EP1134431B1 - Antriebsvorrichtung - Google Patents
Antriebsvorrichtung Download PDFInfo
- Publication number
- EP1134431B1 EP1134431B1 EP01105621A EP01105621A EP1134431B1 EP 1134431 B1 EP1134431 B1 EP 1134431B1 EP 01105621 A EP01105621 A EP 01105621A EP 01105621 A EP01105621 A EP 01105621A EP 1134431 B1 EP1134431 B1 EP 1134431B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- hydraulic
- drive
- unit according
- drive unit
- hydraulic 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.)
- Expired - Lifetime
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Classifications
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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
- F15B9/00—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member
- F15B9/02—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type
- F15B9/04—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type controlled by varying the output of a pump with variable capacity
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
- B25B5/00—Clamps
- B25B5/06—Arrangements for positively actuating jaws
- B25B5/061—Arrangements for positively actuating jaws with fluid drive
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
- B25B5/00—Clamps
- B25B5/06—Arrangements for positively actuating jaws
- B25B5/12—Arrangements for positively actuating jaws using toggle links
- B25B5/122—Arrangements for positively actuating jaws using toggle links with fluid drive
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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
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/003—Systems with load-holding valves
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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
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/18—Combined units comprising both motor and pump
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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
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/20507—Type of prime mover
- F15B2211/20515—Electric motor
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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
- 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
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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
- 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
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/305—Directional control characterised by the type of valves
- F15B2211/30505—Non-return valves, i.e. check valves
- F15B2211/3051—Cross-check valves
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/31—Directional control characterised by the positions of the valve element
- F15B2211/3144—Directional control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional valves
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
- F15B2211/3157—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line
- F15B2211/31576—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line having a single pressure source and a single output member
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/32—Directional control characterised by the type of actuation
- F15B2211/329—Directional control characterised by the type of actuation actuated by fluid pressure
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/505—Pressure control characterised by the type of pressure control means
- F15B2211/50563—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
- F15B2211/50581—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using counterbalance valves
- F15B2211/5059—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using counterbalance valves using double counterbalance valves
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/51—Pressure control characterised by the positions of the valve element
- F15B2211/513—Pressure control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional valves
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
- F15B2211/5153—Pressure control characterised by the connections of the pressure control means in the circuit being connected to an output member and a directional control valve
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/52—Pressure control characterised by the type of actuation
- F15B2211/528—Pressure control characterised by the type of actuation actuated by fluid pressure
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/56—Control of an upstream pressure
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/625—Accumulators
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/63—Electronic controllers
- F15B2211/6303—Electronic controllers using input signals
- F15B2211/6336—Electronic controllers using input signals representing a state of the output member, e.g. position, speed or acceleration
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/665—Methods of control using electronic components
- F15B2211/6651—Control of the prime mover, e.g. control of the output torque or rotational speed
Definitions
- the present invention relates to a drive device with a closed hydraulic circuit, one by hydraulic Medium actuated hydraulic drive and a the Supply and discharge of hydraulic fluid with respect to Includes hydraulic drive inducing hydraulic pump, wherein provided for actuating the hydraulic pump, an electric motor is and the activation of the hydraulic drive by the operating state the hydraulic pump is determined, wherein the Hydraulic drive at least one with a force tapping part having motion-coupled drive piston, the two working chambers fluidly separated from each other, both over in each case a hydraulic circuit connected to the hydraulic pump are, wherein the feeding of hydraulic fluid in the each a working chamber with the simultaneous outflow Hydraulic fluid from the other working chamber is associated.
- JP 09/170 001 A (Patent Abstracts of Japan) is a Electro-hydraulic drive device of the aforementioned Kind out, in which due to a closed hydraulic circuit the leakage problem very easy to handle and is due to the special control by the electromotive activatable hydraulic pump no expensive servo valves are needed to drive the hydraulic to operate in the desired manner.
- the waiver of servo control valves also has the advantage that to the treatment the hydraulic medium used relatively low Requirements are made, making the maintenance very cost-effective designed.
- the activation of the hydraulic drive is expediently solely by the operating state of Hydraulic pump determines and can for example by switching on / off and specification of a specific pump speed be controlled very easily.
- At least one hydraulic circuit a bias valve containing the fluid connection from the relevant working chamber to the hydraulic pump only releases if and while in the outflow side Working chamber constructed a predetermined opening pressure Has.
- the biasing valve is a bias of the in the outflow-side working chamber hydraulic medium causes that can not be immediately displaced when in the supply-side working chamber an increase in pressure takes place. Only when the pressure increase in the feed-side working chamber so strong is that in the outflow Working chamber pressure built up called the opening pressure Minimum pressure achieved, the previously clamped Outflow hydraulic medium. Since in the outflow side However, working pressure prevails at one of the working chamber desired direction of movement of the drive piston opposite oriented counterforce causes, can the drive piston even with a high dynamic running Slow down movement very quickly and precisely by simply the inflow applied pressure by appropriate change the operating state of the hydraulic pump is varied. So it can be a very much without servo-controlled hydraulic valves exact positioning of the drive piston or one with this motion-coupled Kraftabgriffsteilils even at high Operating speeds can be achieved.
