EP1700034B1 - Machine a pistons axiaux pour realiser un acheminement independant dans plusieurs circuits hydrauliques - Google Patents

Machine a pistons axiaux pour realiser un acheminement independant dans plusieurs circuits hydrauliques Download PDF

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Publication number
EP1700034B1
EP1700034B1 EP04803814A EP04803814A EP1700034B1 EP 1700034 B1 EP1700034 B1 EP 1700034B1 EP 04803814 A EP04803814 A EP 04803814A EP 04803814 A EP04803814 A EP 04803814A EP 1700034 B1 EP1700034 B1 EP 1700034B1
Authority
EP
European Patent Office
Prior art keywords
pistons
group
axial piston
piston machine
swash plate
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 - Fee Related
Application number
EP04803814A
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German (de)
English (en)
Other versions
EP1700034A1 (fr
Inventor
Georg Jacobs
Jerzy Kreja
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
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Brueninghaus Hydromatik GmbH filed Critical Brueninghaus Hydromatik GmbH
Publication of EP1700034A1 publication Critical patent/EP1700034A1/fr
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Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F04B1/14—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 stationary cylinders
    • F04B1/16—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 stationary cylinders having two or more sets of cylinders or pistons
    • 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
    • F04B1/2078—Swash plates
    • 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

  • the invention relates to an axial piston machine with a first group of pistons for conveying in a first hydraulic circuit and with a second group of pistons for conveying in a second hydraulic circuit.
  • the pistons of the first group and the pistons of the second group are each arranged on a separate pitch circle, wherein those pistons, which are assigned to the pitch circle with the smaller diameter, are supported on a first swash plate, which forms hemispherical on the side facing away from the piston and is stored in the second swash plate.
  • the first and the second swash plate are pivotable about a common axis for independently adjusting the delivery rates of the first hydraulic circuit and the second hydraulic circuit separately, wherein for adjusting the first swash plate in the second swash plate is provided a recess through which the actuating device to the first Swash plate accesses.
  • the first swash plate may also be slightly inclined to change the dead center about a second axis which is perpendicular to the actual pivot axis.
  • a disadvantage of this arrangement is that the second swash plate can indeed be stored in a known manner with a spherical outer contour, but the second swash plate must be formed simultaneously as a bearing for the first swash plate. Furthermore, it is disadvantageous that a recess in the second swash plate is provided for adjusting the pivot angle of the inner swash plate. Since the swash plates have to absorb considerable pressure forces, the necessary recess can neither be designed arbitrarily nor positioned arbitrarily. However, this leads to a limitation with respect to the adjustment possibility of the first swash plate, whereby the delivery volume of the corresponding hydraulic circuit can only be changed to a limited extent.
  • the axial length of the axial piston machine is extended by the nesting of the two swash plates. Part of the advantage of using a single axial piston machine to feed into two hydraulic circuits is thus lost again.
  • the axial piston machine has a first group of pistons for conveying a pressure medium in a first hydraulic circuit.
  • the swash plate On which the pistons of the first group are supported, is pivotable about a first pivot axis.
  • the same swashplate is also used to support the Piston of the second group for conveying a pressure medium in a second hydraulic circuit.
  • the swash plate In order to adjust the delivery volume for the second hydraulic circuit, the swash plate is pivotable about a second pivot axis, by which an effective stroke volume of the piston of the second group is adjusted.
  • the respective effective displacement for the first hydraulic circuit and for the second hydraulic circuit can be set individually.
  • the possible adjustable swivel angle are not limited by the respective angle set with respect to the other pivot axis.
  • the two pivot axes are arranged so that they intersect at a point together with the central axis of the axial piston machine.
  • the range of application of the reciprocating engine is increased, since a reversal of the conveying direction is easy because of the symmetry.
  • the two pivot axes intersect not only together with the central axis of the axial piston machine in one point, but the pivot axes are perpendicular to each other and the central axis of the piston engine. This largest possible intermediate angle between the two pivot axes allows a particularly large individual adjustment range for the two hydraulic circuits.
  • the pistons of the first and the second group are each arranged longitudinally displaceably in respective first and second cylinder bores.
  • the first and second cylinder bores are each connectable to the first and second hydraulic circuits via a pair of control gears.
  • a pair of control kidneys is arranged symmetrically to the vertical projection of the corresponding pivot axis in the plane of the control kidneys.
