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
  • F01B3/108—Control of working-fluid admission or discharge peculiar thereto for machines with rotary cylinder block by turning the swash plate (with fixed inclination)
• • 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
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
  • F16K31/00—Actuating devices; Operating means; Releasing devices
  • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
  • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
  • F16K31/0603—Multiple-way valves
  • F16K31/061—Sliding valves
  • F16K31/0613—Sliding valves with cylindrical slides
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
  • F16K31/00—Actuating devices; Operating means; Releasing devices
  • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
  • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
  • F16K31/0675—Electromagnet aspects, e.g. electric supply therefor
  • F16K31/0679—Electromagnet aspects, e.g. electric supply therefor with more than one energising coil
• • 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 having at least one actuator piston, the at least one spring 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 includes such an 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.
• 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 with at least one actuator piston, which is associated with at least one spring 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, solves that the actuator piston is associated with a prestressed actuator spring whose
• Biasing force in a force range below the biasing force causes a rigid coupling of the actuator piston and a coupling piston.
• the actuator device is, for example, an actuator in a control and regulation application. However, the actuator device can also comprise an effector, which is 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.
• the actuator piston When the actuator piston is moved out of its actuator center position, first the spring preload force of the actuator spring must be overcome. This will be the
• Actuator optimized with respect to their hysteresis in the de-energized state of the electromagnets.
• the spring biasing force of the actuator spring acts on the actuator piston until it has again reached its actuator center position.
• the force range below the biasing force of the actuator spring is given, for example, when the electromagnets or coils are not energized.
• de-energized magnets or coils leads to the rigid coupling a hysteresis-poor resetting of the adjusting device, in particular a pivoting back of a pivoting cradle, in its basic position.
• a preferred embodiment of the actuator device is characterized in that the actuator spring is clamped between two spring plates, which are supported on the actuator piston so as to be movable toward one another in the axial direction.
• the axial direction is defined by the longitudinal axis of the actuator piston.
• the actuator piston is movable along its longitudinal axis in opposite directions from its Aktorittel ein out.
• the biasing force of the actuator spring can be easily transferred to the actuator piston when it is moved out of its actuator center position.
• a further preferred embodiment of the actuator device is characterized in that the actuator piston is mechanically coupled to the adjusting device with the interposition of the actuator spring via a coupling device. Via the coupling device, an adjusting movement of the adjusting device is transmitted to the actuator piston with the intermediary of the actuator spring.
• a further preferred embodiment of the actuator device is characterized in that the coupling device is mechanically coupled via the spring plate with the actuator piston.
• the spring plates are supported for this purpose in opposite axial directions on the coupling device.
• a further preferred embodiment of the actuator device is characterized in that the coupling device comprises a coupling piston which is mechanically coupled to the actuator piston with the interposition of the actuator spring.
• the coupling piston is preferably designed sleeve-like as a hollow piston. This makes it possible in a simple manner to provide an annular space between the actuator piston and the coupling piston for receiving the actuator spring.
• a further preferred embodiment of the actuator device is characterized in that the coupling device comprises an eccentric, a cam or a cam on which the coupling piston rests.
• the coupling piston for example, a pivoting movement of the adjusting device can be converted into a translational movement of the coupling piston.
• the coupling piston can be advantageously held with a coupling spring in contact with the eccentric, the cam or the cam.
• a further preferred embodiment of the actuator device is characterized in that the adjusting device is designed as a pivoting adjustment.
• the pivoting adjustment device is designed, for example, as a pivoting cradle of an axial piston machine.
• the pivoting cradle of the pivoting adjustment device is preferably pivotable about a pivot axis when one of the electromagnets is energized.
• 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 so that the connections between the hydraulic connections are interrupted when the actuator piston is in its center position. When the actuator piston is pulled one way or the other by actuation of the solenoids, different connections between the hydraulic ports are released.
• 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.
