EP3085960A1 - Hydraulikflüssigkeitsverteiler und hydraulikflüssigkeitverteilungsverfahren - Google Patents

Hydraulikflüssigkeitsverteiler und hydraulikflüssigkeitverteilungsverfahren Download PDF

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Publication number
EP3085960A1
EP3085960A1 EP16165248.2A EP16165248A EP3085960A1 EP 3085960 A1 EP3085960 A1 EP 3085960A1 EP 16165248 A EP16165248 A EP 16165248A EP 3085960 A1 EP3085960 A1 EP 3085960A1
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EP
European Patent Office
Prior art keywords
fluid
outlet
supplying
hydraulic
supplying device
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Granted
Application number
EP16165248.2A
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English (en)
French (fr)
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EP3085960B1 (de
Inventor
Willem Jacobus Reijersen Van Buuren
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Forage Co BV
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Forage Innovations BV
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Publication of EP3085960A1 publication Critical patent/EP3085960A1/de
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    • 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
    • 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
    • F04B1/2035—Cylinder barrels

Definitions

  • the invention refers to a hydraulic fluid distributor and to a method for distributing hydraulic fluid onto two hydraulic actuators, in particular for supplying fluid to two parallel piston-cylinder units mounted on board of an agricultural harvester.
  • DE 102011077253 A1 discloses an axial piston pump (Axialkolbenpumpe) and an axial piston motor (Axialkolbenmotor).
  • a first sequence 16 of piston-cylinder units is arranged along a first, inner circle 58 positioned around a rotating axis 10, cf.
  • a second sequence 38 is arranged along a second, outer circle 60 positioned around the axis 10.
  • the sequences 16, 38 of piston-cylinder units 16, 38 are arranged within a piston drum (Kolbentrommel 36), cf. the side views of Fig. 4 and Fig. 5 and the view parallel to the axis 10 presented by Fig. 6.
  • the piston drum 36 is rotated around the axis 10 with respect to a control element (Steuerelement 56), cf. Fig. 7.
  • Two inner kidney-shaped apertures 74, 76 and two outer kidney-shaped apertures 78, 80 are arranged around the center axis.
  • the apertures 76, 80 provide fluid with different low pressure values (Niedertik N1, N2).
  • the apertures 74, 78 provide fluid with different high pressure values (Hochtik H1, H2).
  • US 4,549,466 discloses a split-type hydraulic oil piston pump with a cylinder block 1.
  • the cylinder block 1 can rotate jointly with a rotating shaft 6.
  • Several pistons 3 are fitted into several cylinder bores 2 which are disposed concentrically around the shaft 6.
  • Several cylinder chambers 4 are provided between the pistons 3 and the walls of the bores 2.
  • the cylinder block 1 can rotate with respect to a valve plate 8 mounted at a valve body 7.
  • a suction slot 9 in the valve plate 8 always opens to a suction port 11 in the valve body 7.
  • Several delivery slots 10_1, 10_2, 10_3 in the valve plate 8 always opens to several delivery ports 12_1, 12_2, 12_3 in the valve body 7, cf. Fig. 2 .
  • the delivery ports 12_1, 12_2, 12_3 are in fluid communication with hydraulic actuators A_1, A_2 which are to be supplied with fluid.
  • a hydraulic fluid is supplied through the suction port 11 into the cylinder chambers and is equally distributed onto the delivery ports 12_1, 12_2, 12_3.
  • JPS 50-083803 A2 discloses a hydraulic axial pump with two delivery slots B, C. By means of these two delivery slots B, C hydraulic flow is shared onto two hydraulic actuators.
  • a problem solved by the invention is to provide a hydraulic fluid distributor with the features of the preamble of claim 1 and a hydraulic fluid distributing method with the features of the preamble of claim 16 wherein both hydraulic actuators can be supplied with fluid such that a significant difference in the amounts or amounts per time of the supplied fluid between the two hydraulic actuators is avoided.
