EP1427914B1 - Machine hydrostatique chemises de cylindres compenses - Google Patents

Machine hydrostatique chemises de cylindres compenses Download PDF

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Publication number
EP1427914B1
EP1427914B1 EP02777007A EP02777007A EP1427914B1 EP 1427914 B1 EP1427914 B1 EP 1427914B1 EP 02777007 A EP02777007 A EP 02777007A EP 02777007 A EP02777007 A EP 02777007A EP 1427914 B1 EP1427914 B1 EP 1427914B1
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EP
European Patent Office
Prior art keywords
recess
piston
machine according
region
cylinder
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
EP02777007A
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German (de)
English (en)
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EP1427914A1 (fr
Inventor
Steven Donders
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
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Brueninghaus Hydromatik GmbH
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Priority claimed from DE10157248A external-priority patent/DE10157248A1/de
Application filed by Brueninghaus Hydromatik GmbH filed Critical Brueninghaus Hydromatik GmbH
Publication of EP1427914A1 publication Critical patent/EP1427914A1/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
    • F04B15/00—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0032—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F01B3/0044—Component parts, details, e.g. valves, sealings, lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0032—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F01B3/0044—Component parts, details, e.g. valves, sealings, lubrication
    • F01B3/0052—Cylinder barrel

Definitions

  • the invention relates to a hydrostatic swash plate machine according to the preamble of claim 1 or 2.
  • a hydrostatic swash plate machine is in the DE 28 12 416 A1 described.
  • the bushings each have in their outer circumferential surface an axially limited annular recess which is located in the longitudinal region of the cylinder bounded by the associated piston. It is the purpose of this recess to collect oil therein which, in particular, cools the area of the piston which never leaves the cylinder when set to small displacement per revolution.
  • a hydrostatic swash plate machine specified in the preamble of claim 2 is in the DE 44 23 023 A1 described.
  • the liners are cooled to avoid seizure with a cooling flow of the hydraulic fluid, which flows in functional operation respectively through a cooling channel extending from the leakage space in a central hole of the cylinder block approximately radially outwards and in the leak space outside Cylinder block opens.
  • the cooling channel extends in each case by an inner annular groove in the wall of the associated bushing receiving bushing hole or by an inner annular groove in the inner circumferential surface of the bushing.
  • the risk of a piston seizure is based on increased heating in the liners, which results in a high friction power between the piston and the liners effective sliding friction.
  • the friction power increases with increasing relative speeds between the pistons and the liners.
  • the relative speed is dependent on the stroke length of the piston and the speed of the hydrostatic machine, z. B. the speed of a rotatably mounted cylinder drum cylinder block.
  • the greatest frictional power is in each case when the cylinder block is formed by a rotatably mounted cylinder drum, generated in the region of the center of gravity of the piston when the cylinder drum rotates at high speed.
  • the largest friction in the region of a directed in the direction of rotation radial component of the piston force is generated.
  • the invention has for its object to reduce the risk of piston seizures in a hydrostatic machine of the type described above and to improve the effectiveness of the measures to prevent seizures.
  • the production cost should be low in order to keep the production costs low.
  • the liners each have in their outer circumferential surface an axially limited recess in its region facing away from the cylinder, wherein the axial dimension of the recess corresponds to about 3/10 to 7/10 of the diameter of the piston hole.
  • the invention is based on the finding that the increased heating between the pistons and the liners is mainly based on two functional criteria.
  • the friction loss and the resulting heating is increased by high relative speeds between the pistons and the liners.
