EP2145106B1 - Machine à pistons axiaux pourvue d'un dispositif de rappel - Google Patents

Machine à pistons axiaux pourvue d'un dispositif de rappel Download PDF

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Publication number
EP2145106B1
EP2145106B1 EP08758514.7A EP08758514A EP2145106B1 EP 2145106 B1 EP2145106 B1 EP 2145106B1 EP 08758514 A EP08758514 A EP 08758514A EP 2145106 B1 EP2145106 B1 EP 2145106B1
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EP
European Patent Office
Prior art keywords
piston
axial
control
piston machine
resetting element
Prior art date
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Active
Application number
EP08758514.7A
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German (de)
English (en)
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EP2145106A1 (fr
Inventor
Herbert Dreher
Clemens Krebs
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP2145106A1 publication Critical patent/EP2145106A1/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
    • F04B1/324—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
    • 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
    • F04B49/002—Hydraulic systems to change the pump delivery
    • 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

Definitions

  • the invention relates to an axial piston machine with an adjusting device and a return device for returning a position of a pivoting cradle.
  • the invention is based on the object to provide an axial piston machine with a compact positioning system and integrated feedback.
  • a return element is provided on an actuating piston of an adjusting device of an axial piston machine, which by its relative position to a housing of the axial piston machine provides information about the relative position of the actuating piston of the adjusting device and thus the pivoting cradle and the adjusted delivery volume by acting on a control device provided on the housing side, wherein this feedback element and the actuating piston are arranged in a plane which is perpendicular to the pivot axis of the pivoting cradle and which is parallel to a rotational axis of the axial piston machine.
  • FIG. 1 is a sectional view of an axial piston machine 1 shown, wherein the cutting plane parallel to a rotation axis of the axial piston machine 1 but eccentrically.
  • the axial piston machine 1 has a cylinder drum 2, in which a plurality of cylinder bores are distributed in a manner not shown distributed over a circumferential circle.
  • pistons are arranged longitudinally displaceable, which promote a pressure medium by their stroke movement when it is a pump in the illustrated axial piston machine 1.
  • the axial piston machine 1 has a housing, which consists of a first cup-shaped housing part 3 and a second housing part, which is designed as a flange 4.
  • a housing which consists of a first cup-shaped housing part 3 and a second housing part, which is designed as a flange 4.
  • One in the Fig. 1 unrecognizable drive shaft is rotatably mounted in the flange 4 and the first cup-shaped housing part 3 and rotatably connected to the cylinder drum 2.
  • Cylinder drum 2 rotated.
  • the arranged in the cylindrical drum 2 longitudinally displaceable piston based in a known manner on sliding blocks on a pivoting cradle 5 from.
  • the pivoting cradle 5 has a running surface 6 for this purpose.
  • a retraction plate 7 is provided.
  • the retraction plate 7 is held at a fixed distance from the running surface 6 of the pivoting cradle 5 and thus prevents lifting of the sliding shoes from the running surface 6.
  • the sliding blocks are pivotally connected to the piston.
  • the pistons in the cylinder drum 2 thus perform a different large stroke per revolution of the drive shaft or the cylinder drum 2.
  • the pivoting cradle 5 On its side facing the flange part 4, the pivoting cradle 5 has a pivotal pivot bearing 8.
  • at least one first bearing region is formed on the pivoting cradle 5, which forms a sliding bearing with a corresponding recess 9 of the flange part 4.
  • the pivoting cradle 5 is rotatable about a pivot axis S by rotating the pivoting cradle 5 in the pivoting pivot bearing. This changes the inclination of the running surface 6 relative to the axis of rotation of the cylinder drum 2.
  • the adjusting system comprises at least a first adjusting device 10.
  • the first adjusting device 10 has a first actuating piston 11.
  • the first control piston 11 defines with its first end 12 a pressure chamber 13.
  • the pressure chamber 13 is formed in a bottom of the cup-shaped housing part 2.
  • a blind bore 14 is introduced into the bottom of the cup-shaped housing part 3, into which a bushing 15 is inserted.