  • the hydraulic fluid distributor according to the invention supplies hydraulic fluid to a first hydraulic actuator and to at least one second hydraulic actuator.
  • the hydraulic fluid distributor according to the invention comprises
  • the fluid-supplying device comprises
  • a first group of outlet apertures and a second group of outlet apertures are cut into the plate. Every outlet group comprises at least two outlet apertures, i.e. at least four outlet apertures are cut into the plate.
  • the outlet apertures of both outlet groups are positioned around a center axis. The common or maximal distance between the midpoints of the outlet apertures of the second outlet group and this center axis is smaller than the common or minimal distance between the outlet apertures of the first outlet group and this center axis.
  • the first fluid connecting device establishes permanently or temporarily a fluid communication between every outlet aperture of the first outlet group and the first hydraulic actuator.
  • the second fluid connecting device establishes permanently or temporarily a fluid communication between every outlet aperture of the second outlet group and the second hydraulic actuator. After the fluid is conveyed through an outlet aperture, the connected fluid connecting device supplies fluid to the connected hydraulic actuator - independently from the current rotational position of the fluid-supplying device with respect to the plate.
  • the fluid-supplying device can be rotated with respect to the plate around that center axis around which the outlet apertures are positioned in the plate.
  • the center axis therefore serves as a rotating axis.
  • the fluid-supplying device and the plate together fulfill the following constraint in every rotational position and therefor that every time point:
  • the first fluid-supplying opening overlaps either with at least one outlet aperture of the first outlet group or with no outlet aperture but does not overlap with an outlet aperture of the second outlet group.
  • the second fluid-supplying opening overlaps either with at least one outlet aperture of the second outlet group or with no outlet aperture but does not overlap with an outlet aperture of the first outlet group.
  • the outlet apertures of the first outlet group and the outlet apertures of the second outlet group are positioned in an alternating sequence around the center axis in the plate. This means: Every outlet aperture of the first outlet group is positioned adjacent to at least one outlet aperture of the second outlet group. Every outlet aperture of the second outlet group is positioned adjacent to at least one outlet aperture of the first outlet group. At least one outlet aperture of the first outlet group is positioned between two outlet apertures of the second outlet group. At least one outlet aperture of the second outlet group is positioned between two outlet apertures of the first outlet group.
  • the fluid distributor operates as follows:
  • the hydraulic fluid distributor at least two different hydraulic actuators can be supplied with fluid from the same fluid reservoir. It suffices to provide one device for conveying the fluid to both actuators, e.g. a pump or a piston-cylinder unit. Thanks to the two fluid-supplying openings and to the two outlet groups the same fluid-supplying device can supply fluid to at least two different hydraulic actuators. It is possible but thanks to the invention not necessary that the fluid-supplying device comprises several fluid-providing units, e.g. several piston-cylinder units. It is also possible that one piston-cylinder unit or one pump serves both fluid-supplying openings.
  • the fluid-supplying device can operate in a continuous manner.
  • the drive for rotating the fluid-supplying device can also operate in a continuous manner.
  • a pump for conveying fluid to the fluids supplying device can also operate in a continuous manner. Neither the pump nor the drive need to be operated in a start-stop operation. It is not necessary to provide a controllable valve for regulating the flow of fluid. It is not necessary that a sensor measures the fluid pressures or fluid amounts supplied to the hydraulic actuators and to compare the measured values in order to detect a high difference when supplying the actuators.
  • the plate reduces the pressure variations in the hydraulic flow to one hydraulic actuator.
  • a fluid connecting device does sometimes not convey fluid to a hydraulic actuator, namely as long as no outlet aperture of the corresponding outlet group overlaps with a fluid-supplying opening.
  • a cavity of the fluid-supplying device connected with the fluid-supplying opening is temporarily blocked by the plate and stores fluid until one outlet aperture of this fluid connecting device overlaps with a fluid-supplying opening.