  • it is enlarged when the hydrostatic machine operates at low pressure, in particular in unpressurized operation, and in particular at high speed. The latter is due to the fact that in the presence of a low pressure less leakage oil is dissipated by the movement between the piston and the liners and thus less heat is removed, resulting in inevitably greater warming.
  • the embodiment of the invention leads in the aforementioned problem and functional cases for the following reasons for the desired improvement.
  • the recess according to the invention results in each case at the radial outer side or inner side of the bushing a clearance between this and the wall of the associated bushing hole (claim 1) or the lateral surface of the associated piston (claim 2), in which extend the wall of the bushing in a warming can. Consequently, the piston clearance is reduced less in an expansion, so that even with a non-pressurized running of the hydrostatic machine, a sufficiently large piston clearance is present and therefore a piston seizure or its danger avoided or at least reduced.
  • the invention is based on the further recognition that a liner expands radially outward when heated due to its sleeve shape, if this is possible. This is due to the annular sleeve shape and in principle also applies to the region in which the recess is arranged. Therefore, in the embodiment according to the invention according to claim 1 or 3, in the region of increased heating, an expansion of the wall of the liner to the inside or this expansion is at least reduced.
  • the recess Due to the axial limitation of the recess, this is closed both to the associated cylinder and to the free interior of the machine.
  • the circumferentially extending width of the recess can - as already its axial length - be made larger than the area in which the increased friction takes place and is expected to increase the extent. But even a smaller education already leads to an improvement.
  • the width of the recess may correspond to its axial length.
  • the recess in the longitudinal direction of the liner can be elongated thoroughlybilet z. B. by the length of the maximum stroke longer than the aforementioned vulnerable area.
  • the recess as an annular recess.
  • Such a configuration can be easily produced by a rotational movement of the bushing, and moreover, when assembling the bushing, no attention is required to be mounted in a certain position with respect to its circumferential direction.
  • the in the FIGS. 1 and 4 shown axial piston machine is designed in swash plate design with adjustable displacement and includes in a known manner as essential components a hollow cylindrical housing 1 with a frontally open end (upper end in Fig. 1 ) fixed to the housing 1, the open end occluding terminal block 2, a swash plate 3, a control body 4, a drive shaft 5 and a cylinder barrel (cylinder block) 6.
  • the axial piston machine may be in the context of the invention is also a constant machine.
  • the axial piston machine can be set up for pump and / or motor operation and / or for operation in alternating directions of rotation.
  • the swash plate 3 is formed as a so-called pivoting cradle with a semi-cylindrical cross-section and is supported by two, with mutual radial distance parallel to the pivot direction extending bearing surfaces under hydrostatic discharge to two correspondingly shaped bearing shells 8, which on the inner surface of the Terminal block 2 opposite housing end wall 9 are attached.
  • the hydrostatic discharge takes place in a known manner via pressure pockets 10 which are formed in the bearing shells 8 and are supplied via connections 11 with pressure medium.
  • a positioning device 13 accommodated in a bulge of the cylindrical housing wall 12 engages on the swashplate 3 via an arm 14 extending in the direction of the connection block 2 and serves to pivot the same about a pivot axis 3a which is perpendicular to the pivoting direction.
  • the control body 4 is fixed to the housing interior facing inner surface of the terminal block 2 and provided with two through openings 15 in the form of kidney-shaped control slots, which are connected via a pressure channel 16D or suction channel 16S in the terminal block 2 to a pressure and suction line, not shown are.
  • the pressure channel 16D has a smaller flow area than the suction channel 16S.
  • the housing interior facing and spherically formed control surface of the control body 4 serves as a bearing surface for the cylinder drum. 6
