EP3561298A1 - Hydraulische kolbenvorrichtung - Google Patents

Hydraulische kolbenvorrichtung Download PDF

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Publication number
EP3561298A1
EP3561298A1 EP18425030.6A EP18425030A EP3561298A1 EP 3561298 A1 EP3561298 A1 EP 3561298A1 EP 18425030 A EP18425030 A EP 18425030A EP 3561298 A1 EP3561298 A1 EP 3561298A1
Authority
EP
European Patent Office
Prior art keywords
directional control
cylinder
conduit
hydraulic device
pressure
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.)
Withdrawn
Application number
EP18425030.6A
Other languages
English (en)
French (fr)
Inventor
Alessandro Sassi
Fabio Natali
Federica Franzoni
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.)
Dana Motion Systems Italia SRL
Original Assignee
Dana Motion Systems Italia SRL
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 Dana Motion Systems Italia SRL filed Critical Dana Motion Systems Italia SRL
Priority to EP18425030.6A priority Critical patent/EP3561298A1/de
Priority to PCT/EP2019/059889 priority patent/WO2019206757A1/en
Publication of EP3561298A1 publication Critical patent/EP3561298A1/de
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
    • F03C1/0636—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
    • F03C1/0678—Control
    • F03C1/0681—Control using a valve in a system with several motor chambers, wherein the flow path through the chambers can be changed
    • 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
    • F04B1/2042—Valves
    • 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
    • F04B1/328—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 axis of the cylinder barrel relative to the swash plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/06—Control using electricity
    • F04B49/065—Control using electricity and making use of computers
    • 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
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/0076—Piston machines or pumps characterised by having positively-driven valving the members being actuated by electro-magnetic means

