EP1174617B1 - Machine hydrostatique à pistons axiaux - Google Patents
Machine hydrostatique à pistons axiaux Download PDFInfo
- Publication number
- EP1174617B1 EP1174617B1 EP01117151A EP01117151A EP1174617B1 EP 1174617 B1 EP1174617 B1 EP 1174617B1 EP 01117151 A EP01117151 A EP 01117151A EP 01117151 A EP01117151 A EP 01117151A EP 1174617 B1 EP1174617 B1 EP 1174617B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure
- control
- piston
- cylinder
- axial
- 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
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F04B1/2014—Details or component parts
- F04B1/2042—Valves
Definitions
- the invention relates to a hydrostatic axial piston machine with a drum-shaped Cylinder block that is mounted on a drive or output shaft so that it cannot rotate and provided concentrically and parallel to the center line with cylinder bores is in which axially displaceable pistons are arranged, which are spherical Heads on a housing-fixed, preferably adjustable in their helix angle, Support the swashplate, with the swashplate opposite Cylinder openings such as kidney-shaped low-pressure and high-pressure control openings of a control body, between which there are reversing areas with additional holes.
- the volumes that are decisive for the pressure build-up in the cylinder space namely the dead volume plus the stroke volume, from the swivel angle of the Swashplate, the volumes to be added to build up pressure the pressure in the high pressure control port and the available one Time interval for pressure changeover and thus depend on the speed, is an optimal pressure reversal with a constant notch in the reversal area or with the reversing areas through channels with the low-pressure and high-pressure control openings connecting channels across the entire operating range not possible.
- the object of the invention is to provide a hydrostatic axial piston machine specified type to create, in which in the or the changeover areas located additional bores, which increase or decrease the pressure Influence the passage of the cylinder openings over the reversing areas, depending on of the operating conditions, namely the pressure, the speed and the Swivel angle of the swash plate are controlled. Furthermore, a hydrostatic Axial piston machine can be created that is simple and reliable Way even with changed operating conditions when running through the Cylinder openings over the reversal areas an undesirable sudden increase or prevent pressure drops in the cylinders.
- an axial piston machine according to claim 1. It is therefore provided that at least one Reversal area of the control body opens a hole through a line is connected to the high pressure side or the high pressure control opening, and that in the line a throttle controlled by the high pressure is arranged, which in the line opens a throttle opening corresponding to the high pressure. About Strokes the open cylinder side the bore, flows out of this under higher Oil under pressure in the cylinder opening, so that the pressure in the passage through the changeover range and a continuous in the cylinder Pressure increase until the open cylinder side enters the high pressure control opening he follows. Unwanted sudden pressure increases and changes in the flow are avoided.
- the hole expediently opens into an area of the reversing area, which faces the high pressure control opening.
- At least one the low pressure control opening facing area of a reversing area of the Control body opens a hole through a line with the low pressure control opening is connected, and that in the line one controlled by the high pressure Throttle is arranged, which corresponds to the high pressure in the line Throttle opening releases.
- This configuration improves pressure compensation and leads in front of the inlet and the inlet of the open cylinder sides in the Low pressure control opening to a continuous, avoiding pressure surges Pressure reduction.
- the two bores are expediently located in the reversing area Pass of each cylinder opening covered by this at the same time. Conveniently, point the two holes in the reversal area or areas equal distances to the low pressure and high pressure control openings.
- the controlled throttle from a cylindrical bore in the control body or one in the Control body-held cylinder, in which or by a compression spring loaded piston is displaceably guided, the opposite of the compression spring Side acted on by the high pressure in the high pressure control opening is that in the cylinder bore or the cylinder at an axial distance from each other to the bore of the reversing area and to the high pressure control opening or lines leading to the low-pressure control opening and that the control piston according to its displacement of different sizes Throttle openings opposite the line leading to the reversing area releases.
- the line of the reversing area opening into the control cylinder can be through an axial groove with a changing cross section of the control piston with the the high-pressure control opening or the low-pressure control opening leading line be connected.
- the changing cross section is due to Adapted calculations or experiences of the respective axial piston machine.
- connection of the Control cylinder to the line leading to the reversing area from one Slit exists, which the control piston due to its displacement releases the high pressure on one side in different lengths.
