end faces greater radial depth than in an area within the base of the tooth base, i.e. in the case of axially continuous depressions, their radial depth is not greater than that entire axial length of the recess in question evenly, but they are Indentations in the interior of the respective base of the tooth flatter than at least one of the two faces of the external toothing.
  • the radial depth of the wells can especially from a flattest point inside the base of the tooth base increase on both ends of the external toothing.
  • the Suction cross section of the relevant feed cell Due to the depression formed according to the invention on the low pressure side Gear chamber on the end face to which the recess extends, the Suction cross section of the relevant feed cell enlarged. On the other hand, it can Extent of increase in volume of the feed cell compared to an axial one Consistently extending recess with the same depth Inlet cross-section on the front side can be reduced. With increasing speed of the Gears become the radially outward-facing ones that act on the fluid Centrifugal forces within the conveyor cells are larger, which in addition to the expansion of the Conveying cells on the low pressure side a suction directed radially outwards causes. Due to the centrifugal force, the fluid is pressed against the outer gear, while an empty space would remain on the inner gear without the depressions.
  • This empty space is due to the formation of the wells according to the invention reduced because the feed cells compared to simple feed cells enlarged suction cross-section on the front side and in comparison to conveyor cells with continuously extending depressions have a smaller cell volume.
  • the degree of filling of the feed cells can be increased by the optimal use of centrifugal force Purposes of fluid intake can be increased.
  • the start of cavitation thus becomes shifted higher speeds.
  • the volumetric efficiency in the The speed range above the start of cavitation decreases less than at conventional internal gear pumps.
  • each of the recesses is in the radial direction without the tooth base contour Depression measured, i.e. exactly in the crown it is on the base of the External teeth measured.
  • the depth can change in a single step.
  • the depth preferably changes continuously from one in the axial direction maximum depth on the end face to a minimum value, preferably to the value "0".
  • the volume of the depression and the relevant delivery cell compared to a one-step drop.
  • the size of one at high speeds fluid-filled space within the delivery cell is accordingly in advantageously also reduced.
  • the on the deepening volume increase due to a one-step drop the increase in depth can be reduced in several stages. It is particularly preferred when the depth in the axial direction of a greatest value at the front of the External toothing degressive to a minimum value inside the base of the tooth base decreases.
  • the recess can be formed by subsequent machining of the inner gear be, for example by milling. In particular, however, you can directly the primary shaping of the gearwheel, preferably in the case of compression molding, as a sintered part formed gear are formed.
  • depressions of the inner gear apply, which are preferably are each the same.
  • Wells of the type according to the invention can be particularly advantageous on both End faces of the inner gear be formed, axially between the two extending depressions of each tooth base preferably remains a web which extends to the base circle of the external toothing, i.e. touches the base circle.
  • two depressions within a tooth base are preferably in the The apex of the base of the tooth base in an axial alignment.
  • they are more preferred Execution mirror-symmetrical to the axial center of the inner gear. If on one or a continuous recess opens on both end faces, so is preferred at least one inlet opening is formed opposite each of the two end faces, which covers the mouths of the depressions in the radial direction.
  • the at least one outlet opening on the high pressure side can be in the radial direction have the same extent as the at least one inlet opening, however, it is preferably narrower in the radial direction than the at least one Inlet opening, namely by the radial depth of the opening opposite here Wells. If indentations open on both faces of the external toothing and at least one outlet opening is formed on both end faces, also cover these at least two outlet openings conveying cells on the high pressure side only each to the base of the tooth base of the external toothing, but not the mouths of the Wells.
  • the invention further corresponds if in the case of both End faces of the recesses opening an external opening or in Direction of the gears one after the other several outlet openings only on one end face is or are formed.
  • Fig. 1 shows an internal gear pump with a housing 3, the housing cover is removed to reveal the view in a gear chamber 4.