  • a further advantage is to arrange the piston of the first or second group for conveying into the first hydraulic circuit or the second hydraulic circuit on a common pitch circle.
  • this results in using the same diameter of the cylinder bores and the piston an identical delivery volume in the two hydraulic circuits.
  • results from the arrangement of all pistons on only one pitch circle improved synchronization of the axial piston machine, with correspondingly lower vibrations and reduced noise.
  • a single swash plate also gives rise to the possibility of either adjusting the inclination of the swashplate with respect to a swivel axis either by two adjusting devices acting separately on the single swashplate, or a common adjustment device can be provided which adjusts the swashplate to its resultant inclination established.
  • a common drive shaft 2 is supported by a roller bearing 3 at one end of a pump housing 4.
  • the common drive shaft 2 is mounted in a sliding bearing 6, which is arranged in a connection plate 5, which closes the pump housing 4 at the opposite end.
  • connection plate 5 In the connection plate 5 is a, the connection plate 5 completely penetrating in the axial direction recess 7 is formed, in which on the one hand the sliding bearing 6 is arranged and which is penetrated to the other of the common drive shaft 2.
  • the auxiliary pump 8 On the side facing away from the pump housing 4 side of the connection plate 5, the auxiliary pump 8 is inserted into a radial extension of the recess 7.
  • the common drive shaft 2 has a toothing 9, which is in engagement with a corresponding toothing of an auxiliary pump shaft 10.
  • the auxiliary pump shaft 10 is mounted in the recess 7 by a first auxiliary pump sliding bearing 11 and by a second auxiliary pump sliding bearing 12 in an auxiliary pump connecting plate 13.
  • a gear 14 is arranged, which is in engagement with a ring gear 15. Via the gear 14, the ring gear 15, which is rotatably arranged in the auxiliary pump connection plate 13, also driven by the auxiliary pump shaft 10 and thus ultimately by the common drive shaft 2.
  • the suction and the pressure-side connection for the auxiliary pump 8 are formed.
  • the auxiliary pump 8 is fixed by a cover 16, which is mounted on the connection plate 5, in the radial extension of the recess 7 of the connection plate 5.
  • the inner ring of the roller bearing 3 is fixed in the axial direction on the common drive shaft 2.
  • the inner ring rests on the one hand on a collar 17 of the common drive shaft 2 and is held on the other side by a locking ring 18 in this axial position, which is inserted in a groove of the common drive shaft 2.
  • the axial position of the roller bearing 3 with respect to the pump housing 4 is determined by a retaining ring 19 which is inserted in a circumferential groove of the shaft opening 20.
  • On the other side is the roller bearing 3, on a housing shoulder, not shown, of the pump housing 4.
  • a sealing ring 21 and finally a further locking ring 22 is disposed in the shaft opening 20, wherein the locking ring 22 is inserted into a circumferential groove of the shaft opening 20.
  • a drive toothing 23 is formed, via which the hydrostatic piston engine is driven by a drive machine, not shown.
  • a cylinder drum 24 is arranged, which has a central passage opening 25, which is penetrated by the common drive shaft 2.
  • the cylinder drum 24 is secured against rotation, but slidably connected in the axial direction with the common drive shaft 2, so that a rotary motion of the common drive shaft 2 transmits to the cylinder drum 24.
  • the compression spring 29 acts on the cylinder drum 24, which is held with a formed on the end face of the cylinder drum 24 spherical recess 31 in abutment against a control plate 32.
  • the control plate 32 in turn bears sealingly against the connection plate 5 with the side remote from the cylinder drum 24. Due to the spherical recess 31, which corresponds to a corresponding spherical shape of the control plate 32, the cylinder drum 24 is centered.
  • the control plate 32 may also be designed as a flat disk, if, for example, would lead by an otherwise realized centering together with a spherical control plate 32 to an over-determination.
  • the position of the control plate 32 in the radial direction is determined by the outer circumference of the sliding bearing 6.
  • the sliding bearing 6 is used for this purpose only partially in the recess in the connection plate 5.
  • cylinder bores 33 are distributed over a common pitch circle introduced, in which pistons 34 are arranged, which are longitudinally displaceable in the cylinder bores 33. At the end remote from the spherical recess 31, the pistons 34 protrude partially out of the cylinder drum 24. At this end, a sliding shoe 35 is attached to the piston 34, via which the pistons 34 are supported on a running surface 36 of a swash plate 37.
  • the angle which the running surface 36 of the swash plate 37 encloses with a central axis 40 can be changed.
  • the swash plate 37 can be adjusted by an adjusting device 38 in its inclination.
  • the swash plate 37 is mounted in the pump housing 4.
  • connection plate 5 For connecting the hydrostatic piston engine 1 to a first hydraulic circuit and to a second hydraulic circuit, a first port 39 and a second port 39 'are schematically shown in the connection plate 5, which can be connected in a manner not shown on the control plate 32 with the cylinder bores 33 ,
