EP2885794A1 - Dispositif d'actionnement et machine à piston axial - Google Patents

Dispositif d'actionnement et machine à piston axial

Info

Publication number
EP2885794A1
EP2885794A1 EP13731741.8A EP13731741A EP2885794A1 EP 2885794 A1 EP2885794 A1 EP 2885794A1 EP 13731741 A EP13731741 A EP 13731741A EP 2885794 A1 EP2885794 A1 EP 2885794A1
Authority
EP
European Patent Office
Prior art keywords
piston
actuator
springs
pivoting
actuator device
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Withdrawn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
EP13731741.8A
Other languages
German (de)
English (en)
Inventor
Dirk SCHNITTGER
Dirk Vahle
Timo Nafz
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2885794A1 publication Critical patent/EP2885794A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/26—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
    • F04B1/324—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 swash plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/10—Control of working-fluid admission or discharge peculiar thereto
    • F01B3/103—Control of working-fluid admission or discharge peculiar thereto for machines with rotary cylinder block
    • F01B3/106—Control of working-fluid admission or discharge peculiar thereto for machines with rotary cylinder block by changing the inclination of the swash plate
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
    • H01F7/00—Magnets
    • H01F7/06—Electromagnets; Actuators including electromagnets
    • H01F7/08—Electromagnets; Actuators including electromagnets with armatures
    • H01F7/16—Rectilinearly-movable armatures
    • H01F7/1607—Armatures entering the winding
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
    • H01F7/00—Magnets
    • H01F7/06—Electromagnets; Actuators including electromagnets
    • H01F7/08—Electromagnets; Actuators including electromagnets with armatures
    • H01F7/16—Rectilinearly-movable armatures
    • H01F2007/1692—Electromagnets or actuators with two coils

