EP2831427A1 - Dispositif hydraulique d'entraînement en rotation - Google Patents

Dispositif hydraulique d'entraînement en rotation

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Publication number
EP2831427A1
EP2831427A1 EP13725056.9A EP13725056A EP2831427A1 EP 2831427 A1 EP2831427 A1 EP 2831427A1 EP 13725056 A EP13725056 A EP 13725056A EP 2831427 A1 EP2831427 A1 EP 2831427A1
Authority
EP
European Patent Office
Prior art keywords
hydro
rotary
rotary actuator
drive
working chambers
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.)
Granted
Application number
EP13725056.9A
Other languages
German (de)
English (en)
Other versions
EP2831427B1 (fr
Inventor
Reinhard Diem
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Individual
Original Assignee
Individual
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Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of EP2831427A1 publication Critical patent/EP2831427A1/fr
Application granted granted Critical
Publication of EP2831427B1 publication Critical patent/EP2831427B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/12—Fluid oscillators or pulse generators
    • F15B21/125—Fluid oscillators or pulse generators by means of a rotating valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/12—Characterised by the construction of the motor unit of the oscillating-vane or curved-cylinder type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/18—Combined units comprising both motor and pump

Definitions

  • the invention relates to a hydro-rotary oscillator, comprising at least one continuously driven hydro-rotary pump which generates a continuous hydro-fluid flow, with a hydro-rotary actuator driven by the hydro-fluid flow, the fully cylindrical rotary actuator inner part and at least one hollow-cylindrical rotary actuator outer part which are arranged concentrically to one another with radial spacing, radially define at least two annular segment-shaped working chambers and are rotatable limited in two directions of rotation, wherein the working chambers by a co-rotating radially extending Drehstellgliedwand separated and resizable and with the Hydro-rotary pump are connected via hydraulic connection lines, and with at least one control means which directs the hydro-fluid flow alternately to the at least two working chambers, said at least one Drehstellglied- outer part rotatable and the Drehstellgl ied inner part is formed rotatably.
  • Such hydraulic rotary drive devices with a hydro-rotary pump and a hydro-rotary actuator driven by this, are known from the prior art in various embodiments.
  • Conventional hydro-rotary pumps usually produce a quasi-continuous fluid flow from a hydraulic fluid, which also remains constant, as a rule, when a pressure builds up in the hydraulic system through resistors such as throttle points, switching elements or drives.
  • Such hydraulic pumps are common designed as vane, gear or screw pumps and can operate in an open or closed circuit. In the closed circuit, the hydro-rotary pump with its suction side and with its pressure side, depending on the number of working chambers of the hydro-actuator, at the same time directly or alternately via a control means, such as a hydraulic multi-way valve, connected to the hydro-actuator.
  • Hydro actuators are known as axial piston or rotary piston actuators.
  • Known hydro-rotary actuators have a rotor and a stator, usually one in a housing (stator) sealed rotatably mounted rotary piston (rotor).
  • Such hydro-rotary actuators usually have at least two working chambers, which are formed by an annular gap portion between the housing and the rotary piston. The working chambers are radially bounded by the housing and the rotary piston and in the circumferential direction of stops of the housing and a rotary wing extension of the rotary piston, which extend radially.
  • Such a hydro-rotary actuator is known from the published patent application DE 102 10 756 A1.
  • This document discloses a rotary piston device with a cylindrical housing which is sealed frontally with bearing caps and in which a piston-shaft-mounted rotary piston is finally rotatable in both directions up to a maximum of a non-rotatable stop body with two lateral stops, wherein the stopper body substantially medium-tight between the cylinder wall and the piston shaft and with respect to the bearing cap is arranged.
  • the rotary piston has a radially extending blade extension, which, together with the stopper body, divides the total displacement as a function of the position of the rotary piston into two working chambers, a pressure chamber and a suction chamber.
  • the two working chambers are alternately used as pressure and suction chambers, i. alternately connected to the pressure and the suction side of a hydro-rotary pump, for example via a hydraulic multi-way valve.
