EP1134431A1 - Transmission installation - Google Patents

Transmission installation Download PDF

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Publication number
EP1134431A1
EP1134431A1 EP01105621A EP01105621A EP1134431A1 EP 1134431 A1 EP1134431 A1 EP 1134431A1 EP 01105621 A EP01105621 A EP 01105621A EP 01105621 A EP01105621 A EP 01105621A EP 1134431 A1 EP1134431 A1 EP 1134431A1
Authority
EP
European Patent Office
Prior art keywords
hydraulic
drive
drive device
hydraulic pump
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
Application number
EP01105621A
Other languages
German (de)
French (fr)
Other versions
EP1134431B1 (en
Inventor
Günther Muschong
Kurt Dr. Stoll
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Festo SE and Co KG
Original Assignee
Festo SE and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Festo SE and Co KG filed Critical Festo SE and Co KG
Publication of EP1134431A1 publication Critical patent/EP1134431A1/en
Application granted granted Critical
Publication of EP1134431B1 publication Critical patent/EP1134431B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • 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
    • 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
    • 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
    • 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
    • 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
    • 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
    • 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
    • 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
    • F15B2211/27—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
    • F15B2211/30—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
    • 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
    • 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
    • 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
    • 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
    • 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
    • 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
    • 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
    • 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
    • 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
    • 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
    • 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 the field of drive devices, which can be activated by supplying energy Have drive from which a driving force is tapped can be.
  • Such a drive device goes out, for example the German utility model No. 299 03 825.4, where they described as part of a toggle clamp device becomes. There it receives one that can be activated by compressed air Pneumatic actuator with associated electrically actuated Control valves to determine the drive direction of the pneumatic actuator to be able to pretend. Alternatively, there would also be a hydraulic drive conceivable, the one with electrically operated servo valves is equipped to influence the drive state. While with pneumatic drives due to the compressibility the actuating medium is usually a larger technical one Effort is needed to make exact positioning and slow Being able to master movements predominates in hydraulic drives the leakage problem and the high maintenance costs to ensure secure hose connections and one high quality hydraulic medium.
  • a drive device with a closed hydraulic circuit, one through hydraulic Medium operated hydraulic drive and a feed and discharge of the hydraulic medium with respect to the hydraulic drive causing hydraulic pump contains, for Actuation of the hydraulic pump, an electric motor is provided and the activation of the hydraulic drive through the operating state the hydraulic pump is determined.
  • Suitable setting means are preferably present, by the variable specification of the pump speed of the hydraulic pump determining motor speed of the electric motor is controllable or regulatable. It can also be a possibility be given to specify speed ramps to accelerate and braking one by the hydraulic drive to make the load to be moved uniform and jerky To avoid movements.
  • the drive device is the hydraulic drive with at least one with a force-tapping part motion-coupled drive piston provided, the two working chambers fluid-tight separated from each other, both via a hydraulic circuit are connected to the hydraulic pump, the Feeding hydraulic fluid into one working chamber with the simultaneous leakage of hydraulic fluid the other Chamber of Labor goes hand in hand with the Shift the drive piston in the desired manner.
  • the Hydraulic pump to either a left-handed or right-handed Rotational movement can be driven - for example by changing the direction of rotation of the electric motor or under Interposition of a changeover gear, can hydraulic medium either in one or the other of the two working chambers be fed in accordingly the direction of movement of the drive piston.
  • the two hydraulic circuits of the drive device included expediently one unblockable check valve each, which is usually a fluid flow from the Hydraulic pump allows for hydraulic drive and in the opposite direction prevented, each check valve by the in the other hydraulic circuit from the hydraulic pump maintained pressure is unlockable to fluid flow from the hydraulic drive back to the hydraulic pump.
  • each check valve by the in the other hydraulic circuit from the hydraulic pump maintained pressure is unlockable to fluid flow from the hydraulic drive back to the hydraulic pump.
  • Another, particularly advantageous equipment of the drive device results if in at least one and preferably both hydraulic circuits a bias valve is turned on, the fluid connection from the associated The working chamber towards the hydraulic pump is normally shut off and only releases if and as long as in the outflow-side working chamber a predetermined opening pressure has built up.
  • the preload valve thus becomes a Biasing of the one located in the outflow-side working chamber Hydraulic medium causes that does not immediately replace can be, if in the feed-side working chamber Pressure increase takes place. Only when the pressure increase in the feed-side working chamber is so strong that in the upstream working chamber the pressure builds up as Opening pressure, the minimum pressure can be reached Flush out previously clamped hydraulic medium.
  • the drive piston can also be operated with a high dynamic range brake the executed movement very quickly and precisely by simply the pressure applied on the inflow side by appropriate Change in the operating state of the hydraulic pump varies becomes. It can, in turn, be operated without servo-controlled hydraulic valves a very exact positioning of the drive piston or a force-tapping part coupled to this movement achieved even at high operating speeds become.
  • the design of the preload valves is expediently so met that the opening pressure causing the opening in Range between 10% and 90% of the maximum of the hydraulic pump generated operating pressure is.
  • the preferred printing area is between 30% and 50% of the maximum mentioned Actuation pressure.
  • the preload valves make it a not inconsiderable one Prestressing effect brought about. It can be the opening pressure expediently by means of suitable setting means specify variable to easily adapt to the to be able to carry out the respective application.
  • the bias valve in question expediently has a movable shut-off element, which can be replaced by the desired one Opening pressure corresponding spring force into the fluid connection interrupted closed position is biased and that of the hydraulic fluid of the working chamber on the outflow side is applied against the spring force in the opening direction.
  • the pressure in the outflow-side working chamber rises results in at least the opening pressure Opening force that overcome the spring force and that Shutoff member can switch to an open position.
  • the preload valve therefore preferably has a digital switching behavior.
  • Each bias valve is conveniently one in the direction opening to the hydraulic drive and locking in the opposite direction Check valve connected in parallel, the corresponding Direction of rotation of the hydraulic pump feeding the Hydraulic medium bypassing the assigned working chamber of the preload valve.
  • volumes of the working chambers can be any hydraulic circuit connected to a hydraulic fluid expansion tank be a movable one exposed to atmospheric pressure Owns the wall.
  • At least the hydraulic drive is expedient, the Hydraulic pump, the hydraulic circuits and the electric motor combined into one unit (drive unit), where only electrical interface means for energy supply may be present to operate the Serve electric motor.
  • On hydraulic interface means can be dispensed with because of the closed hydraulic circuit be designed as an independent component 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 swiveling clamping arm of the clamping device is in drive connection.
  • This configuration is particularly recommended in connection with one to one Drive unit summarized drive device because this enables very compact dimensions and use alternative to a purely fluid or electrically operated Clamping device allowed. Designs can also be found here are obtained in which the cross-sectional dimensions of the Drive unit are equal to or less than those of the bearing head of the tensioning device used for swivel mounting.
  • Figures 1 and 2 show a knee lever tensioning device trained tensioner 1, the essential Components a combined into a structural unit and therefore Drive device 2, which can be designated as drive unit 3 and a clamping unit firmly connected to the drive unit 3 4 contains.
  • the circuit design of the drive device 2 or drive unit 3 is only schematic in Figure 1 reproduced, wherein the Figure 3 is a circuit diagram reproduces a particularly advantageous structure.
  • the drive device 2 contains one by hydraulic Medium actuable hydraulic drive 5, which in the embodiment is designed as a linear drive, with the corresponding Field of application of the drive device 2, however, 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 that one Includes drive piston 8. This is part of an im Frame of a drive movement marked by a double arrow 12 linearly displaceable output unit 13 which at Embodiment another one formed by a piston rod Includes elongated power take-off part 14, which with the drive piston 8 firmly connected and thus motion-coupled is.
  • the force tapping member 14 extends in the direction of the Drive movement 12, it being on the front end face 15 of the housing 6 protrudes and on its outside the housing 6 located section has force tapping means 16, a connection with components to be moved or Enable facilities.
  • the drive piston 8 is located either directly in the Housing 6 or in a sleeve inserted into the housing 6, whereby he sealed the piston receiving space 7 in two Working chambers divided, the following for better distinction referred to as first and second working chambers 17, 18 become.
  • the drive device 2 further contains a hydraulic pump 22 known structure, which preferably with a designed as a DC motor electric motor 23 in Drive connection is established.
  • the electric motor 23 can be selected operate with counterclockwise and clockwise rotation, accordingly the hydraulic pump 22 optionally in one of the two possible directions of rotation.
  • the hydraulic pump is therefore reversible, which is expediently a Volume flow pump, the speed of which is directly the Movement speed of the drive piston determined.