  • the bushing 15 is preferably pressed into the blind bore 14.
  • the inner wall of the bush 15 serves the first end 12 of the actuating piston 11 as a sliding surface and cooperates sealingly with the first end 12 of the first actuating piston 11.
  • the first end 12 of the actuating piston 11 is not cylindrical, but has a slightly convex shape to prevent tilting in the socket 15 at an oblique position of the actuating piston 11 relative to the longitudinal axis of the bushing 15.
  • a sealing ring could also be arranged.
  • a ball head On a side facing away from the first end 12 second end 16 of the actuating piston 12, a ball head is formed.
  • the ball head is connected to a hold-down segment 17, which can be transmitted both tensile and compressive forces.
  • the hold-down segment 17 is firmly connected by means of screws with the pivoting cradle 5.
  • the hold-down segment 17 is screwed onto the running surface 6 in an outer region of the pivoting cradle 5.
  • the hold-down segment 17 also has a hold-down surface 19, which engages over the retraction plate 7 and rests against the retraction plate 7 and thus ensures a constant distance of the retraction plate 7 from the running surface 6 of the pivoting cradle 5.
  • a spherical recess 20 is provided in the hold-down segment 17, which encloses the ball-head-shaped second end 16 of the actuating piston 11.
  • the connection of the actuating piston 11 with the hold-down segment 17 is designed as a locked connection. That is, the ball-head-shaped second end 16 is enclosed further than the equator by the spherical recess of the hold-down segment.
  • a lubricant channel 21 is formed inside the adjusting piston 11 in the first adjusting device 10.
  • the lubricant channel 21 extends from the first end 12 of the actuating piston 11 to the second end 16.
  • the lubricant channel 21 connects the pressure chamber 13 with the ball-head-shaped second end 16 of the actuating piston 11.
  • a pressure prevailing in the pressure chamber 13 thus ensures a discharge of Pressure medium at the ball-head-shaped second end 16 of the actuating piston 11.
  • the articulated connection between the actuating piston 11 and the hold-down segment 17 is lubricated and hydrostatically relieved.
  • the first adjusting device 10 is provided for swiveling out the axial piston machine 1 in the direction of maximum displacement volume.
  • the pressure chamber 13 is connected to the delivery side of the axial piston machine 1 designed as a pump.
  • the pending in the pressure chamber 13 high pressure is also used to cause a hydrostatic discharge of the pivoting cradle 5 in the flange 4.
  • a pressure medium channel 22 or 23 is formed.
  • the pressure medium channel 23 of the Swing cradle 5 outside of the FIG. 1 shown section connected to the storage area 8.
  • a dowel pin 24 is provided, which is inserted into a bore in the pivoting cradle 5 and a corresponding bore in the hold-down segment 17.
  • an adjustable first limiting device 25 is provided in the pot-shaped housing part 3 in the region of an end remote from the ball joint connection between the actuating piston 11 and the hold-down segment 17 of the hold-down segment 17.
  • the first limiting device 25 cooperates with a first stop surface 26, which is formed on the hold-down segment 17.
  • the first stop surface 26 is crowned, so that regardless of the setting of the first limiting device 25, the force is introduced by the limiting device 25 perpendicular to the first stop surface 26 and thus through the center of the crown. The center of this crowning is viewed from the stop surface in the direction of the pivoting cradle. 5
  • the first limiting device 25 comprises an adjusting screw 27, which is screwed into a thread provided for this purpose in a housing bore. Depending on the depth of engagement, the maximum Deflection of the pivoting cradle 5 in a first direction of movement determined by the first limiting device 25.
  • the housing bore is arranged in the region of the jacket of the cup-shaped housing part 3. It encloses with the axis of rotation at an angle such that the central axis of the adjusting screw 27 extends through the center of the crowning of the stop surface 26.
  • the first adjusting device 10, the first limiting device 25 and the first hold-down segment 17 are all associated with a first direction of movement of the pivoting cradle 5. While the first adjusting device 10 attempts to adjust the pivoting cradle 5 in a first direction of movement, the first limiting device 25 serves as an adjustable stop and thus limits the maximum adjustment in this first direction of movement. To secure the adjusting screw 27 in a selected position, a lock nut 28 is provided. The lock nut 28 also serves to seal the housing interior from the environment. A safety cap 29 prevents unauthorized changing of the setting values.