- hydraulic pump optionally to a left-handed or clockwise rotation
- Hydraulic medium optionally in one or the other of the two Working chambers are fed to accordingly the direction of movement of the drive piston to influence.
- the two hydraulic circuits of the drive device included expediently in each case a pilot-operated check valve, normally a fluid flow from the Hydraulic pump allows for hydraulic drive and in the opposite direction prevents, each check valve by the in the other hydraulic circuit of the hydraulic pump unblockable pressure to a fluid flow to allow the hydraulic drive back to the hydraulic pump.
- any intermediate positions maintained the drive piston without constant power supply be because the hydraulic medium when deactivated Hydraulic pump through the check valves in the working chambers is locked up.
- the hydraulic pump is activated, so ensures in the one hydraulic circuit thereby built-up pressure for unlocking in the other HydraulikCltung located check valve and allows thus the unimpeded movement of the drive piston.
- the design of the bias valves is conveniently so taken that the opening effecting opening pressure in Range between 10% and 90% of that of the hydraulic pump maximum producible operating pressure is.
- the preferred pressure range is between 30% and 50% of the mentioned maximum Actuation pressure.
- the bias valves Unlike a simple check valve, that even at very low pressure differences opens, so is by the bias valves a not inconsiderable Bias effect brought about. It is possible the opening pressure expediently by suitable adjusting means variably pretend to be a simple adaptation to the to be able to carry out the respective application.
- the respective biasing valve has over a movable shut-off by a desired Opening pressure corresponding spring force in a fluid connection interrupting closed position is biased and that of the hydraulic fluid of the outflow-side working chamber is acted upon in the opening direction against the spring force. If the pressure rises in the outflow-side working chamber at least the opening pressure, resulting in a resulting Opening force that overcome the spring force and the Shut-off can switch to an open position.
- the preload valve So preferably has a digital switching behavior.
- Each biasing valve is expediently one in the direction for hydraulic drive opening and blocking in the opposite direction
- Check valve connected in parallel, the corresponding at Direction of rotation of the hydraulic pump feeding the Hydraulic medium in the associated working chamber bypassing allows the biasing valve.
- To compensate for temperature fluctuations and / or different Volumes of the working chambers can be any hydraulic circuit connected to a hydraulic fluid reservoir which is a mobile exposed to atmospheric pressure Owns wall.
- At least the hydraulic drive, the Hydraulic pump, the hydraulic circuits and the electric motor combined into a structural unit (drive unit), wherein for energy supply only electrical interface means may be present for the operation of the Electric motors serve.
- drive unit structural unit
- On hydraulic interface means can be omitted, because the closed hydraulic circuit be executed as a self-sufficient part of the drive unit can.
- the drive device as part of a particular as Toggle clamping device trained clamping device executed in which the power take-off part of the hydraulic drive with a pivoting clamping arm of the clamping device is in drive connection.
- This embodiment is particularly recommended in conjunction with a to a Drive unit combined drive device, there this allows very compact dimensions and use alternatively to a purely fluid or purely electrically operated Clamping device allowed.
- FIG. 1 and 2 show a toggle clamping device trained clamping device 1, as the essential Components one combined into a unit and therefore Drive unit 2 designable as drive unit 3 and a clamping unit fixedly connected to the drive unit 3 4 contains.
- the circuit design of the drive device 2 or drive unit 3 is shown in Figure 1 only schematically FIG. 3 shows the circuit diagram of a particularly advantageous construction reproduces.
- the drive device 2 includes a hydraulic Medium actuated hydraulic drive 5, in the embodiment is designed as a linear drive, with appropriate Field of application of the drive device 2 but for example can also be designed as a rotary drive.
- the hydraulic drive 5 has a housing 6 in which there is an elongated piston receiving space 7, the one Drive piston 8 contains. This is part of an im Frame of a drive movement marked by a double arrow 12 linearly displaceable output unit 13, the Embodiment still one of a piston rod formed elongated Kraftabgriffsteil 14 includes that with the drive piston 8 firmly connected and thus motion coupled is.
- the force tapping part 14 extends in the direction of Drive movement 12, wherein it is on the front end side 15th the housing 6 protrudes and at its outside of the housing 6 is located on Kraftabgriffsstoff 16, the connection with moving components or Allow facilities.
- the drive piston 8 is located either directly in Housing 6 or in a sleeve inserted into the housing 6, wherein he the piston receiving space 7 under sealing in two Subdivided working chambers, the following for better distinction referred to as the first and second working chambers 17, 18 become.
- the drive device 2 further includes a hydraulic pump 22 per se known structure, with a preferably as a DC motor running electric motor 23 in Drive connection is.
- the electric motor 23 can be optionally with counterclockwise and clockwise to operate accordingly also the hydraulic pump 22 either in one of the two to operate possible directions of rotation.