  • the drive shaft 5 protrudes through a through hole in the housing end wall 9 in the housing 1 and is by means of a bearing 17 in this through hole and by means of another bearing 18 in a narrower bore portion of an end extended blind bore 19 in the connection block 2 and one closer to this Bore portion adjacent region of a central through hole 20 in the control body 4 rotatably mounted.
  • the drive shaft 5 passes through in the interior of the housing 1 further has a central through hole 21 in the swash plate 3, whose diameter is dimensioned according to the largest swing deflection of the swash plate 3, and a central through hole in the cylinder drum 6 with two bore sections.
  • One of these bore sections is formed in a sleeve-shaped extension 23 projecting beyond the swashplate 3 facing the cylinder drum 6, via which the cylinder drum 6 is connected in a rotationally fixed manner to the drive shaft 5 by means of a keyway connection 24.
  • the remaining bore portion is formed with a conical shape; it tapers from its cross section of largest diameter near the first bore section to its cross section of smallest diameter near the control body 4 abutting front or bearing surface of the cylinder drum 6.
  • the defined by the drive shaft 5 and this conical bore portion annular space is denoted by the reference numeral 25th designated.
  • the cylinder drum 6 has axially parallel or forward convergent, stepped cylinder bores 26 which are arranged uniformly on a coaxial to the drive shaft axis pitch circle, and on the cylinder drum end face 22 directly and on the control body 4 facing cylinder drum bearing surface through mouth channels 27 on the same pitch as the control slots lead out.
  • a bushing 28 is used in each of the cylinder drum end face 22 directly opening cylinder bore portions of larger diameter .
  • the cylinder bores 26 including the liners 28 are referred to herein as cylinders.
  • pistons 29 are provided at their the swash plate 3 facing rear ends with ball heads 30 which are mounted in sliding blocks 31 and are hydrostatically mounted on this attached to the swash plate 5 annular sliding disk 32.
  • Each slide shoe 31 is provided on its sliding disk 32 facing sliding surface, each with a pressure pocket, not shown, which is connected via a through hole 33 in the shoe 31 to an optionally stepped axial passage 34 in the piston 29 and in this way with the piston 29 in the cylinder bore 26 demarcated Working space of the cylinder is connected.
  • a throttle is formed in the region of the associated ball head 30.
  • the space not taken up in the housing interior by the components 3 to 6 accommodated therein serves as a leakage space 37 which, during operation of the axial piston machine, passes through all the gaps, for example between the cylinders 26, 28 and the pistons 29, the control body 4 and the cylinder drum 6, the swash plate 3 and the sliding disk 32 and the bearing shells 8, etc., receiving leaking leakage fluid.
  • the axial piston machine is for the operation z. B. provided with oil as a fluid.
  • the cylinder drum 6 is rotated together with the piston 29 in rotation. If by operation of the adjusting device 13, the swash plate 3 in an inclined position (see FIG. 4 ) is pivoted relative to the cylinder drum 6, so perform all pistons 29 strokes; upon rotation of the cylinder drum 6 through 360 °, each piston 29 passes through a suction stroke on the suction side and on the radially opposite pressure side a compression stroke, with corresponding oil flows are generated, their supply and discharge through the orifice channels 27, the control slots 15 and the pressure and Suction channel 16D, 16S done.
  • a normal force F n which is perpendicular to the swash plate 3 with negligible friction.
  • This normal force is decomposed in the ball head 30 into a piston force F k and a radial or lateral force Fq.
  • the transverse force F q acts in the ball head 30 on the piston 29 as on a clamped in the cylinder drum 6 bar, which the in Fig. 2 drawn, with a corresponding axial effective distance oppositely directed radial and directed in the circumferential direction of the cylinder drum 6 forces F r 1, F r 2 causes, with which the piston 29 is pressed against the bushing 28.
  • the rear radial force F r 1 is greater than the front radial force F r 2, and therefore, only the rear radial force F r 1 is argued below.
  • a comparable load case with comparable radial forces F r 1, F r 2 also results in the engine operation of the axial piston engine, in which the pistons 29 are pressed axially against the swash plate 3 on the pressure side and forces F n and F k result opposite direction of action.