  • a disadvantage is considered in this known hydraulic rotary drive device that the rotor is arranged inside and thus the coupling with a lever arm or the like of an external device is difficult, and that the hydro-rotary pump indirectly via at least one switching valve with the two working chambers of the hydraulic rotary actuator connected, which reduces the maximum oscillation speed of the rotary piston.
  • the invention has the object to provide a way to simplify the coupling to the rotor and the oscillation frequency of the rotor is increased. This object is achieved by a hydro-rotary oscillator with the features of claim 1. Further advantageous embodiments can be found in the dependent claims.
  • the hydro-rotary actuator is an external rotor.
  • the rotary actuator outer part is rotatable as a rotor and the rotary actuator inner part rotatably formed as a stator.
  • the rotary actuator inner part forms an immovable axle shaft, which carries the at least two rotary actuator outer parts in the circumferential direction pivotally.
  • the rotary actuator outer parts are sealed rotatably mounted on the rotary actuator inner part and limited limited rotation in two directions relative to the rotary actuator inner part stop.
  • suitable connecting elements for example threaded bushes or threaded pins.
  • This also allows a shorter in the axial direction design, since the coupling does not have to take place next to the rotor, as is the case with an internal rotary piston.
  • at least one of the rotary actuator outer parts moves on the rotary actuator inner part out of phase to at least one other rotary actuator outer part, preferably opposite.
  • This can be achieved by suitable control of the working chambers via a plurality of controllable hydraulic valves and / or via corresponding hydraulic throttles. If necessary, the common Drehstellglied- inner part further main flow channels.
  • the hydro-rotary actuator has a rotary actuator inner part and three juxtaposed rotary actuator outer parts, wherein the middle rotary actuator outer part always moves in the opposite direction of the two outer rotary actuator outer parts.
  • the Hydro-fluid flow leading hydraulic connection lines preferably lead to the rotatably mounted rotary actuator inner part, since they can then be designed rigid.
  • the connection from the hydro-connecting lines to the at least one first and second working chamber of the hydraulic rotary actuator takes place in a preferred embodiment of the invention over two axially in the fully cylindrical rotary actuator inner part extending main flow channels, from which each side secondary flow channels extend one of the working chambers.
  • the main and the secondary flow channels are formed, for example, as bores, wherein the secondary flow channels transverse to the main flow channels, preferably perpendicular thereto.
  • the working chambers of phase-shift moving rotary actuator outer parts are in opposite directions and the working chambers of in-phase rotating rotary actuator outer parts are in the same direction directly or indirectly connected to the main flow channels.
  • the hydro-rotary oscillator in a preferred embodiment of the hydro-rotary oscillator according to the invention at least one of the rotary actuator outer parts of the at least two rotary actuator outer parts outside at least one radially extending outer part extension on.
  • the outer part extension simplifies the connection of an external device to be oscillated by the hydro-rotary oscillator with the rotary actuator outer part.
  • an extended lever arm is thus provided, which transfers the applied pivoting moment more effective. The effect depends on the length of the lever arm.
  • all rotary actuator outer parts are provided with such outer part extension.
  • the hydro-rotary actuator at at least one of the rotary actuator outer parts on a third and a fourth working chamber, which are diametrically opposed to the first and the second working chamber.
  • the third and the fourth working chamber are directly or indirectly coupled to the first and second working chamber and increase the working volume of the hydro-rotary actuator and thus its pivotal moment.
  • further working chambers can be arranged in pairs in the circumferential direction of the hydro-rotary actuator following the third and fourth working chamber, if sufficient space is available. Also in this case the arrangement of all working chambers is preferably symmetrical.
  • the further working chambers are fluid-technically coupled to the first and second working chambers, as are the third and fourth working chambers.
  • the third and the fourth working chamber is connected crosswise indirectly via secondary flow channels leading to the main flow channels or directly via additional transverse flow channels to the first and second working chamber, respectively.
