EP1406015B1 - Pompe à engrenage interne avec remplissage amélioré - Google Patents

Pompe à engrenage interne avec remplissage amélioré Download PDF

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Publication number
EP1406015B1
EP1406015B1 EP03020503A EP03020503A EP1406015B1 EP 1406015 B1 EP1406015 B1 EP 1406015B1 EP 03020503 A EP03020503 A EP 03020503A EP 03020503 A EP03020503 A EP 03020503A EP 1406015 B1 EP1406015 B1 EP 1406015B1
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EP
European Patent Office
Prior art keywords
toothed wheel
recesses
external toothing
tooth
front 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.)
Expired - Lifetime
Application number
EP03020503A
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German (de)
English (en)
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EP1406015A1 (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
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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.)
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Publication of EP1406015A1 publication Critical patent/EP1406015A1/fr
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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
    • F04C2/082—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 use as lubricating oil pumps for internal combustion piston engines.
  • the DE 1263973 B deals with a rotary piston machine with eccentrically arranged gear-like rotary pistons, of which the outer directly entrains the inner, wherein the teeth of the inner rotary piston constantly touches the inner teeth of the outer rotary piston, or almost touched.
  • a liquid or gaseous working fluid is axially fed and discharged at an end face of the rotary piston.
  • the tooth gaps located between the tooth tips of the inner rotary piston are laterally bevelled and thus increase the volume of the delivery cells formed by the pistons. The purpose of this increase in volume is a reduction in the inflow and outflow velocity of the conveying or working medium to the feed cells.
  • the DE 4 200 883 is considered the closest prior art and discloses an internal gear pump having an internal gear having an axial groove in each root of the gear.
  • an inlet opening is provided, which is so wide in the radial direction that it covers the axial grooves on one end face.
  • the axial grooves in the bottom of the pinion tooth gaps ensure a certain dead space in which cavitation bubbles and squeeze oil filled with vapor of the operating fluid can collect.
  • the grooves can accordingly have in axial section circular arc profile or through the entire tooth width with constant profile.
  • the outlet opening on the pruch side of the pump is so wide in the radial direction that it covers the axial grooves on one end face.
  • the invention relates to an internal gear pump comprising a housing, at least one gear chamber formed in the housing and at least two in the gear chamber has received, meshed gears.
  • One of the gears is an externally toothed, internal gear, the other is an internally toothed, external gear.
  • the gears are rotatable about mutually offset axes of rotation.
  • In the gear chamber open at a low pressure side, which is also referred to as the suction side, at least one inlet opening and at a high pressure side at least one outlet opening for a pumpable from the pump fluid.
  • the fluid is preferably a hydraulic fluid.
  • the internal toothing of the outer gear has at least one tooth more than the outer toothing of the inner gear, preferably it has exactly one more tooth.
  • the gears form delivery cells that expand in the direction of rotation of the gears from a region of deepest meshing engagement to a region of least meshing on the low pressure side of the gear chamber, that is to increase, and then from the region of least meshing to the area of deepest meshing on the high pressure side reduce the gear chamber again, that is they form on the high pressure side compressing feed cells.
  • a rotary drive of the gears is sucked on the low pressure side of the gear chamber from the there expanding delivery cells fluid, promoted over the area of least gear mesh and displaced by the compressive feed cells on the high pressure side through the at least one outlet.
  • At least one depression is formed in the root of the tooth, preferably exactly at the apex, which according to the invention extends from an end face of the external toothing only into the base of the tooth, that is to say the indentations according to the invention are directed towards the relevant end face of the external toothing open and end each in the root of the tooth.
  • the recess formed according to the invention therefore does not extend continuously from one end face to the opposite other end face of the external toothing, but remains in the tooth roots a web which extends to the root circle of the external toothing and determines the root circle.