  • the safety stop between the flange part 4 and the further stop face 30 of the first hold-down segment 17 is preferably formed.
  • the first adjusting device 10 and the first limiting device 25 are, as it is directly from the Fig. 1 results, arranged in a plane which is parallel to the axis of rotation of the cylinder drum 2 and which is in particular perpendicular to the pivot axis S of the pivoting cradle 5.
  • the direction of force both to initiate the actuating force by the first adjusting device 10 and the direction of force when it stops against the adjustable first limiting device 25 is thus also in the plane formed parallel to the axis of rotation. Since this plane runs simultaneously through a first bearing area formed on the pivoting cradle 5 and the flange part 4, torsional forces on the pivoting cradle 5 are avoided.
  • an elastic element is provided on the first adjusting device 10.
  • the elastic element is designed as a spring 33 in the illustrated embodiment.
  • the spring 33 which is preferably a steel spiral spring, is supported on the one hand on a first spring bearing 31 formed in the vicinity of the second end 16.
  • the spring bearing 31 is as radial Section formed in the actuating piston 11 and has a in the axial direction slightly in the direction of the first end 12 of the actuating piston 11 extending guide portion for centering the spring 33.
  • the spring 33 abuts against a second spring bearing 32.
  • the spring bearing 32 also has a guide portion which extends in the axial direction.
  • the spring bearing 32 is arranged in a centering recess 34 of the housing part 3 and rests there against the bottom of the cup-shaped housing part 3.
  • the spring bearing 32 is preferably at the same time at the bottom of the cup-shaped housing 3 at the bottom of the centering recess 34 and at the oriented to the interior of the housing of the axial piston 1 end of the bushing 15 at.
  • the spring may also be arranged at another location of the adjusting system, in particular at a second adjusting device to be described later.
  • Fig. 1 is a section through the first adjusting device 10 and the first adjustable limiting device 25 defined plane shown.
  • the first adjusting device 10 is provided for adjusting the axial piston machine 1 in the direction of larger stroke volume and can therefore be referred to as Ausschwenkvorraum. This is true when the axial piston machine 1 as a hydraulic pump z. B. is used in the open circuit and is provided for promotion in one direction only.
  • a second adjusting device 35 is further provided, which in the illustration of Fig. 1 However, due to the location of the cut is not recognizable.
  • the second adjusting device 35 also has a second variable limiting device 39
  • the second adjusting device 35 and the second limiting device 39 are again arranged in a common plane, this further plane being parallel to the plane of the first adjusting device 10 and the first limiting device 25.
  • the two planes are preferably symmetrical to the axis of rotation of the cylinder drum 2.
  • the first adjusting device 10 and the second adjusting device 35 lie on opposite sides with respect to the axis of rotation.
  • the second adjusting device 35 of the actuating system has an actuating piston, which is mounted with its first end in a second sleeve 36.
  • the second sleeve 36 is also inserted in a blind bore in the bottom of the cup-shaped housing part 3.
  • a second pressure chamber is formed in the sleeve 36, which is closed by the bottom of the cup-shaped housing part 3, as in the first adjusting device 10.
  • the pressure chamber or the pressure chamber is limited by a likewise spherical control piston disc.
  • a ball joint connection is also formed at the other end of the actuating piston of the second adjusting device 35.
  • the second end 37 of the actuating piston of the second adjusting device 35 is also inserted into a spherical recess of a second hold-down segment 38.
  • the second hold-down segment 38 like the first hold-down segment 17, is connected to the pivoting cradle 5 by means of screws 18.
  • the first and second hold-down segments 17 and 38 are preferably identical.
  • the first hold-down segment 17 extends substantially along the plane in which the first adjusting device 10 and the first limiting device 25 are arranged. Accordingly, the second hold-down segment 38 extends substantially along a further plane in which the second adjusting device 35 and a second variable limiting device 39 are arranged.
  • the second variable restricting device 39 is similar in construction to the first variable restricting device 25, so that a description will be omitted.
