EP3837446B1 - Système actionneur électrohydrostatique à réservoir d'aspiration - Google Patents

Système actionneur électrohydrostatique à réservoir d'aspiration Download PDF

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Publication number
EP3837446B1
EP3837446B1 EP19753311.0A EP19753311A EP3837446B1 EP 3837446 B1 EP3837446 B1 EP 3837446B1 EP 19753311 A EP19753311 A EP 19753311A EP 3837446 B1 EP3837446 B1 EP 3837446B1
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EP
European Patent Office
Prior art keywords
valve
actuator system
bar
hydraulic fluid
differential cylinder
Prior art date
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Active
Application number
EP19753311.0A
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German (de)
English (en)
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EP3837446A1 (fr
Inventor
Sascha DANY
Reiner Kohlhaas
Achim Helbig
Werner Händle
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Moog GmbH
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Moog GmbH
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
    • F15B7/005—With rotary or crank input
    • F15B7/006—Rotary pump input
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/26—Supply reservoir or sump assemblies
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20561—Type of pump reversible
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • F15B2211/20584—Combinations of pumps with high and low capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • F15B2211/20592—Combinations of pumps for supplying high and low pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/212—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/27—Directional control by means of the pressure source
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/615—Filtering means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/62—Cooling or heating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/785—Compensation of the difference in flow rate in closed fluid circuits using differential actuators