  • the depressions extend continuously axially from one end face to the other end face, they however have a greater radial depth on at least one of the end faces than in a region within the respective tooth root, ie in the case axially continuous depressions whose radial depth is not uniform over the entire axial length of the depression in question, but it is these recesses in the interior of the respective Zahnfußgrunds flatter than at least one of the two end faces of the outer teeth.
  • the radial depth of the depressions can in particular also increase from a shallowest point in the interior of the respective tooth root to both end faces of the external toothing.
  • the intake cross-section of the relevant delivery cell is enlarged on the low-pressure side of the gear chamber at the end face to which the depression extends.
  • the extent of the increase in the volume of the feed cell can be reduced compared to a uniformly deep axially extending recess with the same inlet cross-section at the end face.
  • This empty space is reduced due to the inventive design of the wells, because the feed cells compared to simple feed cells have an enlarged Ansaugquerites on the front side and compared to feed cells with continuously extending wells a smaller cell volume.
  • the degree of filling of the delivery cells can be increased by the optimal utilization of the centrifugal force for the purpose of fluid intake. The beginning of cavitation is thus shifted to higher speeds. Furthermore, the volumetric efficiency in the speed range above the beginning of cavitation decreases less than with conventional internal gear pumps.
  • each of the depressions is measured in the radial direction to the Zahnfußkontur without depression, ie exactly at the apex, it is measured on the root circle of the external teeth.
  • the depth can change in a single step.
  • the depth preferably varies continuously in the axial direction from a maximum depth on the front side to a minimum value, preferably down to the value "0". This will increase the volume of the Deepening and the relevant conveyor cell compared to a single-stage waste reduced.
  • the size of a space at high speeds with fluid not filled space within the delivery cell is accordingly also reduced in an advantageous manner.
  • the volume increase due to the depression compared to a single-stage waste can also be reduced by increasing the depth in several stages. It is particularly preferable if the depth in the axial direction decreases in a degressive manner from a maximum value on the end face of the external toothing to a lowest value in the interior of the tooth root.
  • the width of the recess measured in the circumferential direction of the external toothing decreases from a maximum value on the end side in the axial direction to the interior of the foot base, whereby this decrease is preferably continuous runs.
  • the recess in the root of the tooth is cone-shaped except with a rounded rounded in the interior of réelle grounds on the provoca Vietnamese end.
  • the recess can be formed by a subsequent machining of the inner gear, for example by milling. However, in particular, it can be formed directly in the initial formation of the gear, preferably in a press forming of a gear formed as a sintered part.
  • Recesses of the type according to the invention can be formed particularly advantageously on both end faces of the inner gear, wherein preferably a web remains between the two axially extending recesses of each Zahnfußgrounds, which extends to the root circle of the external toothing, that touches the root circle.
  • the in this case two depressions within a Zahnfußgrounds are preferably in the apex of the Zahnfußgrounds in an axial alignment. Further, they are in a preferred embodiment to the axial center of the inner gear mirror symmetry. If at both end faces ever one or a continuous recess opens, so preferably each of the two end faces opposite at least one inlet opening is formed, which covers the mouths of the recesses in the radial direction.
  • Recesses of the type according to the invention on both end sides of the external toothing are particularly advantageous if at least one respective inlet opening opens into the gear chamber at both end faces of the toothed wheel set.
  • Inlet ports on either side of the gear train are common in internal gear pumps, which are intended for high speed applications above 7000 rpm to ensure adequate charge pumping on the low pressure side, even at such high speeds.
  • the at least one outlet opening on the high-pressure side is narrower in the radial direction than the at least one inlet opening, specifically around the radial depth of the depressions opening in the opposite direction. If recesses open on both end sides of the external toothing and at least one outlet opening is formed on both end faces, these at least two outlet openings also cover delivery cells on the high-pressure side only up to the root base of the external toothing, but not the mouths of the recesses.
  • the invention further corresponds to when an outlet opening or in the direction of the gears behind one another a plurality of outlet openings is formed only on one end side in the case of opening to both end faces of the external teeth recesses or are.
  • Fig. 1 shows an internal gear pump with a housing 3, the housing cover is removed to release the view into a gear chamber 4.