- the hydraulic pump is therefore reversible, which is expediently a Volume flow pump whose speed is directly the Movement speed of the drive piston determined.
- the electric motor 23 is equipped with adjusting means 24, by both the direction of rotation and the engine speed of the electric motor 23 can specify variable to accordingly also the pump speed of the hydraulic pump 22 to be able to adjust variably, which expediently as a rotary pump is executed. A speed control or too Speed control is thus possible.
- speed ramps be generated such that a jerky acceleration or deceleration of a drive piston 8 is prevented to moving load.
- the hydraulic pump 22 and the electric motor 23 expediently to a fixed unit combined with the housing 6 of the hydraulic drive 5.
- the hydraulic pump 22 is on the housing 6 flanged, wherein the electric motor 23 in turn is attached to the hydraulic pump 22. It is possible also a separate attachment of the two components to the housing 6 as well as an at least partial integration of a or both components in the housing. 6
- the drive unit 3 has a slim design, are the electric motor 23 and the hydraulic pump 22 in Area of the rear end face 25 of the housing 6 installed.
- the hydraulic pump 22 is connected via two parallel and for better distinction as first and second hydraulic circuits 26, 27 designated hydraulic circuits hydraulically connected to the hydraulic drive 5.
- the hydraulic pump 22 has two pump ports 28, 29, the first of which (28) via the first hydraulic circuit 26 to the first working chamber 17 is connected and the second (29) on the second Hydraulic circuit 27 with the second working chamber 18 of the Hydraulic drive 5 is in communication.
- the hydraulic medium is ever in the direction of rotation so within the closed hydraulic circuit promoted it to the first or second working chamber 17, 18 is fed, at the same time hydraulic medium by the thereby moving drive piston. 8 from the other working chamber 18, 17 back to the hydraulic pump 22 is displaced.
- the Output unit 13 to a drive movement 12 in two each other cause opposite directions, the rod-shaped Kraftabgriffsteil 14 in the embodiment either extends out of the housing 6 or enters this.
- the activation of the hydraulic drive 5 and preferably also in the activated hydraulic drive 5 held pressure build-up or volume flow alone is determined by the operating state of the hydraulic pump. In order to stop the output unit 13 in a certain position, the hydraulic pump 22 is stopped.
- the hydraulic pump 22 With a corresponding direction of rotation activated.
- the pressure build-up in the feed-side working chamber and accordingly, the displacement speed the output unit 13 is determined by the pump speed determined by the adjustment means 24 after Demand can be variably specified.
- the speed of the activated Drive piston 8 of the hydraulic drive 5 exclusively by the volume flow of the hydraulic medium in the hydraulic Circuits 26, 27 determined.
- the two hydraulic circuits 26, 27 are common connected to a hydraulic fluid reservoir 32, the excess fluid absorbs and missing Refills fluid.
- a hydraulic fluid reservoir 32 in Fluid connection
- the atmospheric pressure exposed movable wall 34 has.
- the latter can, for example formed by a piston or a membrane be.
- the hydraulic fluid reservoir is 32 expediently also part the drive unit 3 and can be integrated into the housing 6 or attached to the rear end face 25 be.
- the drive device 2 is a monoenergetic Device executed. Due to the internally closed Hydraulic circuit requires no supply and / or discharge hydraulic actuation energy, so that the drive device 2 for energy supply exclusively via electrical Connection means 35 has, over which for the operation the electric motor 23 fed electrical energy required becomes. It may be, for example, plug connection means act or, as in the embodiment, to an outgoing, led to an electrical energy source Connecting cable.
- connection means In unit with the electrical connection means or over separate additional electrical connection means can also be a Connection of the drive device 2 to an external electronic Control device, which also position detection signals can take into account which depending on the position of the output unit 13 are generated.
- the drive device 2 can be in this way if necessary in integrate a manufacturing or assembly system whose operations be electronically controlled.
- the for the specification of the operating state of the hydraulic pump 22nd Serving adjusting means 24 can, if necessary, apart from the Be placed drive device 2 and via corresponding Signal connections with the electric motor 23 cooperate. All needed for the operation of the drive device 2 Signals can also be transmitted wirelessly.
- the hydraulic drive 5 is preferably a position measuring system 61 associated with the position of the drive piston 8 or a with this motion coupled component can capture to depending on certain positions of the electric motor 23rd to be able to control as needed.
- the position detection signals be supplied to the adjusting means 24, this expediently equipped with a position controller are.
- the two hydraulic circuits 26, 27 are in the embodiment integrated into the housing 6 of the hydraulic drive 5, wherein in Figure 1 only dash-dotted schematic are hinted at, while their preferred structure in detail is shown in FIG.
- both hydraulic circuits expediently respectively a pilot-operated check valve 36a, 36b, so a Check valve that unlock under certain circumstances leaves, so it is also in the normally locked Flow direction allows a fluid passage.