- the approved length corresponds to the respective flow cross section of the controlled Throttle, which is adapted to the respective axial piston machine.
- control piston acted upon on one side by at least two compression spring enclosing each other of which the springs following or following the first spring are successive corresponding to the displacement of the control piston in the direction of the springs are used, i.e. they use their force to load the control piston.
- control piston is shifted in the control cylinder by an actuator whose Travel from a control device, for example a computer, depending the high pressure, the speed and the swivel angle of the swash plate is determined.
- a control device for example a computer
- the values influencing the travel of the control piston, the for the respective axial piston machine from the variable high pressure, the variable speed and the variable swivel angle can be stored in tables (ROM) in the memory unit of the computer, so that the computer according to the respectively measured high pressure, the respectively measured Speed and the respective swivel angle of the swash plate Control piston adjusted.
- control piston is designed as a stepped piston, the annular piston surface and the disk-shaped piston surface of the high pressure and another from one of the set helix angle of the swash plate speaking pressure are applied.
- the helix angle of the swashplate corresponding pressure can be, for example, from the pressure in one Derive the actuating cylinder that adjusts the swash plate and is proportional to the angle adjustment the swash plate is.
- control piston is designed as a three-stage piston, through the two ring surfaces and the central disc-shaped piston surfaces each formed by Pressures applied to the high pressure in the high pressure control port, correspond to the helix angle of the swash plate and the speed.
- the the Pressure corresponding to the rotational speed can be achieved, for example, by one of the axial piston machines driven auxiliary pump are derived, the a speed proportional pressure generated.
- each inlet throttle has at least two throttle cross sections on, the one choke a constant choke in the control plate and the other choke or chokes near the control surface of the control body or housed in the control body itself are, the cross section or the cross sections of the controllable chokes controlled according to the operating conditions of the axial piston machine will or can be controlled that the pressure build-up and pressure reduction in the controlled Cylinder space takes the desired course.
- the high pressure side i.e. the high pressure control openings
- a certain volume of the pressure oil is removed, which is then missing from the flowing pressure medium. Missing pressure medium on the high pressure side can in turn lead to undesirable ones Cause pulsations.
- the controlled throttle Pressurized oil is supplied from an external pressurized oil source.
- a control body 1 is shown schematically in FIGS. 1 and 2, of which in FIG. 1 only the control surface with the high pressure control opening 2 and the low pressure control opening 3 and those in the reversal areas between the low pressure and High-pressure control openings located throttle bores 4, 5 and 6, 7 shown are.
- the control surface of the control body is formed by the approximately oval Openings 8 of the cylinder 9 are swept over, which are shown in broken lines in FIG are.
- the hydraulic connections of the low-pressure and high-pressure control openings 2, 3 are of a common type and are therefore not shown.
- the throttle openings 4 to 7 have a constant cross section and form thus, as can be seen from FIG. 2, constant chokes.
- Controlled throttle 12 To control the pressure media flowing through the constant throttles is a Controlled throttle 12 is provided, which will be described with reference to FIG. 5.
- a control piston 16 is arranged displaceably in the cylinder.
- This control piston is loaded by a compression spring 17 which between the bottom of the cylinder 15 and the side of the control piston 16 facing this is clamped.
- the opposite Side of the control piston is acted on by the high pressure, that is the pressure in the high-pressure control opening 2 of the control body 1 prevails.
- the side of the compression spring 17 opposite Cylinder via a line 18 and a branch line 19 with the high pressure control opening 2 connected.
- the high pressure could also be from be derived from another point of the axial piston machine.
- the control piston 16 is provided with an axially closed bore 20 at its ends, which communicates with radial bores or slots 21, 22.
- the radial Bore 21 is via line 18 and an annular space 23 with the pressure of Pressurized medium in the high pressure control opening 2.
- the hole or preferably the slot 22 communicates with an annular space 24, of which a line 25 to the throttle opening 5 in the control surface of the control body 1 leads.
- the piston 16 is in the cylinder bore 15 through the right piston surface acting high pressure shifted against the force of the compression spring 17, a control slot of different lengths according to the displacement path 22 is controlled, each of the length detected by the annular space 24 of the control slot.
