EP1576290B1 - Machine a roues dentees comprenant des plaques laterales axiales - Google Patents

Machine a roues dentees comprenant des plaques laterales axiales Download PDF

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Publication number
EP1576290B1
EP1576290B1 EP03785863A EP03785863A EP1576290B1 EP 1576290 B1 EP1576290 B1 EP 1576290B1 EP 03785863 A EP03785863 A EP 03785863A EP 03785863 A EP03785863 A EP 03785863A EP 1576290 B1 EP1576290 B1 EP 1576290B1
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EP
European Patent Office
Prior art keywords
gear
type machine
sealing
machine according
grooves
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
EP03785863A
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German (de)
English (en)
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EP1576290A1 (fr
Inventor
Walter Wimmer
Matthias Fuchs
Ulrich Zuber
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.)
Concentric Hof GmbH
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Concentric Hof GmbH
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Filing date
Publication date
Application filed by Concentric Hof GmbH filed Critical Concentric Hof GmbH
Publication of EP1576290A1 publication Critical patent/EP1576290A1/fr
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Publication of EP1576290B1 publication Critical patent/EP1576290B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0023—Axial sealings for working fluid
    • F04C15/0026—Elements specially adapted for sealing of the lateral faces of intermeshing-engagement type machines or pumps, e.g. gear machines or 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
    • 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
    • F04C2/18—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 with similar tooth forms