  • the adjusting screw 27 for the first movement direction can be selected with a different length than for the second direction of movement.
  • FIG. 2 shows that a connecting line between the first actuating piston 11 and the adjusting piston of the second adjusting device 35 intersects the axis of rotation of the drive shaft.
  • another imaginary connecting line of the two abutment surfaces 26 and 40 cuts the axis of rotation.
  • the two imaginary connecting lines form an angle of about 70 ° to 90 °.
  • the adjusting devices 10 and 35 are on a first diagonal in the region of the inner corners of the housing and the adjustable limiting devices 25 and 39 on a second diagonal in Area of the inner corners of the housing arranged.
  • the first actuator 10 is in the first quadrant, the first limiting device 25 in the fourth quadrant, the second actuator 35 in the third quadrant and the second adjustable limiting device 39 in the second quadrant arranged.
  • a stop surface 40 is also formed, which is designed crowned.
  • the spherical shape of the abutment surface 40 has, as in the first hold-down segment 30 with the result that regardless of the selected setting of the variable limiting device 39, the force is always perpendicular to the stop surface 40.
  • a further stop surface 41 is also formed on the second hold-down segment 38. The further stop surface 41 is formed at the same end of the second hold-down segment 38 as the ball joint connection with the actuating piston of the second actuator 35.
  • the pivoting pivot bearing 8 of the pivoting cradle 5 is formed by a first bearing surface and a second bearing surface.
  • the first storage area extends in a width in the direction of the pivot axis S, so that the plane in which the first adjusting device 10 and the first adjustable limiting device 25 are arranged, that is, in which the directions of force by the first adjusting device 10 and the first adjustable limiting device 25, through the first bearing surface runs.
  • the second bearing surface also extends over a width in the direction of the pivot axis S, so that the further plane in which the second adjusting device 35 and the second limiting device 39 are arranged extends through the region of the second bearing surface.
  • the first adjusting device 10 and the second adjusting device 35 are in the Fig. 3 shown in a section.
  • a lubricant passage 42 extending in the longitudinal direction is also provided in the adjusting piston of the second adjusting device 35.
  • This lubricant passage 42 connects the second pressure chamber formed in the second sleeve 36 with the ball joint between the actuator piston and the second hold-down segment 38.
  • the first pressure chamber 13 is made smaller in diameter than the second pressure chamber. This makes it possible, in the first pressure chamber 13 always to let the delivery-side high pressure of the axial piston machine designed as a pump 1. A pivoting in the direction of decreasing delivery volumes takes place when corresponding setting pressures in the second pressure chamber of the actuating piston of the second adjusting device 35th
  • pivoting cradle 5 is penetrated centrally by a bore 45.
  • This bore 45 forms a passage for the drive shaft of the axial piston machine. 1
  • the actuating piston 11 is part of a return system. With such a feedback system is used in feedback control of the detection of a displacement and pressure signal.
  • a return element 50 is provided for this purpose as a further component of the return device.
  • the return element 50 is fixedly connected to the actuating piston 11 and supported on the outer circumference from surface.
  • the projecting at a 90 ° angle return element 50 is thus by its relative position to the housing of the axial piston machine 1 information about the relative position of the actuating piston 11 and thus over the set delivery volume.
  • This delivery pressure is, as with reference to the Fig. 1 has already been explained, the pressure chamber 13 is supplied and is therefore also in the lubricant passage 21 of the actuating piston 11 at.
  • the return element 50 acts on a control device provided on the housing side, wherein a force dependent on the delivery pressure is generated by the return element on the regulating device in a position dependent on the set delivery volume.
  • a pivoting angle limit which acts on the actuating piston 11.
  • This swivel angle limitation is provided in the pressure chamber or at the bottom of the cup-shaped housing part 3 and limits the travel of the actuating piston 11.