  • every hydraulic actuator can be brought into in fluid communication subsequently with at least two different outlet apertures of the same outlet group.
  • Every outlet group comprises several outlet apertures. All outlet apertures of one outlet group are connected with this hydraulic actuator by means of one fluid connecting device. Thereby the hydraulic actuator can be supplied with fluid even if the undesired event occurs that one outlet aperture or one line from an outlet aperture to the actuator is permanently blocked, i.e. the invention provides redundancy.
  • the invention enables a simple mechanical construction.
  • the drive can rotate this fluid-supplying device with a constant velocity. No acceleration and deceleration and no start-stop operation needs to be performed. Therefore the drive does not need to provide much kinetic energy.
  • the fluid-supplying device can operate independently from its rotational position with respect to the plate.
  • the outlet apertures of the first outlet group can be positioned at every desired rotational position in the plate - provided that the constraint referring to the distances is fulfilled.
  • the outlet apertures of the second outlet group can also be positioned at every desired rotational position in the plate. This makes it easier to arrange the fluid-supplying device and the fluid connecting devices, in particular if the hydraulic fluid distributor is mounted on board of a vehicle.
  • the operation of the fluid distributor does not depend on the exact proper position of the outlet apertures in the plate. Therefore the operation is less subjected to variations during manufacturing the plate with the apertures, the positions of the fluid-supplying openings with respect to the plate, and to variations in rotating the fluid-supplying device.
  • the invention provides different degrees of freedom for adapting the fluid distributor to constraints and requirements of the hydraulic actuators and to the available space, in particular the following degrees of freedom while constructing and designing the distributor:
  • the plate providing the outlet apertures is stationary and the fluid-supplying device is rotated with respect to the stationary plate. It is also possible that the plate with the outlet apertures is rotated, e.g. in an oscillating manner, around the rotating axis.
  • the fluid-supplying device may be a stationary device.
  • the fluid-supplying device is rotated in the same direction, preferably with the same velocity and without an interruption during the operation.
  • the fluid-supplying device is alternatively rotated in one direction and in the opposite direction around the axis, i.e. the fluid-supplying device performs an oscillating movement around the center axis. This alternative embodiment saves the need that the fluid-supplying device performs a full rotation around the center axis.
  • the distance between the midpoint of the second fluid-supplying opening of the fluid-supplying device and the rotating axis is smaller than the distance between the midpoint of the first fluid-supplying opening of the fluid-supplying device and the rotating axis.
  • the second fluid-supplying device is entirely positioned within a circle around the rotating axis.
  • the first fluid-supplying opening is entirely positioned outside of this circle.
  • the first fluid-supplying opening either overlaps with exactly one or with no outlet aperture of the first outlet group - depending on the rotational position of the fluid-supplying device.
  • the first fluid-supplying opening overlaps in at least one rotational position simultaneously with at least two outlet apertures of the first outlet group.
  • the second fluid-supplying opening always overlaps with exactly one or with no outlet aperture of the second outlet group or may in at least one rotating position simultaneously overlap with two outlet apertures of the second outlet group.
  • either the first hydraulic actuator or the second hydraulic actuator is supplied with hydraulic fluid at one time point. At no time point both actuators are simultaneously supplied with fluid.
  • the hydraulic fluid distributor is arranged such that the following event cannot occur: The first fluid-supplying opening overlaps with one outlet aperture of the first outlet group. Simultaneously, i.e. in the same rotational position and therefore at the same time, the second fluid-supplying opening overlaps with one outlet aperture of the second outlet group.
  • the fluid for the hydraulic actuators is taken from a reservoir. It is possible that the reservoir is also rotated with respect to the plate around the rotating axis.
  • the following embodiment saves the need to rotate the reservoir.
  • This embodiment enables to provide a stationary reservoir.