  • the additional transverse flow channels extend in the axial direction of the hydro-rotary actuator longitudinally offset from each other and to the secondary flow channels and generally inclined to the secondary flow channels.
  • the four working chambers of the hydraulic rotary actuator are arranged one after the other in the circumferential direction of the hydraulic rotary actuator and are numbered consecutively in the description accordingly.
  • Under crosswise connection of the working chambers is understood in this context that the first and the third and the second and the fourth working chamber fluidly communicate with each other. This is to say that the first and the third working chamber are pressurized simultaneously when the second and the fourth working chamber are soakbed together, or vice versa.
  • the rotary actuator inner part depending on its length and that of the rotary actuator outer part, a plurality of rotary actuator outer parts rotatably receive side by side.
  • the existing rotary actuator outer parts can be supplied in each case via its own hydro-rotary pump with a hydro-fluid flow, so that the rotary actuator outer parts are independently rotatable in the two possible directions of rotation.
  • two or more rotary actuator outer parts may be supplied with a hydro-fluid flow via a common hydro-rotary pump. The movement of the driven via the common hydraulic rotary pump rotary actuator outer parts takes place synchronously in this case by the fluidic coupling.
  • the hydro-rotary oscillator according to the invention ideally lead to the hydro-rotary actuator only two hydro-connecting lines, which are alternately pressurized or sobebeetzschlagt.
  • This can in principle also be achieved with four hydraulic connection lines leading to four main flow channels of the rotary actuator inner part.
  • these are preferably connected to different main flow channels.
  • the two outer rotary actuator outer members are then respectively connected in common to a first pair of the main flow channels and the middle rotary actuator outer part to the two other main flow channels.
  • the rotary actuator inner part has only two main flow channels, to which all working chambers are connected. As a result, the movement of all three rotary actuator outer parts is inevitably predetermined.
  • the working chambers of phase-shifted moving rotary actuator outer parts are in opposite directions and the working chambers of in-phase moving rotary actuator outer parts in the same direction connected to the main flow channels.
  • the working chambers of the in-phase moving rotary actuator outer parts are fluid-technically connected directly parallel to each other, while the working chambers of the phase-shifted moving rotary actuator outer parts are preferably connected crosswise with the main flow channels.
  • two hydraulic connection lines to the hydro-rotary actuator and correspondingly two main flow channels in the rotary actuator inner part suffice.
  • the secondary flow channels and, if appropriate, the additional transverse flow channels for the respective rotary actuator outer part are arranged offset to one another in the longitudinal direction of the hydraulic rotary actuator and accordingly do not interfere with each other.
  • control means which control the hydro-fluid flow to the hydro-rotary actuator and in the prior art are usually formed as a separate hydraulic valves and arranged offset from the hydraulic pump, integrated into the hydro-rotary pump.
  • the hydraulic connection lines or the main flow channels is possible.
  • the structure of the invention proper hydro-rotary oscillator simplified and less susceptible to interference.
  • the control means may be, for example, hydro-pressure-controlled valves.
  • the hydro-fluid flow originating from the hydro-rotary pump is oscillating.
  • no additional borrowed control means for reversing the direction of the hydro-fluid flow in the hydraulic connection lines to the hydro-rotary actuator are required.
  • the pressure and suction amplitudes desirably have a sinusoidal rise or fall over time. Thus occur no sudden decelerations or accelerations of the at least one of the hydro-fluid flow driven rotary actuator outer part.
  • Such an oscillating hydro-fluid flow can be generated, for example, with a hydro-rotary pump known from document DE 20 2008 013 877 U1, which has a spherical segment-shaped cavity filled with a hydro-fluid with a circular raised cavity bottom plate.
  • a rotationally driven ball segment is arranged, which is preferably formed as a hemisphere.
  • the ball segment has a planar ball segment bottom and a spherical ball segment cap.
  • the cavity bottom plate and the ball segment bottom are arranged at an angle to each other and define a spherical wedge-shaped space between the cavity bottom plate and the spherical segment bottom.
