EP0849468B1 - Dispositif de réglage de la capacité d'une pompe à pistons axiaux - Google Patents

Dispositif de réglage de la capacité d'une pompe à pistons axiaux Download PDF

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Publication number
EP0849468B1
EP0849468B1 EP97120301A EP97120301A EP0849468B1 EP 0849468 B1 EP0849468 B1 EP 0849468B1 EP 97120301 A EP97120301 A EP 97120301A EP 97120301 A EP97120301 A EP 97120301A EP 0849468 B1 EP0849468 B1 EP 0849468B1
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EP
European Patent Office
Prior art keywords
spring
piston
actuating piston
control
piston pump
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
EP97120301A
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German (de)
English (en)
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EP0849468A2 (fr
EP0849468A3 (fr
EP0849468B2 (fr
Inventor
Werner Hörmann
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.)
Brueninghaus Hydromatik GmbH
Original Assignee
Brueninghaus Hydromatik GmbH
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Publication date
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Application filed by Brueninghaus Hydromatik GmbH filed Critical Brueninghaus Hydromatik GmbH
Publication of EP0849468A2 publication Critical patent/EP0849468A2/fr
Publication of EP0849468A3 publication Critical patent/EP0849468A3/fr
Publication of EP0849468B1 publication Critical patent/EP0849468B1/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
    • 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
    • F04B1/26—Control
    • F04B1/30—Control of machines or pumps with rotary cylinder blocks
    • F04B1/32—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block
    • F04B1/328—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the axis of the cylinder barrel relative to the swash plate