  • This reservoir can be arranged on board of a vehicle with the hydraulic actuators outside of it, e.g. on board of the propelled vehicle.
  • the fluid-supplying device performs at least one sucking stroke and at least one supplying stroke while performing one full rotation around the center axis.
  • the distributor part providing the plate with the outlet apertures and the connecting devices are stationary parts.
  • a reservoir for the fluid can also be a stationary part. Only the fluid-supplying device needs to be rotated. This embodiment enables an even more robust construction. In place of a full rotation the fluid-supplying device can also perform oscillating movements between a position for a sucking stroke and a position for a supplying stroke.
  • the fluid-supplying device In a sucking stroke the fluid-supplying device sucks fluid into at least one cavity. In a supplying stroke the fluid-supplying device presses fluid out of the cavity towards a hydraulic actuator as long as the fluid-supplying opening overlaps with an outlet aperture which is in fluid connection with this hydraulic actuator.
  • the fluid-supplying device performs at least one full rotation around the rotating axis.
  • the entire amount of fluid which is ejected out of the first fluid-supplying opening during one full rotation is substantially equal to the entire fluid amount ejected out of the second fluid-supplying opening.
  • the entire amount of fluid supplied to the outlet apertures of the first group is substantially equal to the entire amount of fluid is supplied to the outlet apertures of the second group.
  • Both hydraulic actuators obtain substantially the same amount of fluid in the timespan of one full rotation.
  • every outlet aperture of the first outlet group and the first fluid-supplying opening have the same (larger) distance to the rotating axis.
  • Every outlet aperture of the second outlet group and the second fluid-supplying opening have the same (smaller) distance to the rotating axis.
  • the tangential velocity of a point which rotates around an axis is 2 ⁇ ⁇ d wherein ⁇ is the current angular velocity and d is the distance between the point and the axis. Therefore the time in which an outlet aperture overlaps with a fluid-supplying opening depends not only on the maximal overlapping area and the angular velocity but also on the distance between the overlapping area and the rotating axis. The larger the distance is the smaller is the timespan of overlapping and thereby the amount of fluid conveyed through the overlapping area.
  • the following embodiment substantially compensates this effect and inhibits a significant difference in the amount of fluid supplied to the hydraulic actuators.
  • the symbols have the following meanings:
  • the first fluid-supplying opening has the same area as the second fluid-supplying opening.
  • the fluid-supplying device is rotated with constant velocity around the rotating axis. If the equation mentioned above and these constraints are fulfilled, the amount through the first fluid-supplying opening is equal to the amount through the second fluid-supplying opening despite of different distances. It is possible to adapt the constraint mentioned above to fluid-supplying openings with different areas.
  • the fluid-supplying device comprises two fixed fluid-supplying openings which do not move with respect to the rest of the fluid-supplying device.
  • the fluid-supplying device comprises one fixed opening and a rotated or otherwise moved element which comprises at least one opening being smaller than the fixed opening.
  • the element with smaller opening can be moved with respect to the fixed opening.
  • the movement of the element with the smaller opening selectively provides the first fluid-supplying opening or the second fluid-supplying opening - depending on the position of the moved element with respect to the fixed opening.
  • the smaller opening temporarily overlaps with the fixed larger opening in a first position or in a second position, thereby providing the first or the second fluid-supplying opening.
  • this moveable element comprises two openings which provides the first and the second fluid-supplying openings.
  • the distance between two adjacent outlet apertures is larger than the dimension of these adjacent outlet apertures in the rotating direction of the fluid-supplying device. This embodiment enables a quite constant hydraulic pressure at the outlet apertures even if a pump or further fluid source provides fluid with larger pressure variations. A cavity behind a fluid-supplying opening is sometimes blocked by the plate such that fluid is stored.
  • the fluid-supplying openings are cut into a further plate.
  • the fluid-supplying device and the further plate can rotate around the center axis.
  • the further plate is rigidly mounted at or connected with the fluid-supplying device.