  • the swivel angle limit is at a provided for conveying in only one direction pump with a maximum flow in this direction from 100% to preferably -10 % set.
  • the adjustment is constructive, ie by determining the maximum travel of the actuating piston 11 in the sleeve 15 against the bottom of the blind bore 14 before the return element 50 reaches the edge of the bush 15. This is in the Fig. 4 shown schematically.
  • Such a fixed pivoting angle limitation preferably replaces the previously described safety stop of the second actuating device.
  • the return element 50 for this purpose has an adjusting bushing 51 and a measuring piston 52 which is partly arranged therein. While the adjusting bushing 51 ensures the correct positioning of the return element, a force corresponding to the pressure in the pressure chamber 13 is generated by the measuring piston 52.
  • the adjusting bushing 51 is inserted in a transverse bore formed perpendicular to the longitudinal axis of the actuating piston 11.
  • the measuring piston 52 has for this purpose a radial gradation. This results in two differently sized annular surfaces on the measuring piston 52 together with the corresponding graduated Meßkolbenfactbohrung 53 of the actuating sleeve 51. These two annular surfaces are oriented opposite to each other, so that a resulting force is generated on the measuring piston 52, which depends on the delivery pressure of the axial piston machine 1.
  • the adjusting bush 51 penetrates the adjusting piston 11 and thus the lubricating oil passage 21 in the transverse direction.
  • a connecting bore 54 is formed in the adjusting bush 51 in the region of the lubricating oil passage 21 as a pressure medium feedthrough.
  • the measuring piston 53 is radially tapered, so that pressure medium can flow over the annular channel thus formed from one section of the lubricating oil channel 21 into the other section of the lubricating oil channel 21.
  • the regions of the measuring piston 52 which are formed on both sides of the radial taper act in a sealing manner and together to guide the measuring piston 52 with the receiving bore 53 of the adjusting bushing 51.
  • at least one flattening at the diameter of the central guide region of the measuring piston 52 in the adjusting bushing 51 is provided at the region which is oriented towards the force-transmitting end 55. By this flattening an overflow channel is formed.
  • the middle guide area of the volumetric flask in the control box could also be omitted.
  • a roller 56 is connected to the measuring piston 52.
  • the roller is oriented so that it rolls on a position change of the actuating piston 11 on the mating surface to which the force is transmitted.
  • the rolling direction coincides with the direction of movement of the actuating piston 11 during an adjusting movement.
  • a biasing spring 57 is inserted into an enlarged region of the stepped receiving bore 53 of the actuating sleeve 51.
  • the biasing spring 57 is supported on the one hand at a second stage of the stepped receiving bore 53 and on the other hand on a collar 58 of the measuring piston 52 from. But the biasing spring 57 could also be omitted.
  • a guide portion 59 is formed on the adjusting bushing 51 at its end remote from the actuating piston 11 end.
  • two flat surfaces 60, 61 are formed, which are directed in opposite directions to the outside and engage in a corresponding recess of the cup-shaped housing part 3.
  • the width of the corresponding recess is dimensioned so that the return element is guided with little play and a rotation of the return element 50 is not possible.
  • each other guide surfaces 62, 63 are formed on the guide portion 59.
  • the force transmitting end 55 of the measuring piston 52 is arranged in the region of the guide surfaces 62, 63.
  • the width of the force transmitting end 55 of the measuring piston 52 is selected so that the measuring piston is guided with little play and a rotation of the measuring piston 52 is prevented by the guide portion 59.
  • journal bearings lead together with the two pins to a locked connection of the roller 56 to the measuring piston 52.
  • the two journal bearings enclose the pins with more than 180 °, so that the roller can not fall out in the unloaded state.
  • the two in the direction of the pins 64, 65 directed side surfaces 68 and 69 of the roller 56 are conical or convex.
  • the guidance and centering is therefore achieved in the region of the side surfaces 68, 69 close to the pin, while the remaining region of the side surfaces does not touch the legs 66, 67. This can reduce the frictional forces.
  • the invention is not limited to the illustrated embodiments. In particular, it is possible to combine individual features of the illustrated embodiments in an advantageous manner.