- the pilot-operated check valves 36a, 36b are so in the respective hydraulic circuit 26, 27 incorporated that they normally a fluid flow from the hydraulic pump 22 allow the respectively connected working chamber 17, 18 and in the opposite direction.
- the pilot operated check valve 36a, 36b of a respective hydraulic circuit 26, 27 is however, indicated by a dashed line in Figure 3 Entsperrkanal 37a, 37b with that channel portion of each other hydraulic circuit 27, 26 in fluid communication, the between the hydraulic pump 22 and the local unlockable Check valve is located. This way will be in a respective hydraulic circuit 26, 27 of the hydraulic pump sustained pressure tapped and the in the other hydraulic circuit placed unlockable Check valve supplied as unlock signal.
- Hydraulic pump 22 for example, operated so that in the first hydraulic circuit 26, a pressure buildup takes place and through the associated openable check valve that opens 36a, an injection of hydraulic fluid into the first working chamber 17 is effected causes the built-up pressure at the same time unlocking and opening the unlockable Check valve 36b of the second hydraulic circuit 27, so that from the second working chamber 18 displaced hydraulic medium can flow back to the hydraulic pump 22.
- the corresponding Sequence results in the reverse direction of the Hydraulic pump 22.
- unlockable check valves 36a, 36b results the advantage that the output unit 13 when deactivated Hydraulic pump 22 held in its current position is because in the working chambers 17, 18 and in the Then it is up to the unlockable check valves 36a and 36b in the hydraulic circuits 26, 27 befindliches fluid is firmly locked. To hold a particular Position of the output unit 13 is thus no Energy needed.
- the bias valves each a movable shut-off member 42 which by a the Opening pressure corresponding spring force in a fluid connection normally biased closing position biased is.
- the spring force is for example by a mechanical Spring device 43 and / or by a gas spring delivered.
- adjustment means 44th can be the spring preload expediently variable adjust to affect the opening pressure and accordingly an adaptation to the current application of the To enable drive device 2.
- the shut-off member 42 is the hydraulic fluid of the aüsström supraen Working chamber against the spring force in the opening direction acts and displaces the shut-off member in the open position, when the force resulting from the opening pressure is greater than the spring force.
- the interpretation is expediently so met that a digital switching behavior is present and the preload valve abruptly in the maximum Open position switches.
- the back of the housing. 6 attached components by a fixed to the housing 6
- the drive device 2 can be in principle to any Use drive purposes, with different types the hydraulic drive 5 would be conceivable, for example also rodless embodiments. Especially advantageous designed the use of the drive device 2 in a summarized to a drive unit 3 design in Connection with a tensioning device 1, wherein the front Front side 15 of the housing 6, the above-mentioned clamping unit 4th is scheduled.
- the latter can be attached to the housing as shown 6 flanged bearing head 47 included in the from the housing 6 outstanding end of the output unit 13th dips and carries a pivotable clamping arm 48.
- This has the embodiment over a non-rotatably connected pivot lever 50, on at a to the pivot axis 52 of the clamping arm 48 spaced bearing point 53 a tab-like intermediate member 54 is articulated, via another bearing 55 with the Kraftabgriffsstoffn 16 is hinged.
- the force tapping part 14 To the force tapping part 14 and the associated, in the Area of a front end wall 59 of the piston receiving space 7 placed seal 58 against excessive wear protect, is the force tapping part 14 with its outer End section guided on guide means 56 longitudinally displaceable and at the same time in the transverse direction with respect to the pivot axis 52 supported.
- the guide means 56 may, for example, of one or more, in particular groove-like guideways be formed.
- the swivel arm 48 By actuating the hydraulic drive 5, the swivel arm 48 according to double arrow 57 to a pivoting movement about the Pivot axis 52 are caused to selectively in a Positioning position or a release position to position. In the clamping position, he can on a not shown Work the workpiece to tighten it so tight that it can be edited.
- the tensioning device 1 is suitable especially for clamping together workpieces to be welded.
- the drive unit 3 allows the drive unit 3 a particularly narrow design. It is particularly possible, the cross-sectional dimensions the drive unit 3 to be chosen so that they equal or less are as those of the storage head 47.
- the direction of movement of the output unit 13 is solely due to the direction of rotation of the DC motor given, as well as the lifting speed of Output unit 13 is a function of the speed of the DC motor or the pump speed is.
- the only Variable during operation of the drive device 2 is in the embodiment of the operating state of the hydraulic pump or their speed.
- a drive device with a by a hydraulic medium operable hydraulic drive 5, which is a hydraulic pump 22 for supplying the associated with hydraulic medium.
- the pressure build-up in the activated Hydraulic drive 5 is controlled by adjustable pressure relief valves (Bias valves 38a, 38b), the pressure dependent are formed opening, as well as to these parallel Check valves 45a, 45b, controlled.