  • the electric motor 23 is equipped with adjusting means 24, through which both the direction of rotation and the motor speed of the electric motor 23 can be set to accordingly also the pump speed of the hydraulic pump 22 to be able to adjust variably, which is expediently used as a rotary pump is executed. A speed control or too Speed control is therefore possible.
  • speed ramps can be set by the setting means 24 if necessary be generated such that a jerky acceleration or braking one by the drive piston 8 load to be moved is prevented.
  • the hydraulic pump 22 and the electric motor 23 expediently into a fixed structural unit summarized with the housing 6 of the hydraulic drive 5.
  • the hydraulic pump 22 is on flanged the housing 6, 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 via two parallel and for better differentiation than first and second hydraulic circuits 26, 27 designated hydraulic circuits hydraulic connected to the hydraulic drive 5.
  • the hydraulic pump 22 has two pump connections 28, 29, the first (28) via the first hydraulic circuit 26 with the first working chamber 17 is connected and the second (29) via the second Hydraulic circuit 27 with the second working chamber 18 of the Hydraulic drive 5 is connected.
  • the hydraulic medium is each according to the direction of rotation within the closed hydraulic circuit promoted that it was in the first or second working chamber 17, 18 is fed, at the same time hydraulic medium due to the moving drive piston 8 from the other working chamber 18, 17 back to the hydraulic pump 22 is ousted.
  • the Output unit 13 for a drive movement 12 in two each other cause opposite directions, the rod-shaped force tapping part 14 in the exemplary embodiment either extends from the housing 6 or enters this. It is essential that the activation of the hydraulic drive 5 and preferably also in the activated hydraulic drive 5 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 pressure build-up in the feed-side working chamber and accordingly the speed of displacement the output unit 13 is determined by the pump speed determined by using the setting means 24 after Requirements can be specified variably.
  • the speed of the activated Drive piston 8 of the hydraulic drive 5 exclusively from 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 expansion tank 32, absorbs the excess fluid and missing Refills fluid.
  • the two hydraulic circuits are there 26, 27 with a variable-volume compensation space 33 in Fluid connection, one the other hand, atmospheric pressure exposed movable wall 34.
  • the latter can for example formed by a piston or a membrane his.
  • the hydraulic fluid reservoir 32 expediently also a component the drive unit 3 and can be integrated into the housing 6 or attached to its rear end face 25 his.
  • the drive device 2 With regard to the energy supply required for operation from the outside is the drive device 2 as a mono-energetic 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 Has connection means 35, which for the operation of the electric motor 23 required electrical energy is fed becomes.
  • electrical Has connection means 35 This can be, for example, plug connection means act or, as in the embodiment, to an outgoing one that leads to an electrical energy source Connection cable.
  • a separate additional electrical connection means can also be used Connection of the drive device 2 to an external electronic Control device take place, 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 integrate a manufacturing or assembly system, its operations can be controlled electronically.
  • the for specifying the operating state of the hydraulic pump 22nd Serving adjustment means 24 can, if necessary, apart from the Drive device 2 can be placed and over corresponding Interact signal connections with the electric motor 23. All required for the operation of the drive device 2 Signals can also be transmitted wirelessly.
  • the hydraulic drive 5 is preferably a displacement measuring system 61 assigned that the position of the drive piston 8 or one with this motion-coupled component can capture to the electric motor 23 as a function of certain positions to be able to control as required.
  • the position detection signals are fed to the setting means 24, which is expediently equipped with a position controller are.
  • the two hydraulic circuits 26, 27 are in the embodiment integrated in the housing 6 of the hydraulic drive 5, where it is only schematically shown in dash-dotted lines in Figure 1 are indicated, while their preferred structure in detail is shown in Figure 3.
  • Both hydraulic circuits expediently each contain an unlockable check valve 36a, 36b, that is Check valve that unlock under certain circumstances leaves so that it is also in the normally locked Flow direction allows a fluid passage.
  • the unlockable check valves 36a, 36b are thus in the respective hydraulic circuit 26, 27 incorporated that they typically fluid flow from hydraulic pump 22 to the connected working chamber 17, 18 and prevent in the opposite direction.
  • the unlockable check valve 36a, 36b of a respective hydraulic circuit 26, 27 however via a dashed line in FIG Unlocking channel 37a, 37b with that channel section of each another hydraulic circuit 27, 26 in fluid communication, which can be unlocked between the hydraulic pump 22 and the one there Check valve is located.
  • Hydraulic pump 22 operated, for example, that in the first hydraulic circuit 26, a pressure build-up takes place and through the associated releasable check valve that opens 36a feeding hydraulic fluid into the first working chamber 17 takes place, causes the pressure built up simultaneously unlocking and opening the unlockable Check valve 36b of the second hydraulic circuit 27, see above that hydraulic medium displaced from the second working chamber 18 can flow back to the hydraulic pump 22.
  • the corresponding one The process results when the conveying direction is reversed 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 that in the working chambers 17, 18 and in the then go all the way to the unlockable check valves 36a and 36b in the hydraulic circuits 26, 27 fluid is firmly locked. To hold a specific one Position of the output unit 13 is therefore not Energy needed.
  • the pressure-dependent valves which can also be referred to as pressure relief valves opening bias valves 38a, 38b cause the Output unit 13 in addition to that actually to be moved Last a braking load is imposed, which it can only by appropriate To overcome pressure generation of the hydraulic pump 22 applies in order to set the output unit 13 in motion. If one neglects the force tapping part 14 external load to be actuated and the friction that occurs, so would then only in the described embodiment set a movement of the output unit 13 when by the hydraulic medium fed is over 50 bar Pressure is built up.
  • the output unit 13 becomes by appropriate pressure build-up shifted at high speed, so the braking process very easy by reducing the pump power dominate because of the fluid bias in the outflow Working chamber prevailing opening pressure one counterforce acting as braking force.
  • the bias valves each contain a movable shut-off member 42, which by a Opening pressure corresponding spring force into the fluid connection normally pre-tensioned closed position is.
  • the spring force is, for example, by a mechanical Spring device 43 and / or by a gas spring delivered.
  • the spring preload can expediently be variable adjust to influence the opening pressure and accordingly an adaptation to the current application of the To enable drive device 2.
  • the shutoff member 42 is the hydraulic fluid on the outflow side Working chamber against the spring force in the opening direction applies and shifts the shut-off element to the open position, if the actuating force resulting from the opening pressure is greater than the spring force.
  • the interpretation is expedient taken so that a digital switching behavior is present and the preload valve suddenly reaches its maximum Open position switches.
  • unlockable check valve 36a, 36b with the parallel connected Bias and check valves 38a, 45a; 38b, 45b connected in series.
  • the preload valve is located here 38a, 38b expediently in that channel section, which is between the unlockable check valve 36a, 36b and the hydraulic drive 5 extends.
  • the hydraulic drive 5 are the Hydraulic pump 22, the hydraulic circuits 26, 27, the Electric motor 23 and the hydraulic fluid reservoir, if any 32 combined to form the drive unit 3.
  • Protective housing 46 must be covered, which prevents the ingress of contaminants and shields moisture.
  • the drive device 2 can in principle be any Use drive purposes, with different types of the hydraulic drive 5 would be conceivable, for example also rodless designs. Particularly advantageous is the use of the drive device 2 in a design combined into a drive unit 3 in Connection with a tensioning device 1, being on the front Face 15 of the housing 6, the clamping unit 4 mentioned above is scheduled.
  • the latter can be attached to the housing as shown 6 flanged bearing head 47 included, in which the end of the output unit 13 protruding from the housing 6 immersed and which carries a pivotable clamping arm 48.
  • the force tapping means 16 are the output unit 13 via a toggle lever mechanism 49 with the tension arm 48 motion-coupled that from the linear movement of the output unit 13 a rotating or swiveling movement of the clamping arm 48 is derived.
  • This has in the embodiment a rotatably connected pivot lever 50, on which at a to the pivot axis 52 of the clamping arm 48 spaced bearing 53 a tab-like intermediate member 54 is articulated, that via a further bearing 55 with the force tapping means 16 is articulated.
  • the force tapping part 14 is with its outer End section on guide means 56 guided longitudinally and at the same time in the transverse direction with respect to the pivot axis 52 supported.
  • the guide means 56 can, for example, from one or more, in particular groove-like guideways be educated.
  • the swivel arm 48 By actuating the hydraulic drive 5, the swivel arm 48 according to double arrow 57 for a pivoting movement around the Swivel axis 52 are caused to selectively in a To position the clamping position or a release position. In the clamping position, he can on a not shown Work in the workpiece in order to clamp it so tight that it can be edited.
  • the tensioning device 1 is suitable especially for clamping workpieces to be welded.
  • the drive unit 3 has a particularly narrow design. It is possible in particular the cross-sectional dimensions to select the drive unit 3 so that it is equal to or less are those of the bearing head 47.
  • the direction of movement of the output unit 13 is determined solely by the direction of rotation of the DC motor specified, as well as the lifting speed of the Output unit 13 a function of the speed of the DC motor or the pump speed is.
  • the only Variable during the operation of the drive device 2 is in the embodiment, the operating state of the hydraulic pump or their speed.
  • the embodiment can be summarized again that it is preferably a drive device with a hydraulic drive operated by a hydraulic medium 5, which is a hydraulic pump 22 for supplying the hydraulic medium is assigned.
  • the pressure build-up in the activated Hydraulic drive 5 is through adjustable pressure relief valves (Preload valves 38a, 38b), which are pressure-dependent are designed to be opening, as well as parallel to these Check valves 45a, 45b controlled.
  • the speed of the drive piston 8 of the activated hydraulic drive 5 is determined exclusively by the volume flow of the hydraulic Medium in the hydraulic circuits 26, 27 certainly.

