WO2006122808A1 - Machine hydrostatique a pistons fonctionnant selon le principe des coupelles flottantes - Google Patents

Machine hydrostatique a pistons fonctionnant selon le principe des coupelles flottantes Download PDF

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Publication number
WO2006122808A1
WO2006122808A1 PCT/EP2006/004729 EP2006004729W WO2006122808A1 WO 2006122808 A1 WO2006122808 A1 WO 2006122808A1 EP 2006004729 W EP2006004729 W EP 2006004729W WO 2006122808 A1 WO2006122808 A1 WO 2006122808A1
Authority
WO
WIPO (PCT)
Prior art keywords
swash plate
cylinder
group
hydrostatic piston
drum unit
Prior art date
Application number
PCT/EP2006/004729
Other languages
German (de)
English (en)
Inventor
Georg Jacobs
Marcus Herrmann
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
Priority to US11/920,659 priority Critical patent/US20090031892A1/en
Priority to EP06753713A priority patent/EP1883743A1/fr
Priority to JP2008511641A priority patent/JP2008540924A/ja
Publication of WO2006122808A1 publication Critical patent/WO2006122808A1/fr

Links

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
    • F04B1/20—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
    • F04B1/22—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 having two or more sets of cylinders or pistons
    • 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
    • F01B3/10—Control of working-fluid admission or discharge peculiar thereto
    • 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
    • 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