Definitions

  • the invention relates to an adjusting device for adjusting the delivery volume Axial piston pump, especially in a sliding axis design.
  • An adjusting device is e.g. from DE 36 21 302 A1 known.
  • the control device resulting from this document comprises one with a control mirror body of the axial piston pump via an adjusting pin non-positively connected control piston, which telescopically in several sleeves is mobile.
  • the actuating piston has two control surfaces on which the actuating piston with pressurized media under different pressure. A Force difference between the control surfaces causes hydraulic control of the Adjusting piston so that the adjusting piston is displaced and the delivery volume of the Axial piston pump is hydraulically adjusted.
  • Such an adjustment device is also known from DE 36 27 375 A1.
  • the hydraulic adjustment device is usually made from the high pressure line the axial piston pump.
  • the problem arises that near the Zero position of the control piston, in which the axial piston pump with or without low delivery volume that works in the high pressure line from the axial piston pump built up delivery pressure is not sufficient to the hydraulic adjustment device from this Swing out the zero position in the direction of a larger delivery volume.
  • This The problem is countered in practice by the fact that the minimum funding volume of the Axial piston pump to one for the hydraulic control of the actuating piston sufficient value is limited or that an auxiliary pressure supply is provided, which supplies the adjustment device with an external auxiliary pressure if the in the High pressure line of the axial piston pump prevailing delivery pressure below one for the hydraulic control of the adjustment device decreases sufficient value.
  • a Limitation of the minimum delivery volume of the axial piston pump considering the Hydraulic controllability of the adjustment device is disadvantageous in that the Adjustment range of the axial piston pump is thus limited down and one No-load operation without or with negligibly low delivery capacity is not possible.
  • An external auxiliary pressure supply is also disadvantageous, since an auxiliary pressure system with an additional auxiliary pressure pump is to be provided, which increases the effort considerably.
  • the invention is therefore based on the object of an adjustment device for adjustment of the delivery volume of an axial piston pump, which is hydraulically controlled works and swings out of the zero position, in which the axial piston pump works without or with minimal delivery volume, without additional auxiliary pressure supply allows.
  • the object is in connection with the characterizing features of claim 1 solved with the generic features.
  • the adjustment device comprises a pilot control with a e.g. Electrically controllable control valve that sets the signal pressure in the high pressure line prevailing delivery pressure wins.
  • a swing-out spring is provided by the actuating piston shortly before reaching its zero position, in which the Axial piston pump works with no or minimal delivery volume, is preloaded.
  • the preload of the swing-out spring is dimensioned so that the swing-out spring Moving the adjusting piston when swiveling out of the zero position until the of the Axial piston pump in the high pressure line delivery pressure for the hydraulic Activation of the control piston is sufficient.
  • a valve piston of the control valve against a return spring be movable and the return spring on an adjustable with an adjusting member Support the support element, the support element by the swing-out spring on the Actuator is held in the system.
  • the swing-out spring comes next to the the above-described function of swinging out of the zero position additional function of a system spring to which the support element on the adjusting member Plant holds.
  • the support element can be a spring plate and that Adjusting element e.g. be a threaded bolt.
  • the feedback element can be a feedback spring according to claim 4, the between a second spring plate non-positively connected to the valve piston and the actuating piston is clamped.
  • the swing-out spring can according to claim 5 between a stop element and the support element can be clamped, the actuating piston shortly before reaching it Strikes zero position on the stop element and carries it so that the Swinging spring is biased. As long as the adjusting piston on the stop element does not stop, the movement of the adjusting piston from the swing-out spring is complete unaffected.
  • the stop element Feedback spring coaxially enclose and according to claim 7, the Swing-out spring in turn enclose the stop element coaxially. This will make one achieved particularly compact design of the adjusting device according to the invention.
  • the stop element can be particularly advantageous as Hollow cylinder with a molded support surface for supporting the swing-out spring and an also integrally formed stop surface for the stop of the actuating piston his.
  • the area in which the swing-out spring moves to the actuating piston position Influence can be varied by varying the axial length of the stop element.