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  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Valve Device For Special Equipments (AREA)
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Abstract

The drive device (2) has a closed hydraulic circuit, which has a hydraulic drive (5) and a hydraulic pump (22) to supply and remove hydraulic medium for operating the hydraulic drive. An electric motor (23) is provided to operate the hydraulic pump. The operation state of the hydraulic pump determines the activation of the hydraulic drive. The operation pressure in the hydraulic drive is varied according to the rpm of the hydraulic pump.

Description

Die vorliegende Erfindung betrifft das Gebiet der Antriebsvorrichtungen, die einen durch Zufuhr von Energie aktivierbaren Antrieb aufweisen, von dem eine Antriebskraft abgegriffen werden kann.The present invention relates to the field of drive devices, which can be activated by supplying energy Have drive from which a driving force is tapped can be.

Eine derartige Antriebsvorrichtung geht beispielsweise aus dem deutschen Gebrauchsmuster Nr. 299 03 825.4 hervor, wo sie als Bestandteil einer Kniehebel-Spannvorrichtung beschrieben wird. Sie erhält dort einen durch Druckluft aktivierbaren Pneumatikantrieb mit zugeordneten elektrisch betätigbaren Steuerventilen, um die Antriebsrichtung des Pneumatikantriebes vorgeben zu können. Alternativ wäre auch ein Hydraulikantrieb denkbar, der mit elektrisch betätigbaren Servoventilen ausgestattet ist, um den Antriebszustand zu beeinflussen. Während bei Pneumatikantrieben auf Grund der Kompressibilität des Betätigungsmediums in der Regel ein größerer technischer Aufwand notwendig ist, um exakte Positionierungen und langsame Bewegungen beherrschen zu können, überwiegt bei Hydraulikantrieben das Leckageproblem und der hohe Unterhaltsaufwand für die Gewährleistung sicherer Schlauchverbindungen und eines qualitativ hochwertigen Hydraulikmediums. Such a drive device goes out, for example the German utility model No. 299 03 825.4, where they described as part of a toggle clamp device becomes. There it receives one that can be activated by compressed air Pneumatic actuator with associated electrically actuated Control valves to determine the drive direction of the pneumatic actuator to be able to pretend. Alternatively, there would also be a hydraulic drive conceivable, the one with electrically operated servo valves is equipped to influence the drive state. While with pneumatic drives due to the compressibility the actuating medium is usually a larger technical one Effort is needed to make exact positioning and slow Being able to master movements predominates in hydraulic drives the leakage problem and the high maintenance costs to ensure secure hose connections and one high quality hydraulic medium.

Auf dem Sektor der Spannvorrichtungen sind daher alternativ auch Bauformen mit Elektroantrieb bekannt, wobei in einem Prospekt der Firma Tünkers Maschinenbau GmbH ein sogenannter "Elektrospanner" gezeigt wird, dessen Elektroantrieb als Spindelantrieb ausgeführt ist. Hier ergibt sich jedoch, insbesondere in Verbindung mit der Übertragung hoher Stellkräfte, ein nicht unbeträchtliches Verschleißproblem.In the clamping device sector are therefore alternative also known designs with electric drive, being in one Brochure of the company Tünkers Maschinenbau GmbH a so-called "Electric tensioner" is shown, its electric drive as Spindle drive is executed. Here, however, arises, in particular in connection with the transmission of high actuating forces, a not inconsiderable problem of wear.