  • the gear chamber 4 is a circular cylindrical chamber whose walls are formed by the housing 3 and the removed housing cover.
  • the walls form a circular cylindrical inner circumferential surface and two end faces, which are axially facing each other.
  • the view is in Fig. 1 directed against the back of these two faces. This rear end face and the circular cylindrical inner circumferential surface are formed by the housing and the other of the end walls is formed by the detached 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 seated against rotation on a drive shaft 8 and is rotatable about the axis of rotation D 1 together with the drive shaft 8.
  • the outer gear 2 is on the circular cylindrical Inner circumferential surface of the gear chamber 4 rotatably mounted about a rotational axis D 2 by means of a sliding bearing.
  • the two axes of rotation D 1 and D 2 are mutually eccentric, ie offset in parallel, with the eccentricity "e".
  • the inner gear 1 is provided with an outer toothing 1a and the outer gear 2 is provided with an inner toothing 2i.
  • the two teeth 1a and 2i are in a meshing tooth engagement.
  • the external toothing 1a has one tooth less than the internal toothing 2i.
  • the two teeth 1a and 2i form in the tooth engagement between them delivery cells 7, which lead a pumped by the pump fluid.
  • inlet opening 5 and an outlet opening 6 for the fluid.
  • a further inlet opening and a further outlet opening which are shaped like the inlet opening 5 and the outlet opening 6, open on the front end face formed by the housing cover.
  • the inlet opening 5 is connected to a fluid inlet via a low-pressure channel formed in the housing 3, and the outlet opening 6 is connected to a fluid outlet of the housing 3 via a high-pressure channel formed in the housing 3.
  • the inlet opening formed in the housing cover is likewise connected to the low-pressure channel and the outlet opening formed in the housing cover is likewise connected to the high-pressure channel.
  • Each of the conveyor cell 7 is closed at least substantially pressure-tight against its in and against the direction of rotation D adjacent conveyor cells 7.
  • the sealing of the high pressure side of the gear chamber 4 from the low pressure side takes place in the region of deepest tooth engagement by the mutually pressing drive tooth flanks and in the region of least tooth engagement by the opposing tooth heads of the teeth 1a and 2i.
  • the gears 1 and 2 form at their end faces in each case sealing gaps with the axially facing opposite Kammerstirnwanditch the gear chamber 4, in which the inlet and the outlet openings are formed.
  • the two chamber end walls each form a sealing ridge.
  • the respective sealing web extends in the direction of rotation D both in the region of deepest tooth engagement and in the region of least tooth engagement between the ends of the inlet opening and the outlet opening facing there, and separates on the basis of its Sealing the respective openings and thus ultimately the low pressure side of the high pressure side.
  • the inner gear 1 is rotationally driven by the drive shaft 8 forth, for example in the drawn direction of rotation D, and takes the outer gear 2 in the same direction D due to the meshing tooth engagement.
  • the delivery cells 7 increase from a region of deepest meshing engagement, in the direction of rotation D, to a region of least meshing engagement, and decrease again from the region of lowest meshing engagement to the region of deepest meshing engagement. Due to the increasing delivery cells 7 is in the gear chamber 4, a low pressure side and by the decreasing delivery cells 7, a high pressure side is formed in the gear chamber 4.
  • the two gearwheels 1 and 2 are rotationally driven, fluid is sucked in through the inlet opening 5 and the inlet opening formed in the housing cover on the low-pressure side due to the delivery cells 7 expanding there and transported in the conveyor cells 7 over the region of least meshing with the high-pressure side.
  • the delivery cells 7 shrink, so that the fluid is displaced by increasing the pressure through the outlet opening 6 and the outlet opening formed in the housing cover, and through the high-pressure channel adjoining these two outlet openings to the housing outlet and finally to one with the fluid to be supplied unit flows.
  • the inner gear 1 of the internal gear pump is in Fig. 2 in a perspective view and in Fig. 3 in the view of Fig. 1 shown individually.
  • two recesses 10 are formed, which extend from an axially central web 11, starting in the axial direction to one of the two end faces of the inner gear 1.
  • Each of the recesses 10 opens at only one of the two end faces of the gear 1.
  • the remaining between the recesses 10 in the bottom of each of the toothed web 11 can be formed as Zahnfußprofil in a known manner, for example as Hypozykloide.
  • Each of the webs 11 touches the root circle F of the external toothing 1a, ie the webs 11 determine the root circle F. Is marked in FIG. 3 Further, the pitch circle W, which divides the profile of the external teeth 1a in tooth tips and tooth roots.