Definitions

  • the present invention relates to an electrohydrostatic actuator system, and more particularly to an electrohydrostatic actuator system having a reservoir.
  • Electrohydrostatic actuator systems are known in the prior art and are mainly used for injection molding machines, presses and deep-drawing devices.
  • prior art actuator systems have at least one cylinder with unequal area ratios. This inequality leads to a difference in volume in the flow of hydraulic fluid in the system, which is not advantageous either for the movement sequence or for the maintenance of the system.
  • the pressure accumulators commonly used in such systems maintain the pressure in the system, but their ability to compensate for a volume difference is at least partially limited by the usually small storage volume and usually lead to a pressure increase or pressure drop.
  • the electrohydrostatic actuator system comprises: a hydraulic machine with variable volume and/or speed, driven by an electric motor, for providing a volume flow of a hydraulic fluid; a Differential cylinder with a piston side and a ring side, and at least one preload source.
  • the actuator system has a closed hydraulic circuit, with pressure being applied to the hydraulic fluid in the hydraulic circuit during operation by means of the hydraulic machine and/or the preload source. Furthermore, according to the invention, the differential cylinder provides the operating modes of a power gear and a rapid gear.
  • a suction tank is connected to the piston side of the differential cylinder via a valve.
  • a second valve designed as a proportional valve is arranged at the connection between the preload source and the piston side of the differential cylinder or between the piston side of the differential cylinder and the replenishment tank.
  • the actuator system according to the invention is referred to as an electrohydrostatic actuator system because it has both an electric motor and a hydraulic machine for providing a volume flow of a hydraulic fluid, and the cylinder is coupled to the hydraulic machine via a hydrostatic transmission.
  • Electric motors are known in the prior art and are used to drive the hydraulic machine.
  • the hydraulic machine is variable in terms of volume and/or speed and can preferably provide two possible directions of flow of the hydraulic fluid in the closed hydraulic circuit during operation.
  • the hydraulic machine can also have either a variable-speed electric motor and a constant pump, or a constant-speed electric motor and a variable-displacement pump, or a variable-speed electric motor and a variable-displacement pump.
  • the selection of the hydraulic machine is determined by factors such as - e.g. - system costs, reliability or permitted noise emissions or efficiency.
  • the actuator system also has a differential cylinder, which includes a ring side and a piston side, as well as a ring surface and a piston surface.
  • a differential cylinder is a hydraulic cylinder in which the cylinder surfaces on the front and rear of the piston differ.
  • the side with the smaller cylinder surface is referred to as the rod side because a piston rod is arranged on this side.
  • the cylindrical surface on the rod side is called the annular surface.
  • the side with the larger cylinder surface of a differential cylinder is the so-called piston side. Either no piston rod is arranged on the piston side, or a piston rod with a smaller diameter than on the rod side.
  • the cylinder surface on the piston side is called the piston surface.
  • the differential cylinder provides the operating modes of power gear and rapid gear.
  • the drive system provides movement of the cylinder, i.e. the differential cylinder, in a first direction, for example towards the workpiece to be machined. This is achieved by means of a volume flow from the hydraulic machine or into or out of the suction tank.
  • the preload source ensures that the hydrostatic transmission is preloaded and provides the hydraulic machine with fluid for compressing the hydraulic fluid.
  • a controller and additional components - e.g. valves - can coordinate the volume flow according to the required movement sequences.
  • the drive system also provides movement of the cylinder in a second direction, e.g., in the opposite direction to the first aforesaid direction. This is also achieved by means of a volume flow of the hydraulic machine and a volume flow into and out of the suction tank.
  • An electro-hydrostatic system provides at least the operating modes of a power gear and a rapid gear. These modes of operation are provided by means of the differential cylinder.
  • the differential cylinder can be implemented as one cylinder or as a plurality of cylinders working in parallel. These additional cylinders can possibly have a different sequence of movements than the differential cylinder (main cylinder); however, they are part of the electro-hydrostatic system according to the invention and part of the closed hydraulic circuit.