• 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;
• 4A is a Cartesian coordinate diagram with a spring characteristic to the actuator device of Figure 3;
• FIG. 4B is a Cartesian coordinate diagram with a spring characteristic to the actuator device from FIGS. 5-13;
• Figure 5 shows an actuator device according to the invention in longitudinal section and the Figures the actuator device of Figure 5 in various switching positions and 6 to 13 states.
• 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 disposed between the coupling piston 9 and the upper end of the actuator piston 2 in Figures 1 to 3.
• 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 hooked 4 of the axial piston machine is designed as a pivoting cradle 20, which, as indicated by a double arrow 21, to a
• 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 pivoting angles about the pivoting axis 22 in order to move the pivoting cradle 20
• 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. At its end facing away from the pivoting cradle 20, the adjusting piston 28 is provided with a Actuation pressure can be acted upon, which runs over the 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.
• 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 Figure 1, perform the working piston 25, 26 in the operation of the axial piston no stroke.
• 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.
• Rotary axis 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 Axialkolbenmaschinenbaurea.
• the designed as a control valve actuator 1 is radially to
• Rotary axis 24 of the axial piston machine arranged. Radial means transverse to the axis of rotation 24, that is, the actuator axis 14 is perpendicular to the axis of rotation 24. 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 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.
• As high pressure 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 element ment 13 away on the eccentric 8 too.
• the armature 40 is executed 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.
• the 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.
• 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 Schwenkwiegenstoffhalose 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, 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.
• 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.
• no actuating force acts on the actuator piston 2.
• 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 electric magnets 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 deviate slightly from the zero feed position, that is, the pivoting cradle 20 may slightly in its normal position, for example up to
• 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.
• FIG. 4A 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 line 44 is a combined spring characteristic for the
• the coordinate origin corresponds to the middle position of the actuator piston 2.
• FIG. 4b shows a Cartesian coordinate diagram with an x-axis 241 and a y-axis 242. On the x-axis 241 is the path of one
• Actuator piston 82 of an actuator device 81 according to the invention which is shown in Figures 5-13, applied in a suitable path unit.
• the combined spring force of a coupling spring 91 and an actuator spring 92 is plotted in a suitable power unit, wherein the coupling piston is in its zero position.
• a combined spring characteristic for the coupling spring 91 and the actuator spring 92 is plotted.
• points 245, 246, the maximum adjustment of the actuator piston 82 are indicated.
• the origin of coordinates corresponds to the center position of the actuator piston 92.
• the actuator spring 92 is biased. When the actuator piston 82 is moved from its center position or middle position, first the spring biasing force must be overcome. When returning the actuator piston 82 in the de-energized state, this spring biasing force acts until it reaches the center position. As a result, a lower hysteresis is achieved.
• the actuator device 81 is shown in various switching positions and states in longitudinal section.
• the actuator device 81 preferably serves, as does the actuator device 1 in FIGS. 1 to 3, as a regulating valve of an axial piston machine (not shown in FIGS. 5 to 13).
• the actuator device 81 comprises the actuator piston 82, which is guided in a guide body 83 movable back and forth.
• the actuator piston 82 is guided in a guide body 83 movable back and forth.
• the axial piston machine only one pivot adjustment device 84 is indicated in FIGS. 5 to 13, which comprises a pivoting cradle 86.
• the pivot adjustment device 84 is mechanically coupled to the actuator device 81 by means of a coupling device 85.
• the coupling device 85 comprises an eccentric 88, which is attached to the pivoting cradle 86.
• On the eccentric 88 is a coupling piston 89 with his in the figures 6 to 13 left end.
• the coupling piston 89 is held by the coupling spring 91 in contact with the eccentric 88.
• the coupling piston 89 is designed as a hollow piston.
• the inner diameter of the coupling piston 89 designed as a hollow piston is greater than the outer diameter of the actuator piston 82 in the region of the coupling piston 89.
• the actuator piston 82 as well as the coupling piston 89, along a Aktorachse 94 translationally movable back and forth.
• the actuator axis 94 corresponds to the longitudinal axis of the actuator piston 82.
• the actuator device 81 further comprises an actuator housing 96, in which two electromagnetic coils are arranged, which serve for the representation of two electromagnets 98, 99.