  • the ball segment in this case has an axis of rotation which extends perpendicular to the cavity bottom plate and inclined relative to the central center axis of the ball segment and aligned with the center of the cavity bottom plate.
  • the spherical wedge-shaped intermediate space is subdivided into two working chambers by a pendulum plate movably arranged between the cavity bottom plate and the spherical segment bottom.
  • the pendulum plate is centered at right angles in the cavity floor plate and touches the ball segment floor with a contact edge, the pendulum plate is pivotable about a virtual pivot point in the middle of the contact edge.
  • Both sides of the pendulum plate are passage channels for the hydro-fluid in the cavity bottom plate intended. These allow the transport of the hydro-fluid from or into the working chambers of the intermediate space between the cavity bottom plate and the spherical segment bottom.
  • the ball segment rotates at an adjustable speed in the spherical segment-shaped cavity at a distance from the cavity bottom plate, the oscillating plate is always on the spherical segment bottom over the entire length of their plant sealingly in abutment.
  • the rotation of the ball segment causes an oscillating hydro-fluid flow in a closed hydraulic system, such as formed by the hydro-rotary pump, the hydro-connecting lines and the hydro-rotary actuator of the hydro-oscillator according to the invention.
  • a closed hydraulic system such as formed by the hydro-rotary pump, the hydro-connecting lines and the hydro-rotary actuator of the hydro-oscillator according to the invention.
  • the amount and pressure of the Hudro fluid flow can be variably set in the hydraulic connection lines leading to the hydro-rotary actuator.
  • the phase position of the rotating spherical segments of the two hydro-rotary pumps to one another preferably between 0 ° and 180 ° can be changed.
  • the delivery rate and the pressure of the hydro-fluid flow in the hydro-connecting lines to the hydraulic rotary actuator are maximal; if the spherical segments are out of phase with each other by 180 °, these are minimal.
  • the respective value varies between the maximum and the minimum value.
  • the minimum value is zero.
  • the maximum value is limited by the rotary stops of the rotary actuator inner part and the rotary actuator outer part.
  • the pivoting frequency is determined only by the oscillation frequency of the hydro-fluid flow and thus by the rotational speed of the hydro-rotary pump, wherein the rotational speed of the hydro-rotary pump is freely adjustable per se to a large extent.
  • the two hydro-rotary pumps have a common drive unit with a drive motor and the drive axes of the ball segments of the hydro-rotary pumps are coupled together via a phase adjustment, which is suitably configured, the position of the drive axes to each other in the opposite direction set synchronously.
  • the drive shaft of the drive motor is connected via a drive chain or a drive belt with the drive axes of the ball segments.
  • the phase adjustment device may have a self-locking drive or a locking device, so that after the adjustment of the phase position of the two spherical segments to each other an unintentional adjustment of the phase position is excluded.
  • the phase adjustment instead of a single adjusting element, which simultaneously acts on the two spherical segments, of course, have two separate adjustment elements with which the phase angle of the spherical segments is independently adjustable from each other.
  • the adjustment of the phase position is preferably carried out by turning the drive axis of at least one spherical segment.
  • the phase adjustment of the drive unit on four deflection points which are arranged on the drive motor to the hydro-rotary pumps and at least one additional rotatable about a rotation deflection roller, wherein in each case the drive motor and a guide roller or two Deflection rollers and the two hydro-rotary pumps are arranged opposite to each other.
  • the phase adjustment of the drive unit has four pulleys for the drive chain or the drive belt, which guide the drive chain or the drive belt cross-shaped, wherein the four pulleys are arranged stationary near the hydraulic rotary pumps.
  • the drive motor and the one guide roller or the two guide rollers are supported by a sliding carriage, which is guided longitudinally displaceable perpendicular to an imaginary connecting line of the two hydro-rotary pumps.
  • the cruciform guide allows only that the circulation path of the drive chain or the drive belt to drive axes of the ball segments, the drive shaft of the drive motor and the axis of rotation of the guide roller when moving the sliding carriage in length is constant, so that is unnecessary to a complex chain tensioning device.