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

Claims (8)

  1. Machine à pistons axiaux comprenant un plateau ou berceau pivotant (5) à inclinaison variable, et au moins un dispositif de réglage (10, 35) qui présente un piston de réglage (11) pour régler le berceau pivotant (5), le dispositif de réglage (10, 35) s'étendant sensiblement dans la direction longitudinale de la machine à pistons axiaux,
    caractérisée par
    par un élément de restitution de rétroaction (50), qui par sa position relative par rapport à un carter de la machine à pistons axiaux (1) renseigne sur la position relative du piston de réglage (11) du dispositif de réglage (10, 35) et ainsi du berceau pivotant (5), et sur le volume de refoulement réglé, par action sur un dispositif de régulation prévu côté carter,
    l'élément de restitution de rétroaction (50) et le dispositif de réglage (10, 35) étant agencés dans un seul plan, qui s'étend parallèlement à un axe de rotation de la machine à pistons axiaux, et qui est d'une orientation perpendiculaire à un axe de pivotement (S) du berceau pivotant (5).
  2. Machine à pistons axiaux selon la revendication 1, caractérisée en ce que l'élément de restitution de rétroaction (50) subdivise un canal d'huile de lubrification (21) du piston de réglage (11) du dispositif de réglage (10), en deux tronçons, qui sont reliés l'un à l'autre par l'intermédiaire de l'élément de restitution de rétroaction (50).
  3. Machine à pistons axiaux selon la revendication 1 ou la revendication 2, caractérisée en ce que l'élément de restitution de rétroaction (50) comprend un piston de mesure (52), qui est sollicité par une pression amenée par l'intermédiaire de l'élément de restitution de rétroaction (50).
  4. Machine à pistons axiaux selon l'une des revendications 1 à 3, caractérisée en ce que l'élément de restitution de rétroaction (50) présente une douille de réglage (51), qui est guidée dans un évidement de carter pour l'arrêt en rotation.
  5. Machine à pistons axiaux selon l'une des revendications 1 à 4, caractérisée en ce que l'élément de restitution de rétroaction (50) présente une douille de réglage (51) et un piston de mesure (52) qui y est guidé, le piston de mesure (52) étant guidé dans la douille de réglage (51) par l'intermédiaire d'un arrêt en rotation, surfacique.
  6. Machine à pistons axiaux selon l'une des revendications 1 à 5, caractérisée en ce que le dispositif de réglage (10) comprend un piston de réglage (52) avec un disque de piston de réglage bombé agencé dans une chambre de pression, et l'élément de restitution de rétroaction (50) est agencé entre le disque de piston de réglage bombé et un anneau d'appui (32) destiné à l'appui d'un ressort de précontrainte (32) sur le piston de réglage (11).
  7. Machine à pistons axiaux selon l'une des revendications 1 à 6, caractérisée en ce que sur l'élément de restitution de rétroaction (50) est prévu un galet (56) pour la transmission de la force à un dispositif de régulation, et le galet (56) présente des surfaces latérales coniques ou convexes.
  8. Machine à pistons axiaux selon l'une des revendications 1 à 7, caractérisée en ce que l'élément de restitution de rétroaction (50) est agencé sur le piston de réglage (11).
EP08758514.7A 2007-05-14 2008-05-14 Machine à pistons axiaux pourvue d'un dispositif de rappel Active EP2145106B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007022569A DE102007022569A1 (de) 2007-05-14 2007-05-14 Axialkolbenmaschine mit Rückführvorrichtung
PCT/EP2008/003866 WO2008138603A1 (fr) 2007-05-14 2008-05-14 Machine à pistons axiaux pourvue d'un dispositif de rappel