  • the drive rotates the fluid-supplying device and the rotatable further plate around the center axis.
  • This embodiment increases the reliability that the fluid-supplying openings are properly positioned with respect to the outlet apertures in the plate despite of manufacturing tolerances.
  • the plate with the outlet apertures and the rotatable further plate with the fluid-supplying openings extend in two parallel planes. Preferably both planes are perpendicular to the rotating axis.
  • the fluid-supplying device comprises at least one piston-cylinder unit. Every fluid-supplying opening of the fluid-supplying device is in fluid communication with one chamber of the or with one piston-cylinder unit of the fluid-supplying device.
  • one piston-cylinder unit is in fluid communication with both fluid-supplying openings and can eject fluid through both fluid-supplying openings.
  • the fluid-supplying device comprises two piston-cylinder units, one unit for one fluid-supplying opening.
  • the plate can have the shape of a disk or an ellipse or of a rectangle, e.g.
  • the respective edge of a fluid-supplying opening can have the shape of a circle, and ellipse, or a rectangle, e.g.
  • the distributor for this application comprises three outlet groups each comprising at least two outlet apertures, i.e. at least six outlet apertures.
  • the fluid-supplying device comprises three fluid-supplying openings. In every rotational position every fluid-supplying opening either overlaps with no outlet aperture or with at least one outlet aperture, always from the same outlet group.
  • the outlet apertures are positioned with different distances in an alternating sequence in the plate, e.g. according to the following sequence:
  • the fluid-supplying device can be driven by a shaft, a chain, or a hydraulic or electric motor, e.g.
  • the fluid supplied to the actuator can be a hydraulic oil or pressurized air e.g. It can also be or contain a lubricating fluid for greasing the hydraulic actuators.
  • the hydraulic fluid distributor is mounted on board of an agricultural vehicle which is moved over ground.
  • a source of hydraulic fluid can be mounted on board of the vehicle itself or can be mounted on board of a further vehicle which pulls or pushes the vehicle with the fluid distributor, e.g. on board of an tractor.
  • the invention is used on board of an agricultural harvester.
  • This harvester is self-propelled or pulled by a motorized vehicle, e.g. by a tractor, and
  • Two parallel hydraulic actuators on board of the harvester have to jointly move a harvester part, e.g. have to jointly
  • This movement must often be performed against the expanding force of compressed crop material or against the force of gravity.
  • a source for supplying the hydraulic actuators with a fluid can be mounted on a board of the harvester itself or on board of the propelled vehicle pulling or pushing the harvester.
  • both actuators In order to perform the movement properly, both actuators must be supplied with approximately the same amount of hydraulic fluid at every time of the movement. Significant variations in the amount of supplied fluid may cause the moved part to cant or not to work properly and may cause undesired and harmful mechanical stress. Therefore a hydraulic fluid distributor according to the invention is mounted on board of the harvester.
  • Fig. 1 and Fig. 2 show the embodiment in a viewing direction perpendicular to the rotating axis, e.g. in a horizontal viewing direction.
  • the first hydraulic actuator comprises a first hydraulic piston-cylinder unit 20 and the second hydraulic actuator comprises a second hydraulic piston-cylinder unit 21.
  • Fig. 1 and Fig. 2 show a fluid source 19 which can be mounted on board of the harvester or the pulling or pushing vehicle.
  • Fig. 1 and Fig 2 further show the following parts of the hydraulic fluid distributor according to the embodiment of the invention:
  • piston-cylinder devices 10, 11, the rotatable disk 5, the rocker arm 12, and the drives 6, 7 together form the fluid-supplying device of the embodiment. It is also possible that one piston-cylinder unit is connected with both fluid-supplying openings. In the place of two piston-cylinder unit 10, 11 or one piston-cylinder unit it is possible to provide one or two hydraulic accumulators which are connected with the fluid-supplying openings 13, 14 and which are rotated around the center axis CA. A stationary pump can fill the accumulators with fluid from the reservoir 19. An accumulator can press the fluid through an outlet aperture towards the hydraulic actuator 20, 21.