  • FIG. 2 An enlarged view of the cooperating in the interior of the pump housing 4 components is shown in Fig. 2.
  • the swash plate 37 is coupled to a sliding block 44, which rotates in a manner not shown, the swash plate 37 about an axis lying in the plane of the drawing.
  • the cylinder bores generally indicated at 33 in FIG. 1 are subdivided into a first group of cylinder bores 33. 1 and a second group of cylinder bores 33. 2.
  • a sliding shoe 35 is arranged on the end of the piston 34 facing away from the control plate 32 in each case.
  • the shoe 35 is fixed with a recess on a spherical head of the piston 34 so that the shoe 35 is movably fixed to the piston 34 and tensile and compressive forces are transferable.
  • a sliding surface 45 is formed, with which the sliding shoe 35 and thus the piston 34 is supported on the running surface 36 of the swash plate 37.
  • Lubricating oil grooves are formed in the sliding surface 45 and are connected to the cylinder bores 33 formed in the cylinder barrel 24 via a lubricating oil passage 46 formed in the sliding shoe 35, which is continued in the piston 34 as a lubricating oil bore 46 '.
  • the pistons 34 By supporting the sliding shoes 35 on the running surface 36, the pistons 34, upon rotation of the common drive shaft 2, perform a lifting movement, by means of which the pressure medium located in the cylinder chambers in the cylinder drum 24 is pressurized.
  • the sliding blocks 35 are hydrostatically relieved on the running surface 36 of the swash plate 37.
  • first connection channels 47.1 and second connection channels 47.2 are connected to the cylinder bores of the first group 33.1 and the cylinder bores of the second group 33.2.
  • the first and second connection channels 47.1 and 47.2 extend from the cylinder bores of the first group 33.1 and the cylinder bores of the second group 33.2 to the spherical recess 31 which is formed on an end face 48 of the cylinder drum 24.
  • a first control kidney 50 and a second control kidney 51 are formed, which penetrate the control plate 32 in the axial direction.
  • control plate 32 is preferably formed a third control kidney and a fourth control kidney, which are not recognizable because of the position of the sectional plane in FIG. While the first and the second control kidneys 50 and 51 via the connection plate 5 with the working lines of the first hydraulic Similarly, the third control kidney and the fourth control kidney are connected to the working lines of the second hydraulic circuit.
  • the geometric design of the control kidneys in the control plate 32 will be explained below with reference to FIG. 5.
  • the first and second control kidneys 50 and 51 have an identical first distance R 1 from the center axis 40 of the cylinder barrel 24, which is greater than the distance R 2, which in turn is identical for the third and fourth control animals.
  • the first connection channels 47.1 are connected in alternation with the first control kidney 50 and the second control kidney 51, so that due to the lifting movement of the arranged in the cylinder bores 33.1 of the first group piston 34, the pressure medium z. B. sucked via the second control kidney 51 and is pumped via the first control kidney 50 in the pressure-side working line of the first hydraulic circuit.
  • the first connection channels 47.1 are arranged in the cylinder drum 24, that the first distance R 1 of the orifice at the end face 48 is greater than the second distance R 2 , in which the second connection channels 47.2 open at the end face 48.
  • the second connecting channels 47.2 have a radial direction component and accordingly open out at the end face 48 of the cylinder drum 24 with the second distance R 2 , which corresponds to the distance of the third and fourth control kidneys from the central axis 40.
  • the cylinder bores of the second group 33.2 are thus alternately connected to the third and fourth control kidneys via the second connection channels 47.2.
  • a retraction plate 52 is provided, which surrounds the sliding shoes 35 at a paragraph provided for this purpose.
  • the retraction plate 52 has z. B. a spherical, central recess 53, with which it is supported on a retraction ball 54 which is disposed at the end facing away from the end face 48 of the cylinder drum 24.
  • Fig. 3 it is shown how starting from an axial piston machine of Figs. 1 and 2, with a swash plate 37 ', an independent adjustment of the flow rates for the two hydraulic circuits can be achieved.
  • the swash plate 37 ' is tiltable about a first pivot axis 55 and about a second pivot axis 56.
  • the first and second pivot axes 55 and 56 are in the plane of the tread 36 of the swash plate 37 and, when the axial piston machine is set to zero delivery volume in both hydraulic circuits, with the central axis 40 at an angle of 90 °.
  • Fig. 3 it is shown that the swash plate 37 'is inclined about the second pivot axis 56.
  • an effective stroke for conveying pressure medium is generated in the second hydraulic circuit.
  • an effective stroke while a movement of the piston 34 is referred to, which leads to an actual conveying of pressure medium.
  • the third control kidneys 57 and the fourth control screens 58 are each arranged symmetrically with respect to a vertical projection 56 'of the second pivot axis 56 in the plane of the control kidneys ,
