EP2711552B1 - Machine à roue dentée pourvue d'un raccord basse pression déviant de la forme circulaire - Google Patents

Machine à roue dentée pourvue d'un raccord basse pression déviant de la forme circulaire Download PDF

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Publication number
EP2711552B1
EP2711552B1 EP13181924.5A EP13181924A EP2711552B1 EP 2711552 B1 EP2711552 B1 EP 2711552B1 EP 13181924 A EP13181924 A EP 13181924A EP 2711552 B1 EP2711552 B1 EP 2711552B1
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EP
European Patent Office
Prior art keywords
low
gear
pressure connection
gear wheels
cross sectional
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.)
Active
Application number
EP13181924.5A
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German (de)
English (en)
Other versions
EP2711552A3 (fr
EP2711552A2 (fr
Inventor
Volker Fissler
Michael Wilhelm
Christian Boehmcker
Michael Fischer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
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Publication of EP2711552A3 publication Critical patent/EP2711552A3/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
    • F04C2/12—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
    • 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
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • 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
    • F04C2250/00—Geometry
    • F04C2250/10—Geometry of the inlet or outlet
    • F04C2250/101—Geometry of the inlet or outlet of the inlet

Definitions

  • the invention relates to a gear machine according to the preamble of claim 1.
  • the gear machine From the DE 10 2009 012 853 A1 is a gear machine known, which can be operated as a pump or as a motor.
  • the gear machine comprises two meshing with each other in external engagement gears, which are surrounded by a housing.
  • the housing has opposite a high and a low pressure port.
  • gear machine When the gear machine is operated as a pump, one of the gears is rotated, for example, with an electric motor in rotary motion, wherein pressurized fluid, in particular hydraulic oil, flows from the low to the high pressure port.
  • pressurized fluid in particular hydraulic oil
  • the gear machine When the gear machine is operated as a motor, the pressurized fluid flows from the high to the low pressure port, thereby causing the gears to rotate.
  • the low-pressure connection has a constant cross-sectional shape in the direction of a central axis, which is circular.
  • the corresponding circle diameter is attempted to be as large as possible at the low-pressure connection so that low flow velocities of the pressure fluid occur there. This avoids cavitation at the low-pressure connection, especially for pumps with high-speed gears.
  • the diameter of the low-pressure connection can only be increased so far as there is still a sufficient seal between the high and the low pressure connection is given to the tooth tips of the gears.
  • the bearing bodies are arranged on both sides next to the gears and are pressed by the pressure fluid sealingly against the side surfaces of the gears.
  • the gears are mounted with circular cylindrical bearing pin in the bearing bodies.
  • the bearing body on one side of the gears may be integrally formed, but it is equally conceivable to assign each gear a separate part of the bearing body.
  • Each gear is associated with at least one Druckaus GmbHsfase on the bearing bodies, which is arranged opposite to the side surfaces of the gears and the inner peripheral surface.
  • the inner peripheral surface is the surface against which the tooth tips of the gear wheels sealingly abut.
  • the pressure equalization bevel extends from the high pressure port towards the low pressure port. In all interdental spaces of the gears, which are the Druckaus GmbHsfase opposite, there is therefore the pressure at the high pressure port, so that the gears are pressed with a good predictable force sealing against the inner peripheral surface of the housing in the region of the low pressure port to effect a seal there.
  • the low-pressure port referred to as the inlet, extends into the region of the casing-gear wrap.
  • the object of the invention is to avoid at high-speed gear machines, especially pumps, cavitation at the low-pressure connection or to use only at higher speeds of the gears.
  • both gears on the inner peripheral surface of the housing is associated with an imaginary boundary line which intersects the end of the Druckaus GmbHsfase, wherein it is parallel to the line of contact between the tooth tips of the gears and the inner peripheral surface, wherein the cutting edge between the two boundary lines is arranged, wherein the minimum distance between the cutting edge and the boundary lines is at least one pitch of the gears, wherein the cross-sectional shape of the low pressure port deviates from the circular shape such that its cross-sectional area covering the gears is greater than the cross-sectional area of an imaginary one covering the gears circular low pressure port, which has the same minimum distance to the boundary lines.
  • a gear two Druckaus GmbHsfasen are assigned, they are preferably designed so that they define the same boundary line. If this is not the case in exceptional cases, then the boundary line which has the smallest distance to the low-pressure connection is decisive.
  • the proposed gear machine has a low-pressure port, which has a larger cross-sectional area than the prior art. As a result, the flow velocities are reduced at the low pressure port, so that cavitation occurs only at higher speeds of the gears.
  • said minimum distance along the inner peripheral surface of the housing is measured, namely in the circumferential direction with respect to the axis of rotation of the respective gear. The same applies to the pitch of the gears, so the distance between two tooth heads, too.