  • a functional difference between the pump operation and the engine operation is that in pump operation, the direction of rotation of the cylinder drum 6 of the piston radial force F r 1 is opposite and in engine operation, the piston radial force F r 1 and the direction of rotation in the same circumferential direction. In both functional operations applies that the piston radial force F r 1 is directed in the circumferential direction in which the inclination angle W is closed.
  • the radial force F r 1 and the piston centrifugal force F f respectively form a resultant radially outwardly effective radial force FR between the radial force F r 1 and the piston centrifugal force F f extending angle range W1 is effective, wherein the respective effective point of action of the resultant radial force FR of the respective existing quantity of the working pressure and radial force F r 1 and of the speed and centrifugal force F f is dependent and thus to the action point of the radial force F r 1 or displaced to the point of action of the piston centrifugal force F f can be arranged.
  • a middle position for the resulting piston force FR can thus be assumed to be particularly advantageous, in which the latter includes an angle W2 of approximately 45 ° with the plane E containing the longitudinal central axis of the axial piston machine and the longitudinal center axis of the relevant piston 29. Since the pistons 29 move back and forth during functional operation, it can be assumed for the purpose of further simplification that - seen transversely to the longitudinal central axis of the respective piston 29 - the resulting piston force FR in an effective range between the piston centrifugal force F f and the radial force F r effect areas is effective.
  • Such a load case or functional case is z. B. then present when the axial piston engine is driven by the working pressure in engine operation and reaches high speeds especially when the axial piston machine has a small throughput volume (constant machine) or is set to a small throughput volume.
  • the axial piston machine may be formed by the engine of a hydrostatic transmission.
  • Another functional criterion or another functional case in which an increased friction and a resulting increased heating of the bushing 28 occurs, is given when the axial piston machine operates substantially without pressure or with low working pressure. In this case, less or substantially no leakage fluid is conveyed through the piston play and therefore less or substantially no frictional heat is dissipated, whereby increased heating of the zone concerned can take place with the above-described functional problems.
  • the liners 28 on its outer lateral surface in each case at least in the area in which they from the associated piston 29 radially with the greatest compressive force, z. B. F r 1 or FR or F f , a recess 41, extending in the circumferential direction of the piston 29 dimension of the heated zone a, z. B. the radius r of the piston 29, may correspond and their axial dimension may correspond to the region A.
  • the recess 41 or its central axis 41a can be arranged in the region of the longitudinal center plane E, in particular when the axial piston machine is operated at high rotational speeds and low working pressure.
  • the recess 41 or its central axis 41a in the region of the outer and circumferential quadrants Q of the bushing 28, the inclination angle W being closed in this circumferential direction.
  • the recess 41 can be arranged in the quadrant or beyond it in terms of rotational speed and working pressure relative to the longitudinal center plane E or in the direction of rotation.
  • the recess 41 may be arranged in a constant machine in the middle stroke range or in an adjustable axial piston machine in the central region of the maximum stroke range.
  • the recess 41 may be arranged in the central stroke region of the approximately radial axis of action of the center of gravity S or in the region of the center of gravity S with the swash plate 3 pivoted out to a minimum.
  • the recess 41, 41b, 41c is present when it is arranged in the rear outlet-side region, preferably completely in the discharge-side half of the bushing 28.
  • the distance b of the recess 41 from the rear or mouth-side end of the bushing 28 may be 3 mm to 10 mm, in particular about 5 mm.
  • the recess 41 or its central axis 41a is arranged in the region of the end region of the piston stroke facing away from the swashplate 3 at approximately swung-out plate 31 which is pivoted out maximally.