  • the second connecting channels 47.2 move during half a revolution of the cylinder drum 24 from the bottom dead center to the top dead center in FIG substantially along the third control kidney 57, so that the pressure means is pushed via the third control kidney 57 into the pressure side working line of the second hydraulic circuit. Accordingly, during the second half of a revolution of the cylinder drum 24, the second communication passages 47.2 move on the way from the top dead center to the bottom dead center substantially along the fourth control screen 58 and perform a suction stroke.
  • the first control kidney 50 and the second control kidney 51 are themselves symmetrical to a vertical projection 55 'of the first pivot axis 55 in the plane of the control kidneys.
  • the first pivot axis 55 and the second pivot axis 56 are arranged at a right angle to each other. Accordingly, the first and second control kidneys 50 and 51 and the third and fourth control screens 57 and 58 in the control plate 32 are also arranged rotated by 90 ° to each other.
  • a promotion in the first hydraulic circuit does not take place in the illustrated deflection of the swash plate 37 '.
  • the location of the first and second control screens 50 and 51 is symmetrical with respect to the top and bottom dead centers, respectively, so that, despite the use of the common swash plate 37 'in the first hydraulic circuit, only a small pulsation will be generated unless the swash plate 37' in addition to the first pivot axis 55 is inclined.
  • the arrangement of the first to fourth control kidneys 50, 51, 57 and 58 in the control plate 32 will be explained again in the description of FIG.
  • first pivot axis 55 and the second pivot axis 56 are arranged at right angles to each other, wherein both pivot axes 55 and 56 in the plane of the tread 36th lie.
  • the intersection of the first pivot axis 55 with the second pivot axis 56 coincides with the intersection of the two pivot axes 55 and 56 with the central axis 40.
  • the swash plate 37 On its side facing away from the running surface 36, the swash plate 37 'is designed hemispherical at least in a region 59 adjacent to the running surface 36.
  • a bearing a ball bearing or a plain bearing can be provided to support the swash plate and to allow their rotation.
  • the hemispherical region 59 is bounded by a flat 63 preferably formed parallel to the running surface 36.
  • the adjustment of the inclination of the swash plate 37 ' can be done either via a separate adjustment for each pivot axis 55 and 56, wherein in Fig. 1, only the adjustment for the pivot axis 55 is shown and the adjustment for the pivot axis 56 in the sectional view can not be seen , or via a common adjusting device, via which a resulting inclination angle of the swash plate 37 'is set.
  • Fig. 4 it is shown that the swash plate 37 'is with respect to the second pivot axis 56 in its neutral position, with respect to its first pivot axis 55, however, is inclined.
  • an effective stroke is generated only for those pistons 34, which are connected via the first connecting channels 47.1 during one revolution of the cylinder drum 24 alternately with the first control kidney 50 and the second control kidney 51.
  • those pistons which can be connected via the second connection channels 47.2 to the third control kidney 57 and the fourth control kidney 58, respectively, run in the Area in which a connection is made with the respective hydraulic circuit, only a slight movement around the bottom dead center or around the top dead center, which in turn generates only a small pulsation in the working lines of the second hydraulic circuit.
  • the control plate 32 is shown in a plan view.
  • the first pivot axis 55 and the second pivot axis 56 are perpendicular to each other.
  • the vertical projections 55 'and 56' shown in FIG. 5 each form an axis of symmetry for the first and the second control kidneys 50 and 51 and for the third and the fourth control screens 57 and 58.
  • the control plate 32 has centrally a centering opening 62, with which the position of the control plate in the axial piston machine 1 is defined.
  • the centering opening 62 centered the control plate for this purpose on the sliding bearing 6.
  • a groove 63.1 and 63.2 In each case a further groove 64.1 and 64.2 extends analogously along the projection 56 'of the further pivot axis 56.
  • the four grooves 63.1, 63.2, 64.1 and 64.2 are connected to one another via an annular groove 60.
  • the annular groove 60 itself is arranged concentrically with the centering opening 62 and the control kidneys.
  • the control kidneys 50 and 51 extend along a circular line having a radius which is greater than the radius of the circular line along which the third and fourth control kidneys 57 and 58 extend.
  • four holes 61.1 to 61.4 are arranged evenly distributed.
  • the bores 61.1 to 61.4 connect the annular groove 60 with the cylinder drum 24 facing side of the control plate 32nd So kann Leakage pressure in the interior of the axial piston machine 1 are discharged.
  • the generation of an effective stroke for conveying pressure medium in a first and in a second hydraulic circuit by pivoting the swash plate 37 ' is not limited to axial piston machines, in which the pistons 34.1 of the first group and the pistons 34.2 of the second group on a single, common pitch are arranged.
  • the two groups of pistons and cylinder bores can be arranged in a cylinder drum, but on two different pitch circles.