  • the cross-sectional shape of the low-pressure connection may be formed so that the cutting edge has a constant distance to the associated boundary line.
  • the cross-sectional shape of the low pressure port may include two first straight lines each extending substantially parallel to an associated boundary.
  • the first straight lines can be made much simpler than the ideal cross-sectional shape described above.
  • the cutting edge between the inner peripheral surface and the low-pressure connection no longer runs exactly parallel to the boundary lines.
  • the deviation is so small that no appreciable deterioration in terms of cavitation formation is to be feared.
  • the ideal state proposed above is realized.
  • the two first straight lines may be connected by at least one, preferably two, second straight lines which run in alignment with the side surfaces of the toothed wheels. This results in the largest possible cross-sectional area of the low-pressure connection.
  • the two first straight lines can be connected to one another by at least one, preferably two, circular arcs.
  • This cross-sectional shape is preferably used when a standardized flange is provided at the low pressure port outside the housing, which is provided for a circular passage opening for the pressurized fluid.
  • the larger of said arcs is preferably formed in alignment with the standardized circular passage opening, in particular having the same radius.
  • the cross-sectional shape of the low pressure port may have rounded corners, so that it can be easily manufactured with an end mill.
  • the radius of the corners corresponds to the radius of the end mill.
  • the cross-sectional shape of the low-pressure connection can be formed by a plurality, preferably two or three, intersecting circles which offset one another Have midpoints.
  • a further simplification of the production is to be achieved.
  • it is intended to produce said circles by separate drilling operations, wherein the axis of rotation of the respective drill are offset from each other. With the preferred two or three holes already a significant improvement in cavitation tendency can be achieved.
  • the low-pressure connection can cover at least one bearing body.
  • Fig. 1 shows a longitudinal section of a gear machine 10 according to the invention.
  • the gear machine 10 comprises a housing 20, which consists of a main body 30; a drive cover 21 and an end cover 22 is composed, which preferably consist of aluminum or gray cast iron.
  • the drive and the end cover 21; 22 abut on flat end surfaces at the opposite ends of the main body 30, wherein at the end faces O-rings 24 are provided made of an elastomer, so that no pressure fluid can escape from the corresponding joint.
  • the drive and the end cover 21; 22 are aligned over cylindrical pins 26 relative to the main body 30 and screwed (not shown) with these bolts firmly.
  • two gears 50 are rotatably received with respect to an associated axis of rotation 51, wherein the gears 50 mesh with each other in external engagement.
  • the aforementioned axes of rotation 51 run parallel to one another.
  • the gears 50 are present helically toothed, but they can also be formed straight toothed. It should be noted that the invention underlying Kavitationsproblematik occurs primarily in helical gears.
  • the two gears 50 have on both sides of a circular cylindrical bearing pin 52 which is rotatably mounted in a bearing shell 61 made of a sliding bearing material such as brass or bronze, wherein the bearing shell 61 is in turn firmly received in an associated bearing body 60 made of steel.
  • each bearing pin 52 is associated with a separate part of the bearing body 60, wherein two adjacent parts abut each other on flat surfaces and are aligned by means of a cylindrical pin 26 to each other.
  • the bearing body 60 may also be integrally formed.
  • the bearing bodies 60 are pressed by the pressure of the pressurized fluid, for example hydraulic oil, in the gear machine 10 against the flat side surfaces 55 of the gears 50 to effect a lateral sealing of the gears 50.
  • the pressurized fluid acts In this case, in a pressure field on the bearing body 60, which is bounded by an associated axial seal 62.
  • One of the bearing journals 52 of a toothed wheel 50 is formed integrally with a drive pin 53 which projects out of the housing 20 through the drive cover 21.
  • the corresponding passage opening is sealed with a radial shaft sealing ring 25, so that no pressure fluid can escape.
  • the drive pin 53 can be rotatably connected, for example, with the drive shaft of an electric motor (not shown) when the gear machine 10 is operated as a pump.
  • the inner circumferential surface 31 of the main body 30 has a constant cross-sectional shape along the axes of rotation 51 prior to the run-in process, which is adapted to the circular cylindrical tip diameter of the gears 50 with very little play.
  • the pressure equalization land 64 is disposed opposite to the side surface 55 of an associated gear 50 and opposite to the inner peripheral surface 31 of the housing 20.
  • Fig. 2 shows a cross section of a gear machine according to the invention 10.
  • the high and the low pressure port 32; 33 are disposed opposite to the housing 20, having a common center axis 34 along which they have a constant cross-sectional shape.
  • the high-pressure port 32 preferably has a circular cross-sectional shape, wherein the cross-sectional shape of the low-pressure port 33 deviates according to the invention from the circular shape.
  • the already mentioned pressure compensating bevel 64 extends from the high pressure port 32 in the direction of the low pressure port 33. It has an end 65 which is arranged at a distance from the low pressure port 33.