Definitions

  • the invention relates to an actuator device with at least one actuator piston, the two springs and two electromagnets are assigned and which is mechanically coupled to an adjusting device which is hydraulically adjustable by actuation of the electromagnets via the actuator piston.
  • the invention further relates to an axial piston machine with at least one working piston and an actuating piston which cooperate with a pivoting cradle, which is adjustable via a control valve that comprises such an actuator device.
  • EP 1 217 209 B1 and EP 1 219 831 B1 disclose adjusting devices for adjusting an actuating piston acting on the displacement volume of a hydrostatic machine.
  • the adjusting piston is movable from a predetermined by the force of at least one return spring neutral position between two end positions.
  • a control valve with a control piston is provided for regulating actuating pressures in actuating pressure chambers.
  • the deflection of the actuating piston is transferable via a rigidly connected to the actuating piston return lever as a linear movement on a spring sleeve, which is in operative connection via a control spring.
  • the control piston consists in the axial direction of a first control piston part and a second control piston part, which are interconnected by a control piston plunger.
  • the first and the second control piston part can be acted on at the ends remote from each other by at least one centering spring and / or adjusting spring with a mutually directed force.
  • a control spring is stretched between two spring seat bodies.
  • the bias of at least one centering spring and / or adjusting spring is for generating in the neutral position of
  • the object of the invention is to further improve an actuator device according to the preamble of claim 1, in particular with regard to the required installation space and / or the functionality, preferably in combination with an axial piston machine.
  • an actuator device having at least one actuator piston, which are associated with two springs and two electromagnets and which is mechanically coupled to an adjusting device which is hydraulically adjustable by actuation of the electromagnets via the actuator piston, achieved in that the actuator device with a hydraulic Centering center is equipped for the adjustment device designed as Schwenkverstell noticed to reset the Schwenkverstell overlooked with de-energized electromagnet hydraulically in a central position.
  • the pivoting adjustment device is preferably a pivoting cradle, as used in axial piston machines. In a middle position of the pivoting cradle, working pistons of the axial piston machine carry out a stroke.
  • the actuator device preferably represents an electromagnetically operable control valve, in particular for adjusting the pivoting cradle of an axial piston machine.
  • one end of the actuator piston is preferably coupled to an armature, which cooperates with the electromagnet.
  • the electromagnets preferably each comprise an electromagnetic coil. By energizing the electromagnetic coils, the actuator piston can be pulled in different directions.
  • a preferred embodiment of the actuator device is characterized in that the actuator piston is arranged between the two springs.
  • the two springs are designed, for example, as helical compression springs.
  • One of the springs is preferably arranged between the actuator piston and a coupling piston. Therefore, this spring is also referred to as a coupling spring.
  • the other spring is also referred to as actuator spring.
  • a further preferred embodiment of the actuator device is characterized in that the actuator piston comprises an armature and a valve body which interrupts or releases connections between hydraulic connections.
  • the valve body is preferably arranged and designed such that the connections between the hydraulic connections are interrupted when the actuator piston is in a central position. If the actuator piston is pulled by actuation of the electromagnets from its central position in one or the other direction, then different connections between the hydraulic ports are released.
  • a further preferred embodiment of the actuator device is characterized in that the springs are designed so that cancel the actuating forces acting on the actuator piston by the springs, when the actuator piston is in a central position, and a coupling piston is in its normal position.
  • the springs are preferably designed so that when reaching the center position of the Schwenkverstell Surprise and the actuator piston reaches its middle position, whereby the connections between the hydraulic connections is interrupted.
  • a middle position a basic position is referred to, which may differ slightly from a zero feed position.
  • a further preferred embodiment of the actuator device is characterized in that the springs are designed so that the actuator piston is adjusted by the springs in its center position between the springs when one of the electromagnets is energized and the Schwenkverstell adopted is in a desired position or a corresponding Schwenkendlage , By energizing one of the coils, the pivoting adjustment device is hydraulically adjusted in one of its two pivot angle end positions.
  • Another preferred exemplary embodiment of the actuator device is characterized in that one of the springs is arranged between one end of the actuator piston or one or the armature and an adjustment element which is accessible from the outside. This can be adjusted from the outside in a simple manner, the center position of the Schwenkverstell issued.
  • a further preferred exemplary embodiment of the actuator device is characterized in that the distance between the adjustment element and the armature can be varied from the outside in order to adjust the centering of the adjusting device designed as a pivoting adjustment device.
  • the adjustment element can be pressed into a corresponding bore differently far enough to change the distance between the adjustment element and the end of the actuator piston.
  • the adjusting element can also be provided with a screw thread, so that the distance between the adjusting element and the end of the actuator piston can be varied from the outside in a simple way by turning the adjusting element in a corresponding threaded bore.