Definitions

  • the invention relates to a gear machine in function as a gear pump or gear motor for one or two directions of rotation.
  • This gear machine has at least two gears, which roll together in external or internal engagement and the shaft journals are mounted in bearings.
  • These bearings may be formed as part of lids, or be formed as a bearing body in one or two parts, which are enclosed together with the gears of a housing of the gear machine.
  • a gear pump with a similar construction as that of the DE 41 24 466 A1 known gear machine goes out of the JP 4112981 A out.
  • This has two gears, two adjacent to the gears side plates and bearing against these bearing body, being provided on the side plates facing and facing side surfaces of the bearing body defined by grooves sealing fields. Between the bearing bodies and the side plates there is a very low pressure.
  • the composite of side plates and bearing is also limited mobility, so that only partially a geometric gap compensation is possible.
  • the advantage of the invention described below is the design and arrangement of the sealing fields and sealing elements on the bearing body.
  • bearing bodies 11,16 in the gear machine these have on both end sides, ie on the gear and the lid facing the side surface grooves 10, 12, 15, 17 for receiving sealing elements, not shown here.
  • Due to the sealing elements inserted on both sides of the bearing bodies, pressure fields of the geared machine on the bearing body result in the formation of sealing fields which act as hydraulically active pressure compensation fields on the bearing bodies as well as on the side plates 13, 14 provided by axial force action.
  • FIG. 3 shows a bearing body 11 and that the gears 4 facing side surface which rests on a side plate 13.
  • the side surface of the groove 12 is introduced, which receives a sealing element 25, not shown here, the bottom of the reference FIG. 7 is explained.
  • a sealing field is defined.
  • the fact that the grooves are configured differently on the front and back of the bearing body, resulting in different sizes hydraulic forces on both sides of the bearing body, which press the bearing body against the housing 3 laterally bounding serving as a lid housing parts 2, 5.
  • the bearing body 11 is pressed by the hydraulic forces caused by the different sized sealing fields against the superior side plate 13. This is displaced axially in the opposite direction to the bearing body 11 by the hydraulic forces acting on both sides of a bearing body as well as on the hydraulically acted surface of the side plate.
  • the articulated movable side plate 13 is pressed against the end face of the gears 4, whereby an operating point-dependent adjusting, axial gap compensation allows optimum sealing action between side plate and bearing.
  • the side plate 14 facing side surface of the bearing body 16 is formed accordingly, so that also described here Adjust hydraulic forces and the side plate 14 is moved in the opposite direction to the bearing body 16 and also a quasi movable hinged side plate is realized.
  • FIG. 4 shows the gear wheels 4 and the side plate 13 opposite side surface of the bearing body 11.
  • the groove 10 is introduced, which in turn has the shape of a "3" or an " ⁇ ", but is oriented opposite, as shown on the FIG. 3 shown side is the case, which faces the side plate 13.
  • FIGS. 3 and 4 A comparison between the FIGS. 3 and 4 shows that large areas of the groove 10 lie on an imaginary concentric to the bearing openings or bearing bores L1 and L2 extending circles, wherein the radius of the circles of the groove 10 is greater than the radius of the circles of the groove 12 which in FIG. 3 is shown. In this way, sealing fields of different sizes are realized and constructed the above-mentioned different sized hydraulic forces.
  • the pressure fields on both sides of the bearing body 11 are in an area ratio between 1.5 and 2.0 to each other.
  • the larger pressure-loaded surface is provided as on the serving as a lid housing part 2 side surface of the bearing body 11. Accordingly, it is provided in the bearing body 16, that on the side plate 16 facing side surface is provided a larger pressurized surface than on the serving as a lid housing part 5 side surface of the bearing body 16th
  • the area ratio of the two pressure fields of each bearing body is selected to be 1.8.
  • This area ratio causes the bearing bodies 11, 16 to be displaced by the hydraulic forces against the laterally delimiting housing parts 2 and 5 of the gear machine.
  • the required for the articulation of the bearing bodies superior side plates 13, 14 sealing gap always formed between the bearing body and side plate, whereby the side plates are pressed against the end faces of the gears 4.
  • hydraulically active sealing fields are arranged on both sides of a bearing body in the high pressure loaded circular ring segments on concentrically shaped sealing fields.
  • the above-mentioned area ratio of the provided on the two sides of the bearing body sealing fields is thus realized in that the grooves 10 and 12 are arranged on both sides of the bearing body on imaginary circular lines which are concentric to the center of the bearing openings L1 and L2, but different radii or Have diameter.