  • the gears 50 are acted upon by a hydraulic force 84, which presses its tooth tips 56 against the inner circumferential surface 31 of the housing 20 in a sealing region 11 on the low-pressure connection 34. Only there takes place at the tooth tips 56 a sealing contact with the housing 20. The remaining tooth tips 56 run with a small distance to the inner peripheral surface 31 to the housing 20 so that there pressure fluid between the interdental spaces 54 can be replaced.
  • the Druckausticiansfase 64 may be present as shown only on one side of the gears 50, but it may also be provided on both sides of the gears 50. In the latter case is to be considered in helical gears 50 that the two pressure equalization bevels 64 must be designed to have different lengths, so that they end at the same tooth of the associated gear 50.
  • Fig. 3 shows a rough schematic front view of the gears 50 and the bearing body 60, wherein the ideal shape of the low pressure port 33 is shown.
  • the viewing direction is parallel to the central axis of the low-pressure connection 33, so that its cross-sectional shape coincides with the cutting edge 85 with the inner peripheral surface of the housing.
  • the two imaginary boundary lines 80 run parallel to the helical contact lines 83 between the tooth tips of the gears 50 and the inner peripheral surface of the housing.
  • the boundary lines 80 therefore extend on the inner peripheral surface of the housing.
  • the border lines 80 each begin at the end 65 of an associated pressure equalization bevel 64 on the bearing body 60.
  • the cross-sectional shape of the low-pressure connection 33 runs parallel to these in the region of the boundary lines 80.
  • the minimum distance 81 from the boundary lines 80 is therefore the same everywhere, so that a maximum cross-sectional area of the low-pressure connection 33 covering the toothed wheels results.
  • This cross-sectional area is in Fig. 3 hatched marked and marked with the reference numeral 79.
  • the cross-sectional shape of the low pressure port 33 is aligned with the side surfaces 55 of the gears 50. In gears 50 with a very large helix angle, it may happen that the low pressure port 33, the in Fig. 3 right side surface 55 of the gears 50 no longer covered.
  • FIG. 3 an imaginary low-pressure port 82 is shown, which has the same minimum distance 81 to the boundary lines 80.
  • the corresponding circle 82 covers the bearing bodies 60, the corresponding surface section 78 not counting the cross-sectional area 79 covering the toothed wheels 50.
  • the fraction of the hatched area 79 detected by the circle 82 is significantly smaller than the hatched area 79 itself, so that the condition according to the characterizing portion of claim 1 is satisfied.
  • the minimum distance 81 between the low pressure port 33 and the boundary line 80 is at least one pitch (No. 57 in FIG Fig. 2 ) of the gears, wherein it is preferably selected to be slightly larger, so that regardless of the rotational position of the gears at least one tooth head completely rests against the inner peripheral surface of the housing.
  • Fig. 4 shows a front view of the low pressure port 33 according to a first embodiment of the invention.
  • the viewing direction is parallel to the central axis of the low pressure port 33.
  • the two boundary lines 80 and the two side surfaces 55 of the gears are shown by dash-dotted lines.
  • the cross-sectional shape of the low-pressure connection 33 has two first straight lines 70, which run essentially parallel to the associated boundary line 80.
  • the two first straight lines 70 are connected by two second straight lines 71, which are arranged in alignment with the side surfaces 55 of the gears. If the gears have a very large width and / or a very large helix angle, it can occur that the first two lines 70 intersect in the area of the gears. In this case, the in Fig. 4 right straight 71.
  • the corners between the first and second straight lines 70; 71 are rounded 74, so that the present low pressure connection can be easily made with an end mill.
  • the corner radius 74 is, for example, 5 mm or 7.5 mm. On the rounding 74 but can also be dispensed with.
  • the low pressure port 33 according to the first embodiment according to Fig. 4 covered with its entire cross-sectional area 79, the gears.
  • the corresponding cross-sectional shape is mirror-symmetrical with respect to a plane of symmetry 86 which contains the central axis of the low-pressure connection 33.
  • Fig. 5 shows a front view of the low pressure port 33 according to a second embodiment of the invention. Except for the differences described below, this embodiment is consistent with the first embodiment Fig. 4 so that reference is made to the corresponding statements. The viewing direction of Fig. 5 agrees with the one of Fig. 4 match.
  • the second straight lines were replaced by arcs 73, which are arched outward.
  • the radius of in Fig. 5 Left circular arc 73 corresponds to the radius of the passage opening, which has a standardized flange with a circular passage opening.
  • the entire width of the low-pressure port 33 is preferably equal to or smaller than twice the said radius.
  • the present low-pressure port 33 covers with the areas 78 and the bearing body of the gear machine.
  • the gear cross-sectional cross-sectional area of the low pressure port 33 is the in Fig. 5 hatched area 79.
  • Fig. 6 shows a front view of the low pressure port 33 according to a third embodiment of the invention. The viewing direction agrees with that of the 4 and 5 match.
  • This low pressure port 33 is formed by two circular holes 76 which overlap.
  • the corresponding cross-sectional shape is therefore composed of two circles 76 that overlap, having offset centers 77.
  • the centers 77 are arranged on the plane of symmetry 86 of the low-pressure connection 33.
  • three or more circles 76 may be provided, wherein two or three circles, the optimum compromise between manufacturing costs and the gear cross-sectional area 79 of the low pressure port 33 result.