- control piston 16 has an axial one Provide slot that has a variable cross section, so that accordingly the displacement of the control piston with that leading to the throttle opening 5 Throttle cross-sections of different sizes can be opened.
- volume from the high pressure control opening via the controlled throttle and the constant throttle in the Cylinder rooms of the cylinder bores can be influenced in such a way that the desired one Pressure curve in the cylinder bore is reached. Influencing the Throttle cross section can on the relationship between that in the control openings prevailing pressure and the open throttle cross section both over the compression spring and the shape of the throttle can be achieved.
- both the Throttle openings 5 constant cross-section on the low pressure and high pressure control openings 2, 3 facing sides with controlled throttles 12.
- the controlled throttles 12 are in both cases on their compression springs 17 opposite sides of the high pressure, which preferably in the form shown in dashed lines via lines from the high pressure control opening 2 is derived.
- a special feature of the invention is to be seen in the fact that the preferably oval cylinder openings over the control surfaces of the control body the cylinder opening 8 covers both throttle openings 4, 5, so that it becomes one smoothing pressure equalization comes.
- throttle bores 5 are arranged via the controlled throttles 12 in connection with variable throttle openings stand so that an optimal pressure compensation when the cylinder openings overflow can take place via the reversing areas.
- control piston is a compression spring 30 acted on, which encloses a compression spring 31 of shorter length in the manner that this only on the control piston after a predetermined displacement 16 attacks and thereby changes the spring characteristic and a hyperbolic Course attacks.
- a displacement device 33 which displaces the control piston 16 via a tappet 34, the displacement device 33 controlled by a control device, for example a computer which is a travel for the plunger 34 from the pressure of the high pressure side, the speed and the swivel angle are calculated.
- a control device for example a computer which is a travel for the plunger 34 from the pressure of the high pressure side, the speed and the swivel angle are calculated.
- the path of the throttle piston is controlled by a proportional magnet, d. H. the positioning force of the magnet depends on the size of the electrical applied Tension. The relationship between tension and the compression spring - Travel made.
- This proportional magnet can be of any electrical Signals are controlled. This allows the pressure curve in the cylinder bore depending on different sizes, for example pressure, Swivel angle and speed can be influenced.
- control piston 16 is a stepped piston executed, wherein the annular surface 36 of the stepped piston from the pressure of the high pressure side and the piston surface 37 of the piston with a smaller cross section of a liquid pressure is applied, which is the helix angle of the swash plate equivalent.
- control piston 16 has three stages Piston formed, the annular surfaces 36 and 38 of the high pressure and one the pressure corresponding to the helix angle of the swash plate and the End face 39 of the piston section with the smallest cross section of a pressure is applied, which is proportional to the speed of the axial piston machine.
- the controlled Throttle 12 a pressure medium via line 40 from an external pressure medium source is fed.
- Fig. 11 shows an embodiment in which both throttle openings in the Reversal area are controlled by controlled throttles, the oil supply the throttle opening 5 facing the high-pressure control opening 2 by a external pressure oil supply takes place.
- all of the holes are in the two Reversal areas provided with controlled throttles, the high-pressure side controlled throttles from an external pressure oil source with pressurized Medium are supplied.
- the supply of pressure oil from external pressure oil sources can be beneficial in certain cases. Firstly, through the external Pressure oil supply the pulsation in the high pressure control opening can be reduced and on the other hand, the higher pressure can supply the throttle system another desired pressure characteristic in the cylinder bores can be achieved.
- 13 and 14 show known control bodies in which the reversing areas with the adjacent low pressure and high pressure control openings connected by wedge-shaped narrowing slots or notches 50 are.