  • the larger diameter is carried out on the serving as a lid housing parts 2, 5 facing side of the bearing body.
  • the smaller pressure field is realized here.
  • the course of the grooves 10 and 12 in the side surfaces of the bearing body follows the shape of the numeral "3" or the letter “ ⁇ ", and indeed at a defined angle.
  • the ends of the groove 12 are at a distance to imaginary diameter lines of the bearing openings L1 and L2 and include with this line an angle ⁇ between 12 ° and 14 °, said angular range preferably symmetrical to the axial centers of the gears or to an imaginary horizontal center axis M2 is arranged. This is evident FIG. 3 ,
  • FIG. 3 also shows that defined pressure supply grooves 19, 20, 21 are provided in the bearing bodies at the parting plane between the bearing body 11 and the side plate 13, ie also at the parting plane between the bearing body 16 and the side plate 14.
  • two Druckzu Documentnuten 19 and 21 in the region of an imaginary vertical center axis M1 above and below.
  • a Druckzu slaughternut 20 is provided which is arranged symmetrically to the imaginary center axis M2.
  • This balancing movement hydraulically adjusts a minimum gap between the side plates 13, 14 and the rotating gears 4 under all operating conditions of the gear machine, which causes the flow of fluid from high pressure areas to areas of low pressure to be minimized.
  • optimum volumetric efficiencies are set depending on the operating point.
  • FIG. 5 shows a cross section through the bearing body 11.
  • the bearing body 16 is constructed in mirror image. In this respect, what has been said about the bearing body 11 applies accordingly.
  • the grooves 10 and 12 are formed differently, wherein the groove 12 has a substantially U-shaped cross-section and the groove is more of a rectangular cross-section.
  • the different cross sections can be seen in the magnifications W and U, where U represents the cross section of the groove 10 and W the cross section of the groove 12.
  • the shape of the groove 12 is characterized in that it extends from the side surface of the bearing body 11 to the groove bottom N1 out at an angle between 3 ° and 16 ° conical, preferably an angle of 8 ° is selected.
  • the groove 12 merges on both sides over a radius in the groove bottom N1.
  • This conical Nutrise increases on the one hand, the fatigue strength of the remaining Restmatrialstegs between sealing ring and bearing bore L1, L2 in the bearing bodies, on the other causes this Nutnosti when pressurizing the in FIG. 5 not shown sealing elements a defined planar contact of the sealing elements on the side surface of the groove 12. This improves the sealing effect and reduces the wear of the sealing elements.
  • the transition radius between groove flank and groove bottom N1 of the groove 12 is chosen so large that practically results in a U-shaped groove cross-section.
  • the cross section of the groove 10 is substantially rectangular.
  • the groove 10 thus has a practically flat groove bottom N2 and two practically perpendicular thereto groove flanks, which pass over a smaller radius in the groove bottom N2 than it is provided in the groove 12.
  • the side plates 13, 14 are coated with a wear resistant material, for example, tungsten disulfide or PVD coated base materials of aluminum or steel are used.
  • the side plates 13, 14 are made of such a wear-resistant material, such as WC / C, SiC, ALO. 2
  • Particularly preferred are multilayer materials on the Base of St / CuPbSn alloys, wherein the hardness of the applied coating material between 55 and 100 HB and the hardness of the support material between 100 and 145 HB is executed.
  • Wear-resistant base materials made of CuPbSn or similar alloys in a hardness range between 65 and 120 HB are also used.
  • the thickness of the side plates 13, 14 is carried out depending on the material used so that over the horizontal and vertical center axis M1, M2 of the side plate a deflection is avoided by the pressurized surface portions.
  • a thickness of the side plate between 2.2 mm and 3.2 mm was preferably selected, with optimum results achieved at a plate thickness of 2.4 mm with a bronze coated side plate made of steel (St / CuPbSn alloy) were.
  • FIG. 6 shows seen in plan view a side plate 13 or 14.
  • the side plates are housed in housing bores. It is provided that the side plates in the area in which they are subjected to system pressure, not directly adjacent to the wall of the housing bores, but that a radial gap between the outer diameter of the side plates and the diameter of the housing bore remains.
  • at least one projection 23 is provided, which abuts with its radially outer outer surface against the wall of the housing bore and therefore has a similar diameter as the housing bore. Thus, therefore, the radial position of the side plates is defined in the housing bore.