Landscapes

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

Claims (8)

  1. Machine à roues dentées (10), en particulier pompe ou moteur, avec deux roues dentées (50) engrenant en prise extérieure l'une avec l'autre, qui sont enveloppées par un boîtier (20), qui présentent en position opposée un raccord haute pression et un raccord basse pression (32; 33), dans laquelle le raccord basse pression (33) présente dans la direction d'un axe central (34) une forme de section transversale constante, dans laquelle il forme une arête d'intersection (85) avec une surface périphérique intérieure (31) du boîtier (30), qui est appliquée de façon étanche sur les têtes de dent (56) des roues dentées (50), dans laquelle un corps de palier (60), de préférence en plusieurs parties, est disposé respectivement de part et d'autre des roues dentées (50), dans lequel les roues dentées (50) sont montées de façon rotative, dans laquelle les corps de palier (60) sont appliqués de façon étanche sur une face latérale associée (55) des roues dentées (50), dans laquelle au moins un chanfrein d'équilibrage de pression (64) est associé aux deux roues dentées (50) sur les corps de palier (60), et s'étend en face de la roue dentée concernée (50) et de la surface périphérique intérieure (31) depuis le raccord haute pression (32) en direction du raccord basse pression (33), dans laquelle il présente à cet endroit une extrémité (65),
    caractérisée en ce qu'une ligne de limitation imaginaire (80) est associée à la surface périphérique intérieure (31) du boîtier (20), qui coupe l'extrémité (65) du chanfrein d'équilibrage de pression (64), dans laquelle elle est parallèle à la ligne de contact (83) entre les têtes de dent (56) des roues dentées (50) et de la surface périphérique intérieure (31), dans laquelle l'arête d'intersection (85) est disposée entre les deux lignes de limitation (80), dans laquelle la distance minimale (81) entre l'arête d'intersection (85) et les lignes de limitation (80) vaut au moins une distance de pas (57) des roues dentées (50), dans laquelle la forme de la section transversale du raccord basse pression (33) s'écarte de la forme circulaire, de telle manière que sa surface de section transversale (79) recouvrant les roues dentées (50) soit plus grande que la surface de section transversale recouvrant les roues dentées (50) d'un raccord basse pression circulaire imaginaire (82), qui présente la même distance minimale (81) des lignes de limitation (80).
  2. Machine à roues dentées selon la revendication 1, dans laquelle la forme de section transversale du raccord basse pression (33) est configurée de telle manière que l'arête d'intersection (85) présente une distance constante (81) de la ligne de limitation associée (80).
  3. Machine à roues dentées selon l'une quelconque des revendications précédentes, caractérisée en ce que la forme de section transversale du raccord basse pression (33) présente deux premières droites (70), qui sont chacune essentiellement parallèles à une ligne de limitation associée (80).
  4. Machine à roues dentées selon la revendication 3, dans laquelle les deux premières droites (70) sont reliées par au moins une, de préférence deux, deuxièmes droites (71), qui s'étendent en alignement avec les faces latérales (55) des roues dentées (50).
  5. Machine à roues dentées selon la revendication 3, dans laquelle les deux premières droites (70) sont reliées l'une à l'autre par au moins un, de préférence deux, arcs de cercle (73).
  6. Machine à roues dentées selon l'une quelconque des revendications précédentes, dans laquelle la forme de section transversale du raccord basse pression (33) présente des coins arrondis.
  7. Machine à roues dentées selon la revendication 1 ou 2, dans laquelle la forme de section transversale du raccord basse pression (33) est formée par plusieurs, de préférence deux ou trois, cercles (76) qui se coupent, qui présentent des centres décalés l'un par rapport à l'autre (77).
  8. Machine à roues dentées selon l'une quelconque des revendications 1 à 3 ou 5 à 7, dans laquelle le raccord basse pression (33) recouvre au moins un corps de palier (60) .
EP13181924.5A 2012-09-24 2013-08-28 Machine à roue dentée pourvue d'un raccord basse pression déviant de la forme circulaire Active EP2711552B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102012217115.0A DE102012217115A1 (de) 2012-09-24 2012-09-24 Zahnradmaschine mit von der Kreisform abweichendem Niederdruckanschluss