  • the large piston surface acts in the power gear, i.e. high power at comparatively low speed.
  • the ring surface which is smaller than the piston surface, acts in rapid traverse, i.e. low force at high speed.
  • the actuator system according to the invention has a preload source.
  • This can additionally have a reservoir for buffering the preload pressure, this reservoir generally having a smaller volume than the replenishment tank.
  • the hydraulic fluid provided from the preload source is pressurized at a pressure of between 5 bar and 50 bar, in particular between 10 bar and 40 bar, preferably between 15 bar and 35 bar, particularly preferably between 20 bar and 30 bar prestressed.
  • the hydraulic machine can be pressurized on both pump connections, ie on the connection in the direction of the piston side of the differential cylinder and on the connection in the direction of the ring side of the differential cylinder.
  • pressure in the pressure accumulator refers to the pressure of the hydraulic fluid in the respective devices.
  • volume refers to the volume of hydraulic fluid in the pressure accumulator.
  • the preload source is hydraulically connected via a valve to the hydraulic machine and the ring side of the differential cylinder.
  • the valve can be a check valve which, at a threshold pressure, feeds preloaded hydraulic fluid from the preload source into the system.
  • the preload source can in particular also include a pressure accumulator and/or an additional pump.
  • the piston side and the ring side have different volumes or areas.
  • the hydraulic fluid flows out of the ring side of the differential cylinder via the hydraulic machine into the piston side of the differential cylinder. Because the ring side has a smaller volume than the piston side, additional volume of hydraulic fluid is required to fill the piston side and provide pressure equalization.
  • the biasing source generally has a small volume of hydraulic fluid; this is usually too small to compensate for the difference in volume between the piston side and the ring side, since the preload source is mainly used to prevent cavitations in the hydraulic machine and not for complete volume compensation.
  • a suction tank is integrated into the system.
  • the suction reservoir is hydraulically connected directly to the piston side of the differential cylinder and preferably by means of a non-return valve.
  • the non-return valve opens, for example, as soon as there is a vacuum on the piston side of the differential cylinder compared to the reservoir. In this way, a flow is provided from the suction reservoir into the piston side, which equalizes the difference in volume.
  • the suction reservoir is preloaded with a lower pressure, preferably and according to a further embodiment of the invention with a pressure of less than 5 bar, in particular less than 4 bar, preferably less than 3 bar, particularly preferably less than 2 bar, and particularly preferably less than 1 bar. This allows the check valve to open only when the pressure in the piston side is actually too low and the volume difference needs to be compensated.
  • the suction tank can be separated from false air or can be charged with a protective gas, which, among other things, reduces oxidation of the hydraulic fluid.
  • the hydraulic fluid in the suction reservoir essentially has the ambient pressure and/or is arranged above the piston side of the differential cylinder.
  • the replenishment container can be arranged below the piston side of the differential cylinder, in which case a volume flow from the replenishment container into the piston side of the differential cylinder must be provided actively, such as by replenishment, and is not automatically guaranteed by gravity.
  • the replenishment container has a volume that is equal to or greater than the difference in volume of the closed system in a force end position and an upper end position of the differential cylinder.
  • the suction tank is hydraulically connected to the piston side of the differential cylinder via a valve.
  • the valve can be a controlled non-return valve, and in particular a pilot-operated non-return valve.
  • the valve can be a pilot operated check valve which can be piloted by means of a control circuit and a directional control valve.
  • valve is a controlled 2-way valve with a flow position and check function or an electrically controlled 3-way valve with a flow position, a blocking position and check function.
  • a controlled non-return valve between the reservoir and the piston side of the differential cylinder is particularly advantageous during rapid traverse to keep the valve actively open, or during decompression.