- FIGS. 15 and 16 Known control bodies can also be seen from FIGS. 15 and 16, at which the low-pressure and high-pressure control openings with the throttle bores are connected directly by lines 51 in the reversal area.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
- Actuator (AREA)
- Hydraulic Motors (AREA)
Claims (9)
- Machine hydrostatique à piston axial comprenant un bloc-cylindres en forme de tambour, qui est logé de façon solidaire en rotation sur un arbre d'entraínement ou un arbre de sortie et est pourvu de façon concentrique et parallèle à sa ligne médiane d'alésages de cylindre, dans lesquels sont disposés des pistons coulissant axialement qui s'appuient au moyen de têtes de forme sphérique sur un disque incliné solidaire du boítier, de préférence déplaçable dans son angle d'inclinaison, les ouvertures de cylindres (8) opposées au disque incliné balayant des ouvertures de commande de basse pression et de haute pression (3, 2), à peu près en forme de haricot, d'un corps de commande (1), entre lesquelles se trouvent des zones de renversement de marche avec des alésages supplémentaires (4, 5, 6, 7), un alésage (5; 7), qui est relié par une conduite au côté haute pression ou à l'ouverture de commande de haute pression (2), débouchant au moins dans une zone de renversement de marche du corps de commande (1), et un étranglement (12) commandé par la haute pression, qui libère dans la conduite un orifice d'étranglement correspondant à la haute pression, étant disposée dans la conduite,
caractérisée en ce que un autre alésage (4; 6), qui est relié par une conduite à l'ouverture de commande de basse pression (3), débouche dans la au moins une zone de renversement de marche, un étranglement (12), qui libère par la conduite un orifice d'étranglement correspondant à la haute pression, étant disposée dans la conduite,
en ce que les ouvertures de cylindre (8) recouvrent les deux alésages (4, 5; 6, 7) lors du passage par la zone de renversement de marche du corps de commande (1), et en ce que les étranglements (12) commandés et attribués aux deux alésages comprennent respectivement un alésage (15) de forme cylindrique dans le corps de commande (1) ou un cylindre maintenu avec le corps de commande, dans lequel est guidé de façon coulissante un piston de commande (16) chargé par un ressort de pression (17), dont le côté opposé au ressort de pression (17; 30, 31) est alimenté par la haute pression, des conduites de transport débouchant dans l'alésage de cylindre (15) ou le cylindre à distance axiale d'une part de l'alésage (4, 5; 6, 7) respectif de la zone de renversement de marche et d'autre part à l'ouverture de commande de haute pression (2) ou à l'ouverture de commande de basse pression (3), et le piston (16) libérant en fonction de son déplacement un orifice d'étranglement de grandeur différente et correspondant à la haute pression par rapport à la conduite respective et aboutissant à la zone de renversement de marche. - Machine à piston axial selon la revendication 1, caractérisée en ce que l'alésage (5; 7) relié au côté haute pression ou à l'ouverture de commande de haute pression débouche dans un secteur de la zone de renversement de marche du corps de commande (1), qui est tourné vers l'ouverture de commande de haute pression (2) et l'autre alésage (4; 6) relié à l'ouverture de commande de basse pression (3) débouche dans une zone, tournée vers l'ouverture de commande de basse pression (3), de la zone de renversement de marche du corps de commande (1).
- Machine à piston axial selon l'une quelconque des revendications 1 ou 2, caractérisée en ce que la conduite, débouchant dans le cylindre de commande (15), de la zone de renversement de marche est reliée par une rainure axiale avec section variable du piston de commande (16) à la conduite conduisant à l'ouverture de commande de haute pression ou l'ouverture de commande de basse pression.
- Machine à piston axial selon l'une quelconque des revendications 1 à 3, caractérisée en ce que la liaison du cylindre de commande (15) à la conduite aboutissant à la zone de renversement de marche se compose d'une fente que le piston de commande (16) libère dans une longueur différente en fonction de son déplacement du fait de la haute pression chargeant sur un côté.
- Machine à piston axial selon l'une quelconque des revendications 1 à 4, caractérisée en ce que le piston de commande (16) est alimenté d'un côté par au moins deux ressorts de pression (30, 31) emboítés l'un sur l'autre, dont le ressort ou les ressorts suivant le premier ressort sont utilisés de façon successive en fonction du déplacement du piston de commande en direction des ressorts.
- Machine à piston axial selon l'une quelconque des revendications 1 à 5, caractérisée en ce que le piston de commande (16) est conçu comme un piston à étages, dont la surface de piston (36) de forme annulaire et dont la surface de piston (37) en forme de disque sont alimentées d'une part par la haute pression et d'autre part par une pression correspondant à l'angle d'inclinaison réglé du disque incliné.
