EP0554537B1 - Machine à pistons axiaux, en particulier pompe hydraulique de type à plateau biais ou à axes inclinés, pourvue d'un dispositif de réglage du débit - Google Patents

Machine à pistons axiaux, en particulier pompe hydraulique de type à plateau biais ou à axes inclinés, pourvue d'un dispositif de réglage du débit Download PDF

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Publication number
EP0554537B1
EP0554537B1 EP92120511A EP92120511A EP0554537B1 EP 0554537 B1 EP0554537 B1 EP 0554537B1 EP 92120511 A EP92120511 A EP 92120511A EP 92120511 A EP92120511 A EP 92120511A EP 0554537 B1 EP0554537 B1 EP 0554537B1
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EP
European Patent Office
Prior art keywords
setting
piston
machine according
throttle
axial piston
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
EP92120511A
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German (de)
English (en)
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EP0554537A1 (fr
Inventor
Hermann Hoffmeister
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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Filing date
Publication date
Application filed by Brueninghaus Hydromatik GmbH filed Critical Brueninghaus Hydromatik GmbH
Publication of EP0554537A1 publication Critical patent/EP0554537A1/fr
Application granted granted Critical
Publication of EP0554537B1 publication Critical patent/EP0554537B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/08—Regulating by delivery pressure
    • 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
    • F04B1/324—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 swash plate

