EP1576290A1 - Machine a roues dentees comprenant des plaques laterales axiales - Google Patents

Machine a roues dentees comprenant des plaques laterales axiales

Info

Publication number
EP1576290A1
EP1576290A1 EP03785863A EP03785863A EP1576290A1 EP 1576290 A1 EP1576290 A1 EP 1576290A1 EP 03785863 A EP03785863 A EP 03785863A EP 03785863 A EP03785863 A EP 03785863A EP 1576290 A1 EP1576290 A1 EP 1576290A1
Authority
EP
European Patent Office
Prior art keywords
gear
machine according
sealing
gear machine
pressure
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
EP03785863A
Other languages
German (de)
English (en)
Other versions
EP1576290B1 (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
Original Assignee
Haldex Hydraulics 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 Haldex Hydraulics GmbH filed Critical Haldex Hydraulics GmbH
Publication of EP1576290A1 publication Critical patent/EP1576290A1/fr
Application granted granted Critical
Publication of EP1576290B1 publication Critical patent/EP1576290B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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 gear wheels which roll with one another in external or internal engagement and whose shaft journals are mounted in bearing points.
  • These bearing points can be designed as a component of covers, or can be designed as a bearing body in one or two parts, which are enclosed together with the gear wheels by a housing of the gear machine.
  • Disc-shaped sealing plates which are also referred to as side plates, are arranged between the bearing bodies and the rotating gear wheels. Due to the undersize of the unit comprising gears, bearing bodies and sealing plates relative to the housing, the unit has an axial play, due to which the side plates can move axially within the scope of this fitting play.
  • different pressure fields are formed, which compress the high-pressure areas (high-pressure side - HD) compared to the low-pressure areas (low pressure side - ND). differentiate from one another.
  • the side plates are designed with a minimal axial sealing gap. pressure-dependent in the direction of the tooth end faces of the meshing gears. As a result, the side plates on the low-pressure side are pressed against the gearwheels with almost no gap with sealing contact, as a result of which the lateral outflow of fluid from the area under high pressure to the area under pressure between the tooth face of the rotating gearwheels and the non-rotating side plate remains extremely low.
  • This optimized gap compensation between the gearwheel and the side plate optimizes the volumetric efficiency and thus the performance of the entire gearwheel machine, in particular under operating conditions with variable speed, starting from the standstill of the gearwheel machine and simultaneous pressure load.
  • the invention is based on a gear machine with the following structure:
  • a housing 3 which has a high-pressure connection and a low-pressure connection through laterally penetrating bores and which is delimited by lateral housing parts 2, 5, also referred to as covers, preferably encloses two bearing bodies 7, 8, wherein a bearing body can be part of the housing 3.
  • two gear wheels 4 meshing in external or internal engagement roll on each other on the tooth flanks, the shaft journals of which are mounted in the bearing bodies 7, 8.
  • At least one bearing pin 1 of these gears is designed as an outwardly leading shaft for driving or driving.
  • the bearing bodies have grooves on the side of the side housing parts 2, 5 6, 9, in which sealing bodies (not shown here) made of rubber, in combination with additional support elements, or one-piece seals made of composite material, preferably made of polyurethane, are inserted, in order to prevent a gap extrusion between the bearing bodies and the laterally delimiting housing parts when the unit is under pressure to prevent.
  • These sealing bodies form sealing fields which have the shape of an open “3” on the low-pressure side of the unit.
  • the side of the bearing bodies 7, 8 facing the end faces of the meshing gearwheels have milled grooves (pilot control geometry) which are designed such that the gearwheels rolling on the line of engagement of the toothing always have at least one sealing point between the one with high pressure and the one with low pressure.
  • milled grooves pilot control geometry
  • the gearwheels rolling on the line of engagement of the toothing always have at least one sealing point between the one with high pressure and the one with low pressure
  • these pressure fields on the bearing bodies 7, 8 generate moments of force about the central axis of the bores designed as bearing points, which prevent the bearing bodies from being pressed flat against the tooth end faces.
  • a gap is formed between the bearing body and the tooth end face, through which a fluid flow can arise from the high pressure sealing fields to the circular segment surfaces of the bearing bore under low pressure.
  • This fluid flow causes an internal, axial leakage flow of the fluid from the high to the low pressure side in the high-pressure area of the bearing body, which leads to the volumetric efficiency of the entire unit being reduced.