  • the hydro-rotary oscillator according to the invention which is designed as an external rotor, has a simpler design and improved accessibility to the rotor compared to the prior art.
  • any external devices can be particularly easily coupled to the outside of the rotor, ie with the Drehstellglied-.
  • the rotary actuator outer part may be temporarily temporarily pivoted to the rear or forth by a desired pivoting angle, or continuously oscillated, by correspondingly controlling the hydro-fluid flow to the hydro-rotary actuator.
  • such a hydro-rotary oscillator can be used for example in a rudder system of an air or sea vehicle, in the second case, for example, as an oscillating drive for a push rod of any machine.
  • the hydro-rotary oscillator can be formed with a plurality of rotary actuator outer parts, which are supported by a common rotary actuator inner part with or without a lateral distance to each other. This can be operated in phase or out of phase with a single hydro-rotary oscillator, a corresponding number of external devices.
  • both the pivot frequency of the at least one rotary actuator outer part, as well as Pivoting angle can be controlled.
  • a controlled hydro-rotary oscillator is suitable for example as a fin drive for a watercraft, when a fin is attached to the outer-part extension of the rotary actuator outer part or molded.
  • a hydro-rotary oscillator with three rotary-actuator outer parts and in each case molded-on fins has proved to be particularly favorable, in which the middle of the three rotary actuator outer parts with fin always moves opposite to the two outer rotary actuator outer parts with fin.
  • the two outer fins are the same in area or size, while the middle fin is designed to be significantly larger, ideally twice as large, ie, the middle fin has a surface or size, as the two outer fins together , It is useful in this case also to provide between the rotary actuator outer parts with fin partitions, so that the outgoing from one of the fins water turbulence does not affect the other fins and affect the water turbulence generated by these.
  • FIG. 1 shows a hydraulic rotary oscillator according to the invention in two rotational positions
  • Figure 2 shows a variant of the hydro-rotary actuator of Figure 1, which has four working chambers with different connection to the main flow channels (Figure 2a, 2b);
  • FIG. 3 shows a second embodiment of the hydro-rotary oscillator according to the invention, with a hydro-rotary actuator with a Drehstellglied- inner part and three arranged thereon rotary actuator outer parts in plan view in plan view ( Figure 3a) and side view ( Figure 3b).
  • Figure 4 shows the hydro-rotary pump of Figure 1, in an enlarged view;
  • Figure 5 shows a third variant of the hydraulic rotary oscillator according to the invention, with two parallel-connected hydro-rotary pumps, with different rotational positions of the rotating ball segment ( Figure 5a, 5b);
  • FIG. 6 shows a phase adjustment device for adjusting the phase offset of the spherical segments of the two parallel-connected hydraulic rotary pumps with different position of the phase adjustment ( Figure 6a, 6b).
  • FIGS 1 a, 1 b show a first embodiment of the inventive hydro-rotary oscillator 1, with a hydro-rotary pump 2 and a hydraulic rotary actuator 3, which are connected to each other via two hydraulic connection lines 4, 4 '.
  • the hydro-rotary actuator 3 has two working chambers 5, 5 ', which extend as an annular gap between a fully cylindrical rotary actuator inner part 6 and a hollow cylindrical rotary actuator outer part 7.
  • the hydro-rotary actuator 3 comprises a rotary actuator inner part 6 and at least two juxtaposed rotary actuator outer parts 7, 7 ', 7 ", of which only the rotary actuator outer part 7 can be seen in the illustrated cross-sectional representation is sealingly arranged on the rotary actuator inner part 6 and rotatable relative thereto in two directions of rotation limited thereto, the rotary actuator outer part 7 has a radially inwardly extending co-rotating rotary actuator wall 8 and the rotary actuator inner part 6 on both sides of the rotary actuator wall 8 each have a transverse wall 9, 1 a and 1 b show the hydraulic rotary oscillator 1 in different rotational positions
  • the working chamber 5 arranged in the circumferential direction to the left of the rotary actuator wall 8 is the first one and the right of the rotary actuator wall 8 located as a second work called shunt 5 '.
  • the hydraulic rotary oscillator 1 generally has a closed hydraulic system.
  • For counterclockwise rotation of the rotary actuator outer part 7 is the pressurized first working chamber 5 and the second working chamber 5 'simultaneously sogbeetzschlagt.
  • the hydro-fluid flow thus flows towards the first working chamber 5 and away from the second working chamber 5 '.
  • the working chambers 5, 5 ' change their size accordingly.