Definitions

  • Axial piston machines can be used for different purposes and in particular different drive solutions. In many applications, a certain throughput volume of the minimum and / or maximum throughput volume is desired.
  • the stroke end positions of the piston of the adjusting device are provided with adjustable stops in the form of adjusting screws.
  • the invention has for its object to design an axial piston machine so that a simple adjustment or adjustment of the minimum and / or maximum throughput volume is possible.
  • the axial piston machine according to the invention there is an adjustment or adjustment device which is accessible on the one hand from the outside and on the other hand enables continuous adjustment, the length of the piston rod not being changed.
  • An axial piston machine according to the invention therefore does not need to be dismantled and reassembled to adjust its minimum throughput.
  • the adjustment can be readjusted in a simple manner after it has been checked and ascertained that it is inadequate without dismantling and reassembling the axial piston machine.
  • the adjustment can thus also be made on the spot, i.e. H. can be set, checked and adjusted in a simple manner at the possibly dirty site on the construction site.
  • the swash plate type axial piston machine 10 shown in FIG. 1 is of basically known design, so that only its main parts are briefly mentioned below.
  • the axial piston machine 10 has a housing 11 with a cup-shaped housing part 11a, which is closed by a cover plate 11b.
  • a control disk 11c is held on the inside of the cover plate 11b and has control slots which are known per se and which interact with the facing surface of a cylinder drum 13 which is rotatably mounted in the housing Bearing shaft 14 is attached.
  • a swash plate 15 in the cavity 12 which is penetrated by the bearing shaft 14 in a clearance, and which is mounted in a pivot bearing 15b so as to be non-rotatable with respect to the longitudinal axis 10a of the axial piston machine 10, but pivotable about a pivot axis 15a running at right angles thereto.
  • a plurality of working cylinders are arranged in the cylinder drum 13, each with a working piston displaceable therein, which are pivotably supported on the swash plate 15 by means of sliding shoes.
  • a supply line and discharge line (pressure line in pump operation) for the hydraulic working medium, in particular hydraulic oil, which are indicated in the drawing, are denoted by 16a, 16b and run in a manner known per se through the cover plate 11b.
  • the throughput volume adjusting device is integrated into the housing 11 and comprises an adjusting cylinder 18 positioned laterally next to the cylinder drum 13, the cylinder 19 of which is arranged axially parallel in the cover plate 11b and is open to the cavity 12.
  • an adjusting piston 21 is slidably mounted, which is dimensioned so long that it delimits a pressure chamber 22 on the front and projects into the cavity 12 on the rear.
  • a piston rod 23 is pivotally mounted in spherical bearings, each of which is preferred, in a manner known per se.
  • the pressure chamber 22 can be acted upon by a preferably throttled hydraulic control line 24 running through the cover plate 11b with a hydraulic control pressure, which can be the working pressure of the axial piston machine or the pressure of an auxiliary pump or other hydraulic control device.
  • the adjusting device 17 is assigned a special adjusting device 25 for adjusting or adjusting the minimum throughput volume.
  • This adjusting device 25 comprises a hydraulic part with an adjustable throttle 26 and a mechanical part with an adjusting device 27 for the stepless pre-adjustment of the throttle cross section of the throttle 26.
  • the throttle 26 is arranged in a discharge line extending from the pressure chamber 22, which is inter alia through a channel 28 is formed in the adjusting piston 21, the channel 28 being open on the end face of the adjusting piston 21, initially running axially and then radially, and opening into a channel opening 29 in the cylindrical outer surface of the adjusting piston 21.
  • the arrangement is such that the channel opening 29 in the rear stroke end region of the adjusting piston 21 (see FIG.
  • the throttle 26 is formed, the peripheral edge of which comprises an immovable throttle edge portion 26a, here on the cylinder side, and a throttle edge portion 26b, which is movable on the piston side here, which can be displaced by the mechanical adjusting device 27.
  • the adjusting device 27 comprises a crank 33, which the hollow cylindrical housing wall 34 is arranged in the vicinity of its free edge 35 in the area in which the adjusting piston 21 projects beyond the inside of the cover plate 11b on the rear.
  • the crank 33 has at its outer end a tool engagement element, e.g. B. a polygonal head 36 and at its inner end a crank pin or eccentric 37 which fits into a longitudinal groove 38 of the adjusting piston 21 with little movement. Consequently, by turning the crank 33, the adjusting piston 21 in the cylinder chamber 19 can be rotated about its longitudinal axis, as a result of which the movable throttle edge section 26b is displaced in the circumferential direction of the adjusting piston 21 depending on the direction of rotation of the crank 33.