Definitions

  • the invention relates to a hydrostatic piston engine according to the floating cup principle.
  • Hydrostatic piston engines according to the floating cup principle are improved in terms of their friction losses compared to conventional reciprocating engines.
  • Such a piston machine which operates on the floating cup principle, is known from WO 03/058035 Al.
  • the hydrostatic piston engine has a drive shaft arranged in a housing, wherein pistons are fixedly connected to the drive shaft via a carrier plate. Also rotatably connected to the drive shaft is for each group of protruding in the opposite direction of the support plate piston in each case a drum plate, are arranged on the cylinder.
  • the axis of rotation of the drum plates is inclined relative to the drive shaft axis by the same amount in each case so that the pistons of the first group and of the second group arranged in the cylinders execute a lifting movement relative to the cylinders.
  • the engine groups formed on both sides of the carrier plate by the respective pistons, cylinders and drum plates promote in a common hydraulic circuit.
  • the high pressure sides of the two drum units and the low pressure sides of the two drum units are connected to each other in the housing of the piston machine.
  • the two drum plates are each supported on a swash plate, wherein the swash plates are mutually adjustable.
  • both groups of pistons merely convey into a common hydraulic circuit and the adjustment of the two swash plates corresponds to one another.
  • Such a common adjustment of the two swash plates is required in the known from WO 03/058035 Al hydrostatic piston engine to equalize the axial forces acting on the pistons of both groups to each other.
  • the hydrostatic piston engine according to the invention has two engine groups.
  • the first group of engines comprises a first swash plate on which a first cylinder drum unit is supported.
  • a first group of pistons is arranged, which are non-rotatably connected to a drive shaft of the hydrostatic piston machine.
  • a second engine group a second swash plate on which a second cylinder drum unit is supported.
  • cylinder recesses are also arranged, in which engages a second group of pistons.
  • the second group of pistons is also non-rotatably connected to the drive shaft of the hydrostatic piston engine.
  • a first group of piston spaces is formed in the cylinder recesses of the first cylinder drum unit.
  • a second group of cylinder recesses is also formed by the second group of pistons in the cylinder recesses of the second cylinder drum unit.
  • the first group of cylinder chambers and the second group of cylinder chambers are connected to achieve two flow rates of pressure medium, each with its own hydraulic circuit.
  • the hydrostatic piston engine designed, for example, as a hydraulic pump feeds through the first engine unit into a first working line and through the second engine group into a second working line.
  • the hydrostatic piston machine can also be used for such applications in which independent hydraulic circuits are to be supplied.
  • the hydrostatic piston engine according to the invention with the features of claim 2 has an independent adjustment of the two engine groups. This makes it possible to carry out an adjustment of the delivery volume initially by the first group of engines when using the hydrostatic piston machine as a hydraulic pump. Subsequently, z. B. made by the second engine groups also an adjustment in the same direction. In particular, an independent flow adjustment when pumping in two hydraulic circuits is advantageous.
  • the independent adjustment of the two engine groups from each other also allows to carry out a group with a constant displacement, the second engine group contrast, perform adjustable.
  • the first group of engines is in turn formed by a cylinder drum unit and the cylinder recesses arranged thereon together with the first group of pistons.
  • the second engine group is accordingly formed by the second group of pistons together with the second cylinder recesses of the second cylinder drum unit.
  • the adjustment takes place by changing the axis of rotation of the respective cylinder drum unit.
  • the change in the axis of rotation of the respective cylinder drum unit is independent of the orientation of the axis of rotation of the respective other cylinder drum unit.
  • the rotational axes of the two cylinder drum units are independently variable, they can be adjusted together.
  • the pressure medium supply and pressure medium discharge to and from the first and second cylinder chambers is preferably effected through the swash plate.
  • pressure medium channels are introduced into the swash plate.
  • the pressure medium channels of the first and the second swash plate open into a channel section of a first or second housing flange part. Furthermore, this arrangement can advantageously bring about a hydrostatic relief of the swashplate.
  • leakage fluid which exits at the transition from the pressure medium channels of the swash plates to the channel sections of the first and second Genzouseflanschteils, used to form a hydrodynamic bearing between the swash plates and the corresponding first bearing surface of the first Genzouseflanschteils or the second corresponding bearing surface of the second Genzouseflanschteils .
  • the first and second swash plate are thus slidably mounted in the first housing flange part and the second housing flange part and hydrostatically relieved of pressure via a small amount of leakage of pressure medium.
  • At least one of the working ports via the pressure medium channels in the first and the second Swash plate with the first cylinder chambers and the second cylinder chambers are connectable, is formed on the first housing flange part and the second Genzouseflanschteil. This is done on a short path within the hydrostatic piston engine, the connection to the outside.
  • Each of the working connections is connected to a feed valve unit, via which not only a make-up with pressure medium takes place, but which also has a high-pressure limiting valve to protect the connected working line.
  • the feed valve units are supplied with the nachzu busynden pressure medium.
