EP3837446A1 - Elektrohydrostatisches aktuatorsystem mit nachsaugbehälter - Google Patents
Elektrohydrostatisches aktuatorsystem mit nachsaugbehälterInfo
- Publication number
- EP3837446A1 EP3837446A1 EP19753311.0A EP19753311A EP3837446A1 EP 3837446 A1 EP3837446 A1 EP 3837446A1 EP 19753311 A EP19753311 A EP 19753311A EP 3837446 A1 EP3837446 A1 EP 3837446A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- actuator system
- valve
- hydraulic fluid
- bar
- pump
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 239000012530 fluid Substances 0.000 claims abstract description 79
- 230000036316 preload Effects 0.000 claims description 16
- 238000004140 cleaning Methods 0.000 claims description 10
- 238000001816 cooling Methods 0.000 claims description 8
- 238000000034 method Methods 0.000 claims description 6
- 230000000903 blocking effect Effects 0.000 claims description 5
- 238000013022 venting Methods 0.000 claims description 5
- 230000002706 hydrostatic effect Effects 0.000 claims description 4
- 238000001746 injection moulding Methods 0.000 claims description 3
- 230000033001 locomotion Effects 0.000 abstract description 10
- 230000006837 decompression Effects 0.000 description 14
- 230000006870 function Effects 0.000 description 4
- 238000001914 filtration Methods 0.000 description 3
- 238000012986 modification Methods 0.000 description 3
- 230000004048 modification Effects 0.000 description 3
- 238000003825 pressing Methods 0.000 description 3
- 230000005540 biological transmission Effects 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 230000001419 dependent effect Effects 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 238000011010 flushing procedure Methods 0.000 description 2
- ZZUFCTLCJUWOSV-UHFFFAOYSA-N furosemide Chemical compound C1=C(Cl)C(S(=O)(=O)N)=CC(C(O)=O)=C1NCC1=CC=CO1 ZZUFCTLCJUWOSV-UHFFFAOYSA-N 0.000 description 2
- 238000012423 maintenance Methods 0.000 description 2
- 238000011084 recovery Methods 0.000 description 2
- 238000007792 addition Methods 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000003139 buffering effect Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000003647 oxidation Effects 0.000 description 1
- 238000007254 oxidation reaction Methods 0.000 description 1
- 230000001681 protective effect Effects 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- 238000003860 storage Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- 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
- Electrohydrostatic actuator system with suction tank
- the present invention relates to an electrohydrostatic actuator system, and in particular to an electrohydrostatic actuator system which has a suction tank.
- Electrohydrostatic actuator systems are known in the prior art and are mainly used for injection molding machines, presses and deep-drawing devices. Actuator systems from the prior art usually have at least one cylinder with unequal area ratios. This inequality leads to a volume difference in the flow of the hydraulic fluid in the system, which is neither advantageous for the movement sequence nor for the maintenance of the system.
- the pressure accumulators usually 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 generally lead to an increase or decrease in pressure.
- Embodiments and modifications are the subject of the dependent claims.
- a method according to the invention for using the system according to the invention is specified in claim 19.
- the electrohydrostatic actuator system comprises: a volume and / or speed variable driven by an electric motor
- Hydro machine for providing a volume flow of a hydraulic fluid; on Differential cylinder with one piston side and one ring side, as well as at least one preload source.
- the actuator system has a closed hydraulic circuit, the hydraulic fluid in the hydraulic circuit being pressurized during operation by means of the hydraulic machine and / or the preload source.
- Differential cylinder according to the invention the operating modes of a power gear and a rapid gear ready.
- Differential cylinder connected via a valve.
- the actuator system according to the invention is referred to as an electrohydrostatic actuator system since it has both an electric motor and a hydraulic machine
- 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 serve to drive the hydraulic machine.
- the hydraulic machine is variable in volume and / or speed and can preferably operate in two possible directions of flow of the hydraulic fluid in the closed mode
- 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 dependent on factors such as - e.g. - System cost, reliability, or approved noise emissions or efficiency determined.
- the actuator system also has a differential cylinder, which comprises an annular side and a piston side, as well as an annular surface and a piston surface.
- a differential cylinder is understood to mean 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 cylinder surface on the rod side is called the ring surface.
- the differential cylinder is the so-called piston side. There is either no piston rod 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 a power gear and rapid gear.
- the drive system provides movement of the cylinder, i.e. of the differential cylinder, ready in a first direction, e.g. B. in the direction of the workpiece to be machined. This is achieved by means of a volume flow from the hydraulic machine or in or out of the suction tank.