  • the invention further relates to an axial piston machine with at least one working piston and an actuating piston, which interact with a pivoting cradle, which is adjustable via a control valve that comprises a previously described actuator device.
  • the Schwenkverstell shark represents a pivoting cradle of the axial piston machine.
  • the pivoting cradle is in addition to the actuating piston preferably associated with a counter-piston which presses permanently against the pivoting cradle to compensate for unwanted play.
  • the control piston can be connected by means of the control valve to a high pressure level or to a low pressure level of the axial piston engine.
  • a preferred embodiment of the axial piston machine is characterized in that the control valve is designed as a 3/3-way valve.
  • the control valve is preferably designed as a proportional valve.
  • a further preferred embodiment of the axial piston machine is characterized in that one of the springs between a coupling device, via which a pivot angle of the Schwenkverstell Stein is returned to the actuator piston, and the actuator piston is arranged.
  • the axial piston machine is preferably arranged in a mobile hydraulic drive in addition to a primary drive unit, for example an internal combustion engine.
  • the mobile hydraulic drive is preferably arranged in a hydraulic hybrid drive train of a hybrid vehicle.
  • the hybrid vehicle is preferably a passenger car or a commercial vehicle.
  • FIG. 1 shows a simplified illustration of an axial piston machine with an actuator device according to the invention and a pivoting adjustment device in a middle position;
  • FIG. 2 shows the axial piston machine from FIG. 1 with a pivoting cradle swiveled out counterclockwise;
  • FIG. 3 is an enlarged view of the actuator device of FIG. 1;
  • Figure 4 is a Cartesian coordinate diagram with a spring characteristic to the actuator device of Figure 3, wherein a coupling piston is in a normal position;
  • Figure 5 is a hydraulic circuit diagram to a similar axial piston machine, as shown in Figures 1 and 2 and
  • Figure 6 is a similar view as in Figure 1 according to an embodiment with two 2/2-way valves for Schwenkwiegenver too.
  • FIGS. 1 to 3 show an actuator device 1 according to the invention in combination with an axial piston machine in various states and views.
  • the actuator device 1 is in the illustrated embodiment, a control valve of the axial piston machine.
  • the actuator device 1 is in the illustrated embodiment, a control valve of the axial piston machine.
  • Actuator 1 an actuator piston 2, which is guided in a guide body 3 movable back and forth.
  • the axial piston machine further comprises a pivoting adjustment device 4, which is mechanically coupled to the actuator device 1 by means of a coupling device 5.
  • the coupling device 5 comprises an eccentric 8, against which an upper end of a coupling piston 9 in FIGS. 1 to 3 rests.
  • the coupling piston 9 is, as indicated by a double arrow 10, in the longitudinal direction from bottom to top in the direction of an actuator axis 14 translationally movable back and forth.
  • the actuator piston 2 is clamped in the longitudinal direction, that is to say in the direction of the actuator axis 14, between a coupling spring 11 and an actuator spring 12.
  • the coupling spring 1 1 is between the coupling piston 9 and in the figures
  • the actuator spring 12 is between the see in the figures 1 to 3 lower end of the actuator piston 2 and an armature 40 and an adjusting element 13 is arranged.
  • the adjusting element 13 is screwed or pressed into an actuator housing 16.
  • the actuator housing 16 is attached to a machine housing 17 of the axial piston machine and comprises two electromagnetic coils 18, 19.
  • the electromagnetic coils 18, 19 represent two electromagnets, which are energized to actuate the actuator device 1.
  • the Schwenkverstell Stein 4 of the axial piston machine is a pivoting cradle
  • Pivot axis 22 is pivotable.
  • the pivot axis 22 is arranged in the figures 1 to 3 perpendicular to the plane.
  • the working pistons 25, 26 are guided in a drum which is rotatable about a rotation axis 24.
  • the drum with the working piston is also referred to as an engine. Consequently, the rotation axis 24 is also referred to as the engine rotation axis 24.
  • the engine rotational axis 24 is perpendicular to the actuator axis 14.
  • the center of the eccentric 8 is spaced from an intersection in which intersect the pivot axis 22 and the engine rotational axis 24 of the drum.
  • the axial piston machine comprises at least two, preferably more than two, working pistons 25, 26, which bear against the pivoting cradle 20 with their left ends in FIGS. 1 to 3.
  • the right in Figures 1 to 3 ends of the working piston 25, 26 limit working pressure chambers of the axial piston machine, which are filled with a hydraulic medium, such as hydraulic oil.
  • a hydraulic medium such as hydraulic oil.
  • the pivoting cradle 20 can be pivoted about limited pivot angle about the pivot axis 22 in order to adjust the stroke of the working piston 25, 26.
  • Figures 1 and 3 is the
  • Swivel cradle 20 shown in its center position. In the center position, the pivoting cradle 20 is arranged with a pivoting bevel axis 27 perpendicular to the axis of rotation 24 of the drum and parallel to the actuator axis 14.
  • the pivoting cradle 20 is pivoted counterclockwise.
  • the pivoting of the pivoting cradle 20 is effected by an actuating piston 28 which engages radially outside of the working piston 25, 26 on the pivoting cradle 20.
  • the adjusting piston 28 is arranged in the figures 1 and 2 above.
  • the control piston 28 can be acted upon by a control pressure, which via the control valve designed as a control valve
  • Actuator 1 is set or regulated.
  • the pivoting cradle 20 is further acted upon in the figures 1 and 2 below with a counter-piston 29 which rests with its left in Figures 1 and 2 end of the pivoting cradle 20.
  • the counter-piston 29 is at its the Swivel cradle 20 facing away from the end with a high pressure, which is generated by the axial piston machine.