Claims (10)

  1. Machine à pistons axiaux comprenant un premier groupe de pistons (34.1) pour refouler dans un premier circuit hydraulique et au moins un second groupe de pistons (34.2) pour refouler dans au moins un second circuit hydraulique,
    caractérisée
    en ce que les pistons (34.1) du premier groupe et les pistons (34.2) du second groupe s'appuient sur un plateau oblique commun (37'), et
    en ce que le plateau oblique (37') est inclinable autour d'un premier axe de pivotement (55) pour régler un premier volume de refoulement du premier groupe de pistons (34.1) dans le premier circuit hydraulique et est inclinable autour d'un second axe de pivotement (56) pour régler un second volume de refoulement du second groupe de pistons (34.2) dans le second circuit hydraulique.
  2. Machine à pistons axiaux selon la revendication 1, caractérisée
    en ce que le premier axe de pivotement (55) et le second axe de pivotement (56) et un axe médian (40) de la machine à pistons axiaux se recoupent en un point (S).
  3. Machine à pistons axiaux selon la revendication 1 ou 2, caractérisée
    en ce que le premier axe de pivotement (55) et le second axe de pivotement (56) sont approximativement perpendiculaires l'un à l'autre.
  4. Machine à pistons axiaux selon l'une des revendications 1 à 3, caractérisée
    en ce que les pistons (34.1) du premier groupe sont disposés à translation longitudinale dans des premiers perçages cylindriques (33.1), lesdits premiers perçages cylindriques (33.1) pouvant être reliés au premier circuit hydraulique via une première came de commande (50) et via une seconde came de commande (51) et la première came de commande (50) et la seconde came de commande (51) étant agencées respectivement à l'opposé par rapport à une projection (55') perpendiculaire du premier axe de pivotement (55) dans le plan des première et seconde cames de commande (50, 51).
  5. Machine à pistons axiaux selon l'une des revendications 1 à 4, caractérisée
    en ce que les pistons (34.2) du second groupe sont disposés à translation longitudinale dans des seconds perçages cylindriques (33.2), lesdits seconds perçages cylindriques (33.2) pouvant être reliés au second circuit hydraulique via une troisième came de commande (57) et via une quatrième came de commande (58) et la troisième came de commande (57) et la quatrième came de commande (58) étant agencées respectivement à l'opposé par rapport à une projection (56') perpendiculaire du second axe de pivotement (56) dans le plan des troisième et quatrième cames de commande (57, 58).
  6. Machine à pistons axiaux selon l'une des revendications 1 à 5, caractérisée
    en ce que le plateau oblique (37') présente, sur son côté opposé aux pistons (34), une zone à géométrie semi-sphérique.
  7. Machine à pistons axiaux selon l'une des revendications 1 à 6, caractérisée
    en ce que les pistons (34.1) du premier groupe et les pistons (34.2) du second groupe sont disposés à translation longitudinale dans des perçages cylindriques (33) qui sont agencés sur un arc de cercle commun dans un tambour cylindrique (24).
  8. Machine à pistons axiaux selon l'une des revendications 1 à 6, caractérisée
    en ce que les pistons (34.1) du premier groupe sont disposés à translation longitudinale dans des premiers perçages cylindriques (33.1) et les pistons (34.2) du second groupe sont disposés à translation longitudinale dans des seconds perçages cylindriques (33.2), les premiers perçages cylindriques (33.1) et les seconds perçages cylindriques (33.2) étant agencés sur des arcs de cercle différents dans un tambour cylindrique (24).
  9. Machine à pistons axiaux selon l'une des revendications 1 à 8, caractérisée
    en ce que, pour régler l'inclinaison du plateau oblique (37') par rapport au premier axe de pivotement (55) et pour régler l'inclinaison du plateau oblique (37') par rapport au second axe de pivotement (56), il est prévu un dispositif de réglage respectif.
  10. Machine à pistons axiaux selon l'une des revendications 1 à 8, caractérisée
    en ce que, pour régler l'inclinaison du plateau oblique (37') par rapport au premier axe de pivotement (55) et par rapport au second axe de pivotement (56), il est prévu un dispositif de réglage commun.
EP04803814A 2003-12-15 2004-12-13 Machine a pistons axiaux pour realiser un acheminement independant dans plusieurs circuits hydrauliques Expired - Fee Related EP1700034B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10358728A DE10358728B4 (de) 2003-12-15 2003-12-15 Axialkolbenmaschine zum unabhängigen Fördern in mehrere hydraulische Kreisläufe
PCT/EP2004/014184 WO2005057009A1 (fr) 2003-12-15 2004-12-13 Machine a pistons axiaux pour realiser un acheminement independant dans plusieurs circuits hydrauliques