  • the common feed pressure channel has the advantage that a central connection is sufficient to demand pressure for feeding, for example by means of a constant pump. The use of only one common connection eliminates additional sealing points and the laying effort of lines on the hydrostatic piston machine is reduced.
  • Fig. 1 is a first perspective view of a hydrostatic according to the invention
  • FIG. 2 shows a second perspective view with a partial section through an adjusting device of the hydrostatic piston machine according to the invention
  • 3 shows an external view of a hydrostatic piston machine according to the invention
  • Fig. 4 is a second external view of a hydrostatic piston machine according to the invention with a
  • Fig. 6 is a first schematic representation of a first
  • FIG. 8 shows a third schematic illustration of a first housing flange part of the hydrostatic piston machine according to the invention.
  • Fig. 9 is a fourth schematic representation of a hydrostatic inventive
  • the hydrostatic piston engine 1 has a housing which comprises a first housing flange part 2 and a second housing flange part 3.
  • the first housing flange part 2 and the second housing flange part 3 are arranged on two opposite sides on a substantially tubular further housing part 4 and supplement this to form a closed housing.
  • a drive shaft 5 is rotatably mounted in the housing of the hydrostatic piston engine 1.
  • a first bearing 6 is arranged in the first housing flange part 2 and a second bearing 7 is arranged in the second housing flange part 3.
  • the first bearing 6 and the second bearing 7 are preferably designed as rolling bearings.
  • the individual parts of the housing are connected to one another via screws 8.
  • a support plate 9 is rotatably connected.
  • the support plate 9 is disc-shaped and arranged approximately centrally in the region of the further housing part 4.
  • a first group of pistons 10 extend from the carrier plate 9.
  • the pistons 10, of which only one is provided with a reference numeral for the sake of clarity, are arranged on a common circumferential circle on the carrier plate 9.
  • the pistons 9 engage in each case a cylindrical recess of a cylinder 11, which are arranged on a first drum plate 14.
  • the first group of pistons 10 together with the first drum plate 14 and the first group of cylinders 11 form a first group of engines.
  • a second group of pistons 12 are arranged, which also engage with their side facing away from the support plate 9 in cylinder recesses of a corresponding group of cylinders 13 and also offset from the piston 11 of the first group 11 can be arranged.
  • Fig. 1 shows the opposite arrangement, in which a through hole in the support plate 9 can be punched.
  • the second group cylinder 13 is arranged on a second drum plate 15. This is formed on the opposite side of the support plate 9, a second group of engines.
  • the fixed fixation of the first group cylinder 11 on the first drum plate 14 and the second group cylinder 13 on the second drum plate 15 takes place only in the axial direction, that is, that a lateral movement on the respective drum plate 14 and 15 is possible.
  • the cylinders 11 and 13 are fixed in a manner not shown in the axial direction.
  • the elliptical projection of the pistons 10 and 12 on the not shown first support surface of the first support plate 14 and the second support surface 15 'of the second Support plate 15 balanced.
  • the first drum plate 14 For tilting the first drum plate 14 and the second drum plate 15, the first drum plate 14 is supported on a not visible in FIG. 1 first tread of a first swash plate 16 from. Accordingly, the second support plate 15 is supported on a second running surface 18 of a second swash plate 17.
  • the first swash plate 16 and the second swash plate 17 are independently adjustable in their angle relative to the drive shaft 5. By the swash plates 16, 17 thus the axes of rotation of the voltage applied to the running surfaces drum plates 14, 15 and thus the entire cylinder drum units are set independently.
  • the first drum plate 14 and the second drum plate 15 are rotatably connected to the drive shaft 5, so that the side facing away from the first group of cylinders 11 side of the first drum plate 14 on the running surface of the first pivot plate 16 slidably rotates.
  • the second drum plate 15 rotatably connected to the drive shaft 5 and rotates on the tread 18 of the second swash plate 17th
  • the first swash plate 16 is designed as a pivoting cradle and on the side facing away from the running surface, not shown, a sliding surface 19 formed on the first swash plate 16.
  • the second swash plate 17 is designed as a pivoting cradle and formed on the side remote from the running surface 18 of the second swash plate 17 side, a second sliding surface 20 on the second swash plate 17.
  • the first sliding surface 19 and the second sliding surface 20 form, in a manner to be described later, a plain bearing with corresponding bearing surfaces of the first housing flange part 2 and of the second housing flange part 3, respectively.
  • the first cylinder chambers are alternately connected to a high-pressure or low-pressure connection.
  • an opening is provided for each cylinder 11 in the cylinder bases supporting the first drum plate 14 of the first cylinder 11 and in the first drum plate 14.
  • the first cylinders 11 on the running surface of the first swash plate 16 these openings are connected in succession with arranged in the running surface of the first swash plate 16 control openings.
  • the control openings are outlets of pressure medium channels, which are formed in the first swash plate 16. The pressure medium ducts thus connect the running surface of the first swash plate 16 with the first sliding surface 19 of the first swash plate 16 oriented in the opposite direction.
  • the outlets of the pressure medium passages on the side of the first sliding surface 19 are designed such that the first swash plate 16 is independent of the respective set swivel angle a connection to the low pressure or high-pressure connection of the first housing flange part 2 is present.
  • grooves or bores may be provided in the tread of the first swashplate, for example to reduce pulsations, in order to improve the reversing behavior.