Publications (3)

Publication Number Publication Date
EP2711552A2 EP2711552A2 (fr) 2014-03-26
EP2711552A3 EP2711552A3 (fr) 2017-05-31
EP2711552B1 true EP2711552B1 (fr) 2019-02-27

Family

ID=49036461

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13181924.5A Active EP2711552B1 (fr) 2012-09-24 2013-08-28 Machine à roue dentée pourvue d'un raccord basse pression déviant de la forme circulaire

Country Status (3)

Country Link
US (1) US9140258B2 (fr)
EP (1) EP2711552B1 (fr)
DE (1) DE102012217115A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6464640B2 (ja) * 2014-09-30 2019-02-06 ダイキン工業株式会社 歯車ポンプ又はモータ
WO2016147217A1 (fr) * 2015-03-17 2016-09-22 株式会社Tbk Pompe à engrenages
JP2017223197A (ja) * 2016-06-17 2017-12-21 住友精密工業株式会社 液圧装置
WO2021044570A1 (fr) * 2019-09-05 2021-03-11 株式会社島津製作所 Pompe à engrenages hélicoïdaux ou moteur à engrenages hélicoïdaux

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1554262A (en) * 1975-06-24 1979-10-17 Kayaba Industry Co Ltd Gear pump
DE2554105C2 (de) * 1975-12-02 1984-04-05 Robert Bosch Gmbh, 7000 Stuttgart Zahnradmaschine (Pumpe oder Motor)
JPS55101786A (en) * 1979-01-26 1980-08-04 Kayaba Ind Co Ltd Construction of body bore in gear pump or motor
US5190450A (en) * 1992-03-06 1993-03-02 Eastman Kodak Company Gear pump for high viscosity materials
JP3830313B2 (ja) * 1999-09-06 2006-10-04 株式会社ジェイテクト ギヤポンプ
DE102007031909A1 (de) * 2007-07-09 2009-01-15 Schwäbische Hüttenwerke Automotive GmbH & Co. KG Umlaufverdrängerpumpe mit Druckpulsation minderndem Auslass
DE102009012853A1 (de) * 2009-03-12 2010-09-16 Robert Bosch Gmbh Hydraulische Zahnradmaschine

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

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Publication number Publication date
DE102012217115A1 (de) 2014-03-27
EP2711552A3 (fr) 2017-05-31
US20140086779A1 (en) 2014-03-27
US9140258B2 (en) 2015-09-22
EP2711552A2 (fr) 2014-03-26

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