  • the fluid-supplying opening 13 of the piston-cylinder device 10 serves as the first fluid-supplying opening and the fluid-supplying opening 14 serves as the second fluid-supplying opening. Both fluid-supplying openings 13, 14 are cut into the rotatable disk 5.
  • the entire fluid supplying device 10, 11 can be rotated around a center axis CA (in the drawing planes of Fig. 1 and Fig. 2 ).
  • the disks 3, 5 extend in two parallel planes which are perpendicular to the center axis CA and to the drawing planes of Fig. 1 and Fig. 2 .
  • the disk 3 serves as the plate of the claims and is stationary, i.e. cannot be moved with respect to the fluid connecting lines 31.x, 32.x or with respect to the fluid connectors 8.x.
  • the rotatable disk 5 serves as the further plate.
  • the pivoting axis PA of the rocker arm 12 is also perpendicular to the drawing planes of Fig. 1 and Fig. 2 .
  • the piston 15 of the first piston-cylinder unit 10 separates a base-side chamber 17 from a rod-side chamber.
  • the piston 16 of the second piston-cylinder unit 11 separates a base-side chamber 18 from a rod-side chamber. Both base-side chambers 18, 19 serve as a cavity for hydraulic fluid.
  • the fluid-supplying openings 13, 14 are cut into the rotatable disk 5 which serves as the further plate. In the embodiment both fluid-supplying openings 13, 14 have the same cross-section area.
  • the outlet apertures 1.x, 2.x and the inlet apertures 4.x are cut into the stationary disk 3.
  • the center axis CA (in the drawing planes of Fig. 1 and Fig. 2 ) forms the common middle axis of the stationary disk 3 and of the rotatable disk 5 and serves as the rotating axis.
  • Fig. 3 shows the stationary disk 3 in a viewing direction parallel to the center axis CA.
  • the outlet apertures 1.1, 1.2, ... of the first outlet group and the outlet apertures 2.1, 2.2, ... of the second outlet group are positioned in the upper half of the stationary disk 3, i.e. above the line 36 through the center axis CA.
  • Several inlet apertures 4.1, 4.2, ... are positioned in the lower half below the line 36.
  • the current positions of the fluid-supplying openings 13, 14 are sketched.
  • every outlet aperture 1.1, 1.2, ..., 2.1, 2.2, ... has the same cross-sectional area.
  • Every inlet aperture 4.x has the same cross-section area which is larger than that of an outlet aperture. It is also possible that one inlet aperture 4.x is larger than a further inlet aperture or that one outlet aperture 1.x, 2.x is larger than a further outlet aperture. It is possible that an outlet aperture 1.x is larger or smaller than the first fluid-supplying opening 13. It is further possible that an outlet aperture 2.x is larger or smaller than the second fluid-supplying opening 14.
  • the number of outlet apertures 1.x of the first outlet group, the number of outlet apertures 2.x of the second outlet group, and/or the number of inlet apertures 4.x can differ from each other.
  • outlet apertures 1.x, 2.x and the inlet apertures 4.x are circular. Other shapes are possible, in particular kidney or elliptic shapes.
  • the fluid-supplying openings 13, 14 are cut into the rotatable disk 5.
  • the midpoint of the second fluid-supplying opening 14 and the respective midpoint of every outlet aperture 1.x have a common distance d1 to the center axis CA.
  • the midpoint of the first fluid-supplying opening 13 and the respective midpoint of every outlet aperture 2.x have a common distance d2 to the center axis CA.
  • the distance d1 is larger than the distance d2.
  • the respective center point of an outlet aperture 2.x has the distance d2 to the center axis CA.