  • two pressure medium channels are formed in the second swash plate 17, which form control openings on the side of the running surface 18.
  • the pressure medium channels On the oppositely oriented second sliding surface 20, the pressure medium channels also open out so that they form a permanent connection with corresponding openings, which are formed in the second flange 3, regardless of the set tilt angle of the swash plate 17.
  • an adjusting device 21 which cooperates with the second swash plate 17.
  • the adjusting device 21 preferably performs a linear adjusting movement, which will be described later with reference to FIG. 2.
  • the adjusting device 21 is arranged on the outside of the further housing part 4 and aligned substantially parallel to the drive shaft 5.
  • the parallel aligned actuator 21 acts via a sliding block and a lever 47 with the second Swash plate 17 together and adjusted by means of a linear movement, the inclination of the tread 18 relative to the drive shaft 5.
  • the adjustment can be done in both directions.
  • the surface normal of the tread 18 coincides in a neutral position, for example, with the axis of the drive shaft 5. From this neutral position pivoting of the second swash plate 17 in the direction of positive and in the direction of negative angle is possible. Thus, the conveying direction of the second engine group can be reversed.
  • the hydrostatic piston machine according to the invention is provided for delivery in two separate hydraulic circuits.
  • the first cylinder drum unit together with the first piston 10 is connected to a first hydraulic circuit via a first working line connection 22 and a second working line connection 23.
  • the first working line connection 22 and the second working line connection 23 are arranged in the first housing flange part 2 and connect the control of the first swash plate 10 via a first working line 24 and a second working line 25 with working lines.
  • the control of the second swash plate 17 are connected via a third working line connection 26 and a fourth working line connection 28 to a second hydraulic circuit.
  • the second hydraulic circuit is also designed as a closed circuit, wherein for the supply of pressure medium in the second Genzouseflanschteil 3, a third working conduit 27 and a fourth working conduit 29 are provided.
  • the third working conduit 27 and the fourth working conduit 29 connect the third working conduit connection 26 and the fourth working conduit connection 28 via the pressure medium channels provided in the second swash plate 17 with the respective control in the tread 18 of the second swash plate 17th
  • first swash plate 16 and the second swash plate 17 both of which can be pivoted from their respective neutral position out in two opposite directions, it is also possible to independently the conveying directions in the first hydraulic circuit and in the second hydraulic circuit choose.
  • a further adjusting device is provided, which is arranged on the not visible in FIG. 1 back of the hydrostatic piston machine 1.
  • the neutral position of the first swash plate 16 as well as the second swash plate 17 does not necessarily correspond to the position in which the running surfaces of the first swash plate 16 and the second swash plate 17 form a right angle with the drive shaft 5.
  • the neutral position of the first swash plate 16 is at a different angle with respect to the axis of the drive shaft 5 than the neutral position of the second swash plate 17th
  • the first working conduit 24 is connected to a feed valve unit which is not visible in FIG. Accordingly, the second working conduit 25 is connected to a second feed valve unit 30. Via the first feed valve unit and the second feed valve unit 30, the first working line channel 24 and the second working line channel 25 can be connected to a first connecting channel 32.
  • the feed valve units is in each case towards the respective working line connection 22 and 23 out opening check valve provided, wherein a high-pressure relief valve is arranged parallel to this check valve. With the help of the high-pressure relief valve, the check valve can be bypassed in the case of a critically high pressure acting in the closing direction of the check valve, and the corresponding working line can thus be relaxed in the direction of the first connecting line 32.
  • the third working-line channel 27 and the fourth working-line channel 29 are connected via a third or fourth feed valve unit 31 to a second connecting channel 33.
  • the first connecting channel 32 and the second connecting channel 33 lead to a feed pressure limiting valve 34, via which the first connecting channel 32 and the second connecting channel 33 are expanded into a tank volume when a certain feed pressure set by a spring is exceeded.
  • the tank volume may for example be identical to the inner housing volume of the hydrostatic piston engine 1, wherein the accumulated in the inner tank volume of the hydrostatic piston engine 1 pressure medium is discharged in a manner not shown via a return line to a further, external tank volume.
  • a feed line connection 35 is provided, via which a feed pressure generated by an auxiliary pump is supplied to the first connection channel 32 and the second connection channel 33.
  • the auxiliary pump may be, for example, a constant displacement pump with through drive, which is arranged in the first or second Genzouseflanschteil 2, 3.
  • the corresponding housing flange part 2, 3 has a suction port in order to be able to suck in pressure medium from a tank volume.
  • the connecting channel 32, 33 is overlapping in the further housing part 4 and in the first Gepuruseflanschteil 2 and the second Housing flange part 3 is formed.
  • the feed line connection 35 and the feed pressure limiting valve 34 are arranged in the further housing part 4 and take over for the feed valve units of the first Genzouseflanschteils 2 and the feed valve units of the second Gescouseflanschteils 3 together the function of pressure relief in the feed system.
  • Fig. 2 is a partially sectioned view of the hydrostatic piston machine according to the invention of Fig. 1 is shown.
  • a first stop 37 and a second stop 38 are formed on a guide rod 36.