Definitions

  • This disclosure relates to the field of piston hydraulic devices such as pumps or motors, particularly to variable displacement piston hydraulic devices, and more particularly to the control of the fluid displacement and of management of early/late connection with the high/low pressure line in the piston hydraulic devices.
  • Piston hydraulic devices may be axial piston machines or radial piston.
  • the piston hydraulic devices may be operated as pumps or motors.
  • Variable axial piston hydraulic devices may be swash plate type devices or bent axis type devices.
  • Swash plate type axial piston devices have a tiltable swash plate that controls the stroke of the piston within a rotating cylinder block.
  • bent axis type axial piston devices the pistons are at an angle to the drive/ driven shaft.
  • the devices comprise a cylinder block carrying the pistons.
  • the cylinder block rotates about a first axis.
  • the devices also comprise a transmission shaft that rotates around a second axis of rotation, also called the transmission axis. Through this shaft mechanical work that is carried out for the compression of fluid (in the case of the pumps) or mechanical work (in the case of the motors) is determined by the pressure of the operating fluid.
  • the swash plate has a variable inclination to vary the stroke of the pistons between the dead points and, accordingly, the displacement of the machine.
  • the inclination of the plate is varied to change the stroke of the pistons.
  • bent-axis type device In bent-axis type device, the first and the second axis are incident. The relative inclination of these axes is varied to vary the stroke of the pistons between the dead points and, accordingly, the displacement of the machine. For varying displacement in the bent-axis type device, the inclination of the cylinder block is varied.
  • the device comprises a port plate having a first port and a second port for the connection of the chamber of each piston, alternately, to the high and low pressure line.
  • the first and second ports are angularly spaced relative to the first rotation axis.
  • the geometry of the first and second ports is fixed and defines the timing for the connection of the chamber of each piston to the high or the low pressure line relative to the dead points of piston travel.
  • the present disclosure is directed, at least in part, to improving or overcoming one or more aspects of the prior art system.
  • the present disclosure describes a piston hydraulic device comprising a cylinder block having a plurality of cylinder assemblies, the cylinder block being rotatable about a first rotation axis wherein each cylinder assembly comprises a cylinder and a piston; a first conduit for the passage of a fluid at a first pressure; a second conduit for the passage of a fluid at a second pressure wherein the first pressure is different from the second pressure; characterized in that, the piston hydraulic device further comprises a plurality of directional control valves fluidly connected to the first and second conduits and the respective cylinders wherein each directional control valve connects the respective cylinder to the first conduit in a first position and to the second conduit in a second position; and a controller operatively associated with the directional control valves for switching between the first and the second positions.
  • the present disclosure describes a method for controlling a piston hydraulic device.
  • the method comprises the steps of providing a cylinder block having a plurality of cylinder assemblies, the cylinder block being rotatable about a first rotation axis wherein each cylinder assembly comprises a cylinder and a piston; supplying or receiving a fluid at a first pressure through a first conduit; supplying or receiving a fluid at a second pressure through a second conduit wherein the first pressure is different from the second pressure; and actuating independently a plurality of directional control valves between a first and a second positions, the plurality of directional control valves being fluidly connected to the first and second conduits and the respective cylinders wherein each directional control valve connects the respective cylinder to the first conduit in the first position and to the second conduit in the second position.
  • This disclosure generally relates to a piston hydraulic device.
  • the device is configured to have continuous variation of fluid displacement and an efficient management of the timing for the connection of a cylinder assembly to the high or the low pressure line relative to the dead points of a piston stroke.
  • Fig. 1 schematically illustrates the piston hydraulic device 10 (hereinafter referred to as "device").
  • the device 10 is an axial piston hydraulic device.
  • the device 10 may be a radial piston hydraulic device.
  • the device 10 comprises a cylinder block 12, a first conduit 14, a second conduit 16, a plurality of directional control valves 56 and a controller 58.
  • the cylinder block 12 comprises a plurality of cylinder assemblies 24.
  • the cylinder block 12 is rotatable about a first rotation axis A (not shown).
  • the cylinder block 12 is rotatably supported in the device 10.
  • Cylinder block 12 is rotatably supported in a housing (not shown) of the device 10.
  • the cylinder assemblies 24 are radially positioned in the cylinder block 12 relative to the first rotation axis A.
  • the cylinder assemblies 24 are mutually angularly spaced.
  • the cylinder block 12 has first block surface 30 and a second block surface 32.
  • First and second block faces 30, 32 are formed on opposite sides of the cylinder block 12.