  • controlled axial piston pump and that generated by the axial piston pump Delivery pressure can be the area in which the swing-out spring adjusts the actuating piston charged to be dimensioned differently.
  • An adaptation of the invention Adjustment device to the conditions of the axial piston pump is simpler Way by varying the length of the hollow cylindrical stop element possible, so that the adjustment device according to the invention for different axial piston pumps can be equipped or converted.
  • the adjustment device according to the invention is, however, not exclusive in a special way for axial piston pumps with a sliding axis design, especially in Swivel carriage design, suitable according to claim 10.
  • the control piston overlaps a setting pin on the control mirror body of the axial piston pump.
  • the axial piston pump 1 shown in longitudinal section in FIG. 1 is in Shooting axis construction, more precisely in swivel carriage construction.
  • the invention is, however, not on axial piston pumps 1 in sliding axis design or Swivel carriage design limited, but also for controlling Axial piston pumps 1 in a different design are equally suitable.
  • the axial piston pump 1 comprises a rotatable in a housing 2 in bearings 3 and 4 mounted drive shaft 5, on which a Tricebwelleflansch 6 is formed.
  • the housing 2 encloses a cylinder drum 7, in which a plurality of cylinder bores 8 and 9 a pitch circle are evenly distributed.
  • pistons 10 and 11 are movably guided, which are on their ball heads 12 and 13 in support spherical bearings 14 and 15 of the drive shaft flange 6.
  • the Cylinder drum 7 is supported in the drive shaft flange 6 via a central pin 16, the ball head 17 of the center pin 16 in the spherical bearing 18 of Drive shaft flange 6 is mounted.
  • the cylinder drum 7 is supported in a known manner with control kidneys provided control mirror body 19 on the in the housing 20 of the invention Adjustment device 21 formed sliding surface 22 and is against this by a spring 25 biased.
  • the delivery volume is in a manner known per se by pivoting the central axis the cylinder drum 7 adjustable against the central axis of the drive shaft 6. It is Maximum delivery volume or the minimum delivery volume of the axial piston pump 1 adjustable by an externally adjustable threaded bolt 23 or 24.
  • the adjusting device 21 includes a more precise one from FIG see adjusting piston 30, in which an adjusting pin 31 is inserted, which with the Control mirror body 19 is in a frictional connection.
  • the actuating piston 30 is in a corresponding manner with others Delivery volume of the axial piston pump 1 defining actuators, e.g. an oblique or apply swashplate in connection.
  • the bolts 56 and 57 are used to connect the adjusting device 21 with the Axial piston pump to be controlled 1.
  • the actuating piston 30 is in an actuating piston bore 32 designed as a stepped bore axially movable and has a first control surface 33 which has a first pressure chamber 34 concludes.
  • the first pressure chamber 34 is via a connecting line, not shown connected to the high pressure line of the axial piston pump 1, so that the first Control surface 33 with that prevailing in the high-pressure line of the axial piston pump 1 Delivery pressure is applied.
  • the actuating piston 30 also has a second control surface 35 on, which closes a second pressure chamber 36, which only partially the signal pressure line 37 shown is connected to the connection 38 of a control valve 39 is.
  • Another port 40 of the control valve 39 is also not shown Connection line connected to the high pressure line of the axial piston pump 1, so that the set pressure in the second pressure chamber 36 from that in the High pressure line of the axial piston pump 1 prevailing delivery pressure through the Control valve 39 is derived.
  • the one that arises in the second pressure chamber 36 Signal pressure is therefore always lower than that prevailing in the first pressure chamber 34 Delivery pressure of the axial piston pump 1.
  • the second control surface 35 is larger dimensioned as the first control surface 33, arises between the forces with which the first control surface 33 and the second control surface 35 of the actuating piston 30 are acted upon be a balance of forces, so that the difference in forces between the Control surfaces 33 and 35 attacking forces in the case of equilibrium is zero.
  • the control valve 39 has a valve piston 41 which is controlled by a proportional Magnet 42 can be acted upon axially via a plunger 43.
  • a proportional Magnet 42 can be acted upon axially via a plunger 43.
  • the Valve piston 41 moved in proportion to the control current against the return spring 44.
  • the return spring 44 engages a connecting member 45, which on the valve piston 41 is non-positively, and is supported on a first spring plate 46.
  • the first Spring plate 46 is by a function to be described in more detail Swing-out spring 47 on a threaded bolt 48 in the exemplary embodiment trained adjusting member held in contact so that the bias of the return spring 44 is adjustable by turning the threaded bolt 48.
  • the restoring force will rather through the one in the first pressure chamber 34 and the first control surface 33 acting delivery pressure of the axial piston machine 1 causes.