  • the hydro-connecting lines 4, 4 ' which connect the hydro-rotary pump 2 with the hydro-rotary actuator 3, lead to main flow channels 10, 10', which extend in the rotary actuator inner part 6 in the axial direction.
  • main flow channel 10 and 10 ' leads in each case a secondary flow channel 1 1 or 1 1' to the working chambers 5 or 5 '.
  • the hydro-rotary pump 2 has two juxtaposed separate pump chambers 12, 12 ', from which the hydraulic connection lines 4, 4' go out. In each case alternately acts one of the pump chambers 12, 12 'as a suction and the other as a pressure chamber.
  • the pump chambers 1 2, 12 ' change their size cyclically. This is based on the hydro-rotary pump 2, a hydro-fluid flow, which is oscillating.
  • the pump chamber 12 is connected to the working chamber 5 and the pump chamber 12 'with the working chamber 5'.
  • the pump chamber 12 acts as a pressure chamber and the pump chamber 12 'acts as a suction chamber 5'.
  • Figure 1 b this is reversed.
  • FIGS 2a, 2b show two variants of the shown in the figure Hydro rotary actuator 3.
  • the illustrated hydro-rotary actuator 3 has in the circumferential direction next to the working chambers 5, 5 ', two further working chamber 13, 13', which in the further description as the third Working chamber 13 and be referred to as a fourth working chamber 13 '.
  • the third working chamber 13 is the first working chamber 5 and the fourth working chamber 13 'of the second working chamber 5' diametrically opposite and are each fluidly connected to each other.
  • the hydro-rotary actuator 3 also has an outer radially extending outer part extension 14 which is integrally formed on the rotary actuator outer part 7. On the outer part extension 14, an external device 15 is attached in the form of a wing or a fin.
  • the external device 15 may also be formed integrally with the outer part extension 14.
  • the working chambers 5, 5 'and the working chambers 13, 13' are each connected indirectly to one another and via secondary flow channels 11, 11 'to the main flow channels 10, 10', wherein the secondary flow channels 11 , 1 1 'to the working chambers 13, 13' in the axial direction of the Hydrostellglied inner part 6 at a distance from the working chambers 5, 5 'leading secondary flow channels 1 1, 1 1' are arranged.
  • FIG. 2a the working chambers 5, 5 'and the working chambers 13, 13' are each connected indirectly to one another and via secondary flow channels 11, 11 'to the main flow channels 10, 10', wherein the secondary flow channels 11 , 1 1 'to the working chambers 13, 13' in the axial direction of the Hydrostellglied inner part 6 at a distance from the working chambers 5, 5 'leading secondary flow channels 1 1, 1 1' are arranged.
  • the working chambers 5, 5 ' are each connected to the main flow channels 10, 10' via secondary flow channels 11, 11 ', while the working chambers 13, 13' are connected directly via additional transverse flow channels 16, 16 ' the working chambers 5, 5 'are connected.
  • the additional transverse flow channels 16, 16 ' extend in the axial direction offset to the secondary flow channels 1 1, 1 1' and can be arranged parallel or inclined to this.
  • FIGS. 3a, 3b show a further embodiment of the hydro-rotary actuator 3 of a hydro-rotary oscillator 1 according to the invention.
  • the rotary rotary actuator 3 has a rotary actuator inner part 6 and three juxtaposed rotary actuator outer parts 7, 7 ', 7 ".
  • the rotary actuator outer parts 7, 7', 7" correspond in shape to the rotary actuator element shown in FIG. Outer part 7 and are provided with corresponding outer part extensions 14, 14 ', 14 ", each of the three rotary actuator outer parts 7, 7', 7” is formed according to the figure 3 with four working chambers 5, 5 ', 13, 13', which are connected to each other in the same way as there and the two main flow channels 10, 10 '.
  • the hydro-rotary pump 2 is designed to generate an oscillating hydro-fluid flow and has a spherical segment-shaped cavity 17, which has a circular cavity bottom plate 18 and a spherical cavity cap 19 having.
  • a rotationally driven ball segment 20 in the form of a hemisphere, with a spherical segment bottom 21 and a spherical spherical segment cap 22, respectively.
  • the spherical segment bottom 21 and the cavity bottom plate 18 are inclined to each other and have a distance from each other. They limit a spherical wedge-shaped gap 23 on opposite sides.
  • the ball segment 20 which is formed slightly smaller than the spherical segment-shaped cavity 17, in the cavity
  • the ball segment 20 has a relative to the central central axis 24 by a few angular degrees inclined rotational axis 25 which is aligned with the center 26 of the cavity bottom plate 18 and perpendicular to the cavity bottom plate