  • the system is decompressed between the power mode and the rapid mode. After machining the workpiece with increased pressure, it must first be relieved before the cylinder can be moved in rapid traverse; this is done by decompressing the hydraulic fluid in the system.
  • the non-return valve between the reservoir and the piston side of the cylinder can be controlled, or if the non-return valve is embedded in a 2-way valve that has a flow position, it can be opened during decompression so that the pressure in the system is relieved and a volume flow from the Piston side of the differential cylinder can be done back in the suction tank.
  • the pressure level of the reservoir is independent of the preload of the pump.
  • the suction tank compensates for the lack of oil volume in the system, which is required in the event of fluctuating temperatures in the system and/or compression of the smaller cylinder surface and generally during the process. Furthermore, the formation of cavitation is thus at least partially prevented.
  • a further valve is arranged in the line between the ring side of the differential cylinder and a connection of the hydraulic machine, which has a flow position and a blocking position.
  • This is preferably to be understood as a safety valve. If there is a problem in the system and it is necessary to stop the cylinder without causing the cylinder to drop, this valve can be set to the off position. In all other situations, this valve is set to flow.
  • the preload source is configured as a pump
  • its pump inlet is connected to the replenishment tank via a line
  • the pump outlet is integrated into the circuit via another line with a valve or check valve.
  • the suction tank is hydraulically connected to two lines.
  • One line connects the replenishment tank to the piston side of the differential cylinder, while the other line hydraulically connects the replenishment tank to a section between the hydraulic machine and the ring side of the differential cylinder.
  • another pump is arranged in this additional line, which at the same time assumes the function of the preload source, i.e. the pump applies sufficient pressure to the hydraulic fluid to preload the hydraulic machine.
  • the hydraulic fluid is taken directly from the suction reservoir.
  • the closed system has a device for cleaning the hydraulic fluid.
  • the device is preferably arranged between the suction tank and a pump inlet of the pump or between a pump outlet of the pump and a check valve.
  • the after-suction tank can have a device for venting the hydraulic fluid and/or a device for cooling the hydraulic fluid
  • the additional pump is thus a volume flow of hydraulic fluid provided to the replenishment tank through the additional line and, according to a further embodiment of the invention, through a cleaning device.
  • additional units in the container such as filtering devices, cooling devices and venting devices for filtering, cooling or venting the hydraulic fluid contained in the container is also advantageous.
  • the hydraulic fluid In order to clean hydraulic fluid, the hydraulic fluid must be in motion.
  • the flow can, for example, be provided by a further circuit in the after-suction tank.
  • the advantage of the embodiment described above is that both cleaning and pressurization take place through a further line, which results in energy, material and cost savings.
  • the contaminated hydraulic fluid is fed into the suction tank, for example during decompression, from where it can be cleaned through this additional line and fed back into the circuit.
  • the valve which is arranged between the piston side and the replenishment container, can be opened according to further embodiments of the invention.
  • hydraulic fluid thus flows from the piston side of the differential cylinder into the replenishment tank.
  • This hydraulic fluid contains dirt and is usually very hot due to friction, which is why filtering and cooling this fluid is also beneficial for the maintenance of the entire system.
  • the system according to the invention is not limited to a single differential cylinder and, in further embodiments according to the invention, can also have several differential cylinders which work together or independently of one another, but are arranged in the same system.
  • the system according to the invention in any of its arbitrary embodiments can be embedded in a method according to the invention in which, when the actuator system is extended in rapid traverse, the suction reservoir pumps hydraulic fluid into the piston side of the differential cylinder to compensate for a volume of hydraulic fluid in the closed system.
  • FIG 1 shows an exemplary embodiment of an actuator system 1 not covered by the claimed invention.
  • the system includes a differential cylinder 20, which has a piston side 22a and a ring side 22b.
  • the piston side 22a is hydraulically connected to the ring side 22b of the differential cylinder 20 by means of a line 71 and a line 72 .