  • the recess 41 Fig. 6 as an embodiment shows in the same or similar parts are provided with the same reference numerals.
  • the clearance formed by the recess 41 is not between the liners 28 and the inner surfaces of the bushing holes 28a but between the liners 28 and the associated piston 29.
  • each of the material of the liners 28 can expand into this space , without the piston clearance is reduced.
  • the bushings 28 can not expand radially outward because they are enclosed by the inner surfaces of the bushing holes 28b.
  • the recesses 41 need the recesses 41 to be located or extend only in the area in which in functional operation with increased heating or temperature increase is expected, for example in the effective range of the radial force F r 1 and / or in the field of centrifugal force F f . Therefore, in the embodiments according to Fig. 1 to 5 above-described arrangement points in the axial direction and / or in the circumferential direction for the recess 41 also in the embodiments according to 6 and 7 , With respect to the embodiment according to Fig.
  • the recess 41b are arranged in the inner circumferential surface of the bushings 28 and the recess 41c in the inner circumferential surface of the receiving holes 28b respectively in the same radial direction, so that they are arranged radially one behind the other.
  • the material of the liners 28 can each extend into the space formed by the recess 41b, so that this also a reduction of the piston clearance is avoided.
  • the axial dimension c of the recess 41, 41b, 41c may correspond to approximately 0.3 times to 0.7 times the inside diameter 2r, preferably 0.5 times the inside diameter 2r, of the bushing 28.
  • the recess 41, 41b, 41c in the circumferential direction is formed so large that it extends over the entire quadrant Q, it is suitable for the above-described functional cases, or functional criteria. This also applies if the recess 41, 41b, 41c is formed by an annular groove. Such a recess 41, 41b, 41c can be easily produced. In addition, when mounting the bushing 28, no attention is required as to the position in which the recess 41, 41b, 41c is located. Due to the annular shape, the recess 41, 41b, 41c fits in every rotational position of the bushing 28, and therefore it can be mounted in any rotational position.
  • the recesses 41, 41b, 41c-here in longitudinal cross-section-each with a concavely rounded shape or spherical segment-shaped.
  • a concavely rounded shape or spherical segment-shaped is also called a dome.
  • the radius r1 of the preferably spherical segment-shaped rounded recessed area corresponds approximately to four to six times, in particular approximately five times, the inner diameter 2r.
  • the depth t of the recess 41, 41b should be about 1% to 10%, in particular about 5%, of the inner radius r. In the case of the recess 41c, this applies to the inner radius of the receiving holes 28b.
  • the liner 28 with the Recess 41 in the contact area to the cylindrical drum 6 comprising them so that when operational heating of the friction pair by thermal compensation, the piston clearance (gap width) between the piston 29 and the bushing 28 in the region of the same value remains (exact compensation).
  • This embodiment is also possible with increasing gap width with increasing heating (overcompensation).
  • this configuration is possible with decreasing the gap width with increasing heating (undercompensation).
  • This configuration is also possible when setting any gap contour by a corresponding Nutwel.
  • the cooling device can itself from the DE 44 23 023 A1 corresponding removable embodiment, in which a bushing bore 28b cutting and approximately radial cooling channel 46 is provided in the cylinder drum 6, which connects the free inner space 25 of the cylinder barrel 6 with the cylinder drum surrounding the inner space 25a.
  • the cooling channel 46 passes through the associated bushing 28 in the region of the recess 41b.
  • the cooling channel 46 may extend into the recess 41c or also into the recess 41b.
  • the cooling channel 46 is arranged so that its central axis intersects the longitudinal central axis of the associated cylinder 26.
  • this cooling device 45 takes place in particular in the embodiment Fig. 1 in functional operation, an automatic delivery of the hydraulic fluid or oil instead, due to the centrifugal force acting on the existing in the cooling channels 46 hydraulic fluid during operation.
  • a the interior 25 to the interior 25a connecting flow circuit is the above-described automatic promotion of the hydraulic Fluids guaranteed.