  • a pendulum plate 27 is recessed centrally at right angles, which is held on the spherical segment bottom 21 with a contact edge 28 sealingly in abutment.
  • the pendulum plate 27 is designed as a semi-circular disc and received in a complementary formed receiving groove 29, wherein the pendulum plate 27 is slidably guided on the semicircular circumference.
  • the pivoting of the pendulum plate 27 about a virtual pivot point 30 takes place during rotation of the ball segment 20 through the ball segment bottom 21, which exerts pressure on one or the other half of the abutment edge 28 of the pendulum plate 27 depending on the position of the ball segment 20 in the cavity 17.
  • the cavity bottom plate 18 also has passageways 31, 31 'for a fluid, not shown in the drawing, which are arranged on both sides of the pendulum plate 27.
  • the passageways 31, 31 ' serve for the oscillating transport of the fluid from or into the gap 23 between the cavity bottom plate 18 and the spherical segment bottom 21, which is divided by the pendulum plate 27 into two pump chambers 12, 12'.
  • the two pump chambers 12, 12 ' act on the fluid in alternating sequence with pressure or suction when the ball segment 20 rotates in the cavity 17, wherein the two passage channels 31, 31' act alternately as inlet and outlet channels.
  • the hydro-rotary pump 2 has a relative to the cavity 17 sealed drive shaft 32 for the ball segment 20, which in extension of the axis of rotation 25 on the ball segment bottom 21st opposite side of the spherical segment cap 22 is arranged.
  • the drive axle 32 of the ball segment 20 can be coupled to a drive shaft of any motor.
  • FIG. 5 shows in FIGS. 5a, 5b the hydro-rotary oscillator 1 shown in FIGS. 1a, 1b, but with two hydro-rotary pumps 2, 2 '.
  • the two hydro-rotary pumps 2, 2 ' are connected in parallel to each other and to the hydro-rotary actuator 3. They have a common drive unit 33, which is shown in the figure 6 in plan view.
  • the drive unit 33 has a drive motor 34, whose drive shaft 35 is connected via a drive chain or a drive belt 36 to the drive axles 32 of the ball segments 20 of the hydro-rotary pumps 2, 2 '.
  • the drive unit 33 also includes a phase adjustment device 37 for the synchronous adjustment of the position of the drive axles 32 of the hydro-rotary pumps 2, 2 'to one another.
  • the phase adjuster 37 is coupled to the drive chain or to the drive belt 36 and moves the drive axles 32 of the ball segments 20 to each other in the opposite direction of rotation.
  • the phase adjustment 37 has, as shown in Figure 6, also four pulleys 38 for the drive chain or the drive belt 36 and an additional guide roller 39 for this, the drive chain or the drive belt 36 together with the drive axles 32 of the conical segments 20 and the drive shaft 35 of the drive motor 34 cross-shaped lead.
  • the drive motor 34 and the guide roller 39 and the two hydro-rotary pumps 2, 2 ' are arranged opposite one another, wherein the drive motor 34 and the guide roller 39 are supported by a sliding carriage 40 which is perpendicular to an imaginary connecting line of the two hydro-rotary pumps 2, 2 'is guided longitudinally displaceable.
  • the four guide rollers 38 are arranged in pairs each near one of the hydro-rotary pumps 2, 2 'stationary.
  • the use of two deflection rollers 39 instead of a deflection roller 39 and the drive motor 34 as deflection points of the sliding carriage 40 allows a simpler structure of the phase adjustment 37, since no electrical connection lines must be moved during the process of Scheibeschlitten 40.
  • the drive motor 34 may also be arranged at a suitable other location of the drive unit 33.
  • a second deflecting roller 39 is arranged on the deflecting point formed by the drive motor 34 in FIG. This embodiment is not shown in the drawing.
  • FIG. 6a show the sliding carriage 40 of the phase adjuster 37 in two different positions.
  • the axes of rotation 32 of the hydro-rotary pumps 2, 2 ' are the same and, in FIG. 6b, mirror-inverted, with the sliding carriage 40 being in different positions relative to the drive unit 33.
  • the two axes of rotation 32 of the spherical segments 20 synchronously with each other in the same direction of rotation.
  • the entire hydraulic fluid flow is conducted in an oscillating manner to the hydro-rotary actuator 3; in the orientation shown in FIG. 6b, the fluid flow oscillates only between the two hydro-rotary pumps 2, 2 '.
  • the rotary actuator outer part 7, 7', 7 “of the hydro-rotary actuator 3 is cyclically moved, ie swung back and forth.
  • the speed of movement, and thus the frequency with which the at least one rotary actuator outer part 7, 7 ', 7 “moves, is dependent on the rotational speed of the drive shaft 35 of the drive motor 34. This can be set arbitrarily per se and is also dependent on the translation of the Drive shaft 35 to the drive axles 32 of the hydro-rotary pumps 2, 2 'influenced.