  • First and second block faces 30, 32 are parallel.
  • Each cylinder assembly 24 comprises a cylinder 26 and a piston 28.
  • the cylinders 26 have respective openings 34 on the first block surface 30.
  • Pistons 28 extend and retract in the cylinders 26. Pistons 28 extend from the openings 34.
  • Cylinders 26 have a base 36.
  • a cylinder conduit 48 extends from the base 36 to the second block face 32. Cylinder conduit communicates with the cylinder 26. Fluid enters and exits the cylinder 26 through the cylinder conduit 48.
  • Pistons 28 have a piston head 42 and a piston base 44. Piston head 42 is positioned external to the cylinder 26.
  • Piston base 44 travels in the cylinder 26 during a stroke of the piston 28. Piston base 44 may move towards the base 36 of the cylinder 26 at the end of the return stroke.
  • Each piston 28 moves along the respective cylinder 26 in parallel to the first rotation axis A.
  • Piston 28 defines a chamber 46 in the cylinder 26.
  • the chamber 46 varies in volume as the piston 28 extends and retracts in the cylinder 26. Change in the fluid in the chamber 46 acts on the piston base 44.
  • the chamber 46 varies in volume from a maximum volume which is reached when the piston 28 is at the top dead centre of an extraction stroke to a minimum volume which is reached when the piston 28 is at the bottom dead centre of a return stroke.
  • the first conduit 14 provides a passage of a fluid at a first pressure.
  • the second conduit 16 provides a passage of a fluid at a second pressure.
  • the first pressure is different from the second pressure.
  • the first pressure is higher than the second pressure.
  • a high pressure fluid flows along the first conduit 14 and a low pressure fluid flows along the second conduit 16.
  • the first pressure is lower than the second pressure.
  • a low pressure fluid flows along the first conduit 14 and a high pressure fluid flows along the second conduit 16.
  • the plurality of directional control valves 56 are fluidly connected to the first conduit 14. Each directional control valve 56 is independently fluidly connected to the first conduit 14. The first conduit 14 supplies/receives fluid at the first pressure to/from the plurality of directional control valves 56.
  • the plurality of directional control valves 56 are fluidly connected to the second conduit 16. Each directional control valve 56 is independently fluidly connected to the second conduit 16. The second conduit 16 supplies/receives fluid at the second pressure to/from the plurality of directional control valves 56.
  • Each directional control valve 56 is fluidly connected to the respective cylinder assembly 24. In a preferred embodiment, each directional control valve 56 is fluidly connected to the respective cylinder 26. In yet a preferred embodiment, each directional control valve 56 is fluidly connected to the respective cylinder 26 through the cylinder conduit 48. Each cylinder assembly 24 is fluidly connected to the respective directional control valve 56. In a preferred embodiment, each cylinder 26 is fluidly connected to the respective directional control valve 56. In yet a preferred embodiment, each cylinder 26 is fluidly connected to the respective directional control valve 56 through the cylinder conduit 48. The plurality of directional control valves 56 are each actuatable independently.
  • Fluid at a first pressure from the first conduit 14 is supplied to/sent out from the cylinder 26 through the respective directional control valve 56.
  • Fluid at a second pressure from the second conduit 16 is supplied to/sent out from the cylinder 26 through the respective directional control valve 56.
  • Each cylinder 26 receives/sends out either the fluid at the first pressure or the fluid at the second pressure from the respective directional control valve 56.
  • the at least one directional valve 56 is actuatable between a first position 57 and a second position 59.
  • the at least one directional valve 56 is actuatable between a first position 57 and a second position 59 through mechanical means.
  • the mechanical means is electronically controlled.
  • the mechanical means is an actuation member 60.
  • Actuation member 60 may be comprised in the at least one directional valve 56.
  • the actuation member 60 may operate in conjunction with a return spring 62.
  • the activation of the actuation member 60 may actuate the at least one directional valve 56 from the first position 57 to the second position 59.
  • the deactivation of the actuation member 60 permits the return spring 62 to return the at least one direction valve 56 from the second position 59 to the first position 57.
  • the directional control valve 56 is a three way two position valve.
  • Each directional control valve 56 connects the respective cylinder 26 to the first conduit 14 in the first position 57.
  • the piston 28 extends or retracts corresponding to the first fluid pressure relative to the fluid pressure in chamber 46.
  • the piston 28 extends or retracts correspondingly in regards to the pressure differential between the chamber 46 and the first pressure in the first conduit 14.
  • Each directional control valve 56 connects the respective cylinder 26 to the second conduit 16 in the second position 59.
  • the piston 28 extends or retracts corresponding to the second fluid pressure relative to the fluid pressure in chamber 46.
  • the piston 28 extends or retracts correspondingly in regards to the pressure differential between the chamber 46 and the second pressure in the second conduit 16.