  • the depressions 10 have a round profile in cross-section with a width B measured in the circumferential direction.
  • the depressions 10 each have their greatest width B at their discharge point on the end face of the inner gearwheel 1.
  • This largest width B is shown as an example for one of the depressions 10.
  • the depth T in the apex of the tooth root is also shown by way of example for one of the depressions 10.
  • the depth T is measured in the radial direction and is related to the toothed profile of the webs 11 that has been extended in the axial direction over the depression 10. Also their greatest depth T, the recesses 10 on the end face of the inner gear 1, where they open. From the point of discharge at the end face to the web 11, the depth T decreases continuously in the axial direction.
  • Fig. 4 shows a portion of the inner gear, in which a recess 10 is formed, in a section.
  • the cutting plane is the axial / radial plane which divides the recess 10 into two equal halves.
  • the depression 10 has its respectively 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 inclination angle ⁇ .
  • the flattening course of the recess 10 is further degressive to a small extent, that is, the inclination angle ⁇ , measured on the axial extension of the Zahnfußprofils the web 11, from the front side to the web 11 is also gradually from.
  • the depression 10 runs obliquely into the web 11, that is to say the angle of inclination ⁇ is unequal to "0" in the transition region between the depression 10 and the web 11.
  • the recesses 10 are each formed by a smooth lateral surface in the base of each of the tooth roots.
  • the recesses 10 are each conical with a round in a radial plan view transition region in the formed by the respective web 11 Zahnfußprofil.
  • the generatrix of the cone formed by each of the recesses 10 is slightly curved because of the changing inclination angle ⁇ . The shape could therefore also be called hyperboloid. A straight cone shape would also be possible.
  • the axially outwardly radially concave shape of the However, depressions 10 results per well 10 an advantageously large ratio of mouth cross-sectional area to volume.
  • the depressions 10 are formed exactly at the apex of the tooth feet, with the root circle F cutting in the apex axial / radial plane as the plane of symmetry.
  • the mouths of the recesses 10 are formed and arranged on the end face of the inner gear 10 in this way. From these mouths, however, the depressions 10 may well also run straight obliquely or arcuately to the axial to the respective web 11 in order to influence the Einströmmik in the relevant conveyor cell 7.
  • the inlet opening 5 and the outlet opening 6 are recessed in the posterior Kammerstirnwandung as kidney-shaped openings. They extend in the circumferential direction depending on several conveyor cells 7, wherein they cover the respective conveyor cells 7 radially.
  • the inlet opening 5 also radially overlaps the depressions 10.
  • the outlet opening 6 extends radially only up to the root circle of the external toothing 1a, so that no fluid is displaced directly from the depressions 10.
  • the comments made regarding the inlet opening 5 and the outlet opening 6 also apply to the inlet opening and the optionally existing outlet opening in the removed housing cover. In the housing cover, but no outlet opening must be formed. During the rotational movement of the toothed wheels 1 and 2, therefore, the recesses 10 sweep the inlet opening 5 and the axially opposite inlet opening in the housing cover.
  • FIGS. 5 and 6 the volumetric efficiency E is plotted against the speed R of the driven gear 1.
  • Fig. 5 shows the curve of the volumetric efficiency E for an internal gear pump with a gear set without recesses
  • Fig. 6 shows for comparison the volumetric efficiency E for an internal gear pump according to the invention.
  • the internal gear pump forms the lubricating oil pump for a Verbrennungshubkolbenmotor a car or truck. This is a particularly preferred example of use for an internal gear pump according to the invention.
  • the installation situation of the pump is in this case such that the driven gear, in the example, the inner gear 1, with a speed R of up to 14,000 revolutions per minute (RPM) is driven, that is, it is from a crankshaft of the engine with a relation to the crankshaft translated speed driven. From a drive speed of about 7,000 rpm, the conventional pump uses cavitation. An arrow K indicates the beginning of cavitation. As the speed increases, the volumetric efficiency E decreases.
  • RPM revolutions per minute
  • the volumetric efficiency E of an internal gear pump identical in construction to those of the recesses 10 according to the invention is shown in FIG Fig. 6 applied in comparison.
  • the beginning of cavitation K can be shifted to significantly higher speeds.
  • the start of cavitation K could be shifted to a speed higher by about 2,000 rpm.
  • the volumetric efficiency E in the upwardly adjoining speed range decreases less sharply than in the case of the conventional internal gear pump without recesses.