  • a first spring bearing 39 and a second spring bearing 40 are slidably mounted on the guide rod 36.
  • a compression spring 41 is arranged, which is formed in the illustrated embodiment as a spiral spring. With their outer circumference, the first spring bearing 39 and the second spring bearing 40 are arranged displaceably in a recess 42 of an adjusting piston.
  • a deflection of the adjusting piston 42 is shown to the right.
  • a driving device is provided, on which the first spring bearing 39 is supported and thus follows the movement of the adjusting piston 42 to the right.
  • the compression spring 31 which is supported on the second spring bearing 38 on the second stop 38 of the guide rod 36, compressed.
  • the spring 41 is supported on the adjusting piston 42 via the first spring bearing 39 until the first spring bearing 39 is in contact with the stop 37.
  • a further movement of the adjusting piston 42 to the left causes entrainment of the second spring plate 40 via a not visible in FIG. 2 driving device of the adjusting piston 42 to the left, so that the spring 41 is now a compression due to the abutment against the first stop 37 and the second driving device of the adjusting 42 undergoes.
  • a first actuating pressure chamber 43 and a second actuating pressure chamber 44 is provided for the deflection of the adjusting piston 42 from its rest position, which is defined by the spring 41.
  • the adjusting pressure chambers 43 and 44 are formed between an outer periphery of the adjusting piston 42 and a housing portion 4 'of the adjusting device 21, which is formed on the further housing part 4.
  • a radially expanded region is formed on the adjusting piston 42, which separates the two actuating pressure chambers 43 and 44 from each other and in each actuating pressure chamber 43, 44 forms a surface acted upon by the control pressure.
  • FIG. 3 once again shows an external view of the hydrostatic piston machine 1 according to the invention.
  • the adjusting device 21 is arranged in a region of the further housing part 4.
  • the guide rod 36 protrudes out of a cover portion 48, which is preferably arranged on the first GeHouseflanschteil 2.
  • the guide rod 36 is preferably fixed by a thread in the cover portion 48, so that by rotating the guide rod 36, the axial position of the guide rod 36 and thus the neutral position of the second swash plate 17 is adjustable.
  • To fix the axial position is a lock nut 49th
  • FIG. 4 once again shows a partial section through a hydrostatic piston machine according to the invention. It can be seen there that in the further housing part 4, which is closed on both sides by the first housing flange part 2 or the second housing flange part 3, a housing section 4 1 is formed for the adjusting device 21.
  • This housing section 4 ' is closed on one side by a first cover section 48 and on the opposite side by a second cover section 50 of the second housing flange part 3.
  • the second cover portion 50 takes on the area of the sliding block 46 and the actuating lever 47.
  • the two further feed valve units 51 and 52 can also be seen.
  • a further adjusting device 53 is provided which cooperates with the first swash plate 16 and is arranged in a on the other housing part 4 the housing portion 4 'opposite housing portion.
  • the further adjusting device 53 for the first swash plate 16 corresponds in its structure to that described Adjustment device 21.
  • a cover section 55 is provided on the first housing flange part 2.
  • the first connection channel 32 consists of a first section 32a and a second section 32b, which are formed in the further housing part 4 and the first housing flange part 2, respectively.
  • the second connection channel 33 consists of a first section 33a formed in the further housing part 4 and a second section 33b in the second housing flange part 3.
  • the second section 32b of the second branches first connecting channel 32 into a first channel section 32 'and a second channel section 32''.
  • the second portion 33b of the second connection channel 33 branches into a third channel portion 33 'and a fourth channel portion 33' '.
  • the branching of the first connection channel 32 and of the second connection channel 33 is formed in the first housing flange part 2 and the second housing flange part 3, respectively.
  • the branching of the first connection channel 32 and of the second connection channel 33 is formed in the first housing flange part 2 and the second housing flange part 3, respectively.
  • the first Gezzauseflanschteil 2 is shown. It can be seen that in the first Gepuruseflanschteil 2 a bearing surface 60 ', 60''is formed, which corresponds to the curvature of the first sliding surface of the first swash plate 16. In the bearing surface 60 ', 60'', the first working conduit 24 and the second working conduit 25 open into a first opening 24' and a second opening 25 ', respectively. For a hydrostatic piston engine 1 with a reversible control are while the expansions of the first opening 24 'and the second opening 25' preferably identical. The first opening 24 'and the second opening 25' preferably extend along a portion of the bearing surface 60 ', 60''.
  • the resulting during the transition from the mouths of the pressure medium channels of the first swash plate 16 on the sliding surface 19 to the first working conduit 24 and the second working conduit 25 leakage fluid is used to form a lubricating film on the bearing surface 60, 60 '.
  • Lubricating the first swash plate 16 rotatably mounted in the bearing surface 60 ', 60 is achieved by the lubricating film on the bearing surface 60', 60".
  • recessed areas 62a, 62b, 62c are formed, which receive the leakage fluid and provide the hydrostatic discharge. Lateral cheeks seal the recessed areas 62a, 62b, 62c against the swashplate 16.
  • FIG. 7 shows a further illustration of a first housing flange part 1 in a slightly different perspective.
  • the formation of the second housing flange part 3 corresponds to the first housing flange part 2.
  • the first housing flange part 2 is shown in a rotated view.
  • a lid portion 55 is formed, in which a recess 61 for receiving the actuating lever 47 and the sliding block 46 of the adjusting piston 42 is provided.
  • FIG. 9 shows a further illustration of the first flange part 2.