- Machine à piston axial selon l'une quelconque des revendications 1 à 6, caractérisée en ce que le piston de commande (16) est conçu comme un piston à trois niveaux, dont les surfaces de piston formées par les deux surfaces annulaires (36, 38) et la surface (39) centrale en forme de disque sont alimentées respectivement par des pressions, qui correspondent à la haute pression dans l'ouverture de commande de haute pression, à l'angle d'inclinaison du disque incliné et au régime.
- Machine à piston axial selon l'une quelconque des revendications 1 à 7, caractérisée en ce que les alésages (4, 5) débouchant dans les zones de renversement de marche sont formés par les alésages d'un étranglement constant.
- Machine à piston axial selon l'une quelconque des revendications 1 à 8, caractérisée en ce que de l'huile de pression est amenée d'une source externe d'huile de pression aux étranglements (12) commandés.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10034857A DE10034857A1 (de) | 2000-07-18 | 2000-07-18 | Hydrostatische Axialkolbenmaschine |
DE10034857 | 2000-07-18 |
Publications (3)
Publication Number | Publication Date |
---|---|
EP1174617A2 EP1174617A2 (fr) | 2002-01-23 |
EP1174617A3 EP1174617A3 (fr) | 2003-05-07 |
EP1174617B1 true EP1174617B1 (fr) | 2004-11-10 |
Family
ID=7649293
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP01117151A Expired - Lifetime EP1174617B1 (fr) | 2000-07-18 | 2001-07-13 | Machine hydrostatique à pistons axiaux |
Country Status (4)
Country | Link |
---|---|
US (1) | US6736048B2 (fr) |
EP (1) | EP1174617B1 (fr) |
JP (1) | JP2002070716A (fr) |
DE (2) | DE10034857A1 (fr) |
Families Citing this family (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10232513B4 (de) * | 2002-07-18 | 2014-02-06 | Linde Hydraulics Gmbh & Co. Kg | Pulsationsoptimierte hydrostatische Verdrängermaschine, insbesondere Axial- oder Radialkolbenmaschine |
DE10232983A1 (de) * | 2002-07-19 | 2004-02-05 | Brueninghaus Hydromatik Gmbh | Kolbenmaschine mit Pulsation |
DE10343222A1 (de) * | 2003-09-18 | 2005-04-14 | Sauer-Danfoss (Neumünster) GmbH & Co OHG | Axialkolbenmaschine der Schrägscheiben- oder Schrägachsen-Bauart |
DE102004007933B3 (de) * | 2004-02-18 | 2005-06-16 | Sauer-Danfoss (Neumünster) GmbH & Co OHG | Axialkolbenmaschine mit einer Vorsteuerungseinrichtung zur Dämpfung von Strömungspulsationen und Herstellungsverfahren |
DE112006000312T5 (de) | 2005-02-10 | 2007-12-13 | Komatsu Ltd. | Hydraulische Kolbenpumpe |
GB2440155A (en) * | 2006-07-18 | 2008-01-23 | Agco Gmbh | An axial piston pump or machine of the swashplate or bent axis type |
US20080307956A1 (en) * | 2007-06-18 | 2008-12-18 | Sauer-Danfoss Inc. | Web-less valve plate |
DE102008062483A1 (de) * | 2008-12-16 | 2010-06-17 | Robert Bosch Gmbh | Axialkolbenmaschine mit Pulsationsminderung |
US20100150741A1 (en) * | 2008-12-17 | 2010-06-17 | Mehta Viral S | Hydraulic unit having orifice plate displacement control |
DE102014208406A1 (de) * | 2014-05-06 | 2015-11-12 | Robert Bosch Gmbh | Hydrostatische Kolbenmaschine |
JP6267598B2 (ja) * | 2014-08-01 | 2018-01-24 | 川崎重工業株式会社 | 液圧回転機 |
US10227964B2 (en) * | 2015-08-28 | 2019-03-12 | Caterpillar Inc. | Hydraulic pump port plate with variable area metering notch |