  • the adjusting piston 28 is associated with a spring 30.
  • the counter-piston 29 is assigned a counter-spring 31.
  • the axial piston machine shown in FIGS. 1 and 2 can work particularly advantageously both as an axial piston pump and as an axial piston motor.
  • the pivoting cradle When the pivoting cradle is in its middle position shown in FIG. 1, the working pistons 25, 26 do not execute a stroke during operation of the axial piston machine.
  • the pivoting cradle 20, as shown in Figure 2 is pivoted by about twenty degrees about its pivot axis 22, then perform the working piston 25, 26 a maximum stroke.
  • the pivotal weighing angle is used as a manipulated variable for the speed and the torque generated on an output shaft of the axial piston machine.
  • the swivel weighing angle is used as a control variable for the delivery volume and pressure.
  • the United position of the pivoting cradle 20 is carried out in de-energized coils 18, 19 based on the position of the eccentric 8, which is mounted on the pivoting cradle 20.
  • the coupling piston 9, which acts on the coupling spring 1 1, follows a movement of the eccentric 8.
  • the path which the coupling piston 9 travels during pivoting of the pivoting cradle 20 from the minimum pivot angle shown in Figure 1 to the maximum pivot angle shown in Figure 2 can be reduced by the eccentric 8 in comparison to conventional axial piston machines.
  • the axial extent of the axial piston machine in the direction of the axis of rotation 24 can be reduced.
  • the axial extent of the axial piston machine ne in the direction of the axis of rotation 24 is also referred to as Axialkolbenmaschinenbauble.
  • the actuator device 1 designed as a control valve is arranged radially to the axis of rotation 24 of the axial piston machine. Radial means across the board
  • Rotation axis 24, that is, the actuator axis 14 is perpendicular to the axis of rotation 24 is arranged. Due to the radial arrangement of the actuator device 1, the Axialkolbenmaschinenbaun in the direction of the axis of rotation 24 can be further reduced. The adjustment of the swivel angle takes place by means of the adjusting piston 28 and the
  • the adjusting piston 28 can be connected to the high-pressure level or to a low-pressure level of the axial piston machine by means of the actuator device 1 designed as a control valve.
  • the pressure is referred to, which is generated by means of the working piston 25, 26 during operation of the axial piston machine.
  • a tank pressure is referred to, which may correspond to the ambient pressure.
  • the control valve represented by the actuator device 1 corresponds to a 3/3-way valve with a low-pressure connection or tank pressure connection 34, a
  • High-pressure port or pump pressure port 35 and a control pressure connection or working pressure port 36 On the actuator piston 2, a valve body 38 is formed.
  • the valve body 38 is integrally connected to the actuator piston 2.
  • the actuator piston 2 with the valve body 38 is translatable between two end positions in the direction of the actuator axis 14. In a middle position of the actuator piston 2 shown in FIG. 1, the valve body 38 of the actuator piston 2 closes the control pressure connection 36.
  • the armature 40 coupled to the actuator piston 2 in FIGS. 1 to 3 is pulled upwards, that is, pulled away from the adjusting element 13 toward the eccentric 8.
  • the armature 40 is designed in the illustrated embodiment as a separate part and is held by the biasing force of the springs 1 1 and 12 in abutment against the actuator piston 2.
  • the armature 40 may also be integrally connected to the actuator piston 2.
  • the valve body 38 provides a connection between pressure connection or pump connection 35 and the control pressure connection or working pressure connection 36 of FIG Control valve to the actuating piston 28 free.
  • the pivoting cradle 20 pivoted counterclockwise to its end position.
  • the coupling spring 1 1 and the actuator spring 12 are designed so that the actuator piston 2 when energized coil 18 reaches its central position when the pivoting cradle 20 is pivoted counterclockwise in its pivoting balancing position.
  • Coupling spring 1 1 connected at its top in Figures 1 to 3 above the coupling piston 9 with the eccentric 8 and thus follows its movements, which are indicated by the double arrow 10. If the pivoting cradle 20, as seen in Figure 2, in energized coils 18,
  • the coupling spring 1 1 and the actuator spring 12 are advantageously designed so that when energized coils 18, 19 with reaching the Schwenkwiegenstoff ein the actuator piston 2 reaches its middle position, whereby the connection to the actuating piston 28 is closed by the valve body 38. If the pivoting cradle 20 is pivoted clockwise in the case of currentless coils 18, 19 (not shown), the actuator piston 2, which is also referred to as a valve piston, is pushed upward by the actuator spring 12 away from the adjusting element 13 in FIGS the adjusting piston 28 is connected to the pressure connection or pump pressure connection 35 and subjected to high pressure. As a result, the pivot cradle 20 is pivoted counterclockwise.
  • the coupling spring 1 1 and the actuator spring 12 are advantageously designed so that upon reaching the Schwenkwiegenstoff ein the valve piston or actuator piston 2 reaches its middle position and thus the connection from the pressure port or pump pressure port 35 to the actuator piston 28 is closed.
  • the swivel cradle 20 is hydraulically returned to its central position or middle position or basic position in the case of currentless coils 18, 19.
  • the actuator piston 2 When the actuator piston 2 is in its center position or middle position and the pivoting cradle assumes its center position, middle position or basic position, that is not swiveled or pivoted, the actuating forces of the coupling spring 1 1 and the actuator spring 12 cancel each other.
  • the coil is de-energized
  • the actuator device 1 shown in Figure 3 works as follows.
  • the pivoting cradle 20 is in the illustrated basic position, as long as the electromagnet or electromagnetic coils 18,19 are not energized.