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

Claims (9)

  1. Pompe à engrenage intérieur comportant :
    a) un carter (3),
    b) une chambre de roues dentées (4) formée dans le carter (3), laquelle chambre comporte une ouverture d'admission (5) sur un côté basse pression et une ouverture de refoulement (6) pour un fluide sur un côté haute pression,
    c) une roue dentée intérieure (1) reçue dans la chambre de roues dentées (4), laquelle roue dentée intérieure peut tourner autour d'un axe de rotation (D1) et comporte une denture extérieure (1a),
    d) une roue dentée extérieure (2) reçue dans la chambre de roues dentées (4), laquelle roue dentée extérieure comporte une denture intérieure (2i) qui engrène avec la denture extérieure (1a) et forme avec la denture extérieure des cellules de refoulement (7) en expansion du côté basse pression et en compression du côté haute pression lorsque les roues dentées (1, 2) sont entraînées en rotation,
    e) dans laquelle la denture intérieure (2i) de la roue dentée extérieure (2) comporte au moins une dent de plus que la denture extérieure (1a) de la roue dentée intérieure (1),
    f) et dans laquelle au moins un évidement (10) est formé dans des pieds de dents de la denture extérieure (1a) dans chaque base de pied de dent, lequel évidement s'étend jusqu'à une face frontale de la denture extérieure (1a) et dont la face frontale présente une profondeur radiale (T) plus grande que dans une zone intérieure de la base de pied de dent axialement espacée de la face frontale,
    g) et dans laquelle l'ouverture d'admission (5) axialement dirigée vers la face frontale de la denture extérieure (1a) recouvre les cellules de refoulement (7) et les évidements (10),
    caractérisée en ce que
    h) l'ouverture de refoulement (6) axialement dirigée vers la face frontale de la denture extérieure (1a) recouvre les cellules de refoulement (7) du côté haute pression, mais pas les évidements (10).
  2. Pompe à engrenage intérieur selon la revendication 1, caractérisée en ce qu'au moins un évidement (10) est formé dans des pieds de dents de la denture extérieure (1a) dans chaque base de pied de dent, lequel évidement s'étend jusqu'à l'autre face frontale de la denture extérieure (1a) et présente sur l'autre face frontale une profondeur radiale (T) plus grande que dans une zone intérieure de la base de pied de dent axialement espacée de l'autre face frontale.
  3. Pompe à engrenage intérieur selon l'une quelconque des revendications précédentes, caractérisée en ce que la profondeur (T) des évidements (10) augmente de manière continue jusqu'à la face frontale.
  4. Pompe à engrenage intérieur selon l'une quelconque des revendications précédentes, caractérisée en ce que les évidements (10) sont radialement concaves vers l'extérieur dans la direction axiale.
  5. Pompe à engrenage intérieur selon l'une quelconque des revendications précédentes, caractérisée en ce que les évidements (10) s'étendent jusqu'à un talon (11) restant dans la zone intérieure de chaque base de pied de dent respective d'un profil de dent, lequel talon forme de préférence le milieu axial de la denture extérieure (1a).
  6. Pompe à engrenage intérieur selon l'une quelconque des revendications précédentes, caractérisée en ce que les évidements (10) s'élargissent jusqu'à la face frontale jusqu'à laquelle ils s'étendent.
  7. Pompe à engrenage intérieur selon l'une quelconque des revendications précédentes, caractérisée en ce que les évidements (10) sont radialement concaves vers l'extérieur en coupe transversale.
  8. Pompe à engrenage intérieur selon la revendication précédente, caractérisée en ce que les évidements (10) sont hyperboloïdes.
  9. Pompe à engrenage intérieur selon l'une quelconque des revendications 1 à 3 ou 5 à 7, caractérisée en ce que les évidements sont coniques avec des génératrices rectilignes ou incurvées dans la direction axiale.
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
DE10245814A DE10245814B3 (de) 2002-10-01 2002-10-01 Innenzahnradpumpe mit verbesserter Füllung
DE10245814 2002-10-01

Publications (2)

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

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EP03020503A Expired - Lifetime EP1406015B1 (fr) 2002-10-01 2003-09-15 Pompe à engrenage interne avec remplissage amélioré

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AT (1) ATE517261T1 (fr)
DE (1) DE10245814B3 (fr)
ES (1) ES2369901T3 (fr)

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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
GB0620646D0 (en) * 2006-10-18 2006-11-29 Concentric Vfp Ltd Pumps with filling slots
DE102007040724A1 (de) 2007-08-29 2009-03-05 Robert Bosch Gmbh Förderaggregat
DE102008003843A1 (de) 2008-01-10 2009-07-16 Robert Bosch Gmbh Förderaggregat
WO2009130433A1 (fr) * 2008-04-22 2009-10-29 Concentric Vfp Limited Pompe avec fentes de remplissage
JP5591049B2 (ja) * 2010-09-30 2014-09-17 富士重工業株式会社 内接歯車式流体装置
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
US10563653B2 (en) 2016-01-12 2020-02-18 Hamilton Sundstrand Corporation Gear pump

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ES2369901T3 (es) 2011-12-09
ATE517261T1 (de) 2011-08-15
DE10245814B3 (de) 2004-02-12
EP1406015A1 (fr) 2004-04-07

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