  • the radial gap between side plate and housing causes a radial force acts on the radially projected surface of the side plate by the pressure load of the gear machine. This force presses the side plate sealingly against the high-pressure surfaces of the housing bore, thereby creating a radial, metallic seal of the side plates 13, 14 on the housing 13.
  • the outer contour of the side plates is selected so that the portion of the side plates contacting the gear machine housing extends through an angle ⁇ which is in a range of 100 ° to 150 ° measured from the center axes of the gears 4 and the bearing holes, respectively L1, L2.
  • Optimum sealing conditions are achieved in gear machines which are designed as pumps and have an angular range of approximately 110 °.
  • the side plates 13 and 14 are characterized in that for gear machines with flank contact of the gears 4 and for gear machines with two-flank contact of the gears 4 in the surfaces of the side plates, which face the end face of the gears 4, in FIG. 6 shown grooves 24 are introduced. These form together with the pitch of the toothing a sealing point between the high pressure and low pressure side of the gear unit.
  • these grooves 24 in the side plate 13, 14 are formed so that the rolling points the intermeshing gears 4 extend laterally sloping from the center axis of the side plate of the gear contacting surface at an angle from the center axis M2 to the outer contour of the side plate 13, 14 at an angle of 5 ° to the side surface of the side plate.
  • the grooves 24 can be parallel to the end face with a distance of at least 1 mm of the gear pointing surface. This causes in cog wheels with two-flank contact damping of trapped Quetschölanteils in the meshing region and gears with flank engagement a clear definition of the sealing point between the high pressure and low pressure region in the gear machine. This leads to a reduced vibration excitation both in Zwefllankenals as well as in a flank engagement of the toothing, which contributes to a reduced noise emission of the gear machine.
  • the hydraulically active engagement lines which are formed by the surfaces of the side plates 13, 14 facing the toothed wheels 4 on a connecting line of the rolling points of the intermeshing toothed wheels 4 and the grooves 24, are thus designed in the case of one and two flank engagement of the toothing the high-pressure grooves 24r, 24r 'with respect to the low pressure acted upon grooves 241, 24l 'of the side plate 13, 14 is displaced in a range between 40% and 60% to the central axis M1 asymmetrically to the low pressure side.
  • the right-hand side of the central axis M1 is the high-pressure region and the left-hand region of the central axis M1 is the low-pressure region.
  • the pilot geometry to the center axis M1 symmetrically between high-pressure and low-pressure side is executed.
  • sealing elements made of polyurethane can be used to avoid Spaltelextrusion.
  • the arrangement of the side plates 13, 14 and the bearing body 11, 16 is an axial compensation for the axial and radial gap compensation between the axially moving and opposing surfaces allows on the gear face and the superior side plates. This is called articulated compensation.
  • the grooves 10, 12 for receiving the sealing elements can, as described, be arranged in the bearing bodies, or else alternatively in the side plates and in the bearing bodies facing side surfaces of the housing parts 2, 5th
  • FIG. 7 shows a sealing element 25 which can be inserted into the groove 12.
  • FIG. 8 shows a sealing element 27 which is inserted into the groove 10 of the bearing body 11, 16.
  • the sealing materials used are each tuned to the fluid used in the system. Other materials can also be used.
  • the sealing elements 25 and 27 are preferably designed so that they have an increased strength against gap extrusion or gap wear in the sealing area between high-pressure and low-pressure field.
  • the ends of the lying between the bearing body and side plates sealing element 25 are L-shaped and optionally thickened. With the L-shaped ends 29, the sealing element 25 is securely anchored. It engages in corresponding recesses 31 of the groove 12, which in FIG. 3 are shown.
  • Sectional cross-sectional thickenings may also be provided, which also provide increased strength against gap extrusion or gap wear in the sealing area between the high-pressure and low-pressure fields.
  • partial thickenings 33 may be provided to form elastic portions with a corresponding bias, through which the respective sealing element is held in the associated groove 10. Such thickening may also be provided at the ends of the seals 27.
  • the gear machine of the type described here is characterized in that the reaction forces, which are absorbed by pressure load of the gear machine in the bearing bodies and are supported against the housing 3, are applied through the bearing body by the realization of the articulated composite of superior side plate and bearing body.
  • the axial compensation which causes a planar contact of the side plates 13, 14 on the end faces of the gears 4 and thus an optimized gap compensation takes place free of bearing load forces of the gear machine via the side plates 13, 14th