  • the basic position is also referred to as zero position or zero production position, because in the basic position no promotion takes place.
  • the basic position may also differ slightly from the zero feed position, that is, the Pivoting cradle 20 may be slightly swung in its normal position, for example up to 10 percent delivery volume.
  • the actuator piston 2 is in its central position or normal position when the valve body 38 closes the control pressure port 36.
  • the coil 18 is energized, then the armature 40 moves upward in FIG.
  • the valve body 38 releases the connection between the pump pressure connection 35 and the control pressure connection 36.
  • the actuating piston of the pivoting cradle 20 is acted on by the pump pressure, so that the actuating piston pivots the pivoting cradle 20 in the counterclockwise direction.
  • a pivoting of the pivoting cradle 20 can be achieved by a defined pivoting angle.
  • the armature 4 moves by the spring forces of the springs 1 1, 12 and the interplay of the valve body 38 with the terminals 34 to 36 back to its original position and the pivot cradle 20 resumes its normal position.
  • FIG. 4 shows a Cartesian coordinate diagram with an x-axis 41 and a y-axis 42.
  • the path of the actuator piston 2 is applied in a suitable path unit.
  • the combined spring force of the coupling spring 1 1 and the actuator spring 12 is applied in a suitable power unit, wherein the coupling piston is in its zero position.
  • a combined spring characteristic for the coupling spring 1 1 and the actuator spring 12 is applied.
  • points 45, 46 the maximum displacement of the actuator piston 2 are indicated.
  • the coordinate origin corresponds to the middle position of the actuator piston 2.
  • a similar axial piston machine 50 as shown in simplified form in Figures 1 to 3, shown in the form of a hydraulic circuit diagram.
  • the axial piston machine 50 comprises an actuator device 51, which is designed as a control valve for a pivoting cradle 55.
  • the pivoting cradle 55 is adjusted by an adjusting piston 52 against the action of an opposing piston 53.
  • a pivoting movement of the pivoting cradle 55 is transmitted via a cam 56 to a coupling piston 58.
  • the pivotal weighing movement is fed back to the designed as a control valve actuator device 51.
  • the control valve 51 is designed as a proportional valve in 3/3-way valve construction.
  • the 3/3-way valve 51 comprises a pump pressure connection or high-pressure connection 47, a tank pressure connection or low-pressure connection 48 and a working pressure connection or control pressure connection 49.
  • control valve 51 is actuated by two symbolically indicated electromagnets. By two also symbolically indicated springs, the control valve 51 is biased in its center position shown. In the middle position of the adjusting piston 52 and the opposing piston 53 are subjected to low pressure or tank pressure. In the left end position of the control valve 51 in FIG. 5, the control piston 52 is subjected to high pressure via a connection between the pump pressure connection 47 and the working pressure connection 49. In a right-hand end position of the control valve 51 in FIG. 5, the control piston 52 is relieved into the tank pressure or low pressure via a connection between the working pressure port 49 and the tank pressure port 48.
  • the tilt angle is returned itself.
  • a pivot angle change is converted proportionally into a stroke change and transmitted to the return spring between the coupling piston 58 and the valve piston of the control valve 51.
  • the return stroke can be changed via the geometry of the cam 56 and thus allows any length of the return spring.
  • the pivot angle is in contrast to the stroke of the actuating piston 52 or the counter-piston 53, regardless of the construction large of the axial piston machine 50, so that the variant shown in Figure 5 can be used without changes for all axial piston engine sizes.
  • FIG. 6 shows a similar axial piston machine as in FIGS. 1 and 2. To denote the same parts, the same reference numerals are used. To avoid repetition, reference is made to the preceding description of Figures 1 and 2. In the following, the differences between the two embodiments are mainly discussed. In the embodiment shown in Figure 6 are two
  • Actuator 60, 70 coupled to the eccentric 8, which is mounted on the pivoting cradle 20.
  • a control valve is shown, which comprises two 2/2 way valves.
  • the two symbolically indicated 2/2-way valves each include an open position and a closed position.
  • the two actuator devices 60, 70 each include an actuator piston 62, 72 and a coupling piston 63, 73.
  • a coupling spring 64, 74 is disposed between the actuator piston 62, 72 and the coupling piston 63, 73.
  • Actuator piston 62, 72 is acted upon by an actuator spring 65, 75 and is actuated by an electromagnet 68, 78.
  • the actuator device 60 comprises a high-pressure connection or pump pressure connection 66 and a working pressure connection or control pressure connection 67.
  • the actuator device 70 comprises a low-pressure connection or tank pressure connection 76 and a control pressure connection or working pressure connection 77. If the actuator device 60 is actuated by energizing the electromagnet 68, then the adjusting piston 28 is acted upon by high pressure via a connection between the pump pressure connection 6 and the working pressure connection 67. If the actuator device 70 is actuated by energizing the solenoid 78, then the actuating piston 28 is acted upon via a connection between the working pressure port 77 and the tank pressure port 76 with low pressure.
  • the Schwenkwiegenver ein works in the embodiment shown in Figure 6 as well as in the embodiment shown in Figures 1 to 3.
  • the valve complexity compared to the embodiment shown in Figures 1 to 3 can be reduced. Since the two actuator devices 60, 70 each have only one electromagnet 68, 78, a smaller extension of the axial piston machine can be realized radially to the axis of rotation 24 with the embodiment shown in Figure 6.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Power Engineering (AREA)
  • Reciprocating Pumps (AREA)