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

Abstract

La présente invention concerne une machine hydrostatique à pistons qui fonctionne selon le principe des coupelles flottantes et qui comprend un premier plateau oscillant (16) et un second plateau oscillant (17). Une première unité de tambour de cylindre (11, 14) s'appuie sur le premier plateau oscillant et une seconde unité de tambour de cylindre (12, 15) s'appuie sur le second plateau oscillant (17). Un premier groupe de pistons (10) et un second groupe de pistons (12) sont reliés fixement à un arbre d'entraînement (5) de la machine hydrostatique à pistons (1). Le premier groupe de pistons (10) vient en prise dans les cavités de cylindre de la première unité de tambour de cylindre (11, 14) et les pistons (12) du second groupe viennent en prise dans des cavités de la seconde unité de tambour de cylindre (12, 15). Les premières et secondes chambres de cylindre formées par les pistons (10, 12) et par les unités de tambour de cylindre (11, 14, 12, 15) peuvent être reliées à un premier circuit hydraulique ou à un second circuit hydraulique. L'axe de rotation de la première unité de tambour de cylindre (11, 14) et/ou l'axe de rotation de la seconde unité de tambour de cylindre (12, 15) peuvent respectivement être réglés de manière indépendante de l'axe de rotation de l'autre unité de tambour de cylindre.
PCT/EP2006/004729 2005-05-20 2006-05-18 Machine hydrostatique a pistons fonctionnant selon le principe des coupelles flottantes WO2006122808A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US11/920,659 US20090031892A1 (en) 2005-05-20 2006-05-18 Hydrostatic piston machine according to the floating cup concept
EP06753713A EP1883743A1 (fr) 2005-05-20 2006-05-18 Machine hydrostatique a pistons fonctionnant selon le principe des coupelles flottantes
JP2008511641A JP2008540924A (ja) 2005-05-20 2006-05-18 フローティングカップの原理に基づく液圧ピストン機械

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102005023423.2 2005-05-20
DE102005023423 2005-05-20
DE102005037618.5 2005-08-09
DE102005037618A DE102005037618A1 (de) 2005-05-20 2005-08-09 Hydrostatische Kolbenmaschine nach dem Floating-Cup-Konzept

Publications (1)

Publication Number Publication Date
WO2006122808A1 true WO2006122808A1 (fr) 2006-11-23

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PCT/EP2006/004729 WO2006122808A1 (fr) 2005-05-20 2006-05-18 Machine hydrostatique a pistons fonctionnant selon le principe des coupelles flottantes

Country Status (6)

Country Link
US (1) US20090031892A1 (fr)
EP (1) EP1883743A1 (fr)
JP (1) JP2008540924A (fr)
KR (1) KR20080009056A (fr)
DE (1) DE102005037618A1 (fr)
WO (1) WO2006122808A1 (fr)

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DE102006058801A1 (de) * 2006-12-13 2008-06-19 Robert Bosch Gmbh Gehäuse für eine hydrostatische Maschine
DE102006062065A1 (de) * 2006-12-29 2008-07-03 Robert Bosch Gmbh Axialkolbenmaschine mit einem einen radial erweiterten Innenraumabschnitt aufweisenden Gehäuse
CN102959243B (zh) * 2010-07-08 2015-12-09 罗伯特·博世有限公司 液压轴向活塞机器
DE102011105465B4 (de) * 2010-07-08 2021-05-27 Robert Bosch Gmbh Hydraulische Doppelaxialkolbenmaschine mit fluchtend zueinander ange-ordneten Stellkolben und an unterschiedlichen Anbauflächen des Gehäuses angebrachten Regelventilen
US20160131118A1 (en) * 2014-11-06 2016-05-12 Robert Bosch Gmbh Tandem axial piston pump with shared cylinder block
US10247178B2 (en) * 2016-03-28 2019-04-02 Robert Bosch Gmbh Variable displacement axial piston pump with fluid controlled swash plate

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US3442181A (en) * 1964-12-22 1969-05-06 Metaalbedrijf Rademakers Nv Hydrostatic axial piston transmission assembly
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KR20080009056A (ko) 2008-01-24
JP2008540924A (ja) 2008-11-20
US20090031892A1 (en) 2009-02-05
EP1883743A1 (fr) 2008-02-06

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