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

Claims (20)

  1. Machine à engrenages, pompe ou moteur à engrenages comprenant au moins deux engrenages, deux plaques latérales reposant sur les engrenages et des corps d'appui reposant sur celles-ci, dans lequel/laquelle des champs d'étanchéité configurés de manière différente sont prévus sur les surfaces latérales des corps d'appui tournées vers et détournées des plaques latérales, lesquels champs d'étanchéité sont définis par des rainures, les champs d'étanchéité des rainures (10, 12) présentant différentes formes et la machine à engrenages étant conçue pour un ou deux sens de rotation, caractérisé(e) en ce que le diamètre supérieur de la rainure d'étanchéité est disposé sur la surface latérale des corps d'appui (11, 16) détournée des engrenages (4).
  2. Machine à engrenages selon la revendication 1, caractérisée en ce que la section transversale des rainures (10, 12) prévues sur les surfaces latérales opposées des corps d'appui (11, 16) diffère.
  3. Machine à engrenages selon la revendication 1 ou 2, caractérisée en ce que le composite constitué des deux corps d'appui et plaques latérales (11, 13 ; 14, 16) est disposé, vu en direction axiale, de manière réfléchie vu depuis le milieu des dents.
  4. Machine à engrenages selon l'une quelconque des revendications précédentes, caractérisée en ce que les champs de pression sont réalisés des deux côtés d'un bloc d'appui dans un rapport de surface compris entre 1,5 et 2, de préférence dans un rapport de surface de 1,8 l'un par rapport à l'autre.
  5. Machine à engrenages selon l'une quelconque des revendications précédentes, caractérisée en ce que les champs d'étanchéité activés par voie hydraulique sont concentriques les uns par rapport aux autres des deux côtés des corps d'appui (11, 16) dans les segments d'anneau de cercle sollicités à haute pression.
  6. Machine à engrenages selon l'une quelconque des revendications précédentes, caractérisée en ce que des rainures d'amenée de pression (19, 20, 21) définies au niveau du plan de séparation entre corps d'appui (11, 16) et plaque latérale (13, 14), qui peuvent être sollicitées avec de la pression du système, sont prévues.
  7. Machine à engrenages selon l'une quelconque des revendications précédentes, caractérisée en ce que les plaques latérales (13, 14) se composent de matériau résistant à l'usure, dans laquelle la dureté du matériau en couche appliqué se situe entre 55 et 100 HB et la dureté du matériau support entre 100 et 145 HB.
  8. Machine à engrenages selon la revendication 7, caractérisée en ce que les plaques latérales se composent de matériau multicouches.
  9. Machine à engrenages selon l'une quelconque des revendications précédentes, caractérisée en ce qu'une fente radiale est prévue au moins par région entre les plaques latérales (13, 14) et le logement (3).
  10. Machine à engrenages selon l'une quelconque des revendications précédentes, caractérisée en ce que les champs d'étanchéité peuvent être définis aussi bien pour un engrènement d'un seul flanc que pour un engrènement de deux flancs des engrenages (4).
  11. Machine à engrenages selon l'une quelconque des revendications précédentes, caractérisée en ce que des rainures (24) qui forment avec le point primitif de la denture un point d'étanchéité entre côté haute pression et côté basse pression du module d'engrenage peuvent être introduites dans la surface latérale des plaques latérales (13, 14) qui est tournée vers les engrenages (4).
  12. Machine à engrenages selon l'une quelconque des revendications précédentes, caractérisée en ce que, dans le cas de machines à engrenages avec engrènement de deux flancs, les rainures déclinent d'un angle, de préférence de 5°, par rapport à l'axe médian (M1) vers le contour externe de la plaque latérale, vers la surface touchant les engrenages (4).
  13. Machine à engrenages selon l'une quelconque des revendications précédentes 1 à 12, caractérisée en ce que les rainures s'étendent parallèlement à la face frontale dans le cas de machines à engrenages avec contact d'un seul flanc.
  14. Machine à engrenages selon l'une quelconque des revendications précédentes 11 à 13, caractérisée en ce que les rainures (24) sont disposées de manière asymétrique dans la surface de la plaque latérale tournée vers les engrenages (4) et que les rainures sollicitées à haute pression (24r, 24r') atteignent plus près l'axe médian (M1) que les rainures sollicitées à basse pression (241, 24l').
  15. Machine à engrenages selon l'une quelconque des revendications précédentes 1 à 13, caractérisée en ce que les rainures sont disposées de manière symétrique dans la surface de la plaque latérale tournée vers les engrenages (4).
  16. Machine à engrenages selon l'une quelconque des revendications précédentes, caractérisée en ce qu'un élément d'étanchéité (25) est à chaque fois disposé dans la fente d'étanchéité entre corps d'appui (11, 16) et plaque latérale (13, 14) et/ou qu'un élément d'étanchéité (27) est à chaque fois disposé dans la fente d'étanchéité entre corps d'appui et partie de logement (2, 5) du logement (3).
  17. Machine à engrenages selon l'une quelconque des revendications précédentes, caractérisée en ce que les éléments d'étanchéité (25, 27) se composent d'éléments d'étanchéité élastiques d'une pièce ou d'éléments de deux pièces, l'un adoptant une fonction de support et l'autre adoptant une fonction d'étanchéité.
  18. Machine à engrenages selon l'une quelconque des revendications précédentes, caractérisée en ce que les forces réactionnelles qui sont reçues dans les corps d'appui par la sollicitation en pression de la machine à engrenages et sont supportées contre le logement (3), sont absorbées par le biais des corps d'appui par le composite articulé entre plaque latérale (13, 14) et corps d'appui (11, 16).
  19. Machine à engrenages selon l'une quelconque des revendications précédentes, caractérisée en ce que les extrémités de l'élément d'étanchéité (25) présentent des épaississements, de préférence des épaississements en L.
  20. Machine à engrenages selon l'une quelconque des revendications précédentes, caractérisée en ce que l'élément d'étanchéité (27) présente des épaississements partiels dans son tracé et/ou aux extrémités.
EP03785863A 2002-12-19 2003-12-18 Machine a roues dentees comprenant des plaques laterales axiales Expired - Lifetime EP1576290B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10261764 2002-12-19
DE10261764 2002-12-19
PCT/EP2003/014440 WO2004057193A1 (fr) 2002-12-19 2003-12-18 Machine a roues dentees comprenant des plaques laterales axiales