  • 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 they have grooves 10, 12, 15, 17 on both end faces, that is to say on the side surface facing the gear and the cover, for receiving sealing elements, not shown here.
  • the sealing elements inserted on both sides of the bearing bodies result in sealing fields which form on the bearing body when the gear machine is subjected to pressure and which act as hydraulically active pressure compensation fields both on the bearing bodies and on the side plates 13, 14 placed in front of the bearing bodies.
  • FIG. 3 shows a bearing body 11, specifically its side surface facing the gear wheels 4, which lies on a side plate 13.
  • the groove 12 which receives a sealing element 25 (not shown here), which is explained below with reference to FIG. 7, is introduced into the side surface.
  • a sealing field is defined by the sealing element introduced into the groove 12.
  • the bearing body 11 is pressed against the front side plate 13 by the hydraulic forces that arise from the different sized sealing fields. This is displaced axially in the opposite direction to the bearing body 11 by the hydraulic forces which act both on both sides of a bearing body and on the hydraulically loaded surface of the side plate.
  • the side plate 13, which is referred to as being articulated and movable, is pressed against the end face of the gear wheels 4, as a result of which an axial gap compensation which is set as a function of the operating point enables an optimal sealing effect between the side plate and the bearing point.
  • the side surface of the bearing body 16 facing the side plate 14 is designed accordingly, so that the described Adjust the hydraulic forces ben and the side plate 14 is moved in the opposite direction to the bearing body 16 and a quasi movable articulated side plate is also realized here.
  • FIG. 4 shows the side surface of the bearing body 11 opposite the gear wheels 4 or the side plate 13.
  • the groove 10 is here introduced into the side surface, which in turn has the shape of a “3” or an “ ⁇ ”, but is oriented in the opposite direction, as this is the case on the side shown in FIG. 3, which faces the side plate 13.
  • FIGS. 3 and 4 show that large areas of the groove 10 lie on an imaginary circle that runs concentrically to the bearing openings or bearing bores L1 and L2, the radius of the circles of the groove 10 being greater than the radius of the circles of the Groove 12, which is shown in Figure 3. In this way, sealing fields of different sizes are realized and the above-mentioned hydraulic forces of different sizes are built up.
  • the pressure fields on both sides of the bearing body 11 are in an area ratio between 1.5 and 2.0 to one another.
  • the larger surface under pressure is provided on the side surface of the bearing body facing the side plate than on the side surface of the bearing facing the housing part 2 serving as a cover. body 11.
  • the larger area under pressure on the side surface facing the side plate 16 is provided than on the side surface of the bearing body 16 facing the housing part 5 serving as a cover.
  • the area ratio of the two pressure fields of each bearing body is preferably chosen 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. As a result, the sealing gap required for the articulated compensation of the side plates 13, 14 placed in front of the bearing bodies is always formed between the bearing body and the side plate, as a result of which the side plates are pressed against the end faces of the gear wheels 4.
  • hydraulically active sealing fields are arranged on both sides of a bearing body in the circular ring segments loaded with high pressure on sealing fields which are designed to be concentric with one another.
  • the above-mentioned area ratio of the sealing fields provided on the two sides of the bearing body is thus realized in that the grooves 10 and 12 on both sides of the bearing body are arranged on imaginary circular lines that are concentric with the center of the bearing openings L1 and L2, but different radii or respectively Have diameter.
  • the larger diameter is carried out on the side of the bearing body facing the housing parts 2, 5 serving as a cover.
  • the smaller pressure field is realized here.
  • the position of the sealing fields concentric to the center of the axis of the gear wheels 4 defines the resulting force fields, which effect the hydraulically optimal gap compensation between the side plates 13, 14 and the gear wheels 4.
  • the course of the grooves 10 and 12 in the side surfaces of the bearing body follows the shape of the number “3” or the letter “ ⁇ ”, specifically at a defined angle.
  • the ends of the groove 12 lie at a distance from the imaginary diameter lines of the bearing openings L1 and L2 and enclose an angle ⁇ between 12 ° and 14 ° with this line, this angular range preferably being symmetrical to the center axes of the gearwheels or to an imaginary horizontal central axis M2 is arranged. This can be seen in 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, that is to say also at the parting plane between the bearing body 16 and the side plate 14.
  • two pressure feed grooves 19 and 21 are located in the region of an imaginary vertical central axis M1 above and below.
  • a pressure feed groove 20 is also provided on the left, which is arranged symmetrically to the imaginary central axis M2.