Publications (2)

Publication Number Publication Date
EP2145106A1 EP2145106A1 (fr) 2010-01-20
EP2145106B1 true EP2145106B1 (fr) 2014-07-16

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP08758514.7A Active EP2145106B1 (fr) 2007-05-14 2008-05-14 Machine à pistons axiaux pourvue d'un dispositif de rappel

Country Status (5)

Country Link
US (1) US8418599B2 (fr)
EP (1) EP2145106B1 (fr)
JP (1) JP5492073B2 (fr)
DE (1) DE102007022569A1 (fr)
WO (1) WO2008138603A1 (fr)

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DE102006062065A1 (de) * 2006-12-29 2008-07-03 Robert Bosch Gmbh Axialkolbenmaschine mit einem einen radial erweiterten Innenraumabschnitt aufweisenden Gehäuse
US9920751B2 (en) 2010-07-08 2018-03-20 Robert Bosch Gmbh Hydraulic axial piston machine
DE102010054044A1 (de) * 2010-12-10 2012-06-14 Robert Bosch Gmbh System mit Gleitschuhen und Kolben für eine Axialkolbenmaschine
DE102011120750A1 (de) * 2011-12-08 2013-06-13 Robert Bosch Gmbh Ansteuergerät für hydrostatische Kolbenmaschinen
DE102012222936A1 (de) * 2012-12-12 2014-06-12 Robert Bosch Gmbh Axialkolbenmaschine
AU2014270792B2 (en) 2013-05-22 2017-08-31 Hydac Drive Center Gmbh Axial piston pump having a swash-plate type construction
CN106894962A (zh) * 2017-03-08 2017-06-27 重庆红江机械有限责任公司 一种高压大流量液压柱塞泵
CN111794927A (zh) * 2020-08-10 2020-10-20 长兴永能动力科技有限公司 一种小型高效汽轮机用顶轴油泵装置

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US5630352A (en) * 1996-03-08 1997-05-20 Vickers, Incorporated Variable displacement hydrualic piston machine saddle bearing
DE19755386C2 (de) 1997-12-12 1999-10-21 Brueninghaus Hydromatik Gmbh Hydrostatische Maschine mit einer drehbar gelagerten Zylindertrommel und einer einstellbaren Schwenkscheibe
DE10001826C1 (de) 2000-01-18 2001-09-20 Brueninghaus Hydromatik Gmbh Vorrichtung zum Regeln der Leistung einer verstellbaren Kolbenmaschine
DE10360452B3 (de) * 2003-12-22 2005-09-08 Brueninghaus Hydromatik Gmbh Axialkolbenmaschine mit fixierbarem Gleitstein an der Schrägscheibe
JP2005320912A (ja) * 2004-05-10 2005-11-17 Shin Caterpillar Mitsubishi Ltd 可変容量型油圧ポンプ

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JP2010526245A (ja) 2010-07-29
WO2008138603A1 (fr) 2008-11-20
EP2145106A1 (fr) 2010-01-20
DE102007022569A1 (de) 2008-11-20
US20100132544A1 (en) 2010-06-03
JP5492073B2 (ja) 2014-05-14
US8418599B2 (en) 2013-04-16

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