  • the adjusting device 27 can be locked in its respective crank position.
  • the crank 23 can be designed as a screwed into the housing wall 34 threaded bolt, which can be locked against the housing wall 34 by locking a lock nut 39 screwed thereon.
  • the throughput of the axial piston machine 10 over the entire adjustment range of the adjusting piston 21 is determined by an equilibrium position, which, taking into account the hydraulic actuating force F of the adjusting piston 31 and the restoring force F1, is an oppositely effective compression spring which is clamped between the housing 11 and the swash plate 15 as Spring 41 adjusts.
  • the adjustable throttle edge section 26b When adjusting the axial piston machine 10 in the direction of the maximum or minimum throughput volume, the adjustable throttle edge section 26b is displaced in the circumferential direction by rotating the adjusting piston 21, and the throttle cross section is enlarged or reduced depending on the direction of movement.
  • the hydraulic medium flowing through the throttle 26 enters the cavity 12 and can flow to the drain connected to it.
  • the adjusting device 27 thus operates essentially without loss.
  • the adjustable throttle 26 is formed by a channel opening 42 in the cylindrical wall 19b and an oblique front edge of the adjusting piston 21, which partially covers the channel opening 42 in the rear stroke end region of the adjusting piston 21.
  • a channel 43 leads from the channel opening 42 to the return in a manner not shown.
  • the adjusting piston 21 can be stepped in a Z-shape on the front.
  • the adjustable throttle 26 is formed by the interaction of the channel opening 29 in the adjusting piston 31 and the channel opening 42 in the cylinder chamber wall 19a.
  • FIGS. 8 and 9 is a further development of the embodiment according to FIGS. 2 and 3.
  • the radial section of the channel 28 is made diametrically continuous, so that in the lateral surface of the adjusting piston 21 there are two orifices 29 opposite one another, which each cooperate with one control edge 32 from one of two associated diametrically opposite recesses 31 and each form an adjustable throttle 26.
  • a corresponding configuration is also possible in the configurations according to FIGS. 4 and 5 and 6 and 7.
  • the adjusting device 27 does not act on the adjusting piston 21, but rather on a sleeve 44 surrounding it and bearing it, which is fitted with play between the adjusting piston 21 and the cylinder chamber wall 19b. While an oblique control edge 32 is required in the embodiments described above in order to allow a change in the throttle cross section to take effect due to a rotation of the adjusting piston 21 about its longitudinal axis, an oblique control edge 32 is only required in the embodiment according to FIGS. 10 and 11 if the Sleeve 44, in which the eccentric 37 of the crank 33 surrounds in a radial hole 45 about the adjusting piston 21 is rotatable.
  • the eccentric 37 of the crank 33 is offset in the circumferential direction of the sleeve 44 relative to the shaft of the crank 33, so that when the crank 33 rotates, the sleeve 44 is displaced longitudinally and thus the overlap of the channel opening 29 with the rear end edge 46 the sleeve takes place, whereby the sleeve-side throttle edge portion 26a is axially displaced and the throttle 26 is enlarged or reduced.
  • the sleeve 44 also projects beyond the cover plate 11b to the rear, the channel opening 29 being at a rearward distance from the inside of the cover plate 11b or the cylinder chamber 19.
  • FIG 12 shows schematically an axial piston machine 10 in the slant plate or inclined axis type with an adjusting device 17a, in which two adjusting cylinders 18a, 18b, each with an adjusting piston 21a, 21b on the adjusting element z. B. the swash plate 15, the axial piston machine 10 act.
  • This adjusting device 17 is a so-called working pressure-controlled adjusting device in which the throughput volume setting is dependent on the working pressure in the discharge line 16b and the throughput volume is reduced with increasing working pressure and the throughput volume is increased with decreasing working pressure.
  • the pressure chamber 22b is connected to the discharge line 16b by a hydraulic connecting line 46, a throttle for damping also being provided near the pressure chamber 22b.
  • a branch line 47 branches off from the connecting line 46 and leads to the pressure chamber 22a of the adjusting cylinder 18a.
  • a control valve 49 in the form of a 3/4-way valve is arranged, the valve body of which is directed against one by a control line 51 starting from the connecting line 46
  • Return spring 52 is hydraulically adjustable.
  • the control valve 49 is a proportional valve.
  • both adjusting cylinders 18a, 18b are provided with a single adjusting device 25a or 25b with a hydraulic and mechanical adjusting device 26, 27a, 27b in accordance with the above-described configurations, specifically in accordance with the configuration in accordance with FIGS. 6 and 7, in which the channel opening 29 on the lateral surface of the existing adjusting piston 21a, 21b cooperates with the associated channel opening 42 in the inner wall of the associated adjusting cylinder 18a, 18b and thereby forms the adjustable throttle 26.