  • the Gear chamber 4 is a circular cylindrical chamber, the walls of which Housing 3 and the removed housing cover are formed.
  • the walls form a circular cylindrical inner surface and two end faces that extend axially facing each other.
  • the view is in Fig. 1 against the rear of these two End faces directed. This rear end face and the circular cylindrical Inner surface area will be from the housing and the other of the end walls formed by the removed housing cover.
  • the gear chamber 4 accommodates a gear set consisting of two spur gears, namely an inner gear 1 and an outer gear 2.
  • the inner gear 1 is secured against rotation on a drive shaft 8 and can be rotated together with the drive shaft 8 about its axis of rotation D 1 .
  • the outer gear 2 is rotatably supported on the circular cylindrical inner surface of the gear chamber 4 about an axis of rotation D 2 by means of a plain bearing.
  • the two axes of rotation D 1 and D 2 run eccentrically to one another, ie offset in parallel, with the eccentricity "e".
  • the inner gear 1 is with an external toothing 1a and the outer gear 2 is provided with an internal toothing 2i.
  • the two toothings 1a and 2i are in a meshing tooth mesh.
  • the external toothing 1a has one tooth less than the internal toothing 2i.
  • the two toothings 1a and 2i form in the tooth engagement between them conveying cells 7 which carry a fluid to be conveyed by the pump.
  • an inlet opening 5 and an outlet opening 6 for the fluid In the gear chamber 4 open at the rear end face, an inlet opening 5 and an outlet opening 6 for the fluid. Likewise lead to the from the housing cover formed front end face a further inlet opening and another Outlet opening shaped like the inlet opening 5 and the outlet opening 6.
  • the inlet opening 5 is connected via a low-pressure channel formed in the housing 3 a fluid inlet and the outlet opening 6 is formed in the housing 3 High pressure channel connected to a fluid outlet of the housing 3.
  • the one in the Housing cover formed inlet opening is also connected to the low pressure duct and the outlet opening formed in the housing cover is also connected to the high pressure duct connected.
  • Each of the conveyor cells 7 is adjacent to it in and against the direction of rotation D. Conveying cells 7 are at least essentially sealed in a pressure-tight manner. The seal the high pressure side of the gear chamber 4 from the low pressure side takes place in the Deepest meshing area due to the opposing drive tooth flanks and in the area of least tooth meshing by the opposing ones Tooth tips of the toothings 1a and 2i. In the axial direction, the gears 1 and 2 at their end faces each sealing gaps with the axially facing opposite Chamber end walls of the gear chamber 4, in which the inlet and the Outlet openings are formed. In the area of deepest meshing and in the In the area of minimal tooth engagement, the two chamber end walls each form one Sealing bar.
  • the respective sealing web extends in the direction of rotation D both in the Area of deepest tooth engagement as well as in the area of lowest tooth engagement between the ends of the inlet opening and the outlet opening facing each other there separates the respective openings due to its sealing effect and thus ultimately the Low pressure side from the high pressure side.
  • the inner gear 1 from the drive shaft 8 rotationally driven, for example in the direction of rotation D shown, and takes Due to the meshing meshing of the outer gear 2 in the same direction of rotation D with.
  • the conveyor cells 7 enlarge from one area deepest meshing, starting in the direction of rotation D to a minimum Meshing, and decrease again from the area of the smallest meshing to to the area of deepest meshing. Due to the enlarging conveyor cells 7 in the gear chamber 4 a low pressure side and by the shrinking Conveying cells 7 a high pressure side is formed in the gear chamber 4.
  • the internal gear 1 of the internal gear pump is shown in perspective in FIG Representation and shown in Fig. 3 in the view of Fig. 1 individually.
  • two recesses 10 are formed, which differ from an axially central web 11 starting in the axial direction up to one of the two Extend the end faces of the inner gear 1.
  • Each of the wells 10 opens only one of the two end faces of the gear 1.
  • the two formed per tooth base Depressions 10 end in the respective tooth base and form the web 11 between them.
  • the web remaining between the depressions 10 in the base of each of the tooth feet 11 can be formed as a tooth root profile in a known manner, for example as Hypozykloide.
  • Each of the webs 11 touches the root circle F of the external toothing 1a, i.e. the webs 11 determine the root circle F.
  • the Rolling circle W which divides the profile of the external toothing 1a into tooth heads and tooth feet.
  • the depressions 10 have a round profile in cross section with an in Circumferential direction measured width B.