  • This compensating movement hydraulically sets a minimum gap between the side plates 13, 14 and the rotating gear wheels 4 under all operating conditions of the gear machine, which causes the outflow of fluid from surfaces subjected to high pressure to areas with low pressure to be minimized. This leads to optimal volumetric efficiencies 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.
  • FIG 5 shows the groove 12 made in the side face facing the side plate 13 and the groove 10 made in the side face facing the housing part 2 serving as a cover.
  • the grooves 10 and 12 are designed differently, the groove 12 having an essentially U-shaped cross section and the groove rather showing a rectangular cross section.
  • the different cross sections can be seen in the magnifications W and U, U representing the cross section of the groove 10 and W representing the cross section of the groove 12.
  • the shape of the groove 12 is distinguished by the fact that it runs conically from the side surface of the bearing body 11 to the groove base N1 at an angle between 3 ° and 16 °, an angle of 8 ° preferably being selected.
  • the groove 12 merges on both sides over a radius into the groove base N1.
  • This conical groove design on the one hand increases the fatigue strength of the remaining residual web between the sealing ring groove and the bearing bore L1, L2 in the bearing bodies, and on the other hand this groove design, when pressure is applied to the sealing elements (not shown in FIG. 5), results in a defined flat 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 the groove flank and the groove base N1 of the groove 12 is chosen to be large enough to result in a practically U-shaped groove cross section.
  • the cross section of the groove 10 is essentially rectangular.
  • the groove 10 thus has a practically flat groove base N2 and two groove flanks which run practically perpendicularly thereto and which merge into the groove base N2 over a smaller radius than 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 made of aluminum or steel are used.
  • the side plates 13, 14 preferably consist of such a wear-resistant material, for example of WC / C, SiC, ALO 2 .
  • Multi-layer materials are particularly preferred on the Basis of St / CuPbSn alloys, the hardness of the applied layer material between 55 and 100 HB and the hardness of the carrier material between 100 and 145 HB.
  • 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 designed in such a way that deflection by the pressurized surface portions is avoided via the horizontal and vertical central axis M1, M2 of the side plate.
  • a thickness of the side plate between 2.2 mm and 3.2 mm was preferably chosen, optimal results being achieved with a plate thickness of 2.4 mm with a bronze-coated side plate made of steel (St / CuPbSn alloy) were.
  • FIG. 6 shows a side plate 13 or 14 seen in plan view.
  • the side plates are accommodated in housing bores. It is provided that the side plates in the area in which they are subjected to system pressure do not lie directly against the wall of the housing bores, but that a radial gap remains between the outer diameter of the side plates and the diameter of the housing bore.
  • at least one projection 23 is provided, which lies with its radially outer outer surface against the wall of the housing bore and therefore has a diameter similar to that of the housing bore. This defines the radial position of the side plates in the housing bore.
  • the radial gap between the side plate and the housing causes a radial force to act on the radially projected surface of the side plate due to the pressure load on the gear machine. This force presses the side plate against the surfaces of the housing bore that are exposed to high pressure, thereby creating a radial, metallic seal on the side plates 13, 14 on the housing 13.
  • the outer contour of the side plates is selected such that the area of the side plates that comes into contact with the housing of the gear machine extends over an angle ⁇ which is in a range from 100 ° to 150 °, measured from the central axes of the gear wheels 4 or the bearing openings L1, L2. Optimal sealing conditions are achieved with gear machines that are designed as pumps and have an angular range of approximately 110 °.
  • gear machines with front side plates 13, 14 and defined sealing fields in the bearing points is possible both for gear machines with single-flank engagement of the gear wheels 4 and for gear machines with double-flank engagement of the gear wheels 4.
  • the side plates 13 and 14 are distinguished by the fact that for gear machines with single-flank contact of the gear wheels 4 and for gear machines with double-flank contact of the gear wheels 4, grooves 24 shown in FIG. 6 are introduced into the surfaces of the side plates that face the end face of the gear wheels 4. Together with the pitch point of the toothing, these form 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 designed in such a way that the rolling point te of the meshing gears 4 from the central axis of the side plate of the surface in contact with the gear falling laterally at an angle from the central axis M2 to the outer contour of the side plate 13, 14, preferably at an angle of 5 ° to the side surface of the side plate.
  • the grooves 24 can be made parallel to the end face with a distance of at least 1 mm from the surface facing the gearwheel.