  • the Feedback spring 50 acts on the valve piston 41 with one against the Force applied by the proportional magnet 42 directed counterforce, so that the signal pressure prevailing in the second pressure chamber 36 increases with increasing Displacement of the adjusting piston 30 in the upward direction in FIG. 2 is reduced becomes. There is therefore a new balance of power in a shifted Actuating piston position of the actuating piston 30, which is due to the control pressure on the Actuating piston 30 actuating force exerted by the in the high pressure line prevailing delivery pressure cancels the restoring force exerted.
  • a swing-out spring 47 is provided which is between the first Spring plate 46 and a stop element designed essentially as a hollow cylinder 52 is clamped.
  • the stop element 52 has an integrally formed support surface 53, on which the swing-out spring 47 rests, and also a molded one Stop surface 54 on.
  • Swiveling spring 47 swiveling out the axial piston machine 1 again from the zero position, in which the axial piston machine 1 without or with very little Funding volume works, but is still enabled safely.
  • the setting piston 30 is not in the range for hydraulic control sufficient delivery volume through the swing-out spring 47 via the stop element 52 acted upon and moved so far in the direction directed downward in FIG. 2 until the delivery pressure built up by the axial piston pump 1 in the high-pressure line for a hydraulic control of the actuating piston 30 is sufficient again.
  • the end surface 55 of the Adjusting piston 30 then lifts off the stop surface 54 of the stop element 52 and the further actuation of the actuating piston 30 takes place in the area of the increasing Delivery volume of the axial piston pump 1 exclusively hydraulically in the above described way.
  • the swing-out spring 47 in that shown in FIGS. 1 and 2 Exemplary embodiment fulfills two separate functions: On the one hand, the pivoting out the actuating piston 30 supports from the zero position; on the other hand, the first Spring plate 46 on the threaded bolt 48 serving as an adjusting member continuously in Stop held. The first spring plate 46 is therefore by turning the Threaded bolt 48 axially adjustable without moving freely in the actuating piston bore 32 his. The bias of the return spring 44 is therefore simple from the outside adjustable. Due to the additional function of the swing-out spring 47 as a contact spring the structural compactness of the adjusting device 21 according to the invention still further increased and a reliable working arises even with low funding volume Adjustment device 21, which manages with a small construction volume.
  • the length of the hollow cylindrical stop element 52 can be the area in which the swing-out spring 47 and the actuating piston 30 acted upon, depending on the circumstances of the controlled Axial piston pump 1 can be varied.
  • the area in which the swing-out spring 47 acts on the actuating piston 30, can be limited to that area in which the delivery pressure provided by the axial piston pump 1 to a purely hydraulic control is not sufficient.
  • the length of the Stop element 52 can also have a minimum delivery volume of the axial piston pump 1 be specified that enables sufficient heat dissipation in the idle range.
  • Fig. 3 For a better understanding of the invention in Fig. 3 is the above Embodiment corresponding hydraulic block diagram shown. Already elements described are provided with the same reference numerals, so that the Assignment is facilitated.
  • the axial piston pump 1 delivers into the high-pressure line 70 and builds one there corresponding delivery pressure.
  • the pressure medium is sucked out of the tank 71.
  • the control valve 39 is connected via the connecting line 72 and the check valve 43 the high pressure line 70 connected so that the delivery pressure is present at the inlet 40.
  • the delivery pressure also acts on the first control surface 33 of the first pressure chamber 34.
  • a signal pressure is set in his Relationship to the delivery pressure at port 40 of a control flow is proportional with which the electrical proportional magnet 42 is controlled. The described balance of forces is established between the control surfaces 33 and 35 a, the position of the actuating piston 30 and thus the delivery volume of the Axial piston pump 1 specifies.
  • this measure according to the invention has the Advantage that the axial piston pump 1 can be swiveled out again, although in this area the one built up by the axial piston pump 1 in the high-pressure line 70 Delivery pressure for a purely hydraulic control of the actuating piston 30 is not sufficient. As soon as a sufficient delivery pressure is established in the high-pressure line 70, the pressure rises Surface 55 from the swing-out spring 47 and the adjusting device 21 controls the Actuating piston 30 purely hydraulically.
  • Auxiliary pressure supply which swings out the axial piston pump 1 even when it drops of the delivery pressure below that for the hydraulic control of the actuating piston 30 necessary threshold value is possible with the adjusting device according to the invention 21 not necessary.
  • the swing-out spring 47 also supports rapid pressure and flow rate build-up.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Control Of Positive-Displacement Pumps (AREA)