Publications (2)

Publication Number Publication Date
EP1576290A1 EP1576290A1 (fr) 2005-09-21
EP1576290B1 true EP1576290B1 (fr) 2013-02-20

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EP03785863A Expired - Lifetime EP1576290B1 (fr) 2002-12-19 2003-12-18 Machine a roues dentees comprenant des plaques laterales axiales

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EP (1) EP1576290B1 (fr)
JP (1) JP2006510841A (fr)
AU (1) AU2003294889A1 (fr)
WO (1) WO2004057193A1 (fr)

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DE102007060758A1 (de) * 2007-12-17 2009-06-18 Robert Bosch Gmbh Flüssigkeitspumpe
ITMI20090045U1 (it) * 2009-02-16 2010-08-17 Fluid O Tech Srl Pompa volumetrica ad ingranaggi perfezionata
DE102009012853A1 (de) 2009-03-12 2010-09-16 Robert Bosch Gmbh Hydraulische Zahnradmaschine
DE102009012916A1 (de) * 2009-03-12 2010-09-16 Robert Bosch Gmbh Hydraulische Zahnradmaschine
DE102009012854A1 (de) * 2009-03-12 2010-09-16 Robert Bosch Gmbh Hydraulische Zahnradmaschine
DE102013202918A1 (de) * 2013-02-22 2014-08-28 Robert Bosch Gmbh Zahnradmaschine mit einem Stützkörper für eine Axialfelddichtung
KR101339451B1 (ko) 2013-05-03 2013-12-06 주식회사조양 소음방지수단이 일체 형성되는 기어식 차량 조향펌프
DE102016124849A1 (de) * 2016-12-19 2018-06-21 Schaeffler Technologies AG & Co. KG Zahnradpumpe
DE102018104976A1 (de) 2018-03-05 2019-09-05 Schaeffler Technologies AG & Co. KG Außenzahnradmaschine
DE102018106857A1 (de) 2018-03-22 2019-09-26 Schaeffler Technologies AG & Co. KG Hydraulikbaugruppe zum Deaktivieren einer Axialspaltkompensation
DE102021100341A1 (de) 2021-01-12 2022-07-14 Schaeffler Technologies AG & Co. KG Außenzahnradmaschine
DE102021100339A1 (de) 2021-01-12 2022-07-14 Schaeffler Technologies AG & Co. KG Außenzahnradmaschine

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DE1553133A1 (de) * 1966-12-23 1970-07-30 Maag Zahnraeder & Maschinen Ag Hochdruck-Zahnradpumpe
JPS5943687U (ja) * 1982-09-16 1984-03-22 カヤバ工業株式会社 ギヤポンプ又はモ−タの液圧密封構造
JPH0543275Y2 (fr) * 1986-12-29 1993-10-29
JP2787706B2 (ja) * 1989-04-30 1998-08-20 株式会社島津製作所 歯車ポンプ
JPH03123991U (fr) * 1990-03-28 1991-12-17
JPH03123992U (fr) * 1990-03-30 1991-12-17
JP2794918B2 (ja) * 1990-08-31 1998-09-10 株式会社島津製作所 歯車ポンプ
DE4124466C2 (de) 1991-07-24 1999-04-01 Bosch Gmbh Robert Zahnradmaschine (Pumpe oder Motor)
JP4172877B2 (ja) * 1999-05-26 2008-10-29 株式会社小松製作所 歯車ポンプ

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EP1576290A1 (fr) 2005-09-21
AU2003294889A1 (en) 2004-07-14
WO2004057193A1 (fr) 2004-07-08
JP2006510841A (ja) 2006-03-30

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