EP2885536A1 - Dispositif d'actionnement et machine à piston axial - Google Patents

Dispositif d'actionnement et machine à piston axial

Info

Publication number
EP2885536A1
EP2885536A1 EP13730262.6A EP13730262A EP2885536A1 EP 2885536 A1 EP2885536 A1 EP 2885536A1 EP 13730262 A EP13730262 A EP 13730262A EP 2885536 A1 EP2885536 A1 EP 2885536A1
Authority
EP
European Patent Office
Prior art keywords
piston
actuator
pivoting
coupling
spring
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Withdrawn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
EP13730262.6A
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 EP2885536A1 publication Critical patent/EP2885536A1/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Withdrawn legal-status Critical Current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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/002—Hydraulic systems to change the pump delivery
    • 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, which are associated with two springs and which is coupled to an adjusting device.
  • 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.
  • EP 1 217 209 B1 and EP 1 219 831 B1 adjustment devices are known 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 adjustable for generating in the neutral position of the control valve balanced spring forces. Disclosure of the invention
  • 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, to which two springs are assigned and which is coupled to an adjusting device, in that the adjusting device acts as a
  • Actuator is, for example, an actuator in a control and control application.
  • the actuator device may also include an effector used in robotics.
  • the actuator device can be embodied both as an actuating device and as a drive device, for example in a mechatronic application.
  • Actuator can be used, for example, to drive a fluid machine, in particular a fluid pump. Particularly advantageous is the
  • Actuator associated with an axial piston machine with a pivoting cradle which is represented by the Schwenkverstell issued. Due to the centering, the adjusting device in a de-energized state of
  • Actuator be held in a simple manner in a middle position or neutral position. In the middle position or neutral position perform working piston of the axial piston machine no stroke.
  • the actuator device preferably comprises two electromagnets or electromagnetic coils with which the actuator piston can be pulled in opposite directions. In this case, one end of the actuator piston is preferably coupled to an armature, which cooperates with the electromagnet.
  • a preferred embodiment of the actuator device is characterized in that the pivoting adjustment device comprises a mechanical coupling device, via which a pivoting angle of the pivoting adjustment device is returned to the actuator piston. This provides the advantage that a sensor device for detecting the pivoting angle of the pivoting adjustment device can be omitted.
  • a further preferred exemplary embodiment of the actuator device is characterized in that the mechanical coupling device comprises an eccentric, a cam, or a cam disc.
  • the swivel angle of the swivel adjustment device can be transmitted or returned to the actuator piston in a simple manner via the eccentric, the cam or the cam disk.
  • a further preferred exemplary embodiment of the actuator device is characterized in that the mechanical coupling device comprises at least one coupling piston.
  • the coupling piston is preferably used to the
  • the coupling piston is preferably translatable in the same direction as the actuator piston back and forth.
  • a further preferred embodiment of the actuator device is characterized in that the mechanical coupling device comprises a coupling spring, which is arranged between the coupling piston and the actuator piston.
  • the mechanical coupling device comprises a coupling spring, which is arranged between the coupling piston and the actuator piston.
  • a further preferred embodiment of the actuator device is characterized in that the actuator piston between the coupling spring and an actuator spring is arranged.
  • the actuator spring and the coupling spring are preferably designed so that when reaching the center position or neutral position of the Schwenkverstellinnate and the actuator piston reaches its center position. In the middle position of the actuator piston, a connection to the actuating piston of the pivoting adjustment device is preferably interrupted.
  • a further preferred embodiment of the actuator device is characterized in that the actuator piston is arranged radially or axially to an engine rotational axis, which is arranged perpendicular to a pivot axis of the Schwenkverstell Surprise. Due to the radial arrangement of the actuator piston, the space in the axial direction can be significantly reduced. At one With two 2/2-way valves, two actuator pistons are preferably arranged diametrically.
  • 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 comprises two electromagnetic coils or electric magnets which allow movements of the actuator piston in opposite directions.
  • the control valve comprises two electromagnetic coils or electric magnets which allow movements of the actuator piston in opposite directions.
  • a first electromagnetic coil is energized, the actuator piston is pulled in a first direction.
  • a second electromagnetic coil is energized, the actuator piston is pulled in a second direction opposite to the first direction.
  • a further preferred embodiment of the axial piston machine is characterized in that the control valve is designed as a 3/3-way valve, or comprises two 2/2-way valves.
  • the control valve is preferably designed as a proportional valve.
  • each control valve comprises an actuator piston.
  • 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 arranged between the lower end of the actuator piston 2 or an armature 40 and an adjusting element 13 in FIGS.
  • 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 hooked 4 of the axial piston machine is designed as a pivoting cradle 20, which, as indicated by a double arrow 21, about a pivot axis 22 is pivotable.
  • the pivot axis 22 is shown in Figures 1 to
  • 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 rotation axis 24 runs perpendicular to the actuator axis 14.
  • the center of the eccentric 8 is spaced from an intersection in which the pivot axis 22 and the engine rotational axis 24 of the drum intersect.