Es ist die Aufgabe der vorliegenden Erfindung, eine Antriebsvorrichtung zu schaffen, mit der bei geringer Verschleißanfälligkeit und geringem Wartungsaufwand hohe Antriebskräfte übertragen werden können.It is the object of the present invention to provide a drive device to create with the low susceptibility to wear and low maintenance, high driving forces can be transferred.

Gelöst wird diese Aufgabe durch eine Antriebsvorrichtung, mit einem geschlossenen Hydraulikkreis, der einen durch hydraulisches Medium betätigbaren Hydraulikantrieb und eine die Zufuhr und Abfuhr des hydraulischen Mediums bezüglich dem Hydraulikantrieb veranlassende Hydraulikpumpe enthält, wobei zur Betätigung der Hydraulikpumpe ein Elektromotor vorgesehen ist und die Aktivierung des Hydraulikantriebes durch den Betriebszustand der Hydraulikpumpe bestimmt wird.This task is solved by a drive device with a closed hydraulic circuit, one through hydraulic Medium operated hydraulic drive and a feed and discharge of the hydraulic medium with respect to the hydraulic drive causing hydraulic pump contains, for Actuation of the hydraulic pump, an electric motor is provided and the activation of the hydraulic drive through the operating state the hydraulic pump is determined.

Auf diese Weise ergibt sich eine elektro-hydraulische Antriebsvorrichtung, bei der auf Grund des geschlossenen Hydraulikkreises die Leckageproblematik sehr einfach in den Griff zu bekommen ist und auf Grund der besonderen Ansteuerung durch die elektromotorisch aktivierbare Hydraulikpumpe keine teuren Servoventile benötigt werden, um den Hydraulikantrieb in der gewünschten Weise zu betätigen. Der Verzicht auf Servo-Steuerventile hat dabei auch den Vorteil, dass an die Aufbereitung des verwendeten Hydraulikmediums relativ geringe Anforderungen gestellt sind, was den Unterhalt sehr kostengünstig gestaltet. Die Aktivierung des Hydraulikantriebes wird zweckmäßigerweise allein durch den Betriebszustand der Hydraulikpumpe bestimmt und kann beispielsweise durch Ein-/Ausschalten sowie Vorgabe einer bestimmten Pumpendrehzahl sehr einfach gesteuert werden.This results in an electro-hydraulic drive device due to the closed hydraulic circuit the problem of leakage very easily in the Is to get a grip and because of the special control thanks to the hydraulic pump that can be activated by an electric motor No expensive servo valves are needed to power the hydraulic system to operate in the desired manner. The waiver on servo control valves also has the advantage that the preparation of the hydraulic medium used is relatively low Requirements are met, which is very maintenance designed inexpensively. The activation of the hydraulic drive is expediently solely by the operating state the hydraulic pump determines and can for example by Switching on / off and specifying a certain pump speed can be controlled very easily.

Vorteilhafte Weiterbildungen der Erfindung gehen aus den Unteransprüchen hervor.Advantageous developments of the invention emerge from the subclaims forth.

Während des Betriebes des Hydraulikantriebes benötigte unterschiedliche Betätigungsdrücke lassen sich zweckmäßigerweise allein in Abhängigkeit von der Drehzahl der Hydraulikpumpe vorgeben. Somit lassen sich Lasten beschleunigen oder bremsen, ohne auf eine zwischengeschaltete Servoventileinrichtung zurückgreifen zu müssen, die den Strömungsquerschnitt beeinflusst. Dabei sind vorzugsweise geeignete Einstellmittel vorhanden, durch die eine variable Vorgabe der die Pumpendrehzahl der Hydraulikpumpe bestimmenden Motordrehzahl des Elektromotors steuerbar oder regelbar ist. Es kann auch die Möglichkeit gegeben sein, Drehzahlrampen vorzugeben, um die Beschleunigung und Abbremsung einer durch den Hydraulikantrieb zu bewegenden Last gleichförmig zu gestalten und ruckartige Bewegungen zu vermeiden.Different required during the operation of the hydraulic drive Operating pressures can be conveniently solely depending on the speed of the hydraulic pump pretend. This means that loads can be accelerated or braked, without an intermediate servo valve device to have to resort, which influences the flow cross-section. Suitable setting means are preferably present, by the variable specification of the pump speed of the hydraulic pump determining motor speed of the electric motor is controllable or regulatable. It can also be a possibility be given to specify speed ramps to accelerate and braking one by the hydraulic drive to make the load to be moved uniform and jerky To avoid movements.

Bei einer besonders zweckmäßigen Ausführungsform der Antriebsvorrichtung ist der Hydraulikantrieb mit mindestens einem mit einem Kraftabgriffsteil bewegungsgekoppelten Antriebskolben versehen, der zwei Arbeitskammern fluiddicht voneinander abteilt, die beide über jeweils eine Hydraulikschaltung mit der Hydraulikpumpe verbunden sind, wobei das Einspeisen von Hydraulikfluid in die jeweils eine Arbeitskammer mit dem gleichzeitigen Ausströmen von Hydraulikfluid aus der anderen Arbeitskammer einhergeht, um dementsprechend den Antriebskolben in gewünschter Weise zu verlagern. Indem die Hydraulikpumpe wahlweise zu einer linksdrehenden oder rechtsdrehenden Rotationsbewegung antreibbar ist - beispielsweise durch Änderung des Drehsinnes des Elektromotors oder unter Zwischenschaltung eines Umschaltgetriebes - , kann Hydraulikmedium wahlweise in die eine oder andere der beiden Arbeitskammern eingespeist werden, um dementsprechend die Bewegungsrichtung des Antriebskolbens zu beeinflussen.In a particularly expedient embodiment of the drive device is the hydraulic drive with at least one with a force-tapping part motion-coupled drive piston provided, the two working chambers fluid-tight separated from each other, both via a hydraulic circuit are connected to the hydraulic pump, the Feeding hydraulic fluid into one working chamber with the simultaneous leakage of hydraulic fluid the other Chamber of Labor goes hand in hand with the Shift the drive piston in the desired manner. By the Hydraulic pump to either a left-handed or right-handed Rotational movement can be driven - for example by changing the direction of rotation of the electric motor or under Interposition of a changeover gear, can hydraulic medium either in one or the other of the two working chambers be fed in accordingly the direction of movement of the drive piston.

Die beiden Hydraulikschaltungen der Antriebsvorrichtung enthalten zweckmäßigerweise jeweils ein entsperrbares Rückschlagventil, das normalerweise eine Fluidströmung von der Hydraulikpumpe zum Hydraulikantrieb zulässt und in Gegenrichtung verhindert, wobei jedes Rückschlagventil durch den in der jeweils anderen Hydraulikschaltung von der Hydraulikpumpe aufrecht erhaltenen Druck entsperrbar ist, um eine Fluidströmung vom Hydraulikantrieb zurück zur Hydraulikpumpe zu ermöglichen. Auf diese Weise können beliebige Zwischenstellungen des Antriebskolbens ohne ständige Energiezufuhr aufrecht erhalten werden, weil das Hydraulikmedium bei deaktivierter Hydraulikpumpe durch die Rückschlagventile in den Arbeitskammern eingesperrt wird. Wird hingegen die Hydraulikpumpe aktiviert, so sorgt der in der einen Hydraulikschaltung dadurch aufgebaute Druck für ein Entsperren des in der anderen Hydraulikschaltung befindlichen Rückschlagventils und ermöglicht somit die ungehinderte Bewegung des Antriebskolbens.The two hydraulic circuits of the drive device included expediently one unblockable check valve each, which is usually a fluid flow from the Hydraulic pump allows for hydraulic drive and in the opposite direction prevented, each check valve by the in the other hydraulic circuit from the hydraulic pump maintained pressure is unlockable to fluid flow from the hydraulic drive back to the hydraulic pump. In this way, any intermediate positions of the drive piston without constant energy supply because the hydraulic medium is deactivated Hydraulic pump through the check valves in the working chambers is locked up. However, if the hydraulic pump is activated, this ensures that in one hydraulic circuit pressure built up to unlock the in the other hydraulic circuit check valve located and allows thus the unimpeded movement of the drive piston.