- the bias source provides a bias for the
- the drive system provides movement of the cylinder in a second direction, e.g. in the opposite direction to the first aforementioned direction. This is also achieved by means of a volume flow of the hydraulic machine and a volume flow into or out of the suction tank.
- An electro-hydrostatic system according to the invention provides at least that
- the differential cylinder can be implemented as one cylinder or as a plurality of cylinders that work in parallel. These additional cylinders can possibly have a different sequence of movements than that
- electro-hydrostatic system according to the invention and part of the closed hydraulic circuit.
- the large piston surface acts in the power path, i.e. high power at comparatively low 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 biasing source.
- This can additionally have a memory for buffering the prestressing pressure, this memory generally having a smaller volume than the suction tank.
- the hydraulic fluid provided from the preload source is at a pressure 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 biased.
- An increased pressure of the hydraulic fluid is necessary in particular in the power gear operating mode; wherein the hydraulic fluid is applied by means of the hydraulic machine.
- the biasing source provides the necessary fluid for compression.
- the hydraulic machine is 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 can be pressurized.
- pressure in the pressure accumulator means the pressure of the hydraulic fluid in the respective devices.
- volume means a low volume of hydraulic fluid in the pressure accumulator.
- the biasing source is hydraulically connected to the hydraulic machine and the ring side of the differential cylinder via a valve.
- the valve can be a non-return valve which feeds hydraulic fluid that is preloaded at a threshold pressure from the preload source into the system.
- the biasing source can in particular also comprise a pressure accumulator and / or an additional pump.
- valve in particular a proportional valve, at the connection between the biasing source and the
- Differential cylinder and the suction tank arranged.
- the piston side and the ring side have different volumes or areas. For example, when the cylinder is pushed toward the tool, the hydraulic fluid flows from the ring side of the differential cylinder via the hydraulic machine into the piston side of the differential cylinder. Since the ring side has a smaller volume than the piston side, additional hydraulic fluid volume is necessary around the
- the biasing source generally has a small volume of hydraulic fluid; this is
- a suction tank is integrated into the system.
- the suction tank is hydraulically connected directly to the piston side of the differential cylinder and preferably by means of a check valve.
- the check valve opens e.g. as soon as there is a vacuum on the piston side of the differential cylinder in relation to the suction tank. This provides a flow from the suction tank into the piston side, which compensates for the difference in volume.
- the suction tank is prestressed at a lower pressure, preferably and according to a further embodiment according to 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 enables the check valve to only open when the pressure in the piston side is actually too low and the volume difference has to be compensated for.
- the suction tank can be separated from false air or a protective gas can be applied, oxidation of the hydraulic fluid is reduced.
- the hydraulic fluid in the suction tank essentially knows the ambient pressure and / or is arranged above the piston side of the differential cylinder.
- Differential cylinder can be arranged, then a volume flow from
- the suction container has a volume that is equal to or greater than the volume difference of the closed system in a force end position and an upper end position of the
- the Nachsaugbc dockcr is hydraulically connected to the piston side of the differential cylinder via a valve.
- the valve can be a controlled check valve, and in particular an unlockable check valve.
- the valve can be an unlockable check valve, which can be unlocked by means of a control circuit and a directional 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 division and check function.
- suction tank and the piston side of the differential cylinder are particularly advantageous for rapid traverse in order to keep the valve actively open, or also for
- the system is decompressed between the force mode and the rapid mode. After machining the workpiece with increased pressure, it must be relaxed for the first time before the cylinder can be moved in rapid traverse; this is done by decompression of the hydraulic fluid in the system.
- check valve between the suction tank and the piston side of the cylinder is controllable, or if the check 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 relaxes 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 suction tank is independent of the preload of the pump.
- the lack of oil volume in the system is compensated for by the suction tank, which is required in the event of fluctuating temperatures in the system and / or when the smaller cylinder area is compressed and generally during the process. Furthermore, the formation of cavitations at least partially prevented.
- Hydromachine arranged a further valve, which has a flow position and a blocking position.
- the pump inlet is connected to the suction tank via a line, while the pump outlet is integrated into the circuit via a further line with a valve or check valve.
- the suction tank is hydraulically connected to two lines.
- One line connects the suction tank to the piston side of the differential cylinder, while the other line hydraulically connects the suction tank to a section between the hydraulic machine and the ring side of the differential cylinder.
- a further pump is arranged in accordance with this embodiment of the invention, which at the same time takes over 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 in this case
- Embodiment taken directly from the suction tank.
- 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.
- a volume flow of hydraulic fluid is thus by the additional pump the suction tank through the additional line and, according to a further embodiment of the invention, provided by a cleaning device.