Claims (10)

  1. Dispositif de réglage (21) qui sert à régler le volume convoyé d'une pompe à pistons axiaux (1), comportant
    un piston de positionnement (30) qui est relié positivement à un organe de positionnement (19) réglant le volume convoyé de la pompe à pistons axiaux (1) et sur lequel sont réalisées une première surface de commande (33) reliée à une conduite sous haute pression (70) de la pompe à pistons axiaux (1) et une deuxième surface de commande (35) reliée à une conduite de commande (37) pour le pilotage hydraulique du piston de positionnement (30),
    caractérisé par
    une valve de commande (39) via laquelle la conduite de commande (37) est reliée à la conduite sous haute pression (70),
    un élément de rétroaction (49) agencé entre le piston de positionnement (30) et la valve de commande (39), le piston de positionnement (30) étant déplacé, en étant piloté par voie hydraulique, en fonction de la différence de forces qui s'établit entre les surfaces de commande (33, 35), jusqu'à ce que la différence de forces devienne nulle en raison de la rétroaction de la position du piston de positionnement via l'élément de rétroaction (49) vers la valve de commande (39), et
    un ressort de pivotement (47) qui est précontraint par le piston de positionnement (30) peu avant d'atteindre sa position nulle dans laquelle la pompe à pistons axiaux (1) travaille sans volume de convoyage ou avec un volume de convoyage minimal, la précontrainte du ressort de pivotement (47) étant dimensionnée de telle sorte que le ressort de pivotement (47) déplace le piston de positionnement (30) lors du pivotement hors de la position nulle jusqu'à ce que la pression de convoyage établie par la pompe à pistons axiaux (1) dans la conduite sous haute pression (70) suffise pour le pilotage hydraulique du piston de positionnement (30).
  2. Dispositif de réglage selon la revendication 1, caractérisé en ce que la valve de commande (39) comprend un piston de valve (41) qui est mobile à l'encontre d'un ressort de rappel (44), le ressort de rappel (44) prenant appui contre un élément d'appui (46) déplaçable avec l'organe de réglage (48), qui est maintenu en appui contre l'organe de réglage (48) par le ressort de pivotement (47).
  3. Dispositif de réglage selon la revendication 2, caractérisé en ce que l'élément d'appui est une première coupelle de ressort (46) et l'organe de réglage est un boulon (48).
  4. Dispositif de réglage selon la revendication 2 ou 3, caractérisé en ce que l'élément de rétroaction est un ressort de rétroaction (49) qui est serré entre une deuxième coupelle de ressort (50) reliée positivement au piston de valve (41) et le piston de positionnement (30).
  5. Dispositif de réglage selon l'une des revendications 2 à 4, caractérisé en ce que le ressort de pivotement (47) est serré entre un élément de butée (52) et l'élément d'appui (46), et en ce que le piston de positionnement (30) vient buter contre l'élément de butée (52) peu avant d'atteindre sa position nulle et emmène celui-ci pour précontraindre le ressort de pivotement (47).
  6. Dispositif de réglage selon la revendication 4 et 5, caractérisé en ce que l'élément de butée (52) entoure coaxialement le ressort de rétroaction (49).
  7. Dispositif de réglage selon la revendication 6, caractérisé en ce que le ressort de pivotement (47) entoure coaxialement l'élément de butée (52) et le ressort de rétroaction (49).
  8. Dispositif de réglage selon l'une des revendications 5 à 7, caractérisé en ce que l'élément de butée (56) est réalisé sous forme de cylindre creux présentant une surface d'appui conformée (53) sur laquelle repose le ressort de pivotement (47) et présentant une surface de butée conformée (54) contre laquelle vient buter le piston de positionnement (30).
  9. Dispositif de réglage selon la revendication 8, caractérisé en ce que la zone dans laquelle le ressort de pivotement (47) sollicite le piston de positionnement (30) par une force de pivotement est déterminée par la longueur axiale de l'élément de butée (52).
  10. Dispositif de réglage selon l'une des revendications 1 à 9,
    caractérisé en ce que la pompe à pistons axiaux (1) est réalisée en mode de construction à axe oblique, et en ce que le piston de positionnement (30) attaque via un tenon de positionnement (31) un corps formant disque de commande (19), pourvu de lobes de commande, de la pompe à pistons axiaux (1).
EP97120301A 1996-12-19 1997-11-19 Dispositif de réglage de la capacité d'une pompe à pistons axiaux Expired - Lifetime EP0849468B2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19653165 1996-12-19
DE19653165A DE19653165C2 (de) 1996-12-19 1996-12-19 Verstelleinrichtung zur Verstellung des Fördervolumens einer Axialkolbenpumpe