  • a hydraulic machine 11 which is driven by an electric motor 10 and is variable in volume and/or speed, with the hydraulic machine being a pump 11 in this exemplary embodiment.
  • the line 71 thus connects the piston chamber 22a of the differential cylinder 20 to a connection of the pump 11 and the line 72 connects the ring side 22b of the differential cylinder to the other connection of the pump 11.
  • a 2-way valve 80 is also connected in the line 72 which has a flow position and has a locked position. This valve 80 serves as a safety valve and prevents, among other things, the piston from falling out in the event of a defect in the actuator system 1 or in the course of operation. Except in such emergency situations, the valve 80 is switched to flow.
  • the pump 11 can rotate in both directions of rotation according to the arrow shown and thus provide either a volume flow of hydraulic fluid in the direction of the piston side 22a or in the direction of the ring side 22b of the differential cylinder 20 .
  • a bias source 60 which may include an accumulator 30 and a source 65 , is also connected to line 72 via a check valve 70 .
  • the hydraulic fluid in the pressure accumulator 30 has a pressure which is preferably higher than the ambient pressure. In the event of a pressure loss in the system 1, the necessary pressure is fed from the pressure accumulator 30 or from the preload source 60 via the check valve 70 into the actuator system 1.
  • the source 65 provides the actual pressure in the accumulator 30, while the accumulator generally functions as an accumulator to compensate for volume.
  • figure 1 The position of the valves in the description of figure 1 is only to be understood as an example, since this figure serves to show the individual devices and their connection to describe, and not to determine operating modes or the position of the valves in different operating situations; this is done in the following figures 2 .
  • Figure 2a Figure 12 shows the exemplary embodiment of the system figure 1 , which is not covered by the claimed invention, in the "down" rapid traverse mode. Most of the elements used and the reference numbers are the same as in FIG 1 This operating condition is caused when the piston of the differential cylinder needs to be brought down quickly towards the tool.
  • the pump 11 operates to provide a flow of hydraulic fluid from the ring side 22a of the differential cylinder 20 towards the piston side 22a of the differential cylinder.
  • the safety valve 80 is set to flow.
  • the volume of ring side 22a of differential cylinder 20 is smaller than the volume of piston side 22a of differential cylinder 20.
  • the directional control valve 48 is set in such a way that the check valve 40 between the replenishment tank 50 and the piston side 22a is opened and hydraulic fluid flows from the replenishment tank into the piston side.
  • the differential cylinder 20 is moved in the direction of the broken arrow.
  • Figure 2b shows the exemplary embodiment of the system figure 1 , which is not covered by the claimed invention, in the power gear "down" operating state. Most of the elements used and the reference numbers are the same as in FIG 1 .
  • the required increased pressure in the hydraulic fluid is provided by the hydraulic machine.
  • the pump 11 works as in the Figure 2a , in which it provides a flow of hydraulic fluid from the ring side 22b of the differential cylinder 20 into the piston side 22a of the differential cylinder 20 .
  • the missing volume flow is supplemented from the pressure accumulator 30 or preload source 60.
  • the check valve 48 remains closed and there is no flow from or into the suction tank 50.
  • Figure 2c Figure 12 shows an exemplary embodiment of the system, not covered by the claimed invention, during decompression.
  • the directional control valve 48 is switched from the check valve position to the flow position; thus, a volume flow into the after-suction container 50, according to the arrows shown, is made possible.
  • FIG. 2d An alternative type of decompression is described in Figure 2d shown.
  • the system off Figure 2b has, instead of a single check valve 70, a controlled 2-way valve 75, which is arranged between the pressure accumulator 30 and the line 72.
  • the 2-way valve 75 is switched as a check valve; on decompression it becomes - as in Figure 2d evident - switched to flow. Since the pressure of the hydraulic fluid in the cylinder chambers and the lines 71 and 72 is higher than in the accumulator 30, two events take place when the valve 75 switches to flow.
  • the pressure in the entire system 1 relaxes so that decompression occurs; secondly, there is a volume flow from the line 71 through the pump 11 into the pressure accumulator 30, as a result of which the volume of the pressure accumulator 30 is refilled and the pressure of the hydraulic fluid in the pressure accumulator 30 is increased again.