- the speed of the drive piston 8 of the activated hydraulic drive 5 is exclusively based on the volume flow of the hydraulic Medium in the hydraulic circuits 26, 27th certainly.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
- Control Of Positive-Displacement Pumps (AREA)
- Control Of Fluid Gearings (AREA)
- Seal Device For Vehicle (AREA)
- Valve Device For Special Equipments (AREA)
- Vehicle Body Suspensions (AREA)
Description
- Figur 1
- in schematischer Darstellung und teilweise im Längsschnitt eine Spannvorrichtung, die mit einer bevorzugten Ausgestaltung der erfindungsgemäßen Antriebsvorrichtung ausgestattet ist,
- Figur 2
- die Anordnung aus Figur 1 in einer Rückansicht mit Blickrichtung gemäß Pfeil II, und
- Figur 3
- den elektro-hydraulischen Schaltplan der bei der Spannvorrichtung gemäß Figuren 1 und 2 bevorzugt zum Einsatz gelangenden Antriebsvorrichtung.
Claims (24)
- Antriebsvorrichtung, mit einem geschlossenen Hydraulikkreis, der einen durch hydraulisches Medium betätigbaren Hydraulikantrieb (5) und eine die Zufuhr und Abfuhr des hydraulischen Mediums bezüglich dem Hydraulikantrieb (5) veranlassende Hydraulikpumpe (22) enthält, wobei zur Betätigung der Hydraulikpumpe (22) ein Elektromotor (23) vorgesehen ist und die Aktivierung des Hydraulikantriebes (5) durch den Betriebszustand der Hydraulikpumpe (22) bestimmt wird, wobei der Hydraulikantrieb (5) mindestens einen mit einem Kraftabgriffsteil (14) bewegungsgekoppelten Antriebskolben (8) aufweist, der zwei Arbeitskammern (17, 18) fluiddicht voneinander abteilt, die beide über jeweils eine Hydraulikschaltung (26, 27) mit der Hydraulikpumpe (22) verbunden sind, wobei das Einspeisen von Hydraulikfluid in die eine Arbeitskammer (17, 18) mit dem gleichzeitigen Ausströmen von Hydraulikfluid aus der anderen Arbeitskammer (18, 17) einhergeht, dadurch gekennzeichnet, dass mindestens eine Hydraulikschaltung (26, 27) ein Vorspannventil (38a, 38b) enthält, das die Fluidverbindung von der betreffenden Arbeitskammer (17, 18) hin zur Hydraulikpumpe (22) nur freigibt, wenn und solange sich in der ausströmseitigen Arbeitskammer ein vorbestimmter öffnungsdruck aufgebaut hat.
- Antriebsvorrichtung nach Anspruch 1, gekennzeichnet durch einen allein in Abhängigkeit von der Drehzahl der Hydraulikpumpe (22) erfolgenden Druckaufbau unterschiedlicher Betätigungsdrücke im Hydraulikantrieb (5).
- Antriebsvorrichtung nach Anspruch 1 oder 2, gekennzeichnet durch Einstellmittel (24) zur variablen Vorgabe der die Pumpendrehzahl der Hydraulikpumpe (22) bestimmenden Motordrehzahl des Elektromotors (23).
- Antriebsvorrichtung nach Anspruch 3, dadurch gekennzeichnet, dass durch die Einstellmittel (24) Drehzahlrampen erzeugbar sind, die eine gleichförmige Antriebsbewegung des Hydraulikantriebes (5) hervorrufen.
- Antriebsvorrichtung nach Anspruch 3 oder 4, dadurch gekennzeichnet, dass dem Hydraulikantrieb (5) ein Wegmesssystem zugeordnet ist, dessen Signale den Einstellmitteln (24) zugeführt werden, welche hierbei zweckmäßigerweise einen Positionsregler enthalten.
- Antriebsvorrichtung nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass der Elektromotor (23) als drehzahlgesteuerter oder drehzahlgeregelter Antriebsmotor ausgebildet ist.
- Antriebsvorrichtung nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass die Drehzahl der Hydraulikpumpe (22) die Bewegungsgeschwindigkeit des Antriebskolbens (8) des Hydraulikantriebes bestimmt.
- Antriebsvorrichtung nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, dass die Hydraulikpumpe als reversierbare Volumenstrompumpe ausgebildet ist.
- Antriebsvorrichtung nach einem der Ansprüche 1 bis 8, dadurch gekennzeichnet, das die Hydraulikpumpe (22) wahlweise zu einer linksdrehenden oder einer rechtsdrehenden Rotationsbewegung antreibbar ist, um Hydraulikmedium wahlweise in die eine oder andere der beiden Arbeitskammern (17, 18) einzuspeisen und dementsprechend die Bewegungsrichtung des Antriebskolbens (8) vorzugeben.
- Antriebsvorrichtung nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, dass beide Hydraulikschaltungen (26, 27) ein entsperrbares Rückschlagventil (36a, 36b) enthalten, das normalerweise eine Fluidströmung von der Hydraulikpumpe (22) zum Hydraulikantrieb (5) zulässt und in Gegenrichtung verhindert, wobei jedes Rückschlagventil (36a, 36b) durch den in der jeweils anderen Hydraulikschaltung von der Hydraulikpumpe (22) aufrecht erhaltenen Druck entsperrbar ist, um eine Fluidströmung vom Hydraulikantrieb (5) zurück zur Hydraulikpumpe (22) zu ermöglichen.