Eine weitere, besonders vorteilhafte Ausstattung der Antriebsvorrichtung ergibt sich, wenn in mindestens eine und vorzugsweise beide Hydraulikschaltungen ein Vorspannventil eingeschaltet ist, das die Fluidverbindung von der zugeordneten Arbeitskammer hin zur Hydraulikpumpe normalerweise absperrt und nur dann freigibt, wenn und solange sich in der ausströmseitigen Arbeitskammer ein vorbestimmter Öffnungsdruck aufgebaut hat. Durch das Vorspannventil wird also eine Vorspannung des in der ausströmseitigen Arbeitskammer befindlichen Hydraulikmediums bewirkt, das nicht sofort verdrängt werden kann, wenn in der einspeiseseitigen Arbeitskammer eine Druckerhöhung stattfindet. Erst wenn die Druckerhöhung in der einspeiseseitigen Arbeitskammer so stark ist, dass der in der ausströmseitigen Arbeitskammer sich aufbauende Druck den als Öffnungsdruck bezeichneten Mindestdruck erreicht, kann das zuvor eingespannte Hydraulikmedium ausströmen. Da der in der ausströmseitigen Arbeitskammer herrschende Druck dabei jedoch ständig eine der gewünschten Bewegungsrichtung des Antriebskolbens entgegengesetzt orientierte Gegenkraft verursacht, läßt sich der Antriebskolben auch bei einer mit hoher Dynamik ausgeführten Bewegung sehr schnell und präzise abbremsen, indem einfach der einströmseitig angelegte Druck durch entsprechende Änderung des Betriebszustandes der Hydraulikpumpe variiert wird. Es kann also wiederum ohne servogesteuerte Hydraulikventile eine sehr exakte Positionierung des Antriebskolbens bzw. eines mit diesem bewegungsgekoppelten Kraftabgriffsteils auch bei hohen Betriebsgeschwindigkeiten erreicht werden.Another, particularly advantageous equipment of the drive device results if in at least one and preferably both hydraulic circuits a bias valve is turned on, the fluid connection from the associated The working chamber towards the hydraulic pump is normally shut off and only releases if and as long as in the outflow-side working chamber a predetermined opening pressure has built up. The preload valve thus becomes a Biasing of the one located in the outflow-side working chamber Hydraulic medium causes that does not immediately replace can be, if in the feed-side working chamber Pressure increase takes place. Only when the pressure increase in the feed-side working chamber is so strong that in the upstream working chamber the pressure builds up as Opening pressure, the minimum pressure can be reached Flush out previously clamped hydraulic medium. Since the in the outflow-side working chamber however prevailing pressure constantly one of the desired directions of movement of the drive piston oppositely oriented counterforce causes the drive piston can also be operated with a high dynamic range brake the executed movement very quickly and precisely by simply the pressure applied on the inflow side by appropriate Change in the operating state of the hydraulic pump varies becomes. It can, in turn, be operated without servo-controlled hydraulic valves a very exact positioning of the drive piston or a force-tapping part coupled to this movement achieved even at high operating speeds become.

Die Auslegung der Vorspannventile ist zweckmäßigerweise so getroffen, dass der das Öffnen bewirkende Öffnungsdruck im Bereich zwischen 10% und 90% des von der Hydraulikpumpe maximal erzeugbaren Betriebsdruckes liegt. Der bevorzugte Druckbereich liegt dabei zwischen 30% und 50% des erwähnten maximalen Betätigungsdruckes. Anders als ein einfaches Rückschlagventil, das schon bei sehr geringen Druckdifferenzen öffnet, wird also durch die Vorspannventile ein nicht unbeträchtlicher Vorspanneffekt herbeigeführt. Dabei läßt sich der Öffnungsdruck zweckmäßigerweise durch geeignete Einstellmittel variabel vorgeben, um eine einfache Anpassung an den jeweiligen Anwendungsfall durchführen zu können.The design of the preload valves is expediently so met that the opening pressure causing the opening in Range between 10% and 90% of the maximum of the hydraulic pump generated operating pressure is. The preferred printing area is between 30% and 50% of the maximum mentioned Actuation pressure. Unlike a simple check valve, even with very small pressure differences opens, the preload valves make it a not inconsiderable one Prestressing effect brought about. It can be the opening pressure expediently by means of suitable setting means specify variable to easily adapt to the to be able to carry out the respective application.

Zweckmäßigerweise verfügt das betreffende Vorspannventil über ein bewegliches Absperrglied, das durch eine dem gewünschten Öffnungsdruck entsprechende Federkraft in eine die Fluidverbindung unterbrechende Schließstellung vorgespannt ist und das vom Hydraulikfluid der ausströmseitigen Arbeitskammer entgegen der Federkraft im Öffnungssinne beaufschlagt wird. Steigt der Druck in der ausströmseitigen Arbeitskammer auf mindestens den Öffnungsdruck an, ergibt sich eine resultierende Öffnungskraft, die die Federkraft überwinden und das Absperrglied in eine Offenstellung umschalten kann. Das Vorspannventil hat also vorzugsweise ein digitales Schaltverhalten. The bias valve in question expediently has a movable shut-off element, which can be replaced by the desired one Opening pressure corresponding spring force into the fluid connection interrupted closed position is biased and that of the hydraulic fluid of the working chamber on the outflow side is applied against the spring force in the opening direction. The pressure in the outflow-side working chamber rises results in at least the opening pressure Opening force that overcome the spring force and that Shutoff member can switch to an open position. The preload valve therefore preferably has a digital switching behavior.

Soweit eine Hydraulikschaltung sowohl mit einem entsperrbaren Rückschlagventil als auch mit einem Vorspannventil ausgestattet ist, sind diese Ventile zweckmäßigerweise in Reihe geschaltet, wobei das Vorspannventil vorzugsweise zwischen dem entsperrbaren Rückschlagventil und dem Hydraulikantrieb platziert ist.As far as a hydraulic circuit both with an unlockable Check valve and also equipped with a preload valve these valves are expediently connected in series, wherein the bias valve is preferably between the unlockable check valve and the hydraulic drive placed is.

Jedem Vorspannventil ist zweckmäßigerweise ein in Richtung zum Hydraulikantrieb öffnendes und in Gegenrichtung sperrendes Rückschlagventil parallel geschaltet, das bei entsprechender Drehrichtung der Hydraulikpumpe ein Einspeisen des Hydraulikmediums in die zugeordnete Arbeitskammer unter Umgehung des Vorspannventils ermöglicht.Each bias valve is conveniently one in the direction opening to the hydraulic drive and locking in the opposite direction Check valve connected in parallel, the corresponding Direction of rotation of the hydraulic pump feeding the Hydraulic medium bypassing the assigned working chamber of the preload valve.