Publications (2)

Publication Number Publication Date
EP1700034A1 EP1700034A1 (fr) 2006-09-13
EP1700034B1 true EP1700034B1 (fr) 2007-03-21

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP04803814A Expired - Fee Related EP1700034B1 (fr) 2003-12-15 2004-12-13 Machine a pistons axiaux pour realiser un acheminement independant dans plusieurs circuits hydrauliques

Country Status (4)

Country Link
US (1) US7458312B2 (fr)
EP (1) EP1700034B1 (fr)
DE (2) DE10358728B4 (fr)
WO (1) WO2005057009A1 (fr)

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DD136285A1 (de) * 1978-12-28 1979-06-27 Wolfgang Tautenhahn Hydrostatische axialkolbenmaschine
DE3026765A1 (de) * 1980-07-15 1982-02-11 Linde Ag, 6200 Wiesbaden Axialkolbenpumpe fuer zwei foerderstroeme
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JPH10184532A (ja) * 1996-12-26 1998-07-14 Daikin Ind Ltd 可変容量形ピストンポンプ
US7406911B2 (en) 2001-03-06 2008-08-05 Honda Giken Kogyo Kabushiki Kaisha Expander

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DE10358728B4 (de) 2006-01-05
US7458312B2 (en) 2008-12-02
EP1700034A1 (fr) 2006-09-13
DE502004003321D1 (de) 2007-05-03
WO2005057009A1 (fr) 2005-06-23
DE10358728A1 (de) 2005-07-14
US20070101858A1 (en) 2007-05-10

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