  • the depressions 10 have their greatest width B. each at their mouth on the end face of the inner gear 1. 3 is this greatest width B is shown as an example for one of the depressions 10.
  • the depth T in the apex of the tooth base is shown as an example of one of the Indentations 10.
  • the depth T is measured in the radial direction and is based on that in Axial direction via the recess 10 extends the imaginary tooth base profile of the webs 11 based.
  • the depressions 10 also have their greatest depth T on the end face of the inner gear 1 on which they open. From the muzzle at the front to to the web 11, the depth T decreases continuously in the axial direction.
  • the cutting plane is the axial / radial plane that the recess 10 in divides two equal halves.
  • the recess 10 has its respective in this sectional plane greatest depth T in the cross-sectional plane perpendicular to the axial / radial cutting plane.
  • the recess 10 flattens from the end face of the inner gear 1 to the web 11 continuously at an angle of inclination ⁇ .
  • the flattening course of the Well 10 is also slightly degressive, that is Tilt angle ⁇ , measured on the axial extension of the tooth profile of the bar 11, also gradually decreases from the end face to the web 11.
  • Tilt angle ⁇ measured on the axial extension of the tooth profile of the bar 11
  • the angle of inclination ⁇ is in Transition area between recess 10 and web 11 not equal to "0".
  • the depressions 10 each have a smooth one Shell surface formed in the bottom of each of the tooth feet.
  • the depressions 10 are each conical with a round transition area in a radial plan view into the from the respective base 11 formed tooth base profile.
  • the generator of each of the Recesses 10 formed cone is a due to the changing angle of inclination little curved. The shape could therefore also be called hyperboloid. A straight cone shape would also be possible.
  • the concave shape of the depressions 10 results in an advantageously large one per depression 10 Ratio of mouth cross-sectional area to volume.
  • the depressions 10 are exactly in the apex of the tooth feet formed with the axial / radial plane intersecting the root circle F in the apex as Plane of symmetry. Forms deviating from this are, however, also conceivable. However, it is advantageous if the mouths of the depressions 10 on the end face of the inner gear 10 are shaped and arranged in this manner. Of these Outlets from the depressions 10 can also be straight or oblique run out in an arc towards the axial towards the respective web 11, around which Influencing inflow conditions into the relevant delivery cell 7.
  • the inlet opening 5 and the outlet opening 6 are in the rear Except for the end wall of the chamber as kidney-shaped openings. They extend in Circumferential direction each over a plurality of feed cells 7, being the relevant ones Cover conveyor cells 7 radially.
  • the inlet opening 5 also radially covers the Wells 10.
  • the outlet opening 6 extends radially only up to the base of the External toothing 1a, so that no fluid is displaced directly from the depressions 10 becomes. What has been said about the inlet opening 5 and the outlet opening 6 also applies to the Inlet opening and the possibly existing outlet opening in the removed housing cover. No, but not necessarily, in the housing cover Outlet opening be formed.
  • Fig. 5 shows the course of the volumetric Efficiency E for an internal gear pump with a gear set without Wells
  • Fig. 6 shows the volumetric efficiency E for comparison an internal gear pump according to the invention.
  • the Internal gear pump is the lubricating oil pump for a combustion piston engine Cars or trucks. This is a particularly preferred example of use for a Internal gear pump according to the invention.
  • the installation situation of the pump is that the driven gear, in the example the inner gear 1, with a speed R is driven by up to 14,000 revolutions per minute (rpm), that is is from a crankshaft of the engine with one opposite the crankshaft driven speed driven. Starting at a drive speed of around 7,000 rpm cavitation in the conventional pump.
  • An arrow K points to the Cavitation inception.
  • the volumetric decreases with increasing speed Efficiency E from.
  • the volumetric efficiency E with the exception of those according to the invention Recesses 10 of identical internal gear pump is compared in FIG. 6 applied.
  • the start of cavitation K can be shifted to significantly higher speeds become. in the comparison case, the start of cavitation K could be around 2,000 RPM higher speed to be shifted.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
EP03020503A 2002-10-01 2003-09-15 Pompe à engrenage interne avec remplissage amélioré Expired - Lifetime EP1406015B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10245814 2002-10-01
DE10245814A DE10245814B3 (de) 2002-10-01 2002-10-01 Innenzahnradpumpe mit verbesserter Füllung