- Filtering devices, cooling devices and venting devices for filtering, cooling or venting the hydraulic fluid contained in the container are further advantageous.
- the flow can be provided, for example, in the suction tank by a further circuit. It is advantageous in the embodiment described above that both cleaning and pressurization take place through a further line, which results in energy, material and cost savings.
- the contaminated hydraulic fluid is passed, for example, during decompression into the suction tank, from where it can be cleaned and fed back into the circuit through this additional line.
- the valve which is arranged between the piston side and the suction tank, can be opened according to further embodiments according to the invention.
- hydraulic fluid flows from the piston side of the differential cylinder in the suction tank.
- This hydraulic fluid contains dirt and is usually very warm due to the friction, which is why filtering and cooling this fluid is also advantageous 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 a plurality of differential cylinders which work with one another or independently of one another, but are arranged in the same system.
- the system according to the invention in any of its embodiments can be embedded, in particular, in a method according to the invention, in which when the actuator system extends in rapid traverse, the suction tank to compensate for a volume of hydraulic fluid in the closed system, hydraulic fluid conveys into the piston side of the differential cylinder.
- the entire system according to the invention, as well as the method according to the invention for operating the system are according to the invention for use in a
- Hydraulic press a deep-drawing device, an injection molding device or
- Fig. 3 a schematic representation of another invention
- Fig. 4 a schematic representation of another invention
- Embodiment of the system with a cleaning device Embodiment of the system with a cleaning device
- Fig. 5 a schematic representation of another invention
- Figure 1 shows an exemplary embodiment of an inventive
- Actuator system 1 The system comprises a differential cylinder 20 which has a piston side 22a and an annular 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 volume and / or speed-variable hydraulic machine 11 driven by an electric motor 10 is arranged, in which it is exemplary
- Embodiment according to the invention the hydraulic machine is a pump 11.
- 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, which is a flow position and has a locking division. This valve 80 serves as a safety valve and prevents, among other things. the falling of the piston in the event of a defect in the actuator system 1 or in
- valve 80 is switched to flow.
- the pump 11 can rotate in both directions of rotation according to the arrow shown and thus either provide 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 biasing source 60 which can include a pressure accumulator 30 and a source 65, is also connected to the 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 from the pressure accumulator 30 or from the biasing source 60 is via the
- the source 65 provides the actual pressure in the pressure accumulator 30, while the pressure accumulator generally has the function of a memory for balancing the volume.
- FIG. 1 The position of the valves in the description of FIG. 1 is only to be understood as an example, since this figure serves the individual devices and their connection to describe, and not about operating modes or the position of the valves in
- FIG. 2a shows the exemplary embodiment according to the invention of the system from FIG. 1 in the rapid downward operating state. Most of the elements used and the reference numerals are the same as in FIG. 1
- This operating state is caused when the piston of the differential cylinder is to be brought down quickly in the direction of the tool.
- the pump 11 operates such that a flow of hydraulic fluid from the ring side 22a of the
- Differential cylinder 20 is provided in the direction of the piston side 22a of the differential cylinder.
- the safety valve 80 is set to flow.
- the volume of the ring side 22a of the differential cylinder 20 is smaller than the volume of the piston side 22a of the differential cylinder 20.
- the directional control valve 48 is set such that the check valve 40 between the suction tank 50 and the piston side 22a is opened and hydraulic fluid flows from the suction tank into the piston side.
- the differential cylinder 20 is moved according to the direction of the dashed arrow.
- FIG. 2b shows the exemplary embodiment according to the invention of the system from FIG. 1 in the “downward” power mode. Most of the elements used and the reference numerals are the same as in FIG. 1.
- the required increased pressure in the hydraulic fluid is determined by the
- the pump 11 operates, as in FIG. 2a, by providing a hydraulic fluid flow from the ring side 22b of the differential cylinder 20 into the piston side 22a of the differential cylinder 20.
- Volume flow is supplemented from the pressure accumulator 30 or biasing source 60.
- the check valve 48 remains closed and there is no flow from or into the suction tank 50.
- Decompression can include according to two different exemplary
- Embodiments take place.
- FIG. 2c shows an exemplary embodiment of the system according to the invention during decompression.
- the directional control valve 48 is from the position of the
- FIG. 2d An alternative type of decompression is shown in Figure 2d.
- the system from FIG. 2b has a controlled 2-way valve 75, which is arranged between the pressure accumulator 30 and the line 72.
- the 2-way valve 75 is used as
- the recovered energy can be reused according to the needs of system 1, for example for the hydraulic machine.
- Differential cylinder can be moved upwards again.
- the position of the valves and the volume flow of hydraulic fluid is shown in more detail in FIG. 2e. Most of the elements used and the reference numerals are the same as in the previous figures.