- Antriebsvorrichtung nach einem der Ansprüche 1 bis 10, dadurch gekennzeichnet, dass die Auslegung so getroffen ist, dass der Öffnungsdruck im Bereich zwischen 10% und 90% und dabei vorzugsweise im Bereich zwischen 30% und 50% des von der Hydraulikpumpe (22) maximal erzeugbaren Betriebsdruckes liegt.
- Antriebsvorrichtung nach einem der Ansprüche 1 bis 11, gekennzeichnet durch Einstellmittel (44) zur veränderlichen Vorgabe des Öffnungsdruckes.
- Antriebsvorrichtung nach einem der Ansprüche 1 bis 12, dadurch gekennzeichnet, dass das Vorspannventil (38a, 38b) ein bewegliches Absperrglied (42) aufweist, das durch eine dem Öffnungsdruck entsprechende Federkraft in eine die Fluidverbindung unterbrechende Schließstellung vorgespannt ist und das vom Hydraulikfluid der ausströmenden Arbeitskammer entgegen der Federkraft im Öffnungssinne beaufschlagt wird.
- Antriebsvorrichtung nach einem der Ansprüche 1 bis 13, dadurch gekennzeichnet, dass jede Hydraulikschaltung (26, 27) ein Vorspannventil (36a, 36b) enthält.
- Antriebsvorrichtung nach einem der Ansprüche 1 bis 14, in Verbindung mit Anspruch 11, dadurch gekennzeichnet, dass in einer betreffenden Hydraulikschaltung (26, 27) das entsperrbare Rückschlagventil (36a, 36b) und das Vorspannventil (38a, 38b) in Reihe geschaltet sind.
- Antriebsvorrichtung nach einem der Ansprüche 1 bis 15, dadurch gekennzeichnet, dass jedem Vorspannventil (38a, 38b) ein in Richtung zum Hydraulikantrieb (5) öffnendes und in Gegenrichtung sperrendes Rückschlagventil (45a, 45b) parallel geschaltet ist.
- Antriebsvorrichtung nach einem der Ansprüche 1 bis 16, dadurch gekennzeichnet, dass jede Hydraulikschaltung (26, 27) mit einem Hydraulikfluid-Ausgleichsbehältnis (33) verbunden ist.
- Antriebsvorrichtung nach einem der Ansprüche 1 bis 17, dadurch gekennzeichnet, dass zumindest der Hydraulikantrieb (5), die Hydraulikpumpe (22), die gegebenenfalls vorhandene Hydraulikschaltung (26, 27) und der Elektromotor (23) zu einer Antriebseinheit (3) zusammengefasst sind.
- Antriebsvorrichtung nach Anspruch 18, dadurch gekennzeichnet, dass die Antriebseinheit (3) zur Energieeinspeisung ausschließlich über elektrische Anschlussmittel (35) verfügt.
- Antriebsvorrichtung nach einem der Ansprüche 1 bis 19, als Bestandteil einer insbesondere als Kniehebel-Spannvorrichtung ausgebildeten Spannvorrichtung (1), wobei das Kraftabgriffsteil (14) des Hydraulikantriebes (5) mit einem schwenkbeweglichen Spannarm (48) in Antriebsverbindung steht.
- Antriebsvorrichtung nach Anspruch 20 in Verbindung mit Anspruch 18 oder 19, dadurch gekennzeichnet, dass stirnseitig an der Antriebseinheit (3) ein den Schwenkarm (48) tragender Lagerungskopf (47) angeordnet ist.
- Antriebsvorrichtung nach Anspruch 21, dadurch gekennzeichnet, dass die Querschnittsabmessungen der Antriebseinheit (3) gleich oder geringer sind als diejenigen des Lagerungskopfes (47).
- Antriebsvorrichtung nach einem der Ansprüche 1 bis 22, dadurch gekennzeichnet, dass der Hydraulikantrieb (5) ein Drehantrieb ist.