  • This embodiment is advantageous because energy is recovered into the accumulator. Furthermore, a movement of the pump 11 is caused by the volume flow from the piston chamber 22a through the pump 11 into the pressure accumulator 30 .
  • the prime mover 10 operates as an energy generator and further improves energy recovery or reduces energy loss.
  • the energy recovered can be reused according to the needs of the system 1, for example for the hydraulic machine.
  • the pump 11 works in the opposite direction than in the case of rapid traverse downwards, so that a volume flow is provided from the piston side 22a of the differential cylinder into the ring side 22b of the differential cylinder 20.
  • the directional control valve 48 is switched to flow, as a result of which the difference in volume of the hydraulic fluid flows in the direction of the arrow from the piston side 22a of the differential cylinder 20 into the replenishment tank 50 .
  • the piston of the differential cylinder is pushed up by the increased pressure in ring side 22b and the low pressure in piston side 22a.
  • FIG 3 a further example embodiment of the system 1 not covered by the claimed invention is presented. Most of the elements used and the reference numbers are the same as in FIG 1 .
  • the check valve 40 by means of a control circuit - comprising a 2-way valve 45 - controlled.
  • a line 44 connects the piston side 22a of the differential cylinder 20 to the check valve 40 via the 2-way valve.
  • the directional valve 45 has a flow position and a position in which the overpressure from the upper part of the line 44 is decompressed and deviates into a container.
  • the check valve 40 is thus opened depending on the pressure in the piston side 22a. If the pressure in the piston side 22a of the differential cylinder 20 is high enough and the valve 45 is switched to flow, the check valve 40 opens due to the pressure on the piston side 22a. Since the valve 40 is open, the remaining hydraulic fluid can flow back into the replenishment tank.
  • FIG 4 shows another exemplary embodiment of the system not covered by the claimed invention figure 3 .
  • the check valve 40 is controlled by means of the control circuit or the 2-way valve 45 .
  • the accumulator 30 of the previous figures has been replaced by a pump 65 in this exemplary embodiment.
  • the pump 65 only works in one direction and accordingly has a pump inlet and a pump outlet.
  • the pump inlet is connected to the after-suction tank 50 by means of a line 62
  • the pump outlet is connected to the line 72 by means of a line 63 via the check valve 70 .
  • the pump 65 works like the pressure accumulator 30 from the previous figures, in that it generates an overpressure which is used to preload the system.
  • the hydraulic fluid used in the pump 65 is shown in this example
  • a cleaning device 90 for cleaning the hydraulic fluid is shown in this exemplary embodiment of the system 1, arranged between the suction tank 50 and the pump 65.
  • the hydraulic fluid that is sucked in by the pump 60 and accordingly fed into the line 72 is thus cleaned beforehand and preferably also vented.
  • This embodiment is advantageous because a closed circuit is provided in which the after-suction tank 50 is used as a static device, for example for cooling the hydraulic fluid, and the hydraulic fluid can be cleaned by the cleaning device 90 and fed back into the system instead of providing a further circuit. which promotes and cleans the fluid in the suction tank, but cannot be reused immediately.
  • the figure 5 1 shows a system 1 corresponding to the system described above, but with a different arrangement according to the invention.
  • a line 72 connects the replenishment tank 50 via a check valve 73 to the node 100, through which the hydraulic fluid can be directed both into the ring side 22b of the differential cylinder 20 and through the pump 11 into the line 71. Furthermore, the replenishment tank 50 is hydraulically connected to the preload source 60 and in particular to the input of the pump 65 by means of the line 72 and the line 62 .
  • the pump 11 is connected to both the line 71 and the line 72 .
  • the hydraulic fluid is preloaded by means of the preload source 60, with the pump 65 providing the preload of the hydraulic fluid, similar to the embodiment in FIG figure 4 .
  • This is a pump which can only work on one side.
  • an additional controlled proportional valve in particular a controlled proportional pressure relief valve 85 on the line 71, is arranged between the preload source 60 or the pump 65 and the piston side 22a.
  • the proportional valve 85 is preferably used for decompression of the system 1, as in previous
  • a preload valve 68 is hydraulically connected to the line 71 and hydraulically connected via the line 75 and a check valve 69 to the line 63 and also to a connection of the hydraulic machine 11 .