- the pump 11 operates in the opposite direction to the rapid downward movement, so that a volume flow from the piston side 22a of the
- Differential cylinder is provided in the ring side 22b of the differential cylinder 20.
- the directional control valve 48 is switched to flow, whereby the volume difference of the hydraulic fluid in the direction of the arrow from the piston side 22a of the differential cylinder 20 into the
- FIG. 3 shows a further exemplary embodiment of the system 1 according to the invention. Most of the elements used are and
- the suction tank 50 and the piston side 22a of the differential cylinder 20 are different in contrast to FIG. 1.
- the check valve 40 is 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 control valve 45 has a flow position and a position in which the excess pressure is decompressed from the upper part of the line 44 and escapes into a container.
- the check valve 40 is thus opened depending on the pressure in the piston side 22a. So is the pressure in the piston side 22a
- FIG. 4 shows a further exemplary, non-limiting embodiment of the system from FIG. 3.
- the check valve 40 is controlled by means of the control circuit or the 2-way valve 45.
- the pressure accumulator 30 from the previous figures in this exemplary embodiment according to the invention was replaced by a pump 65.
- the pump 65 operates in one direction only, and accordingly has a pump inlet and a pump outlet.
- the pump inlet is connected to the suction tank 50 by means of a line 62, while the pump outlet is connected to the line 72 by means of a line 63 via the check valve 70.
- the pump 65 operates like the pressure accumulator 30 from the previous figures, in which it generates an overpressure which is used to pretension the system.
- the hydraulic fluid used by the pump 65 is exemplary in this Embodiment removed from the suction tank via line 62.
- Embodiment of the system 1 a cleaning device 90 for cleaning the hydraulic fluid, arranged between the suction tank 50 and the pump 65.
- the hydraulic fluid that is sucked in by the pump 60 and correspondingly fed into the line 72 is cleaned beforehand and preferably also vented.
- This embodiment is advantageous because a closed circuit is provided in which the suction tank 50 is used as a static device, for example for cooling the hydraulic fluid and the hydraulic fluid through the
- Cleaning device 90 can be cleaned and fed back into the system instead of providing a further circuit which conveys and cleans the fluid in the suction tank, but cannot be reused immediately.
- FIG. 5 shows a system 1 corresponding to the system described above, but with a different arrangement.
- connection between the suction tank 50 and the piston side 22a of the differential cylinder 20 is by means of a through
- Control valve 45 controlled check valve 40 guaranteed.
- a line 72 connects the via a check valve 73
- 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, the pump 65 providing the preload of the hydraulic fluid, similar to that in FIG.
- Embodiment of Figure 4. This is a pump that can only work on one side.
- Proportional pressure relief valve 85 is arranged on line 71, between the preload source 60 or the pump 65 and the piston side 22a.
- the proportional valve 85 is preferably used to decompress the system 1, as in previous ones Embodiments has been explained.
- a preload valve 68 is hydraulically connected to line 71 and hydraulically connected via line 75 and a check valve 69 to line 63 and also to a connection of 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)
Abstract
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Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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DE102018120000.5A DE102018120000A1 (de) | 2018-08-16 | 2018-08-16 | Elektrohydrostatisches Aktuatorsystem mit Nachsaugbehälter |
PCT/EP2019/071360 WO2020035398A1 (de) | 2018-08-16 | 2019-08-08 | Elektrohydrostatisches aktuatorsystem mit nachsaugbehälter |
Publications (2)
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EP3837446A1 true EP3837446A1 (de) | 2021-06-23 |
EP3837446B1 EP3837446B1 (de) | 2022-09-28 |
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EP19753311.0A Active EP3837446B1 (de) | 2018-08-16 | 2019-08-08 | Elektrohydrostatisches aktuatorsystem mit nachsaugbehälter |