  • the two adjusting pistons 21a, 21b are effective in the same direction of action.
  • the respective throughput volume setting results from an equilibrium, the adjusting force generated by the adjusting cylinder 18a and the adjusting force generated by the adjusting cylinder 18b, which are illustrated by F2 and F3.
  • the passage of the connecting line 47 is throttled in the control valve 49, the throughput volume setting shown in FIG. 12, namely an adjustment of the maximum throughput volume, being obtained.
  • the control valve 49 opens the passage in the connecting line section 47 so that the adjusting cylinder 18a is subjected to increasing pressure, and preferably this adjusting cylinder 18a is dimensioned larger in cross section than the adjusting cylinder 18b. Due to the increasing pressurization of the setting cylinder 18a, the setting cylinder 18b is overpressed and the throughput volume of the axial piston machine 10 is reduced until a minimum throughput volume is reached. The adjusting piston 21b is pushed in and the adjusting piston 21a pushed out until the associated throttle 26 comes into operation in the setting for minimum throughput volume (not shown).
  • the invention is implemented on an inclined-axis machine with a variable throughput volume, with an adjusting device 17 for adjusting your throughput volume, which has only one adjusting cylinder 18, the adjusting piston 21 of which delimits pressure chambers 22a, 22b at both ends, which are connected to hydraulic control lines 24a, 24b and can be acted upon by a control pressure or the like through these control lines for the purpose of controlled displacement of the adjusting piston 21.
  • the only available adjusting piston 21 is assigned both an adjusting device 27a for adjusting the minimum throughput volume and an adjusting device 27b for adjusting the maximum throughput volume.
  • the inclined axis machine according to FIG. 13 is fundamentally of a known construction, so that no further description is required.
  • the cylinder drum 13, which is pivotably mounted with the spherically convex control disc 11c, can be pivoted about a pivot axis 15c between a drive or output shaft 14 and a correspondingly spherically concave guide surface 11e on the inside of the cover plate 11b.
  • the cover plate 11b is mounted in a cylinder chamber 19, which is displaceable back and forth in a cylinder chamber 19 which is arranged transversely to the longitudinal axis 10a and which in its central region has a spherical or cylindrical driver pin 21c projecting inward from its outer surface, which fits into an engagement hole 21d in of the control disk 11c and thus can pivot the cylinder drum 13 which forms a unit with the control disk 11c.
  • the existing cylinder chamber is open to the cavity 12.
  • the adjusting piston 21 is a stepped piston, the right end of which is larger in diameter than the left end in FIG.
  • the cylinder chamber 19 is also manufactured in a correspondingly stepped manner, so that the piston ends are sealingly displaceably guided in the corresponding cylinder chamber sections.
  • the adjusting devices 25a, 25b provided for adjusting the minimum and maximum throughput volumes correspond in principle to the above-described configurations, namely they comprise a mechanical part with the adjusting device 27a, 27b and a hydraulic part with the associated throttle 26, each between the movable piston 21 and an immovable part of the adjusting cylinder 18 or another part of the same is effective.
  • the adjusting piston 21 consists of three parts lying one behind the other in its longitudinal direction, of which the middle part 21d has the driving pin 21c and the other two end parts 21e, 21f each of the associated adjusting device 27a , 27b and each have a longitudinal groove 38 into which the associated crank 39 with the eccentric 37 fits in a corresponding manner in order to be able to rotate these piston parts 21e, 21f in the circumferential direction.
  • the throttle configurations in this exemplary embodiment essentially correspond to the exemplary embodiments according to FIGS. 4 and 5.
  • the inclined front edges of the associated piston part 21e, 21f are formed by notch-shaped end recesses.
  • the piston middle part 21d has at both ends coaxial cylindrical pins 21g, on which the associated piston end parts 21e, 21f sit with corresponding blind bores with little movement play and can be rotated independently of one another. This makes it possible to adjust the minimum and / or maximum throughput volume independently of one another.
  • the adjusting device 27 encompasses the housing wall 34 in the area in which the adjusting piston 22 projects beyond the adjusting cylinder 18 or the cover plate 11b on the rear, with a free space 55 for the crank arm between the adjusting piston 22 and the housing wall 34 33a is provided.
  • the adjusting device 27 or the adjusting devices 27a, 27b can also be provided in the area in which the adjusting piston 21 or its end parts 21e, 21f are guided in the cylinder chamber 19 are. In this case, however, an inner recess 56 forming the free space 55 in the cylinder chamber wall is required for the crank arm.
  • the adjusting devices 27a, 27b engage in the cover plate 11b from the free end face 11e thereof.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)