Zur Kompensation von Temperaturschwankungen und/oder unterschiedlichen Volumina der Arbeitskammern kann jede Hydraulikschaltung mit einem Hydraulikfluid-Ausgleichsbehältnis verbunden sein, das eine dem Atmosphärendruck ausgesetzte bewegliche Wand besitzt.To compensate for temperature fluctuations and / or different ones Volumes of the working chambers can be any hydraulic circuit connected to a hydraulic fluid expansion tank be a movable one exposed to atmospheric pressure Owns the wall.

Zweckmäßigerweise sind zumindest der Hydraulikantrieb, die Hydraulikpumpe, die Hydraulikschaltungen und der Elektromotor zu einer Baueinheit (Antriebseinheit) zusammengefasst, wobei zur Energieeinspeisung ausschließlich elektrische Schnittstellenmittel vorhanden sein können, die zum Betrieb des Elektromotors dienen. Auf hydraulische Schnittstellenmittel kann verzichtet werden, weil der geschlossene Hydraulikkreis als autarker Bestandteil der Antriebseinheit ausgeführt sein kann. At least the hydraulic drive is expedient, the Hydraulic pump, the hydraulic circuits and the electric motor combined into one unit (drive unit), where only electrical interface means for energy supply may be present to operate the Serve electric motor. On hydraulic interface means can be dispensed with because of the closed hydraulic circuit be designed as an independent component of the drive unit can.

Bei einer besonders vorteilhaften Ausgestaltung ist die Antriebsvorrichtung als Bestandteil einer insbesondere als Kniehebel-Spannvorrichtung ausgebildeten Spannvorrichtung ausgeführt, bei der das Kraftabgriffsteil des Hydraulikantriebes mit einem schwenkbeweglichen Spannarm der Spannvorrichtung in Antriebsverbindung steht. Diese Ausgestaltung empfiehlt sich insbesondere in Verbindung mit einer zu einer Antriebseinheit zusammengefassten Antriebsvorrichtung, da dies sehr kompakte Abmessungen ermöglicht und einen Einsatz alternativ zu einer rein fluidisch oder rein elektrisch betätigten Spannvorrichtung gestattet. Hier können auch Bauformen erhalten werden, bei denen die Querschnittsabmessungen der Antriebseinheit gleich oder geringer sind als diejenigen des zur Schwenklagerung dienenden Lagerungskopfes der Spannvorrichtung.In a particularly advantageous embodiment, 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 swiveling clamping arm of the clamping device is in drive connection. This configuration is particularly recommended in connection with one to one Drive unit summarized drive device because this enables very compact dimensions and use alternative to a purely fluid or electrically operated Clamping device allowed. Designs can also be found here are obtained in which the cross-sectional dimensions of the Drive unit are equal to or less than those of the bearing head of the tensioning device used for swivel mounting.

Nachfolgend wird die Erfindung anhand der beiliegenden Zeichnung näher erläutert. In dieser zeigen:

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.
The invention is explained in more detail below with reference to the accompanying drawing. In this show:
Figure 1
in a schematic representation and partially in longitudinal section a tensioning device which is equipped with a preferred embodiment of the drive device according to the invention,
Figure 2
the arrangement of Figure 1 in a rear view looking in the direction of arrow II, and
Figure 3
the electro-hydraulic circuit diagram of the drive device preferably used in the tensioning device according to FIGS. 1 and 2.

Die Figuren 1 und 2 zeigen eine als Kniehebel-Spannvorrichtung ausgebildete Spannvorrichtung 1, die als wesentliche Komponenten eine zu einer Baueinheit zusammengefasste und daher als Antriebseinheit 3 bezeichenbare Antriebsvorrichtung 2 und eine fest mit der Antriebseinheit 3 verbundene Spanneinheit 4 enthält. Der schaltungstechnische Aufbau der Antriebsvorrichtung 2 bzw. Antriebseinheit 3 ist in Figur 1 nur schematisch wiedergegeben, wobei die Figur 3 den Schaltplan eines besonders vorteilhaften Aufbaus wiedergibt.Figures 1 and 2 show a knee lever tensioning device trained tensioner 1, the essential Components a combined into a structural unit and therefore Drive device 2, which can be designated as drive unit 3 and a clamping unit firmly connected to the drive unit 3 4 contains. The circuit design of the drive device 2 or drive unit 3 is only schematic in Figure 1 reproduced, wherein the Figure 3 is a circuit diagram reproduces a particularly advantageous structure.

Die Antriebsvorrichtung 2 enthält einen durch hydraulisches Medium betätigbaren Hydraulikantrieb 5, der beim Ausführungsbeispiel als Linearantrieb ausgeführt ist, bei entsprechendem Einsatzgebiet der Antriebsvorrichtung 2 aber beispielsweise auch als Drehantrieb konzipiert sein kann.The drive device 2 contains one by hydraulic Medium actuable hydraulic drive 5, which in the embodiment is designed as a linear drive, with the corresponding Field of application of the drive device 2, however, for example can also be designed as a rotary drive.

Der Hydraulikantrieb 5 verfügt über ein Gehäuse 6, in dem sich ein länglicher Kolbenaufnahmeraum 7 befindet, der einen Antriebskolben 8 enthält. Dieser ist Bestandteil einer im Rahmen einer durch einen Doppelpfeil markierten Antriebsbewegung 12 linear verschiebbaren Abtriebseinheit 13, die beim Ausführungsbeispiel noch ein von einer Kolbenstange gebildetes längliches Kraftabgriffsteil 14 enthält, das mit dem Antriebskolben 8 fest verbunden und somit bewegungsgekoppelt ist. The hydraulic drive 5 has a housing 6 in which there is an elongated piston receiving space 7 that one Includes drive piston 8. This is part of an im Frame of a drive movement marked by a double arrow 12 linearly displaceable output unit 13 which at Embodiment another one formed by a piston rod Includes elongated power take-off part 14, which with the drive piston 8 firmly connected and thus motion-coupled is.

Das Kraftabgriffsteil 14 erstreckt sich in der Richtung der Antriebsbewegung 12, wobei es an der vorderen Stirnseite 15 des Gehäuses 6 herausragt und an seinem außerhalb des Gehäuses 6 befindlichen Abschnitt über Kraftabgriffsmittel 16 verfügt, die eine Verbindung mit zu bewegenden Bauteilen oder Einrichtungen ermöglichen.The force tapping member 14 extends in the direction of the Drive movement 12, it being on the front end face 15 of the housing 6 protrudes and on its outside the housing 6 located section has force tapping means 16, a connection with components to be moved or Enable facilities.

Der Antriebskolben 8 befindet sich entweder unmittelbar im Gehäuse 6 oder in einer in das Gehäuse 6 eingesetzten Hülse, wobei er den Kolbenaufnahmeraum 7 unter Abdichtung in zwei Arbeitskammern unterteilt, die nachfolgend zur besseren Unterscheidung als erste und zweite Arbeitskammern 17, 18 bezeichnet werden.The drive piston 8 is located either directly in the Housing 6 or in a sleeve inserted into the housing 6, whereby he sealed the piston receiving space 7 in two Working chambers divided, the following for better distinction referred to as first and second working chambers 17, 18 become.