  • the hydraulically active engagement lines which are formed by the teeth of the side plate 13, 14 facing the gearwheels 4 on a connecting line between the rolling points of the meshing gear wheels 4 and the grooves 24, are thus designed in the case of single and double flank engagement of the toothing that the high pressure grooves 24r, 24r 'compared to the low pressure pressure-loaded grooves 241, 241 'of the side plate 13, 14 is shifted asymmetrically towards the low-pressure side in a range between 40% and 60% to the central axis M1.
  • the high-pressure area lies to the right of the central axis M1 and the low-pressure area to the left of the central axis M1.
  • control geometry is shifted by 50% from the high-pressure to the low-pressure side, that is to say if the grooves in the side surface of the side plate 13, 14 facing the gearwheels 4 are symmetrical, optimal results are achieved with regard to the squeezing oil pulsation.
  • the pilot geometry to the central axis M1 is to be carried out symmetrically between the high pressure and low pressure side.
  • sealing elements made of polyurethane can be used to avoid gap extrusion.
  • Bearing body 11, 16 and side plates 13, 14 forming sealing gap, which limits the pressure fields, presses the side plates against the end faces of the gearwheels 4 in accordance with the system pressurization.
  • the arrangement of the side plates 13, 14 and the bearing bodies 11, 16 provides axial compensation for the axial and radial gap compensation between the axially moving and opposite surfaces on the face of the gear and the front side plates. This is known as articulated compensation.
  • the grooves 10, 12 for receiving the sealing elements can be arranged in the bearing bodies, or alternatively in the side plates and in the side surfaces of the housing parts 2, 5 facing the bearing bodies.
  • FIG. 7 shows a sealing element 25 which can be inserted into the groove 12.
  • Figure 8 shows a sealing element 27 which can be inserted into the groove 10 of the bearing body 11, 16.
  • the sealing elements 25, 27 sealing in the axial direction, which are inserted on both sides into the grooves 12, 10 of the bearing bodies 11, 16, are designed such that they either consist of one-piece elastic polyurethane sealing elements, or two-piece, in which one element Perbutane has the sealing effect and an element made of glass fiber reinforced polyamide has the supporting function.
  • the sealing materials used are matched to the fluid used in the system. Other materials can also be used.
  • the sealing elements 25 and 27 are preferably designed in such a way that they have increased strength against gap extrusion or gap wear in the sealing region between the high-pressure and low-pressure fields.
  • the ends of the sealing element 25 lying between the bearing body and side plates are preferably L-shaped and, if appropriate, thickened.
  • the sealing element 25 is securely anchored with the L-shaped ends 29. It engages in corresponding recesses 31 in the groove 12, which are shown in FIG. 3.
  • Sectional thickened sections can also be provided in sections, which likewise offer increased strength against gap extrusion or gap wear in the sealing area between the high-pressure and low-pressure fields.
  • partial thickenings 33 can be provided in order to form elastic partial areas with a corresponding preload, by means of which the respective sealing element is held in the associated groove 10. Such thickenings can 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 in the bearing bodies by pressure loading of the gear machine and are supported against the housing 3 are applied to the bearing bodies by the realization of the articulated connection of the front side plate and the bearing body.
  • the axial compensation which brings about a flat contact of the side plates 13, 14 on the end faces of the gear wheels 4 and thus an optimized gap compensation, takes place free of the bearing load forces of the gear machine via the side plates 13, 14.

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

Abstract

La présente invention concerne une machine, une pompe ou un moteur à roues dentées destiné(e) à un ou deux dispositifs de rotation, comprenant au moins deux roues dentées (4), deux plaques latérales (13, 14) appliquées contre les roues dentées (4), et des corps d'appui (11, 16) appliqués contre lesdites plaques. L'invention se caractérise en ce que des éléments d'étanchéité de conceptions différentes se trouvent sur les faces latérales opposées entre elles et opposées aux plaques latérales (13, 14).
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 true EP1576290A1 (fr) 2005-09-21
EP1576290B1 EP1576290B1 (fr) 2013-02-20

Family

ID=32667562

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03785863A Expired - Lifetime EP1576290B1 (fr) 2002-12-19 2003-12-18 Machine a roues dentees comprenant des plaques laterales axiales

Country Status (4)

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

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2004057193A1 *

Also Published As

Publication number Publication date
AU2003294889A1 (en) 2004-07-14
WO2004057193A1 (fr) 2004-07-08
JP2006510841A (ja) 2006-03-30
EP1576290B1 (fr) 2013-02-20

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