  • the m outlet apertures 1.1, 1.2, ... of the first outlet group are positioned in an outer torus 41 which is defined by the circumferential surface 51 of the disk 3 and by an outer circle 52.
  • the n outlet apertures 2.1, 2.2, ... of the second outlet group are positioned in an inner torus 42 which is defined by the outer circle 52 and an inner circle 53 in the interior of the outer circle 52. Both circles are concentrically positioned around the center axis CA.
  • the outlet apertures 1.1, 1.2, ... are therefore positioned outside of the outer circle 52 and the outlet apertures 2.1, 2.2, ... inside of it.
  • every outlet aperture 1.x, 2.x touches the outer circle 52.
  • every fluid-supplying opening 13, 14 overlaps either with exactly one outlet aperture 1.x, 2.x or with no outlet aperture - depending on the current rotational position of the fluid-supplying device 10, 11.
  • the rotation-creating drive 7 rotates the following parts around the center axis CA and thereby with respect to the stationary disk 3:
  • the rotation-creating drive 7 rotates these parts in a continuous operation with constant angular velocity - at least as long as the actuator 20, 21 are to be supplied with fluid.
  • the cylinders of the piston-cylinder units 10, 11 move around the center axis CA and do not perform a movement relative to the rotatable disk 5 and perpendicular to the center axis CA while being rotated.
  • the oscillation-creating drive 6 oscillates the rotated rocker arm 12 around the pivoting axis PA which is perpendicular to the center axis CA and perpendicular to the drawing plane of Fig. 1 and Fig. 2 .
  • a guiding rail for the rocker arm 12 can be used. This guiding rail (not shown) urges the rotated rocker arm 12 to oscillate around the pivoting axis PA when being rotated around the center axis CA.
  • Both implementations (drive 6 or guiding rail) force the rocker arm 12 to rotate around the center axis CA and to oscillate around the pivoting axis PA (perpendicular to the center axis CA and to the drawing planes of Fig. 1 and Fig. 2 ) while being rotated around the center axis CA.
  • the rocker arm 12 is rotated around the center axis CA by the drive 7.
  • the rocker arm 12 is moved such that both pistons 15, 16 of the piston-cylinder units 10, 11 simultaneously perform one sucking stroke and subsequently one supplying stroke.
  • the sucking stroke is performed while both fluid-supplying openings 13, 14 are positioned adjacent to the lower half of the stationary disk 3 (below the line 36 in Fig. 3 ).
  • the supplying stroke is performed while both fluid-supplying openings 13, 14 are positioned sufficiently adjacent to the upper part (above the line 36).
  • the two fluid-supplying openings 13, 14 are positioned close to each other.
  • the piston-cylinder units 10, 11 have substantial the same dimensions.
  • Fig. 1 illustrates a sucking stroke.
  • the pistons 15, 16 are moved away from the fluid-supplying openings 13, 14.
  • the outlet apertures 1.x, 2.x are blocked by the rotatable disk 5 during a sucking stroke.
  • Every fluid-supplying opening 13, 14 serves as a cylinder inlet.
  • the size of every inlet aperture 4.x is sufficiently big such that every fluid-supplying opening 13, 14 temporarily overlaps with at least one inlet aperture 4.x in every rotational position during a sucking stroke. In some rotational positions of the disk 5 both fluid-supplying openings 13, 14 overlap with the same inlet aperture 4.x.
  • a pump conveys or presses fluid from the reservoir 19 through the fluid connectors 8.1, 8.2, ... to the disk 3 and thereby supports a sucking stroke. It is also possible that the fluid is only taken out of the reservoir 19 by means of the piston-cylinder units 10, 11.
  • Fig. 2 shows a supplying stroke.
  • the pistons 15, 16 are moved towards the fluid-supplying openings 13, 14.
  • the inlet apertures 4.x are blocked by the rotatable disk 5 during a supplying stroke.