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)

Claims (13)

  1. Système actionneur électrohydrostatique (1) comprenant :
    une machine hydraulique (11) à volume et/ou vitesse variable entraînée par un moteur électrique (10), pour la fourniture d'un flux volumique d'un fluide hydraulique ;
    un vérin différentiel (20) comprenant un côté piston (22a) et un côté joint (22b) ;
    au moins une source de précontrainte (60) ;
    le système actionneur (1) présentant un circuit hydraulique fermé et le liquide hydraulique étant mis sous pression dans le circuit hydraulique au moyen de la machine hydraulique (11) et/ou de la source de précontrainte (60) durant le fonctionnement ; et
    le vérin différentiel (20) fournissant les modes de fonctionnement d'une course de force et d'une course rapide, et
    un réservoir d'aspiration (50) étant connecté au côté piston (22a) du vérin différentiel (20) à travers une première soupape (40) pour la compensation d'un volume du fluide hydraulique dans le circuit hydraulique fermé (1), une deuxième soupape (85) connectant le côté piston (22a) à la source de précontrainte (60) ou au réservoir d'aspiration (50),
    caractérisé en ce que
    la deuxième soupape est formée comme une soupape proportionnelle (85).
  2. Système actionneur électrohydrostatique (1) selon la revendication 1, dans lequel le fluide hydraulique dans le réservoir d'aspiration (50) est précontraint avec une pression inférieure à 5 bar, de préférence inférieure à 4 bar, de préférence inférieure à 3 bar, encore plus préférablement inférieure à 2 bar, et encore plus préférablement inférieure à 1 bar.
  3. Système actionneur électrohydrostatique (1) selon l'une quelconque des revendications précédentes, dans lequel le réservoir d'aspiration (50) présente un volume qui est égal ou supérieur à la différence de volume du système fermé (1) dans une position de force finale et position finale supérieure du vérin différentiel (20).
  4. Système actionneur électrohydrostatique (1) selon l'une quelconque des revendications précédentes, dans lequel la première soupape (4) est un clapet anti-retour (40) commandé, en particulier un clapet anti-retour pouvant être déverrouillé.
  5. Système actionneur électrohydrostatique (1) selon l'une quelconque des revendications précédentes, dans lequel le fluide hydraulique de la source de précontrainte (60) présente une pression située entre 5 bar et 50 bar, de préférence entre 10 bar et 40 bar, encore plus préférablement entre 15 bar et 35 bar, encore plus préférablement entre 20 bar et 30 bar.
  6. Système actionneur électrohydrostatique (1) selon l'une quelconque des revendications précédentes, dans lequel la source de précontrainte (60) est connectée hydrauliquement à travers une troisième soupape (70) à la conduite (72) entre le raccord de la machine hydraulique (11) au côté joint (22b) et le côté joint (22b) du vérin différentiel (20).
  7. Système actionneur électrohydrostatique (1) selon la revendication 6, dans lequel la troisième soupape (70) est un clapet anti-retour.
  8. Système actionneur électrohydrostatique (1) selon l'une quelconque des revendications 6 ou 7, dans lequel la source de précontrainte (60) comprend une pompe (65), dont l'entrée de pompe est connectée à travers une conduite (62) au réservoir d'aspiration (50) et une sortie de pompe de la pompe (65) est connectée à travers une conduite (63) à la troisième soupape (70).
  9. Système actionneur électrohydrostatique (1) selon l'une quelconque des revendications précédentes, dans lequel au moins une quatrième soupape (80) comprenant une position de circulation et une position de blocage, laquelle est disposée dans une conduite (72) entre le côté joint (22b) du vérin différentiel (20) et un raccord de la machine hydraulique (11) ;
  10. Système actionneur électrohydrostatique (1) selon l'une quelconque des revendications précédentes, dans lequel la machine hydraulique (11) peut être soumise à une pression sur les deux raccords de pompe.
  11. Système actionneur électrohydrostatique (1) selon l'une quelconque des revendications précédentes, dans lequel le réservoir d'aspiration (50) présente un dispositif pour purger le fluide hydraulique et/ou un dispositif pour refroidir le fluide hydraulique.
  12. Système actionneur électrohydrostatique (1) selon l'une quelconque des revendications précédentes, dans lequel le système (1) présente plusieurs vérins différentiels.
  13. Utilisation du système actionneur électrohydrostatique (1) selon l'une quelconque des revendications 1 à 12 dans une presse hydraulique, dans un dispositif d'emboutissage ou dans un système de moulage par injection.
EP19753311.0A 2018-08-16 2019-08-08 Système actionneur électrohydrostatique à réservoir d'aspiration Active EP3837446B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018120000.5A DE102018120000A1 (de) 2018-08-16 2018-08-16 Elektrohydrostatisches Aktuatorsystem mit Nachsaugbehälter
PCT/EP2019/071360 WO2020035398A1 (fr) 2018-08-16 2019-08-08 Système actionneur électrohydrostatique à réservoir d'aspiration

Publications (2)

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EP3837446A1 EP3837446A1 (fr) 2021-06-23
EP3837446B1 true EP3837446B1 (fr) 2022-09-28

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EP (1) EP3837446B1 (fr)
CN (1) CN112567139B (fr)
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WO (1) WO2020035398A1 (fr)

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DE102018128318A1 (de) * 2018-11-13 2020-05-14 Moog Luxembourg S.à.r.l. Elektrohydrostatisches Aktuatorsystem
US11512716B2 (en) * 2020-01-31 2022-11-29 Bosch Rexroth Corporation Hydraulic axis with energy storage feature
CN118375643A (zh) * 2024-06-25 2024-07-23 中联重科股份有限公司 电静液执行器系统的控制方法、控制器、作业机械和车辆

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US20210332831A1 (en) 2021-10-28
CN112567139A (zh) 2021-03-26
DE102018120000A1 (de) 2020-02-20
WO2020035398A1 (fr) 2020-02-20
EP3837446A1 (fr) 2021-06-23
CN112567139B (zh) 2023-06-13
US11603867B2 (en) 2023-03-14

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