Abstract

Un dispositif d'actionnement comprenant au moins un piston d'actionnement (2) auquel sont associés deux ressorts (11,12) et deux électroaimants (18,19), est couplé mécaniquement à un dispositif de déplacement. L'actionnement des électroaimants (18,19) permet un déplacement hydraulique du dispositif de déplacement par l'intermédiaire du piston d'actionnement (2). Le dispositif d'actionnement est équipé d'un centrage médian hydraulique destiné au dispositif de déplacement réalisé en tant que dispositif de déplacement pivotant (4), pour permettre, lorsque les électroaimants (18,19) ne sont pas alimentés, le retour hydraulique du dispositif de déplacement pivotant (4) à une position médiane. L'invention concerne aussi une machine à piston axial comprenant un berceau pivotant, le berceau pivotant pouvant être déplacé par l'intermédiaire d'une soupape de réglage qui comprend un dispositif d'actionnement de ce type.
EP13731741.8A 2012-08-17 2013-06-21 Dispositif d'actionnement et machine à piston axial Withdrawn EP2885794A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012214626.1A DE102012214626A1 (de) 2012-08-17 2012-08-17 Aktoreinrichtung und Axialkolbenmaschine
PCT/EP2013/063034 WO2014026791A1 (fr) 2012-08-17 2013-06-21 Dispositif d'actionnement et machine à piston axial

Publications (1)

Publication Number Publication Date
EP2885794A1 true EP2885794A1 (fr) 2015-06-24

Family

ID=48699766

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13731741.8A Withdrawn EP2885794A1 (fr) 2012-08-17 2013-06-21 Dispositif d'actionnement et machine à piston axial

Country Status (3)

Country Link
EP (1) EP2885794A1 (fr)
DE (1) DE102012214626A1 (fr)
WO (1) WO2014026791A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014225152A1 (de) 2014-12-08 2016-06-09 Robert Bosch Gmbh Verfahren zum Betreiben eines Hydrostaten

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1271830B (de) * 1962-06-07 1968-07-04 Spuhr & Co M Elektromagnetisch betaetigte Stellvorrichtung
DE10063526C1 (de) 2000-12-20 2002-07-11 Brueninghaus Hydromatik Gmbh Verstellvorrichtung zum Verstellen eines auf das Verdrängungsvolumen einer hydrostatischen Maschine einwirkenden Stellkolbens
DE10063525B4 (de) 2000-12-20 2005-07-07 Brueninghaus Hydromatik Gmbh Verstellvorrichtung zum Verstellen eines auf das Verdrängungsvolumen einer hydrostatischen Maschine einwirkenden Stellkolbens
WO2005066490A1 (fr) * 2004-01-05 2005-07-21 Hitachi Construction Machinery Co., Ltd. Dispositif de commande de rotation incline destine a une pompe hydraulique a deplacement variable

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
None *
See also references of WO2014026791A1 *

Also Published As

Publication number Publication date
DE102012214626A1 (de) 2014-02-20
WO2014026791A1 (fr) 2014-02-20

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