  • the controller 58 is operatively associated with the plurality of directional control valves 56 for switching between the first and the second positions 57, 59. Controller 58 electronically sends signals to the actuation member 60 for actuation of the at least one directional control valve 56 between the first and the second positions 57, 59. In embodiment, controller 58 electronically sends signals to the actuation member 60 for actuation of the at least one directional control valve 56 from the first position 57 to the second position 59. Controller 58 comprises a programmable memory module. The memory module is programmable for the actuation of the at least one directional control valve 56. The timing and operation of the actuation may be performed in accordance to the programmable memory.
  • a controller 58 is connected to the plurality of directional control valves 56. In yet a further embodiment, a plurality of controllers 58 are connected to each directional control valve 56.
  • the device 10 may further comprises a positioning sensor 80.
  • the positioning sensor 80 senses the angular position of the cylinder block 12.
  • the positioning sensor 80 senses the angular position of a shaft [not shown].
  • the positioning sensor 80 is connected to the controller 58.
  • the positioning sensor 80 provides information of the angular position to the controller 58.
  • the information in relation to the angular position may be used to compute the timing of the connection of the respective cylinders 26 to the first or second conduit 14, 16.
  • the device 10 further comprises a plurality of connecting conduits 64.
  • the plurality of connecting conduits 64 are interposed between the plurality of directional control valves 56 and the respective cylinders 26.
  • Fig. 2 illustrates the device 10 as a swash plate type axial piston hydraulic device.
  • Device 10 comprises a housing 72.
  • a shaft 76 is coupled to the cylinder block 12.
  • shaft 76 may be a drive shaft.
  • shaft 76 may be a driven shaft.
  • shaft 76 may be coupled to a drive shaft.
  • shaft 76 may be coupled to a driven shaft.
  • the shaft 76 is rotatably supported by the housing 72 around the rotation axis A.
  • a swash plate 74 is coupled to the housing 72.
  • the shaft 76 is inserted passing through the swash plate 74.
  • the swash plate 74 has ring conformation.
  • the plurality of directional control valves 56 are coupled to the housing 72.
  • the directional control valves 56 are separately connected to the first and the second conduits 14, 16.
  • the cylinder block 12 is rotatably supported in the housing 72.
  • Pistons 28 are movably positioned in the respective cylinders 26. Pistons 28 are coupled to the swash plate 74.
  • the positioning sensor 80 is coupled to the housing 72.
  • the positioning sensor 80 is located to sense the angular position of the shaft 76.
  • a plurality of annular grooves 78 are interposed between the connecting conduits 64 and cylinder conduits 48.
  • the annular grooves 78 are defined in the housing 72.
  • Each annular groove 78 is fluidly connected to a respective directional control valve 56.
  • Sealing gaskets (not shown) are interposed between the annular grooves 78, the housing 72 and the cylinder block 12.
  • Fig. 3 illustrates the device 10, as a bent axis type axial piston hydraulic device.
  • Device 10 comprises a housing 72.
  • a shaft 76 is coupled to the cylinder block 12.
  • shaft 76 may be a drive shaft.
  • shaft 76 may be a driven shaft.
  • shaft 76 may be coupled to a drive shaft.
  • shaft 76 may be coupled to a driven shaft.
  • the shaft 76 is rotatably supported by the housing 72 around the rotation axis A.
  • the shaft 76 is rotatably supported by the housing 72 around a second rotation axis B inclined in respect of the first rotation axis A.
  • the plurality of directional control valves 56 are coupled to the housing 72.
  • the directional control valves 56 are separately connected to the first and the second conduits 14, 16.
  • the cylinder block 12 is rotatably supported in the housing 72.
  • Pistons 28 are movably positioned in the respective cylinders 26. Pistons 28 are coupled to the shaft 76.
  • the positioning sensor 80 is coupled to the housing 72. The positioning sensor 80 is located to sense the angular position of the shaft 76.
  • a plurality of annular grooves 78 are interposed between the connecting conduits 64 and cylinder conduits 48.
  • the annular grooves 78 are defined in the housing 72.
  • Each annular groove 78 is fluidly connected to a respective directional control valve 56.
  • Sealing gaskets (not shown) are interposed between the annular grooves 78, the housing 72 and the cylinder block 12.
  • the device 10 controls the displacement through the plurality of directional control valves 56.
  • the switching between the first and second conduit 14, 16 by the directional control valves 56 controls the level of fluid displacement and the timing of the fluid connection of the cylinders 26 to the first or the second conduit 14, 16 during the rotation about the first rotation axis A.
  • the actuation of the directional control valves 56 are in turn controlled by the controller 58.
  • Controller 58 controls the actuation of each directional control valve 56 for switching between the first and the second position 57, 59. Controller 58 controls the time in the first or second position 57, 59 as a function of the rotation speed. This enables the management of an early or late connection of the cylinders 46 with either the first or second conduit 14, 16 with respect to the travel of the piston 28 between the top or bottom dead points.
  • Continuous control of displacement of the axial piston hydraulic device 10 is effected over a complete rotation of the cylinder block 12.