Publications (4)

Publication Number Publication Date
EP0849468A2 EP0849468A2 (fr) 1998-06-24
EP0849468A3 EP0849468A3 (fr) 1999-09-15
EP0849468B1 true EP0849468B1 (fr) 2004-01-07
EP0849468B2 EP0849468B2 (fr) 2012-09-05

Family

ID=7815450

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97120301A Expired - Lifetime EP0849468B2 (fr) 1996-12-19 1997-11-19 Dispositif de réglage de la capacité d'une pompe à pistons axiaux

Country Status (2)

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EP (1) EP0849468B2 (fr)
DE (2) DE19653165C2 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10711771B2 (en) 2015-08-10 2020-07-14 Eaton Intelligent Power Limited Electrohydraulic proportional pressure control for open circuit pump

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DE19842029B4 (de) * 1998-09-14 2005-02-17 Sauer-Sundstrand Gmbh & Co. Verstellung von hydrostatischen Axialkolbenmaschinen mittels Schrittmotor
DE19857082A1 (de) * 1998-12-10 2000-06-21 Brueninghaus Hydromatik Gmbh Axialkolbenmaschine
DE19860023C5 (de) * 1998-12-23 2011-04-28 Brueninghaus Hydromatik Gmbh Kolbenmaschine mit einer Dichtungsanordnung
US6260468B1 (en) * 1999-02-26 2001-07-17 Sauer-Danfoss Inc. Single-piece proportional control
DE19949169C2 (de) 1999-10-12 2001-10-11 Brueninghaus Hydromatik Gmbh Verstellvorrichtung
DE10035631C2 (de) * 2000-07-21 2003-01-30 Brueninghaus Hydromatik Gmbh Nullastschaltung
DE10119236C1 (de) * 2001-04-19 2002-12-12 Brueninghaus Hydromatik Gmbh Axialkolbenmaschine in Schrägachsen-Bauweise, mit einem Schwenkwinkel-Sensor
DE102005060960B3 (de) * 2005-12-20 2007-06-28 Sauer-Danfoss Gmbh & Co Ohg Axialkolbenmaschine mit einem verstellbaren Schrägachsen-Ventilsegment und einer Verstelleinheit zur elektrisch proportionalen Verstellung des Schluckvolumens
WO2009024337A1 (fr) 2007-08-20 2009-02-26 Robert Bosch Gmbh Système hydraulique à machine hydrostatique réglable
DE102008031768A1 (de) 2008-07-04 2010-01-07 Alpha Fluid Hydrauliksysteme Müller GmbH Regelanordnung für proportionale Winkelverstellung
DE102011006102A1 (de) * 2011-03-25 2012-09-27 Zf Friedrichshafen Ag Stellvorrichtung eines Hydrostatmoduls
DE102012214372A1 (de) 2012-03-01 2013-09-05 Robert Bosch Gmbh Hydraulische Axialkolbenmaschine in Schrägachsenbauweise
DE102013208025A1 (de) 2013-05-02 2014-11-06 Robert Bosch Gmbh Verstelleinheit zur Verstellung eines Hubvolumens einer Axialkolbenmaschine
DE102013224112B4 (de) 2013-11-26 2024-01-18 Robert Bosch Gmbh Hydromaschine in Axialkolbenbauweise mit einer durch einen Proportionalmagneten verstellbaren Schrägscheiben-Stelleinrichtung
DE102014206755B4 (de) 2014-02-18 2024-09-19 Robert Bosch Gmbh Verstelleinrichtung einer Axialkolbenmaschine mit einem Druckmittel beaufschlagten Steuerventil
DE102015205549B4 (de) * 2015-03-26 2019-01-03 Danfoss Power Solutions Gmbh & Co. Ohg Verfahren zur kalibrierung einer hydraulikmaschine und hydraulikmaschine mit verstellelement
EP3314122B1 (fr) * 2015-06-26 2021-09-15 Casappa S.p.A. Pompe à déplacement variable et procédé permettant de réguler la pompe
DK3374639T3 (da) 2015-11-15 2021-03-08 Eaton Intelligent Power Ltd Styresystem til hydraulikpumpe
DE102017200244A1 (de) 2017-01-10 2018-07-12 Robert Bosch Gmbh Hydrostatischer Axialkolbenmotor in Schrägachsenbauweise
DE102017204461A1 (de) 2017-03-17 2018-09-20 Robert Bosch Gmbh Hydrostatischer Fahrantrieb
DE102019205140A1 (de) 2019-04-10 2020-10-15 Robert Bosch Gmbh Axialkolbenmaschine mit in die Anschlussplatte integrierten Ventilschiebern

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DE3232695C2 (de) * 1982-09-02 1984-08-16 Hydromatik GmbH, 7915 Elchingen Leistungsregel-Vorrichtung für eine Hydropumpe
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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10711771B2 (en) 2015-08-10 2020-07-14 Eaton Intelligent Power Limited Electrohydraulic proportional pressure control for open circuit pump
US11378068B2 (en) 2015-08-10 2022-07-05 Danfoss Power Solutions Ii Technology A/S Electrohydraulic proportional pressure control for open circuit pump
US11885317B2 (en) 2015-08-10 2024-01-30 Danfoss A/S Electrohydraulic proportional pressure control for open circuit pump

Also Published As

Publication number Publication date
EP0849468A2 (fr) 1998-06-24
EP0849468A3 (fr) 1999-09-15
DE19653165C1 (de) 1998-04-02
DE19653165C2 (de) 2002-04-25
EP0849468B2 (fr) 2012-09-05
DE59711184D1 (de) 2004-02-12

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