  • the axial piston machine comprises at least two, preferably more than two,
  • Working piston 25, 26, which rest with their left in Figures 1 to 3 ends on the pivoting cradle 20.
  • 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 middle position is the
  • Pivoting cradle 20 is arranged with a pivoting pivot 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 acted upon at its end facing away from the pivoting cradle 20 with a high pressure, which is generated by the axial piston machine.
  • the adjusting piston 28 is associated with a spring 30.
  • Opposite piston 29 is associated with a return spring 31. Through the two springs 30, 31, the two pistons 28, 29 are held in contact with the pivoting cradle 20.
  • 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 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 swinging angle is used as a control variable for the delivery volume and pressure.
  • the distance traveled by the coupling piston 9 during pivoting of the pivoting cradle 20 from the minimum pivoting angle illustrated in FIG. 1 to the maximum pivoting angle shown in FIG. 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 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 transverse to the axis of rotation 24, that is, the actuator axis 14 is arranged perpendicular to the axis of rotation 24. Due to the radial arrangement of the actuator device 1, the Axialkolbenmaschinenbauin in the direction of the axis of rotation 24 can be further reduced. The adjustment of the pivot angle takes place with the aid of the adjusting piston 28 and the counter-piston 29, which each generate an opposite moment on the pivoting cradle 20.
  • 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 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
  • Directional control valve with a low pressure port or tank pressure port 34, a high pressure port or pump pressure port 35 and a control pressure connection or working pressure port 36.
  • a valve body 38 is formed on the actuator piston 2 connected.
  • the actuator piston 2 with the valve body 38 is translatable between two end positions in the direction of the actuator axis 14 back and forth. In a middle position of the actuator piston 2 shown in Figure 1, the valve body 38 of the actuator piston 2 closes the control pressure port 36.
  • the coil 18 When the coil 18 is energized, then coupled to the actuator piston 2 armature 40 in Figures 1 to 3 upwards, that is from the adjusting member 13 is pulled away on 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 releases a connection between pressure connection or pump connection 35 and the control pressure connection or working pressure connection 36 of the control valve to the control piston 28.
  • 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.
  • Actuator spring 12 are designed so that the actuator piston 2 reaches its middle position when energized coil 19, when the pivoting cradle 20 is pivoted clockwise into its pivoting balancing position.
  • the position of the actuator piston 2 is predetermined by the coupling spring 1 1 and the actuator spring 12.
  • the coupling spring 1 1 is 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.
  • pivoting cradle 20 is pivoted counterclockwise with de-energized coils 18, 19, the actuator piston 2 is pressed by the coupling spring 1 1 down, and the control piston 28 is connected via the working pressure port 36 with the low pressure port 34th connected. As a result, the pivoting cradle 20 is pivoted in the clockwise direction in the middle position, which is referred to as the centering of the pivoting cradle 20.
  • 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.
  • the actuator piston 2 which is also referred to as a valve piston, moves away from the actuator spring 12 away from the adjusting element 13 into the
  • 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 11 and the actuator spring 12 cancel each other out.
  • no actuating force acts on the actuator piston 2.
  • the Schwenkwiegensch ein can be adjusted from the outside.
  • the coupling of the Schwenkweeping position with the actuator device 1 leads to a positive influence on the control characteristics.
  • 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 a zero position or zero production position because there is no funding in the basic position.
  • the basic position may also deviate slightly from the zero feed position, that is, the pivoting cradle 20 may be in its basic position slightly, for example, up to 10 percent delivery volume, swung out.
  • the actuator piston 2 is in its central position or normal position when the valve body 38 closes the control pressure port 36. When the coil 18 is energized, then the armature 40 moves upward in FIG. In this case, the valve body 38 releases the connection between the pump pressure connection 35 and the control pressure connection 36.
  • FIG. 4 shows a Cartesian coordinate diagram with an x-axis 41 and a y-axis 42. On the x-axis 41, the path of the actuator piston 2 is applied in a suitable path unit.
  • FIG. 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 swivel-weighing is on the designed as a control valve actuator device
  • the control valve 51 is designed as a proportional valve in 3/3-way valve construction.
  • the 3/3-way valve 51 includes a pump pressure port or high-pressure port 47, a tank pressure port or low-pressure port 48 and a working pressure port or control pressure port 49.
  • the control valve 51 is actuated by two symbolically indicated electromagnet. By two also symbolically indicated springs, the control valve 51 is biased in its center position shown.
  • the control piston 52 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 pivoting angle is independent of the size of the axial piston machine 50, so that the variant shown in FIG. 5 can be used without changes for all axial piston machine 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.
  • Actuator 60, 70 coupled to the eccentric 8, which is mounted on the pivoting cradle 20.
  • a Control valve shown which includes 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 a high pressure via a connection between the pump pressure port 6 and the working pressure port 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. Otherwise, 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.