Die Antriebsvorrichtung 2 enthält desweiteren eine Hydraulikpumpe 22 an sich bekannten Aufbaues, die mit einem vorzugsweise als Gleichstrommotor ausgeführten Elektromotor 23 in Antriebsverbindung steht. Der Elektromotor 23 läßt sich wahlweise mit Linkslauf und Rechtslauf betreiben, um dementsprechend auch die Hydraulikpumpe 22 wahlweise in einer der beiden möglichen Drehrichtungen zu betreiben. Die Hydraulikpumpe ist also reversierbar, wobei es sich zweckmäßigerweise um eine Volumenstrompumpe handelt, deren Drehzahl unmittelbar die Bewegungsgeschwindigkeit des Antriebskolbens bestimmt.The drive device 2 further contains a hydraulic pump 22 known structure, which preferably with a designed as a DC motor electric motor 23 in Drive connection is established. The electric motor 23 can be selected operate with counterclockwise and clockwise rotation, accordingly the hydraulic pump 22 optionally in one of the two possible directions of rotation. The hydraulic pump is therefore reversible, which is expediently a Volume flow pump, the speed of which is directly the Movement speed of the drive piston determined.

Der Elektromotor 23 ist mit Einstellmitteln 24 ausgestattet, durch die sich sowohl die Drehrichtung als auch die Motordrehzahl des Elektromotors 23 variabel vorgeben läßt, um dementsprechend auch die Pumpendrehzahl der Hydraulikpumpe 22 variabel einstellen zu können, die zweckmäßigerweise als Rotationspumpe ausgeführt ist. Eine Drehzahlsteuerung oder auch Drehzahlregelung ist somit möglich.The electric motor 23 is equipped with adjusting means 24, through which both the direction of rotation and the motor speed of the electric motor 23 can be set to accordingly also the pump speed of the hydraulic pump 22 to be able to adjust variably, which is expediently used as a rotary pump is executed. A speed control or too Speed control is therefore possible.

Ferner können durch die Einstellmittel 24 bei Bedarf Drehzahlrampen derart erzeugt werden, dass eine ruckartige Beschleunigung oder Abbremsung einer durch den Antriebskolben 8 zu bewegenden Last verhindert wird.Furthermore, speed ramps can be set by the setting means 24 if necessary be generated such that a jerky acceleration or braking one by the drive piston 8 load to be moved is prevented.

Es versteht sich, dass die Änderung der Richtungsumkehr der Pumpenrotation auch durch ein zwischen den Elektromotor 23 und die Hydraulikpumpe 22 zwischengeschaltetes Getriebe realisiert werden könnte.It is understood that the change of direction reversal of the Pump rotation also by a between the electric motor 23 and the hydraulic pump 22 realizes intermediate gear could be.

Wie aus Figur 1 hervorgeht, sind die Hydraulikpumpe 22 und der Elektromotor 23 zweckmäßigerweise zu einer festen Baueinheit mit dem Gehäuse 6 des Hydraulikantriebes 5 zusammengefasst. Beim Ausführungsbeispiel ist die Hydraulikpumpe 22 an das Gehäuse 6 angeflanscht, wobei der Elektromotor 23 seinerseits an der Hydraulikpumpe 22 befestigt ist. Möglich wäre auch eine separate Befestigung der beiden Komponenten am Gehäuse 6 wie auch eine zumindest partielle Integration einer oder beider Komponenten in das Gehäuse 6.As can be seen from Figure 1, the hydraulic pump 22 and the electric motor 23 expediently into a fixed structural unit summarized with the housing 6 of the hydraulic drive 5. In the exemplary embodiment, the hydraulic pump 22 is on flanged the housing 6, 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.

Damit die Antriebseinheit 3 über eine schlanke Bauweise verfügt, sind der Elektromotor 23 und die Hydraulikpumpe 22 im Bereich der rückwärtigen Stirnseite 25 des Gehäuses 6 installiert. So that 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.

Die Hydraulikpumpe 22 ist über zwei zueinander parallele und zur besseren Unterscheidung als erste und zweite Hydraulikschaltungen 26, 27 bezeichnete Hydraulikschaltungen hydraulisch mit dem Hydraulikantrieb 5 verbunden. Die Hydraulikpumpe 22 hat zwei Pumpenanschlüsse 28, 29, deren erster (28) über die erste Hydraulikschaltung 26 mit der ersten Arbeitskammer 17 verbunden ist und deren zweiter (29) über die zweite Hydraulikschaltung 27 mit der zweiten Arbeitskammer 18 des Hydraulikantriebs 5 in Verbindung steht. Dabei liegt ein geschlossener, komplett mit Hydraulikmedium gefüllter Hydraulikkreis vor, wobei sich als Hydraulikmedium beispielsweise Öl oder Wasser anbietet.The hydraulic pump 22 is via two parallel and for better differentiation than first and second hydraulic circuits 26, 27 designated hydraulic circuits hydraulic connected to the hydraulic drive 5. The hydraulic pump 22 has two pump connections 28, 29, the first (28) via the first hydraulic circuit 26 with the first working chamber 17 is connected and the second (29) via the second Hydraulic circuit 27 with the second working chamber 18 of the Hydraulic drive 5 is connected. There is a closed, Hydraulic circuit completely filled with hydraulic medium before, for example as a hydraulic medium Offers oil or water.

Im Betrieb der Hydraulikpumpe 22 wird das Hydraulikmedium je nach Drehrichtung derart innerhalb des geschlossenen Hydraulikkreises gefördert, dass es in die erste oder zweite Arbeitskammer 17, 18 eingespeist wird, wobei gleichzeitig Hydraulikmedium durch den sich dabei bewegenden Antriebskolben 8 aus der jeweils anderen Arbeitskammer 18, 17 zurück zur Hydraulikpumpe 22 verdrängt wird. Auf diese Weise läßt sich die Abtriebseinheit 13 zu einer Antriebsbewegung 12 in zwei einander entgegengesetzte Richtungen veranlassen, wobei das stangenförmige Kraftabgriffsteil 14 beim Ausführungsbeispiel entweder aus dem Gehäuse 6 ausfährt oder in dieses einfährt. Wesentlich ist dabei, dass die Aktivierung des Hydraulikantriebes 5 und vorzugsweise auch der im aktivierten Hydraulikantrieb 5 stattfindende Druckaufbau bzw. Volumenstrom allein durch den Betriebszustand der Hydraulikpumpe bestimmt wird. Um die Abtriebseinheit 13 in einer bestimmten Position anzuhalten, wird die Hydraulikpumpe 22 stillgesetzt. Um die Abtriebseinheit 13 zu verlagern, wird je nach gewünschter Bewegungsrichtung die Hydraulikpumpe 22 mit entsprechendem Drehsinn aktiviert. Der Druckaufbau in der einspeiseseitigen Arbeitskammer und dementsprechend auch die Verlagerungsgeschwindigkeit der Abtriebseinheit 13 wird durch die Pumpendrehzahl bestimmt, die mit Hilfe der Einstellmittel 24 nach Bedarf variabel vorgegeben werden kann.In the operation of the hydraulic pump 22, the hydraulic medium is each according to the direction of rotation within the closed hydraulic circuit promoted that it was in the first or second working chamber 17, 18 is fed, at the same time hydraulic medium due to the moving drive piston 8 from the other working chamber 18, 17 back to the hydraulic pump 22 is ousted. In this way, the Output unit 13 for a drive movement 12 in two each other cause opposite directions, the rod-shaped force tapping part 14 in the exemplary embodiment either extends from the housing 6 or enters this. It is essential that the activation of the hydraulic drive 5 and preferably also in the activated hydraulic drive 5 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. To the output unit 13 will shift depending on the desired direction of movement the hydraulic pump 22 with a corresponding direction of rotation activated. The pressure build-up in the feed-side working chamber and accordingly the speed of displacement the output unit 13 is determined by the pump speed determined by using the setting means 24 after Requirements can be specified variably.