• the electromagnets 98, 99 cooperate with an armature 100, which at the end facing away from the eccentric 88 of the
• Actuator piston 82 is attached.
• the actuator piston 82 serves to release or interrupt fluid connections between hydraulic connections 101, 102, 103.
• the hydraulic connection 101 is a pressure supply connection or pump connection or high-pressure connection.
• the hydraulic connection 102 is a control pressure connection or working pressure connection or control connection.
• the hydraulic connection 103 is a low-pressure connection or tank pressure connection or diversion connection.
• a valve body 104 is formed, which is arranged in a basic position of the actuator device 81 shown in Figure 5 axially overlapping to the control pressure port 102.
• the control pressure port 102 is connected neither to the pressure supply connection 101 nor to the low-pressure connection 103.
• the coupling spring 91 is supported by its right end in FIGS. 5 to 13 on a shoulder 105 which is formed on the guide body 83. With its left end in FIGS. 5 to 13, the coupling spring 91 is supported on a collar 106, which is formed on the coupling piston 89. In this case, the coupling spring 91 is biased to pressure between the shoulder 105 and the collar 106, that the coupling piston 89 is stably held with its in Figures 5 to 13 left end in contact with the eccentric 88 of the coupling device 85 and the Schwenkverstell Surprise 84.
• the actuator spring 92 is clamped in the axial direction between two spring plates 1 1 1, 1 12.
• the spring plate 1 1 1 is supported in the axial direction on a sleeve 1 13, which, for example, by a press fit, firmly connected to the left in Figures 5 to 13 end of the actuator piston 82.
• Radially outside the sleeve 1 13, the spring plate 1 1 1 1 further supported on a stop sleeve 1 14, which, for example, by a press fit, is firmly connected to the coupling piston 89.
• the spring plate 1 12 is supported in the axial direction on a paragraph 1 16 of the actuator piston 82. Radially outside the paragraph 1 16, the spring plate 1 12 is supported on a radially inwardly angled collar 1 17 of the coupling piston 89.
• Swivel cradle 20 with de-energized coils 18, 19 returned to its central position hydraulically.
• the actuator piston 2 is in its center position, the actuating forces of the coupling spring 11 and the actuator spring 12 cancel each other out.
• a hydraulic connection between the control pressure port 102 and the low pressure port 103 is released by the valve body 104 of the actuator piston 82, as indicated by arrows 132 and 133.
• the hydraulic connection between the control line and the Abêt ein causes the pivoting cradle 86 pivots back, as indicated by an arrow 134, the pivoting cradle 86 is still shown swung out.
• An arrow 135 indicates that the coupling piston 89 and the actuator piston 82 retract.
• Actuator piston 82 is completed, the actuator device 81 assumes its basic position shown in Figure 5 again.
• Figure 10 is indicated by an arrow 141 that the actuator piston 82 is pulled by the solenoid 99 to the right, that is away from the eccentric 88.
• the control pressure port 102 and the control line to the diversion line or the low pressure port 103 is connected.
• an arrow 144 indicates that the pivoting cradle 86 pivots outward with the eccentric 88 in the clockwise direction.
• An arrow 145 indicates that the coupling piston 89 follows the eccentric movement, as a result of which the actuator piston 82 is moved back into its middle position.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Physics & Mathematics (AREA)
• Electromagnetism (AREA)
• Power Engineering (AREA)
• Reciprocating Pumps (AREA)
• Reciprocating, Oscillating Or Vibrating Motors (AREA)

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• 2012
  • 2012-08-17 DE DE102012214622.9A patent/DE102012214622A1/de not_active Withdrawn
• 2013
  • 2013-06-21 WO PCT/EP2013/063021 patent/WO2014026789A1/de active Application Filing
  • 2013-06-21 CN CN201380049592.XA patent/CN104685155A/zh active Pending
  • 2013-06-21 EP EP13731740.0A patent/EP2885501A1/de not_active Withdrawn
• 2015
  • 2015-02-16 IN IN1258DEN2015 patent/IN2015DN01258A/en unknown

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