DE102018218548A1 (de) * | 2018-10-30 | 2020-04-30 | Robert Bosch Gmbh | Hydrostatische Kolbenmaschine |
US11946462B2 (en) * | 2019-12-02 | 2024-04-02 | Danfoss Power Solutions, Inc. | Hydraulic axial piston unit and method for controlling of a hydraulic axial piston unit |
DE102022107860A1 (de) | 2022-04-01 | 2023-10-05 | Danfoss Power Solutions Inc. | Hydraulische Axialkolbeneinheit und Verfahren zum Steuern einer hydraulischen Axialkolbeneinheit |
Family Cites Families (19)
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DE953767C (de) | 1952-10-30 | 1956-12-06 | Krauss Maffei Imp G M B H & Co | Mit Unterdruck arbeitende Rundsiebentwaesserungsmaschine |
US3180274A (en) * | 1962-06-04 | 1965-04-27 | Francis J Sisk | Silent variable delivery hydraulic pump |
US3283726A (en) * | 1964-12-14 | 1966-11-08 | American Brake Shoe Co | Construction for pump/motor devices |
FR2110550A5 (fr) * | 1970-10-21 | 1972-06-02 | Citroen Sa | |
JPS6085267A (ja) * | 1983-09-05 | 1985-05-14 | Daikin Ind Ltd | アキシアル・ピストン機械 |
JPS60162081A (ja) * | 1984-02-03 | 1985-08-23 | Tokyo Keiki Co Ltd | タイミング弁機構 |
JPS63159676A (ja) * | 1986-12-22 | 1988-07-02 | Daikin Ind Ltd | 可変モ−タの速度制御装置 |
JPH05321815A (ja) * | 1992-05-22 | 1993-12-07 | Nachi Fujikoshi Corp | 液圧ポンプモータ |
JP2606758Y2 (ja) * | 1992-12-22 | 2001-01-09 | 株式会社小松製作所 | 油圧ポンプ・モータのシリンダ室内圧力コントロール装置 |
JPH07180654A (ja) * | 1993-12-24 | 1995-07-18 | Aisin Seiki Co Ltd | アキシャルポンプ |
JPH07332225A (ja) * | 1994-06-10 | 1995-12-22 | Kayaba Ind Co Ltd | ピストンポンプ |
US5555726A (en) * | 1995-03-31 | 1996-09-17 | Caterpillar Inc. | Attenuation of fluid borne noise from hydraulic piston pumps |
US5634776A (en) * | 1995-12-20 | 1997-06-03 | Trinova Corporation | Low noise hydraulic pump with check valve timing device |
DE19706114C9 (de) * | 1997-02-17 | 2014-02-06 | Linde Hydraulics Gmbh & Co. Kg | Vorrichtung zur Pulsationsverminderung an einer hydrostatischen Verdrängereinheit |
JPH10331996A (ja) * | 1997-06-03 | 1998-12-15 | Koyo Seiko Co Ltd | 可変絞り弁 |
DE19804374B4 (de) * | 1998-02-04 | 2004-09-30 | Brueninghaus Hydromatik Gmbh | Axialkolbenmaschine mit Mitteldrucköffnung |
DE19818721A1 (de) * | 1998-04-27 | 1999-10-28 | Mannesmann Rexroth Ag | Hydrostatische Maschine |
EP1013928A3 (fr) * | 1998-12-22 | 2000-11-08 | Parker Hannifin GmbH | Pompe à pistons axiaux à plateau en biais avec disposif d'amortissement de pulsation |
US6510779B2 (en) * | 2001-02-02 | 2003-01-28 | Sauer-Danfoss, Inc. | Electronic bore pressure optimization mechanism |
-
2000
- 2000-07-18 DE DE10034857A patent/DE10034857A1/de not_active Withdrawn
-
2001
- 2001-07-13 EP EP01117151A patent/EP1174617B1/fr not_active Expired - Lifetime
- 2001-07-13 DE DE50104460T patent/DE50104460D1/de not_active Expired - Lifetime
- 2001-07-18 JP JP2001218281A patent/JP2002070716A/ja active Pending
- 2001-07-18 US US09/908,107 patent/US6736048B2/en not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
DE50104460D1 (de) | 2004-12-16 |
US6736048B2 (en) | 2004-05-18 |
US20020108489A1 (en) | 2002-08-15 |
JP2002070716A (ja) | 2002-03-08 |
EP1174617A3 (fr) | 2003-05-07 |
DE10034857A1 (de) | 2002-01-31 |
EP1174617A2 (fr) | 2002-01-23 |
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