  • the fluid displacement of a cylinder assembly 24 is control through the actuation of the directional control valve 56 over a rotation of 360 degrees of the cylinder block 12 relative to said cylinder assembly 24.
  • the device 10 is configured to operate as a hydraulic motor. In an alternate embodiment, the device 10 is configured to operate as a pump.
  • a method for controlling of a piston hydraulic device 10 comprising the following steps: providing a cylinder block 12 having a plurality of cylinder assemblies 24, the cylinder block 12 being rotatable about a first rotation axis A wherein each cylinder assembly 24 comprises a cylinder 26 and a piston 28; supplying/receiving a fluid at a first pressure through a first conduit 14; receiving/supplying a fluid at a second pressure through a second conduit 16 wherein the first pressure is different from the second pressure; and actuating independently a plurality of directional control valves 56 between a first and a second positions 57, 59, the plurality of directional control valves 56 being fluidly connected to the first and second conduits 14, 16 and the respective cylinders 26 wherein each directional control valve 56 connects the respective cylinder 26 to thefirst conduit 14 in the first position 57 and to the second conduit 16 in the second position 59.
  • the direction of rotation of the cylinder block 12 relative to the housing 72 is determined by relative pressures of the respective fluids flowing through the first and the second conduit 14, 16.
  • the cylinder block 12 may rotate in a first direction with a low pressure fluid flowing through the first conduit 14 and a high pressure fluid flowing through the second conduit 16.
  • the cylinder block 12 may rotate in a second direction with a high pressure fluid flowing through the first conduit 14 and a low pressure fluid flowing through the second conduit 16
  • the directional control valve 56 is actuated to the first position 57 for a rotation of 180 degrees of the respective cylinder assembly 24 about the rotational axis A.
  • the directional control valve 56 is actuated to the second position 59 for the following rotation of 180 degrees of the respective cylinder assembly 24 about the rotational axis A.
  • the first conduit 14 supplying/ receiving a high pressure fluid and the second conduit 16 supplying/ receiving a low pressure fluid or vice versa.
  • the cylinder assembly 24 operates normally and contributes 100 percent to fluid displacement over a complete rotation of the cylinder block 12 relative to the cylinder assembly 24.
  • the cylinder assembly 24 operates normally and contributes 100 percent to fluid displacement over a complete rotation of the cylinder block 12 about the rotational axis A.
  • the cylinder assembly 24 contributes to determining the fluid displacement for an amount equal to the difference between the maximum volume and the minimum volume of the corresponding chamber 46.
  • the directional control valve 56 is actuated to the first position 57 for a rotation of less than 180 degrees of the respective cylinder assembly 24 about the rotational axis A.
  • the directional control valve 56 is actuated to the second position 59 for the rotation of an angle for completion of the rotation of the respective cylinder assembly 24 about the rotational axis A.
  • the first conduit 14 supplying/ receiving a high pressure fluid and the second conduit 16 supplying/ receiving a low pressure fluid or vice versa.
  • the cylinder assembly 24 operates normally and contributes partially to fluid displacement over a complete rotation of the cylinder block 12 relative to the cylinder assembly 24.
  • the cylinder assembly 24 operates normally and contributes partially to fluid displacement over a complete rotation of the cylinder block 12 about the rotational axis A.
  • the cylinder assembly 24 contributes to determining the displacement only for a partial amount of the difference between the maximum volume and the minimum volume of the corresponding chamber 46.
  • the directional control valve 56 is actuated to either the first or the second position 57, 59 for a rotation of 360 degrees of the respective cylinder assembly 24 about the rotational axis A.
  • the cylinder assembly 24 is non-operational and does not contribute to fluid displacement over a complete rotation of the cylinder block 12 relative to the cylinder assembly 24.
  • the cylinder assembly 24 is non-operational and does not contribute to fluid displacement over a complete rotation of the cylinder block 12 about the rotational axis A.
  • This disclosure describes a piston hydraulic device 10 that has individually variable pistons.
  • the piston hydraulic device 10 provides for the continuous variation in fluid displacement.
  • the continuous variation of displacement is enabled without modifying the geometric configuration piston hydraulic device 10.
  • the relative inclination of the various structures such as the swash plate or the housing, are not varied to obtain the same objectives.
  • the device 10 manages efficiently the timing for the connection of a cylinder 26 to the high or the low pressure line (as determined by the fluid flowing in the first or second conduit 14, 16 relative to the dead points of piston 28 travel during the rotation about the rotational axis A.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Computer Hardware Design (AREA)
  • Reciprocating Pumps (AREA)
EP18425030.6A 2018-04-24 2018-04-24 Hydraulische kolbenvorrichtung Withdrawn EP3561298A1 (de)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP18425030.6A EP3561298A1 (de) 2018-04-24 2018-04-24 Hydraulische kolbenvorrichtung
PCT/EP2019/059889 WO2019206757A1 (en) 2018-04-24 2019-04-17 Piston hydraulic device