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  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Hydraulic Motors (AREA)

Abstract

L'invention concerne un oscillateur rotatif hydraulique (1) présentant un actionneur rotatif hydraulique (3), qui présente une pièce interne (6) d'actionneur rotatif complètement cylindrique et au moins deux pièces externes (7, 7') adjacentes d'actionneur rotatif pouvant être tournées par rapport à la pièce interne (6) de l'actionneur rotatif , et au moins une pompe rotative hydraulique (2, 2') entraînée en continu, qui entraîne, par un flux de fluide hydraulique continu, les pièces externes (7, 7') de l'actionneur rotatif, qui sont disposées concentriquement par rapport à la pièce interne (6) d'actionneur rotatif et à une distance radiale l'une par rapport à l'autre. La pièce interne (6) d'actionneur rotatif et les différentes pièces externes (7, 7') d'actionneur rotatif délimitent radialement au moins deux chambres de travail en forme de segment annulaire (5, 5') et peuvent être tournées l'une par rapport à l'autre de manière limitée dans deux sens de rotation. Les chambres de travail (5, 5') sont séparées l'une de l'autre par une première paroi (8) d'actionneur rotatif tournant conjointement, s'étendant radialement, peuvent être modifiées en taille et sont reliées à la pompe rotative hydraulique (2, 2'), le flux de fluide hydraulique étant dévié alternativement vers les chambres de travail (5, 5') au moyen d'au moins un moyen de commande (27). De préférence, les pièces externes (7, 7') d'actionneur rotatif se déplacent avec un décalage de phase, de préférence de manière opposée l'une par rapport à l'autre.
EP13725056.9A 2012-03-29 2013-03-28 Dispositif hydraulique d'entraînement en rotation Not-in-force EP2831427B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE202012101137U DE202012101137U1 (de) 2012-03-29 2012-03-29 Hydraulische Drehantriebsvorrichtung
PCT/DE2013/100116 WO2013143538A1 (fr) 2012-03-29 2013-03-28 Dispositif hydraulique d'entraînement en rotation

Publications (2)

Publication Number Publication Date
EP2831427A1 true EP2831427A1 (fr) 2015-02-04
EP2831427B1 EP2831427B1 (fr) 2018-07-25

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Application Number Title Priority Date Filing Date
EP13725056.9A Not-in-force EP2831427B1 (fr) 2012-03-29 2013-03-28 Dispositif hydraulique d'entraînement en rotation

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EP (1) EP2831427B1 (fr)
DE (2) DE202012101137U1 (fr)
WO (1) WO2013143538A1 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9816537B2 (en) 2013-02-27 2017-11-14 Woodward, Inc. Rotary piston type actuator with a central actuation assembly
US9476434B2 (en) 2013-02-27 2016-10-25 Woodward, Inc. Rotary piston type actuator with modular housing
US8955425B2 (en) 2013-02-27 2015-02-17 Woodward, Inc. Rotary piston type actuator with pin retention features
US9234535B2 (en) 2013-02-27 2016-01-12 Woodward, Inc. Rotary piston type actuator
US9593696B2 (en) 2013-02-27 2017-03-14 Woodward, Inc. Rotary piston type actuator with hydraulic supply
US9163648B2 (en) 2013-02-27 2015-10-20 Woodward, Inc. Rotary piston type actuator with a central actuation assembly
US9631645B2 (en) 2013-02-27 2017-04-25 Woodward, Inc. Rotary piston actuator anti-rotation configurations
DE202013011687U1 (de) * 2013-11-13 2015-02-23 C. & E. Fein Gmbh Oszillierend antreibbare Werkzeugmaschine
DE102013112455A1 (de) * 2013-11-13 2015-05-13 C. & E. Fein Gmbh Oszillierend antreibbare Werkzeugmaschine
US11199248B2 (en) 2019-04-30 2021-12-14 Woodward, Inc. Compact linear to rotary actuator
WO2021207482A1 (fr) 2020-04-08 2021-10-14 Woodward, Inc. Actionneur du type à piston rotatif, doté d'ensemble d'actionnement central

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US2930434A (en) * 1957-08-15 1960-03-29 Englesson John Elov Hatch operating device
NL267764A (fr) * 1960-08-03
FR2278968A1 (fr) * 1973-12-21 1976-02-13 Mysliwiec Jean Actionneur a mouvement angulaire alternatif
FR2421414A1 (fr) * 1978-03-31 1979-10-26 Basfer Srl Machine operatrice automatique a asservissement en boucle
DE10210756A1 (de) 2002-03-12 2003-10-16 Sorg Reinhard Drehkolbenvorrichtung
DE202008013877U1 (de) 2008-10-20 2009-01-08 Diem, Reinhard Vorrichtung zum Erzeugen eines oszillierenden Fluidstroms sowie Vorrichtung zum Erzeugen eines oszillierenden Hubes eines Werkzeugs

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Also Published As

Publication number Publication date
DE202012101137U1 (de) 2012-04-18
WO2013143538A1 (fr) 2013-10-03
DE112013001736A5 (de) 2015-02-26
EP2831427B1 (fr) 2018-07-25

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