- Antriebsvorrichtung nach einem der Ansprüche 1 bis 23, dadurch gekennzeichnet, dass der Hydraulikantrieb (5) ein Linearantrieb ist.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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DE10013194A DE10013194B4 (de) | 2000-03-17 | 2000-03-17 | Antriebsvorrichtung |
DE10013194 | 2000-03-17 |
Publications (2)
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EP1134431A1 EP1134431A1 (de) | 2001-09-19 |
EP1134431B1 true EP1134431B1 (de) | 2005-05-11 |
Family
ID=7635226
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EP01105621A Expired - Lifetime EP1134431B1 (de) | 2000-03-17 | 2001-03-07 | Antriebsvorrichtung |
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US (1) | US6543223B2 (de) |
EP (1) | EP1134431B1 (de) |
AT (1) | ATE295482T1 (de) |
DE (2) | DE10013194B4 (de) |
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CN102200151A (zh) * | 2011-06-14 | 2011-09-28 | 赵铁栓 | 一种流量控制装置和控制液压泵输出恒定流量的方法 |
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Families Citing this family (45)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2831226B1 (fr) * | 2001-10-24 | 2005-09-23 | Snecma Moteurs | Actionneur electrohydraulique autonome |
DE10216982B4 (de) * | 2002-04-16 | 2005-12-22 | Dorma Gmbh + Co. Kg | Hydraulischer Drehflügelantrieb |
FR2845628B1 (fr) * | 2002-10-10 | 2006-02-24 | Smc Kk | Dispositif de serrage |
US7111835B2 (en) | 2002-10-10 | 2006-09-26 | Smc Kabushiki Kaisha | Clamp apparatus |
GB0329243D0 (en) * | 2003-12-17 | 2004-01-21 | Thales Plc | Apparatus and methods for actuation |
DE102004029409A1 (de) * | 2004-06-18 | 2006-01-05 | Jungheinrich Ag | Druckmittelbetätigte Stelleinrichtung, insbesondere für eine Fahrzeuglenkvorrichtung |
DE102004061559A1 (de) | 2004-12-21 | 2006-06-29 | Brueninghaus Hydromatik Gmbh | Hydraulischer Antrieb |
US7191593B1 (en) | 2005-11-28 | 2007-03-20 | Northrop Grumman Corporation | Electro-hydraulic actuator system |
US20070157612A1 (en) * | 2006-01-10 | 2007-07-12 | Xinhua He | Compact hydraulic actuator system |
CN100424361C (zh) * | 2006-03-07 | 2008-10-08 | 太原理工大学 | 闭式电液控制*** |
US7434395B2 (en) * | 2006-07-25 | 2008-10-14 | Delphi Technologies, Inc. | Apparatus and method for dual mode compact hydraulic system |
US8448432B2 (en) * | 2007-02-13 | 2013-05-28 | The Board Of Regents Of The University Of Texas System | Actuators |
JP5319556B2 (ja) * | 2007-03-05 | 2013-10-16 | ゾディアック シーツ ユーケー リミテッド | 制御弁を備える油圧アクチュエータ |
GB2454908B (en) * | 2007-11-23 | 2012-04-11 | Schlumberger Holdings | Hydraulic manifold pump |
DE102010020132A1 (de) * | 2010-05-11 | 2011-11-17 | Hydac Electronic Gmbh | Antriebssystem mit zumindest einem hydraulischen Aktuator |
PL225323B1 (pl) * | 2010-08-20 | 2017-03-31 | Nowak Wiesław Przedsiębiorstwo Innowacyjno Wdrożeniowo Handlowe | Siłownik teleskopowy |
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EP3036437A4 (de) | 2013-08-19 | 2017-09-20 | Purdue Research Foundation | Miniaturhochdruckpumpe und elektrisch-hydraulisches betätigungssystem |
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US10072676B2 (en) | 2014-09-23 | 2018-09-11 | Project Phoenix, LLC | System to pump fluid and control thereof |
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US20160221171A1 (en) * | 2015-02-02 | 2016-08-04 | Caterpillar Inc. | Hydraulic hammer having dual valve acceleration control system |
EP3109488B1 (de) * | 2015-06-25 | 2017-12-13 | MOOG GmbH | Betriebssicherer hydraulischer antrieb |
EP3344874B1 (de) | 2015-09-02 | 2021-01-20 | Project Phoenix LLC | System zum pumpen einer flüssigkeit und steuerung dafür |
EP3344853B1 (de) | 2015-09-02 | 2020-11-04 | Project Phoenix LLC | System zum pumpen einer flüssigkeit und steuerung dafür |
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DE102016109103A1 (de) | 2016-05-18 | 2017-11-23 | Hoerbiger Automatisierungstechnik Holding Gmbh | Elektrohydraulischer Linearaktuator |
EP3615814A4 (de) | 2017-04-28 | 2021-01-27 | Eaton Intelligent Power Limited | System zur dämpfung von masseninduzierten schwingungen in maschinen mit hydraulisch gesteuerten auslegern oder länglichen elementen |