Claims (18)

  1. Machine à pistons axiaux, en particulier de type à disque oblique ou axe oblique, dont le volume est réglable au moyen d'un dispositif de réglage (27 ; 27a, 27b), qui comporte un piston de réglage (21 ; 21a, 21b) monté coulissant dans un cylindre de réglage (18 ; 18a, 18b), qui est alimenté par la pression de travail ou une pression de commande et qui agit sur un organe de réglage (15 ; 11c,), caractérisée en ce qu'un organe d'étranglement d'évacuation (26) est prévu dans un canal d'évacuation (28, 43) partant de la chambre de pression (22) du cylindre de réglage (18a, 18b), dont la section transversale d'étranglement est libérée pour le débit, par le piston de réglage dans sa position de fin de course, et en ce qu'il est prévu un dispositif d'ajustage (25), pour l'ajustage de l'organe d'étranglement d'évacuation (26), accessible de l'extérieur de la machine à pistons axiaux (1).
  2. Machine à pistons axiaux selon la revendication 1, caractérisée en ce que l'organe d'étranglement d'évacuation (26) est formé par la portion de bord d'étranglement (26a) d'un composant fixe et la portion de bord d'étranglement (26b) d'un composant réglable ou ajustable, et le composant ajustable est déplaçable par le dispositif d'ajustage (25).
  3. Machine à pistons axiaux selon la revendication 1 ou 2, caractérisée en ce que le dispositif d'ajustage (25) comporte un dispositif d'ajustage mécanique (27 ; 27a, 27b).
  4. Machine à pistons axiaux selon l'une au moins des revendications précédentes, caractérisée en ce que l'organe d'étranglement d'évacuation (26) est formé par une portion de bord d'étranglement (26b), qui est prévue sur le piston de réglage (21 ; 21a, 21b) et par une portion de bord d'étranglement (26a), qui est prévue sur un composant (44), entourant le piston de réglage (21 ; 21a, 21b), lequel composant est réglable ou ajustable par rapport au piston de réglage (21 ; 21a, 21b), au moyen du dispositif d'ajustage (25).
  5. Machine à pistons axiaux selon la revendication 4, caractérisée en ce que le composant est ajustable dans la direction axiale du piston de réglage (21) ou dans sa direction périphérique.
  6. Machine à pistons axiaux selon la revendication 5, caractérisé en ce que le composant est un manchon (44) entourant, de préférence guidant, le piston de réglage (21).
  7. Machine à pistons axiaux selon l'une des revendications précédentes, caractérisée en ce que le piston de réglage (21) peut tourner avec le dispositif d'ajustage (25) et peut être fixé dans la position de rotation respective.
  8. Machine à pistons axiaux selon l'une au moins des revendications précédentes, caractérisée en ce que l'organe d'étranglement d'évacuation (26) est formé par une ouverture de canal (29) d'un canal d'évacuation (28), partant du côté frontal du piston de réglage (21), dans la surface d'enveloppe du piston et par le bord arrière (19a) de la paroi (19b) du cylindre de réglage ou à une ouverture de canal (42) d'un canal d'évacuation (43), traversant la paroi (19b) de la chambre de cylindre.
  9. Machine à pistons axiaux selon l'une au moins des revendications 1 à 7, caractérisée en ce que l'organe d'étranglement d'évacuation (26) est formé par l'ouverture de canal (42) d'un canal d'évacuation (43), traversant la paroi (19b) de la chambre de cylindre, et un bord avant oblique du piston de réglage (21) ou une ouverture du canal (29) d'un canal d'évacuation (28) partant du côté frontal du piston de réglage (21) et débouchant sur sa surface d'enveloppe.
  10. Machine à pistons axiaux selon l'une au moins des revendications 4 à 7, caractérisée en ce que l'organe d'étranglement d'évacuation (26) est formé par l'ouverture de canal (29) d'un canal d'évacuation (28), partant du côté frontal du piston de réglage (21), dans la surface d'enveloppe du piston et par le bord arrière (46) du composant (44) ou l'ouverture d'un canal d'évacuation traversant le composant.
  11. Machine à pistons axiaux selon l'une au moins des revendications précédentes, caractérisée en ce que le piston de réglage (21, 21a, 21b, 21e, 21f) présente une rainure longitudinale (38) dans laquelle s'engage le dispositif d'ajustage (25) avec une partie d'engagement, en particulier un tenon excentré (37).
  12. Machine à pistons axiaux selon l'une au moins des revendications précédentes, caractérisée en ce que le composant ou le manchon (44) présente un trou (45), dans lequel s'engage le dispositif d'ajustage (25) avec une partie d'engagement, en particulier un tenon excentré (37).
  13. Machine à pistons axiaux selon l'une au moins des revendications 3 à 12, caractérisée en ce que le dispositif d'ajustage (27 ; 27a, 27b) comporte une manivelle (39) traversant le carter (11).
  14. Machine à pistons axiaux selon la revendication 13, caractérisée en ce qu'entre le piston de réglage (21 ; 21a, 21b) et la paroi (34 ; 11e) du carter, traversée par la manivelle (39), il est prévu un espace libre (55) ou un évidement (56) pour le bras de manivelle (33a).
  15. Machine à pistons axiaux selon l'une au moins des revendications précédentes, caractérisée en ce que le piston de réglage (21) et/ou le composant ou le manchon (44) dépassent vers l'intérieur de la chambre (19) du cylindre de réglage et le dispositif d'ajustage (27) est placé dans cette zone de dépassement.
  16. Machine à pistons axiaux selon l'une au moins des revendications précédentes, caractérisée en ce que le piston de réglage (21) est constitué de deux ou de trois parties (21d, 21e, 21f), situées l'une derrière l'autre dans sa direction longitudinale, les deux parties terminales (21e, 21f) du piston délimitant une chambre de pression (22a, 22b), peuvent tourner l'une par rapport à l'autre ainsi que par rapport à l'éventuelle partie centrale (21d) et un dispositif d'ajustage (25) est associé à chaque partie terminale (21e, 21f) du piston.
  17. Machine à pistons axiaux selon l'une au moins des revendications précédentes, caractérisée en ce que dans le cas d'une machine à axe oblique, le dispositif d'ajustage (27 ; 27a, 27b) pour l'ajustage du débit minimal et/ou du débit maximal, est ou sont placés sur le côté frontal de la plaque de couvercle (11b).
  18. Machine à pistons axiaux selon l'une au moins des revendications précédentes, caractérisée en ce que sur l'organe de réglage (13 ; 15) de la machine à pistons axiaux (10) agissent deux cylindres de réglage (18a, 18b), dont les pistons (21a, 21b) peuvent être extraits et introduits dans des sens opposés l'un à l'autre, et en ce qu'à chacun des deux cylindres de réglage (18a, 18b) est associé un dispositif d'ajustage (25), pour l'ajustage du débit minimal et du débit maximal.
EP92120511A 1992-01-30 1992-12-01 Machine à pistons axiaux, en particulier pompe hydraulique de type à plateau biais ou à axes inclinés, pourvue d'un dispositif de réglage du débit Expired - Lifetime EP0554537B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4202631 1992-01-30
DE4202631A DE4202631C2 (de) 1992-01-30 1992-01-30 Axialkolbenmaschine, insbesondere Hydropumpe der Schiefscheibenbauart oder der Schrägachsenbauart, deren Durchsatzvolumen durch eine Einstellvorrichtung einstellbar ist