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

Claims (12)

  1. Machine hydrostatique, en particulier machine avec disque en nutation, avec un bloc cylindre (6), dans lequel sont disposés des trous de chemise de cylindre (28b), dans lesquels sont logées des chemises de cylindre (28) qui enserrent les trous de piston (28a), dans lesquels sont logés les pistons (29) se déplaçant en va-et-vient,
    les pistons (29) délimitant, par leurs extrémités frontales plongeant dans le bloc cylindre (6) des cylindres (26),
    les chemises de cylindre (28) présentant respectivement, dans leur zone modifiée du cylindre (26) et au moins dans la zone de la force radiale de piston (Ff, Fr1) maximale comprimant le piston (29) contre la paroi perforée de piston, un évidement axialement délimité (41) dans sa surface de chemise de cylindre extérieure,
    la dimension axiale de l'évidement (41) correspond sensiblement à 3/10 jusqu'à 7/10 du diamètre (2r) du trou de piston (28a) et
    l'évidement (41) est disposé dans la zone médiane de levage de l'axe efficace sensiblement radial du point de gravité (S) du piston (29) ou dans la zone du point de gravité (S) du disque en nutation (3) basculé de façon minimale ou dans la machine à piston axial déplaçable dans la zone médiane de la zone de levage maximale.
  2. Machine hydrostatique selon la revendication 1,
    caractérisée en ce que
    l'évidement (41, 41b, 41c) est disposé dans la zone du point de gravité (S) du piston (29).
  3. Machine hydrostatique selon la revendication 2,
    caractérisée en ce que
    le volume débitmétrique de la machine à piston axial est ajustable et l'évidement (41, 41b, 41c) se trouve dans la zone du point de gravité (S) lorsque la machine à piston axial est réglée sur un volume débitmétrique minimum.
  4. Machine hydrostatique selon l'une des revendications 1 à 3,
    caractérisée en ce que - dans la direction axiale de la machine à piston axial - l'évidement (41, 41b, 41c) ou son axe médian (41a) est disposé dans la zone du quadrant extérieur (Q) de la chemise de cylindre (28), le quadrant (Q) étant dirigé dans la direction périphérique, dans laquelle est renfermé l'angle d'inclinaison (W).
  5. Machine hydrostatique selon l'une des revendications précédentes,
    caractérisée en ce que
    l'évidement (41, 41b) et/ou l'autre évidement (41c) présentent un évidement annulaire
  6. Machine hydrostatique selon l'une des revendications précédentes,
    caractérisée en ce que
    l'évidement (41) est disposé complètement dans la moitié longitudinale de la chemise de cylindre (28) détournée des cylindres (26).
  7. Machine hydrostatique selon l'une des revendications précédentes,
    caractérisée en ce que
    l'évidement (41) présente respectivement un espace par rapport aux extrémités des chemises de cylindre(28) détournées des cylindres (26) d'environ 3 mm jusqu'à 10 mm, en particulier environ 5 mm.
  8. Machine hydrostatique selon l'une des revendications précédentes,
    caractérisée en ce que
    la dimension axiale de l'évidement (41) correspond aux 5/10 du diamètre (2r) du trou de piston (28a).
  9. Machine hydrostatique selon l'une des revendications précédentes,
    caractérisée en ce que
    au moins la surface de base de l'évidement (41) est arrondie, de préférence sous une forme de section d'arc circulaire.
  10. Machine hydrostatique selon la revendication 9,
    caractérisée en ce que
    le rayon (r1) de l'arrondi correspond à quatre jusqu'à six fois, en particulier cinq fois, la dimension de section transversale du trou de piston (28a).
  11. Machine hydrostatique selon l'une des revendications précédentes,
    caractérisée en ce que
    l'évidement (41) est raccordé par un canal de refroidissement (46) à un dispositif de refroidissement (45) qui, de préférence, comporte un circuit de refroidissement.
  12. Machine hydrostatique selon la revendication 11,
    caractérisée en ce que
    le canal de refroidissement (46) relie un espace de fluide (25) disposé dans le bloc cylindre (6) avec un espace de fluide (25a) entourant le bloc cylindre (6).
EP02777007A 2001-09-19 2002-09-05 Machine hydrostatique chemises de cylindres compenses Expired - Lifetime EP1427914B1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE10146137 2001-09-19
DE10146137 2001-09-19
DE10157248 2001-11-22
DE10157248A DE10157248A1 (de) 2001-09-19 2001-11-22 Hydrostatische Maschine mit kompensierten Laufbuchsen
PCT/EP2002/009954 WO2003025347A1 (fr) 2001-09-19 2002-09-05 Machine hydrostatique à chemises de cylindres compensées

Publications (2)

Publication Number Publication Date
EP1427914A1 EP1427914A1 (fr) 2004-06-16
EP1427914B1 true EP1427914B1 (fr) 2008-06-25

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Application Number Title Priority Date Filing Date
EP02777007A Expired - Lifetime EP1427914B1 (fr) 2001-09-19 2002-09-05 Machine hydrostatique chemises de cylindres compenses

Country Status (3)

Country Link
US (1) US7073427B2 (fr)
EP (1) EP1427914B1 (fr)
WO (1) WO2003025347A1 (fr)

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WO2013037611A1 (fr) * 2011-09-15 2013-03-21 Robert Bosch Gmbh Manchon de guidage de piston pour une machine à piston axial, et machine à piston axial pourvue d'un manchon de guidage de piston
JP2018076826A (ja) * 2016-11-10 2018-05-17 川崎重工業株式会社 シリンダブロックとそれを備えた斜板形液圧回転装置
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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102022206073A1 (de) 2022-06-15 2023-12-21 Robert Bosch Gesellschaft mit beschränkter Haftung Hydrostatische Axialkolbenmaschine

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US20040247454A1 (en) 2004-12-09
US7073427B2 (en) 2006-07-11
WO2003025347A1 (fr) 2003-03-27
EP1427914A1 (fr) 2004-06-16

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