  • Every fluid-supplying opening 13, 14 serves as a cylinder outlet. If the fluid-supplying opening 13 of the first piston-cylinder unit 10 overlaps with an outlet aperture 1.x of the first outlet group, the piston 15 presses fluid out of the base-side chamber 17 through the fluid-supplying opening 13 now serving as a cylinder outlet, the outlet aperture 1.x, and the fluid connecting line 31.x to the first hydraulic actuator 20. Thereby the first hydraulic actuator 20 is supplied with fluid. In this rotational position no further outlet aperture overlaps with a fluid-supplying opening 13 or 14.
  • the piston 16 presses fluid out of the base-side chamber 18 through the second fluid-supplying opening 14 now serving as a cylinder outlet, the outlet aperture 2.x, and the fluid connecting line 32.x to the second hydraulic actuator 21. Thereby the second hydraulic actuator 21 is supplied with fluid.
  • the first fluid-supplying opening 13 never (in no rotational position of the disk 5) overlaps with a second outlet aperture 2.x and the second fluid-supplying opening 14 never overlaps with a first outlet aperture 1.x. Therefore the first actuator 20 is only supplied with fluid pressed out of the base-side chamber 17.
  • the second actuator 21 is only supplied with fluid pressed out of the base-side chamber 18.
  • the midpoints of the two fluid-supplying openings 13, 14 and an intersection between the rotatable disk 5 and the center axis CA are on one line L (cf. Fig. 3 ).
  • the distance between the midpoints of the two fluid-supplying openings 13, 14 can be larger such that it is possible that one piston-cylinder unit 10, 11 performs a sucking stroke and the other piston-cylinder unit 10, 11 performs at the same time a supplying stroke.
  • both actuators 20, 21 are supplied with substantially the same amount of fluid during a supplying stroke. It is also possible to supply the first actuator 20 with a fluid amount of F1 and the second actuator 21 with a fluid amount of F2 whereas F1 significantly differs from F2.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
EP16165248.2A 2015-04-20 2016-04-14 Hydraulikflüssigkeitsverteiler und hydraulikflüssigkeitverteilungsverfahren Not-in-force EP3085960B1 (de)

Applications Claiming Priority (1)

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NL2014672A NL2014672B1 (en) 2015-04-20 2015-04-20 Hydraulic fluid distributor and hydraulic fluid distributing method.

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EP3085960A1 true EP3085960A1 (de) 2016-10-26
EP3085960B1 EP3085960B1 (de) 2018-06-06

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0044070A1 (de) * 1980-07-15 1982-01-20 Linde Aktiengesellschaft Axialkolbenpumpe für zwei Förderströme
US4549466A (en) 1983-04-27 1985-10-29 Kabushiki Kaisha Komatsu Seisakusho Split type oil hydraulic piston pump and pressurized oil feed circuit making use of the same pump
WO2003091571A1 (en) * 2002-04-26 2003-11-06 Rousset Patrick W Circumferential piston machines
DE102011077253A1 (de) 2011-06-09 2012-12-13 Robert Bosch Gmbh Axialkolbenmaschine in Schrägscheibenbauweise

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0044070A1 (de) * 1980-07-15 1982-01-20 Linde Aktiengesellschaft Axialkolbenpumpe für zwei Förderströme
US4549466A (en) 1983-04-27 1985-10-29 Kabushiki Kaisha Komatsu Seisakusho Split type oil hydraulic piston pump and pressurized oil feed circuit making use of the same pump
WO2003091571A1 (en) * 2002-04-26 2003-11-06 Rousset Patrick W Circumferential piston machines
DE102011077253A1 (de) 2011-06-09 2012-12-13 Robert Bosch Gmbh Axialkolbenmaschine in Schrägscheibenbauweise

Also Published As

Publication number Publication date
NL2014672A (en) 2016-10-24
NL2014672B1 (en) 2017-01-20
EP3085960B1 (de) 2018-06-06

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