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Country | Link |
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US (1) | US11603867B2 (de) |
EP (1) | EP3837446B1 (de) |
CN (1) | CN112567139B (de) |
DE (1) | DE102018120000A1 (de) |
WO (1) | WO2020035398A1 (de) |
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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 |
Family Cites Families (22)
Publication number | Priority date | Publication date | Assignee | Title |
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DE4429782A1 (de) * | 1993-09-02 | 1995-03-09 | Mueller Weingarten Maschf | Verfahren zur Regelung des Antriebs einer hydraulischen Presse und Vorrichtung zur Durchführung des Verfahrens |
WO2001066340A1 (en) * | 2000-03-06 | 2001-09-13 | Amada Company, Limited | Device and method for controlling stop of hydraulic press and device and method for detecting trouble of speed selector valve |
DE102008036980A1 (de) | 2008-08-08 | 2010-02-11 | Robert Bosch Gmbh | Stelleinrichtung und mit einer derartigen Stelleinrichtung ausgeführte Ventilanordnung |
DE102008056378A1 (de) | 2008-11-08 | 2010-05-12 | Robert Bosch Gmbh | Hydraulischer Kraftübersetzer |
DE102009058408A1 (de) * | 2009-07-09 | 2011-01-13 | Robert Bosch Gmbh | Elektrohydraulische Steuerung |
DE102009043034A1 (de) * | 2009-09-25 | 2011-03-31 | Robert Bosch Gmbh | Vorgespannter hydraulischer Antrieb mit drehzahlvariabler Pumpe |
TR201008886A2 (tr) * | 2010-10-27 | 2011-04-21 | Coşkunöz Metal Form Maki̇na Endüstri̇ Ve Ti̇c. A.Ş. | Bir servo hidrolik pres |
EP2637852B1 (de) * | 2010-11-11 | 2017-01-18 | Robert Bosch GmbH | Hydraulische achse |
US8820064B2 (en) * | 2012-10-25 | 2014-09-02 | Tenneco Automotive Operating Company Inc. | Recuperating passive and active suspension |
EP2725241A1 (de) | 2012-10-29 | 2014-04-30 | MOOG GmbH | Verfahren und Vorrichtung zur Bestimmung des Füllstandes eines Volumens |
DE102014209132A1 (de) | 2014-05-14 | 2015-11-19 | Robert Bosch Gmbh | Hydrauliksystem |
WO2015177228A1 (en) | 2014-05-20 | 2015-11-26 | Wittur Holding Gmbh | Hydraulic elevator car brake unit with controllable braking power |
EP2952750B1 (de) * | 2014-06-04 | 2018-09-05 | MOOG GmbH | Hydrauliksystem |
DE102014218886B3 (de) | 2014-09-19 | 2015-11-12 | Voith Patent Gmbh | Hydraulischer Antrieb mit Eilhub und Lasthub |
DE102015204333A1 (de) | 2014-12-08 | 2016-06-09 | Robert Bosch Gmbh | Druckmitteleinspeisung für einen hydrostatischen Antrieb |
DE102014226672B3 (de) | 2014-12-19 | 2015-12-24 | Voith Patent Gmbh | Stellantrieb für ein Regelventil, insbesondere Dampfturbinenregelventil und Verfahren zum Betreiben desselben |
DE102015105400B4 (de) * | 2015-04-09 | 2022-06-02 | Langenstein & Schemann Gmbh | Umformmaschine, insbesondere Schmiedehammer, und Verfahren zum Steuern einer Umformmaschine |
DE102015210350A1 (de) | 2015-06-05 | 2016-12-08 | Robert Bosch Gmbh | Hydraulische Schaltung zur Druckmittelversrgung eines hydraulischen Verbrauchers in einem geschlossenen hydraulischen Kreis |
EP3109488B1 (de) * | 2015-06-25 | 2017-12-13 | MOOG GmbH | Betriebssicherer hydraulischer antrieb |
DE102016113294A1 (de) * | 2016-07-19 | 2018-01-25 | Dorst Technologies Gmbh & Co. Kg | Hydraulische Antriebseinrichtung |
DE102016113882A1 (de) | 2016-07-27 | 2018-02-01 | Moog Gmbh | Elektro-hydrostatisches Antriebssystem |
DE102016215080A1 (de) | 2016-08-12 | 2018-02-15 | Robert Bosch Gmbh | Elektrohydraulischer Verstellantrieb, Verfahren für einen elektrohydraulischen Verstellantrieb und Rotor |
-
2018
- 2018-08-16 DE DE102018120000.5A patent/DE102018120000A1/de active Pending
-
2019
- 2019-08-08 US US17/268,318 patent/US11603867B2/en active Active
- 2019-08-08 EP EP19753311.0A patent/EP3837446B1/de active Active
- 2019-08-08 WO PCT/EP2019/071360 patent/WO2020035398A1/de active Search and Examination
- 2019-08-08 CN CN201980053102.0A patent/CN112567139B/zh active Active
Also Published As
Publication number | Publication date |
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CN112567139B (zh) | 2023-06-13 |
WO2020035398A1 (de) | 2020-02-20 |
US11603867B2 (en) | 2023-03-14 |
CN112567139A (zh) | 2021-03-26 |
US20210332831A1 (en) | 2021-10-28 |
EP3837446B1 (de) | 2022-09-28 |
DE102018120000A1 (de) | 2020-02-20 |
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