CN109366385A (zh) * | 2018-10-18 | 2019-02-22 | 九江精密测试技术研究所 | 一种大偏载轴系电液混合驱动五轴复合转台 |
WO2020106291A1 (en) * | 2018-11-21 | 2020-05-28 | Aoi (Advanced Oilfield Innovations, Dba A. O. International Ii, Inc.) | Prime mover system and methods utilizing balanced fluid flow |
TWI717112B (zh) * | 2019-11-19 | 2021-01-21 | 科頡工業股份有限公司 | 活塞泵及具有該活塞泵的夾持裝置 |
CN112901474B (zh) * | 2019-11-19 | 2023-03-31 | 科颉工业股份有限公司 | 活塞泵及具有该活塞泵的夹持装置 |
NO20230045A1 (en) * | 2020-07-15 | 2023-01-19 | Coretrax Americas Ltd | Hydraulic thruster |
DE102022204211A1 (de) * | 2022-04-29 | 2023-11-02 | Robert Bosch Gesellschaft mit beschränkter Haftung | Verfahren zum Betreiben eines hydraulischen Systems mit mindestens einem hydraulisch betätigbaren Steller |
Family Cites Families (19)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE1916266A1 (de) * | 1968-05-21 | 1970-10-08 | Bbc Brown Boveri & Cie | Elektrohydraulisches Stellgeraet |
DE1776139C3 (de) * | 1968-09-27 | 1978-06-01 | Tullio Mailand Levrini (Italien) | Hydraulische Antriebsvorrichtung |
DE2929442A1 (de) * | 1979-07-20 | 1981-01-29 | Elmeg | Elektrohydraulisches stellgeraet |
US4696163A (en) * | 1983-03-28 | 1987-09-29 | Rexa Corporation | Control valve and hydraulic system employing same |
DE3637404A1 (de) * | 1986-11-03 | 1987-11-26 | Bornemann & Haller Kg | Stellantrieb |
US5125324A (en) * | 1988-02-10 | 1992-06-30 | Daia Industry Co. Ltd. | Portable hydraulically operated device incorporating automatic drain valve |
DE3919823C3 (de) * | 1989-06-14 | 1998-04-09 | Mannesmann Ag | Spritzgießmaschine mit hydraulischen Verbrauchern |
DE4137103C2 (de) * | 1991-11-12 | 1994-02-17 | Elmeg | Elektrohydraulisches Gerät |
DE4207764C2 (de) * | 1992-03-11 | 1994-08-25 | Hugo Junkers Werke Gmbh | Hydraulik-Werkzeug mit vollständig integriertem Hydraulik-Kreislauf |
DE4302889C2 (de) * | 1993-02-02 | 1997-03-27 | Emg Eltma Hebezeuge Oschersleb | Elektro-hydraulische Betätigungsvorrichtung |
DE4335328A1 (de) * | 1993-10-18 | 1995-04-20 | Battenfeld Gmbh | Hydraulisches Betriebssystem für Spritzgießmaschinen |
DE19517582C2 (de) * | 1995-05-05 | 1998-08-20 | Mannesmann Ag | Antrieb für die Einspritz- und Plastifiziereinheit einer Kunststoffspritzgießmaschine |
DE19535691C1 (de) * | 1995-09-26 | 1997-01-23 | Rothenberger Werkzeuge Masch | Hydraulisch angetriebenes Handwerkzeug |
JP3668543B2 (ja) * | 1995-12-18 | 2005-07-06 | 株式会社トキメック | 液圧閉回路における回路圧保持装置 |
JPH09170601A (ja) * | 1995-12-20 | 1997-06-30 | Tokimec Inc | 液圧閉回路 |
DE19603012C1 (de) * | 1996-01-18 | 1997-09-04 | Mannesmann Ag | Plastifizier- und Einspritzeinheit einer Kunststoffspritzgießmaschine |
FR2752446B1 (fr) * | 1996-08-13 | 1998-10-30 | Thomson Csf | Procede de commande optimise d'un actionneur electrofluidique et actionneur le mettant en oeuvre |
US6092290A (en) * | 1996-12-24 | 2000-07-25 | Rescue Technology, Inc. | Rescue tool |
DE29903281U1 (de) * | 1999-02-24 | 1999-07-01 | Festo AG & Co, 73734 Esslingen | Kniehebel-Spannvorrichtung |
-
2000
- 2000-03-17 DE DE10013194A patent/DE10013194B4/de not_active Expired - Fee Related
-
2001
- 2001-03-07 EP EP01105621A patent/EP1134431B1/de not_active Expired - Lifetime
- 2001-03-07 AT AT01105621T patent/ATE295482T1/de not_active IP Right Cessation
- 2001-03-07 DE DE50106158T patent/DE50106158D1/de not_active Expired - Fee Related
- 2001-03-14 US US09/808,438 patent/US6543223B2/en not_active Expired - Fee Related
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US11209027B2 (en) | 2014-07-15 | 2021-12-28 | Eaton Intelligent Power Limited | Methods and apparatus to enable boom bounce reduction and prevent un-commanded motion in hydraulic systems |
US11536298B2 (en) | 2017-04-28 | 2022-12-27 | Danfoss Power Solutions Ii Technology A/S | System with motion sensors for damping mass-induced vibration in machines |
Also Published As
Publication number | Publication date |
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DE10013194A1 (de) | 2001-09-27 |
DE50106158D1 (de) | 2005-06-16 |
EP1134431A1 (de) | 2001-09-19 |
DE10013194B4 (de) | 2005-02-24 |
ATE295482T1 (de) | 2005-05-15 |
US20010022083A1 (en) | 2001-09-20 |
US6543223B2 (en) | 2003-04-08 |
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