Landscapes

  • 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), est couplé à un dispositif de déplacement. Le dispositif de déplacement est réalisé en tant que dispositif de déplacement pivotant (4) comprenant un centrage médian. L'invention concerne aussi une machine à piston axial comprenant un berceau pivotant. Le berceau pivotant peut être déplacé par l'intermédiaire d'une soupape de réglage qui comprend un dispositif d'actionnement de ce type.
EP13730262.6A 2012-08-17 2013-06-21 Dispositif d'actionnement et machine à piston axial Withdrawn EP2885536A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201210214619 DE102012214619A1 (de) 2012-08-17 2012-08-17 Aktoreinrichtung und Axialkolbenmaschine
PCT/EP2013/063016 WO2014026788A1 (fr) 2012-08-17 2013-06-21 Dispositif d'actionnement et machine à piston axial

Publications (1)

Publication Number Publication Date
EP2885536A1 true EP2885536A1 (fr) 2015-06-24

Family

ID=48669981

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13730262.6A Withdrawn EP2885536A1 (fr) 2012-08-17 2013-06-21 Dispositif d'actionnement et machine à piston axial

Country Status (5)

Country Link
EP (1) EP2885536A1 (fr)
CN (1) CN104641110A (fr)
DE (1) DE102012214619A1 (fr)
IN (1) IN2015DN01306A (fr)
WO (1) WO2014026788A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN116576101B (zh) * 2023-06-27 2024-02-23 北京工业大学 一种机动阀配流的双向轴向柱塞装置

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Publication number Priority date Publication date Assignee Title
DE2204466A1 (de) * 1972-01-31 1973-08-09 Linde Ag Bewegungsuebertragungsmechanik
US4381702A (en) * 1980-11-21 1983-05-03 Sundstrand Corporation Displacement control for a hydraulic pump or motor with failure override
US4722186A (en) * 1986-01-24 1988-02-02 Sundstrand Corporation Dual pressure displacement control system
JPS63134869A (ja) * 1986-11-25 1988-06-07 Daikin Ind Ltd 可変容量形ピストン機械
DE19540654C1 (de) * 1995-10-31 1996-12-19 Brueninghaus Hydromatik Gmbh Verstellvorrichtung mit hydraulischer Zentriereinrichtung
AT408898B (de) * 1998-04-27 2002-03-25 Joerg Thurner Axialkolbenverstellmaschine
US6158969A (en) * 1999-09-16 2000-12-12 Eaton Corporation Hydrostatic pump and disable control therefor
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

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Title
See references of WO2014026788A1 *

Also Published As

Publication number Publication date
WO2014026788A1 (fr) 2014-02-20
CN104641110A (zh) 2015-05-20
IN2015DN01306A (fr) 2015-07-03
DE102012214619A1 (de) 2014-02-20

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