Publications (2)

Publication Number Publication Date
EP1406015A1 true EP1406015A1 (fr) 2004-04-07
EP1406015B1 EP1406015B1 (fr) 2011-07-20

Family

ID=30128864

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03020503A Expired - Lifetime EP1406015B1 (fr) 2002-10-01 2003-09-15 Pompe à engrenage interne avec remplissage amélioré

Country Status (4)

Country Link
EP (1) EP1406015B1 (fr)
AT (1) ATE517261T1 (fr)
DE (1) DE10245814B3 (fr)
ES (1) ES2369901T3 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2443088A (en) * 2006-10-18 2008-04-23 Concentric Vfp Ltd Gerotor pump with filling axial rotor slot.
WO2009130433A1 (fr) * 2008-04-22 2009-10-29 Concentric Vfp Limited Pompe avec fentes de remplissage
CN102444577A (zh) * 2010-09-30 2012-05-09 富士重工业株式会社 内接齿轮式流体装置
EP3193019A1 (fr) * 2016-01-12 2017-07-19 Hamilton Sundstrand Corporation Pompe à engrenages

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006125391A (ja) * 2004-09-28 2006-05-18 Aisin Seiki Co Ltd 内接ギヤ型ポンプのロータ構造
DE102006047312A1 (de) * 2006-10-06 2008-04-10 Sauer-Danfoss Aps Hydraulische Maschine
DE102007040724A1 (de) * 2007-08-29 2009-03-05 Robert Bosch Gmbh Förderaggregat
DE102008003843A1 (de) 2008-01-10 2009-07-16 Robert Bosch Gmbh Förderaggregat
DE102012022787A1 (de) 2012-11-22 2014-05-22 Volkswagen Aktiengesellschaft Zahnradpumpe sowie Regelsystem mit Zahnradpumpe und Regelkolben
JP6382674B2 (ja) * 2014-10-07 2018-08-29 豊興工業株式会社 内接歯車ポンプ

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB370474A (en) * 1930-12-11 1932-04-11 Thomas Winter Nichols Improvements in rotary pumps
FR977730A (fr) * 1942-10-23 1951-04-04 Procédé et dispositifs pour l'équilibrage des pignons de pompes à engrenages
DE1263973B (de) * 1956-07-17 1968-03-21 Borsig Ag Innerer Drehkolben einer Drehkolbenmaschine mit exzentrisch ineinander angeordneten Drehkolben
DE2829417A1 (de) * 1978-07-05 1980-01-17 Rexroth Gmbh G L Kreiskolbenmaschine
DE2933493A1 (de) * 1979-08-18 1981-03-26 Daimler-Benz Aktiengesellschaft, 70567 Stuttgart Zahnradpumpe
JPH04187883A (ja) * 1990-11-21 1992-07-06 Nippondenso Co Ltd トロコイドギヤポンプ
DE4200883C1 (fr) * 1992-01-15 1993-04-15 Siegfried A. Dipl.-Ing. 7960 Aulendorf De Eisenmann

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05164059A (ja) * 1991-12-13 1993-06-29 Aisin Seiki Co Ltd トロコイド型オイルポンプ
DE4227301A1 (de) * 1992-08-18 1994-02-24 Bosch Gmbh Robert Einrichtung zum Fördern von Kraftstoff aus einem Vorratstank zur Brennkraftmaschine eines Kraftfahrzeuges

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB370474A (en) * 1930-12-11 1932-04-11 Thomas Winter Nichols Improvements in rotary pumps
FR977730A (fr) * 1942-10-23 1951-04-04 Procédé et dispositifs pour l'équilibrage des pignons de pompes à engrenages
DE1263973B (de) * 1956-07-17 1968-03-21 Borsig Ag Innerer Drehkolben einer Drehkolbenmaschine mit exzentrisch ineinander angeordneten Drehkolben
DE2829417A1 (de) * 1978-07-05 1980-01-17 Rexroth Gmbh G L Kreiskolbenmaschine
DE2933493A1 (de) * 1979-08-18 1981-03-26 Daimler-Benz Aktiengesellschaft, 70567 Stuttgart Zahnradpumpe
JPH04187883A (ja) * 1990-11-21 1992-07-06 Nippondenso Co Ltd トロコイドギヤポンプ
DE4200883C1 (fr) * 1992-01-15 1993-04-15 Siegfried A. Dipl.-Ing. 7960 Aulendorf De Eisenmann

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 016, no. 507 (M - 1327) 20 October 1992 (1992-10-20) *

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2443088A (en) * 2006-10-18 2008-04-23 Concentric Vfp Ltd Gerotor pump with filling axial rotor slot.
GB2443088B (en) * 2006-10-18 2011-10-12 Concentric Vfp Ltd Pumps with filling slots
WO2009130433A1 (fr) * 2008-04-22 2009-10-29 Concentric Vfp Limited Pompe avec fentes de remplissage
CN102444577A (zh) * 2010-09-30 2012-05-09 富士重工业株式会社 内接齿轮式流体装置
CN102444577B (zh) * 2010-09-30 2015-07-29 富士重工业株式会社 内接齿轮式流体装置
EP3193019A1 (fr) * 2016-01-12 2017-07-19 Hamilton Sundstrand Corporation Pompe à engrenages
US10563653B2 (en) 2016-01-12 2020-02-18 Hamilton Sundstrand Corporation Gear pump

Also Published As

Publication number Publication date
ATE517261T1 (de) 2011-08-15
DE10245814B3 (de) 2004-02-12
ES2369901T3 (es) 2011-12-09
EP1406015B1 (fr) 2011-07-20