Publications (2)

Publication Number Publication Date
EP0554537A1 EP0554537A1 (fr) 1993-08-11
EP0554537B1 true EP0554537B1 (fr) 1995-06-28

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Family Applications (1)

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EP92120511A Expired - Lifetime EP0554537B1 (fr) 1992-01-30 1992-12-01 Machine à pistons axiaux, en particulier pompe hydraulique de type à plateau biais ou à axes inclinés, pourvue d'un dispositif de réglage du débit

Country Status (2)

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EP (1) EP0554537B1 (fr)
DE (2) DE4202631C2 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2116506C1 (ru) * 1997-10-31 1998-07-27 Геннадий Андреевич Баев Самовсасывающий аксиально-поршневой регулируемый насос
DE19755386C2 (de) 1997-12-12 1999-10-21 Brueninghaus Hydromatik Gmbh Hydrostatische Maschine mit einer drehbar gelagerten Zylindertrommel und einer einstellbaren Schwenkscheibe
DE102007022569A1 (de) * 2007-05-14 2008-11-20 Robert Bosch Gmbh Axialkolbenmaschine mit Rückführvorrichtung
CH703535B1 (de) * 2010-07-22 2012-09-14 Liebherr Machines Bulle Sa Einstellmittel für einen Stellzylinder, Stellzylinder und Hydraulikmaschine.
AU2014270792B2 (en) 2013-05-22 2017-08-31 Hydac Drive Center Gmbh Axial piston pump having a swash-plate type construction

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4017219A (en) * 1975-12-22 1977-04-12 Abex Corporation Control system for variable displacement pumps
DE2908332A1 (de) * 1979-03-03 1980-09-18 Paul Hammelmann Plungerpumpe mit druckabhaengig sich aendernder foerdermenge
FR2503273B1 (fr) * 1981-04-02 1986-02-21 Messier Hispano Sa Pompe hydraulique
DE3310747A1 (de) * 1982-03-26 1983-10-06 Linde Ag Einstellbare axialkolbenpumpe mit einem regelorgan und regelorgan fuer solche
DE3345264A1 (de) * 1983-12-14 1985-06-27 Brueninghaus Hydraulik Gmbh, 7240 Horb Drehmomenten-regeleinrichtung fuer eine verstellbare hydropumpe
DE8400727U1 (de) * 1984-01-12 1985-05-09 Robert Bosch Gmbh, 7000 Stuttgart Folgesteuereinrichtung für eine verstellbare Pumpe
JPS63134869A (ja) * 1986-11-25 1988-06-07 Daikin Ind Ltd 可変容量形ピストン機械
DE3644769A1 (de) * 1986-12-30 1988-07-14 Brueninghaus Hydraulik Gmbh Regeleinrichtung fuer eine verstellbare hydrostatische maschine
US5076145A (en) * 1990-06-04 1991-12-31 Hagglunds Denison Corporation Axial piston pump having a blocking valve in a manually controlled valve plate

Also Published As

Publication number Publication date
DE4202631C2 (de) 1995-07-06
EP0554537A1 (fr) 1993-08-11
DE59202729D1 (de) 1995-08-03
DE4202631A1 (de) 1993-08-05

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