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP18425030.6A EP3561298A1 (de) 2018-04-24 2018-04-24 Hydraulische kolbenvorrichtung

Publications (1)

Publication Number Publication Date
EP3561298A1 true EP3561298A1 (de) 2019-10-30

Family

ID=62495735

Family Applications (1)

Application Number Title Priority Date Filing Date
EP18425030.6A Withdrawn EP3561298A1 (de) 2018-04-24 2018-04-24 Hydraulische kolbenvorrichtung

Country Status (2)

Country Link
EP (1) EP3561298A1 (de)
WO (1) WO2019206757A1 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2618342A (en) * 2022-05-03 2023-11-08 Domin Fluid Power Ltd A hydraulic device and a hydraulic system for controlling a hydraulic actuator

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10020453A1 (de) * 1999-04-27 2000-12-21 Komatsu Mfg Co Ltd Axialkolbenpumpe/-motor mit Antriebschaltung
DE102007030833A1 (de) * 2007-07-03 2009-01-08 Robert Bosch Gmbh Ventilgesteuerte Hydromaschine und Verfahren zu deren Ansteuerung
US20110031422A1 (en) * 2009-08-04 2011-02-10 Alejandro Lopez Pamplona Valve-controlled positive-displacement machine
US20110083553A1 (en) * 2009-10-14 2011-04-14 Michael Duerr Hydraulic machine
DE102015206721A1 (de) * 2015-04-15 2016-10-20 Robert Bosch Gmbh Schrägscheibenmaschine

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10020453A1 (de) * 1999-04-27 2000-12-21 Komatsu Mfg Co Ltd Axialkolbenpumpe/-motor mit Antriebschaltung
DE102007030833A1 (de) * 2007-07-03 2009-01-08 Robert Bosch Gmbh Ventilgesteuerte Hydromaschine und Verfahren zu deren Ansteuerung
US20110031422A1 (en) * 2009-08-04 2011-02-10 Alejandro Lopez Pamplona Valve-controlled positive-displacement machine
US20110083553A1 (en) * 2009-10-14 2011-04-14 Michael Duerr Hydraulic machine
DE102015206721A1 (de) * 2015-04-15 2016-10-20 Robert Bosch Gmbh Schrägscheibenmaschine

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2618342A (en) * 2022-05-03 2023-11-08 Domin Fluid Power Ltd A hydraulic device and a hydraulic system for controlling a hydraulic actuator

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Publication number Publication date
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