Similar Documents

Publication Publication Date Title
DE4200883C1 (fr)
EP0043899B1 (fr) Pompe à engrenages annulaires
DE4241320C2 (de) Drehkolbenmaschine
EP0619430B1 (fr) Pompe à engrenage internes pour gamme de vitesses rotatives élévées
EP1340913B1 (fr) Pompe à engrenages
DE2655670A1 (de) Rotations-kompressor mit labyrinthdichtung
DE102008036273B4 (de) Rotationskolbenpumpe mit Taschen für Schmiermittel
DE10245814B3 (de) Innenzahnradpumpe mit verbesserter Füllung
WO2009092719A2 (fr) Pompe à engrenage intérieur, à volume variable
DE1403541A1 (de) Umlaufmaschine,insbesondere Schraubenverdichter fuer Gase
WO2007039405A1 (fr) Pompe a palettes
DE10296838B4 (de) Zahnradpumpe
DE1503544B2 (de) Drehkolbenvakuumpumpe
DE69928172T2 (de) Vacuumpumpe
DE102007038966B4 (de) Mehrstufige Drehkolbenvakuumpumpe bzw. - verdichter
DE10010170A1 (de) Inverser Verzahnungsrotorsatz
DE3416400C2 (de) Kraftfahrzeugölpumpe
DE102016207093B4 (de) Zahnradfluidmaschine
EP0578853B1 (fr) Machine rotative avec profiles conjugués en contact continu
DE858448C (de) Drehkolbenmaschine mit Schraubenraedern
DE3737961A1 (de) Innenzahnradpumpe
WO1997017545A1 (fr) Compresseur helicoidal
DE2134241A1 (de) Mehrstufige außenachsige Drehkolben maschine fur elastische Arbeitsmedien
DE4302242A1 (fr)
DE19709202C2 (de) Drehkolbenmaschine mit axial verdrehten Drehkolben

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): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL LT LV MK

17P Request for examination filed

Effective date: 20040427

17Q First examination report despatched

Effective date: 20040709

AKX Designation fees paid

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PT RO SE SI SK TR

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: SCHWAEBISCHE HUETTENWERKE AUTOMOTIVE GMBH & CO. KG

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: SCHWAEBISCHE HUETTENWERKE AUTOMOTIVE GMBH

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

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): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PT RO SE SI SK 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: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 50313822

Country of ref document: DE

Effective date: 20110908

REG Reference to a national code

Ref country code: NL

Ref legal event code: VDEP

Effective date: 20110720

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2369901

Country of ref document: ES

Kind code of ref document: T3

Effective date: 20111209

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

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: 20110720

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: 20110720

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: 20111121

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: 20110720

REG Reference to a national code

Ref country code: IE

Ref legal event code: FD4D

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: 20111021

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: 20110720

Ref country code: CY

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: 20110720

BERE Be: lapsed

Owner name: SCHWABISCHE HUTTENWERKE AUTOMOTIVE G.M.B.H.

Effective date: 20110930

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 FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20110720

Ref country code: MC

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

Effective date: 20110930

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: 20110720

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: 20110720

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

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

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: 20110720

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: 20110720

26N No opposition filed

Effective date: 20120423

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: 20110930

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: 20110720

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

Ref country code: LI

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

Effective date: 20110930

Ref country code: CH

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

Effective date: 20110930

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 50313822

Country of ref document: DE

Effective date: 20120423

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: 20110915

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

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: 20111020

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: 20110720

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

Effective date: 20110720

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

Ref country code: DE

Payment date: 20140922

Year of fee payment: 12

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

Ref country code: GB

Payment date: 20140919

Year of fee payment: 12

Ref country code: AT

Payment date: 20140911

Year of fee payment: 12

Ref country code: FR

Payment date: 20140919

Year of fee payment: 12

Ref country code: ES

Payment date: 20140926

Year of fee payment: 12

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

Ref country code: IT

Payment date: 20140923

Year of fee payment: 12

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 50313822

Country of ref document: DE

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

Ref country code: IT

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

Effective date: 20150915

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 517261

Country of ref document: AT

Kind code of ref document: T

Effective date: 20150915

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

Effective date: 20150915

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20160531

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

Ref country code: GB

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

Effective date: 20150915

Ref country code: DE

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

Effective date: 20160401

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

Ref country code: AT

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

Effective date: 20150915

Ref country code: FR

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

Effective date: 20150930

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20161027

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

Ref country code: ES

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

Effective date: 20150916