Vorzugsweise wird also die Geschwindigkeit des aktivierten Antriebskolbens 8 des Hydraulikantriebes 5 ausschließlich von dem Volumenstrom des hydraulischen Mediums in den hydraulischen Schaltungen 26, 27 bestimmt.Preferably, the speed of the activated Drive piston 8 of the hydraulic drive 5 exclusively from the volume flow of the hydraulic medium in the hydraulic Circuits 26, 27 determined.

Bedingt durch das die zweite Arbeitskammer 18 durchsetzende Kraftabgriffsteil 14, stellen sich beim Verlagern der Abtriebseinheit 13 in den beiden Arbeitskammern 17, 18 unterschiedliche Volumenänderungen pro Zeiteinheit ein. Um dies zu kompensieren, sind die beiden Hydraulikschaltungen 26, 27 gemeinsam an ein Hydraulikfluid-Ausgleichsbehältnis 32 angeschlossen, das überschüssiges Fluid aufnimmt und fehlendes Fluid nachfüllt. Dabei stehen die beiden Hydraulikschaltungen 26, 27 mit einem volumenveränderlichen Ausgleichsraum 33 in Fluidverbindung, der eine andererseits dem Atmosphärendruck ausgesetzte bewegliche Wand 34 aufweist. Letztere kann beispielsweise von einem Kolben oder von einer Membran gebildet sein. Wie aus Figur 1 hervorgeht, ist das Hydraulikfluid-Ausgleichsbehältnis 32 zweckmäßigerweise ebenfalls Bestandteil der Antriebseinheit 3 und kann in das Gehäuse 6 integriert oder an dessen rückwärtige Stirnseite 25 angesetzt sein. Due to the penetration of the second working chamber 18 Force tapping part 14, arise when moving the output unit 13 in the two working chambers 17, 18 different Volume changes per unit of time. To do this compensate, the two hydraulic circuits 26, 27 are common connected to a hydraulic fluid expansion tank 32, absorbs the excess fluid and missing Refills fluid. The two hydraulic circuits are there 26, 27 with a variable-volume compensation space 33 in Fluid connection, one the other hand, atmospheric pressure exposed movable wall 34. The latter can for example formed by a piston or a membrane his. As can be seen from Figure 1, the hydraulic fluid reservoir 32 expediently also a component the drive unit 3 and can be integrated into the housing 6 or attached to its rear end face 25 his.

Hinsichtlich der für den Betrieb notwendigen Energiezufuhr von außen her ist die Antriebsvorrichtung 2 als monoenergetisches Gerät ausgeführt. Bedingt durch den intern geschlossenen Hydraulikkreis bedarf es keiner Zufuhr und/oder Abfuhr hydraulischer Betätigungsenergie, so dass die Antriebsvorrichtung 2 zur Energieeinspeisung ausschließlich über elektrische Anschlussmittel 35 verfügt, über die die für den Betrieb des Elektromotors 23 benötigte elektrische Energie eingespeist wird. Es kann sich dabei beispielsweise um Steckanschlussmittel handeln oder, wie beim Ausführungsbeispiel, um ein abgehendes, zu einer elektrischen Energiequelle geführtes Anschlusskabel.With regard to the energy supply required for operation from the outside is the drive device 2 as a mono-energetic 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 Has connection means 35, which for the operation of the electric motor 23 required electrical energy is fed becomes. This can be, for example, plug connection means act or, as in the embodiment, to an outgoing one that leads to an electrical energy source Connection cable.

In Baueinheit mit den elektrischen Anschlussmitteln oder über separate weitere elektrische Anschlussmittel kann auch eine Anbindung der Antriebsvorrichtung 2 an eine externe elektronische Steuereinrichtung erfolgen, die auch Positionserfassungssignale berücksichtigen kann, welche in Abhängigkeit von der Position der Abtriebseinheit 13 erzeugt werden. Die Antriebsvorrichtung 2 läßt sich auf diese Weise bei Bedarf in ein Fertigungs- oder Montagesystem integrieren, dessen Betriebsabläufe elektronisch gesteuert werden.As a unit with the electrical connection means or via A separate additional electrical connection means can also be used Connection of the drive device 2 to an external electronic Control device take place, 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 integrate a manufacturing or assembly system, its operations can be controlled electronically.

Die zur Vorgabe des Betriebszustandes der Hydraulikpumpe 22 dienenden Einstellmittel 24 können bei Bedarf abseits von der Antriebsvorrichtung 2 platziert sein und über entsprechende Signalverbindungen mit dem Elektromotor 23 zusammenwirken. Sämtliche für den Betrieb der Antriebsvorrichtung 2 benötigten Signale können auch drahtlos übermittelt werden. The for specifying the operating state of the hydraulic pump 22nd Serving adjustment means 24 can, if necessary, apart from the Drive device 2 can be placed and over corresponding Interact signal connections with the electric motor 23. All required for the operation of the drive device 2 Signals can also be transmitted wirelessly.

Vorzugsweise ist dem Hydraulikantrieb 5 ein Wegmeßsystem 61 zugeordnet, das die Position des Antriebskolbens 8 oder einer mit diesem bewegungsgekoppelten Komponente erfassen kann, um in Abhängigkeit von bestimmten Positionen den Elektromotor 23 nach Bedarf ansteuern zu können. Dabei können die Positionserfassungssignale den Einstellmitteln 24 zugeführt werden, die hierbei zweckmäßigerweise mit einem Positionsregler ausgestattet sind.The hydraulic drive 5 is preferably a displacement measuring system 61 assigned that the position of the drive piston 8 or one with this motion-coupled component can capture to the electric motor 23 as a function of certain positions to be able to control as required. The position detection signals are fed to the setting means 24, which is expediently equipped with a position controller are.

Die beiden Hydraulikschaltungen 26, 27 sind beim Ausführungsbeispiel in das Gehäuse 6 des Hydraulikantriebes 5 integriert, wobei sie in Figur 1 nur strichpunktiert schematisch angedeutet sind, während ihr bevorzugter Aufbau im einzelnen in Figur 3 gezeigt ist.The two hydraulic circuits 26, 27 are in the embodiment integrated in the housing 6 of the hydraulic drive 5, where it is only schematically shown in dash-dotted lines in Figure 1 are indicated, while their preferred structure in detail is shown in Figure 3.

So enthalten beide Hydraulikschaltungen zweckmäßigerweise jeweils ein entsperrbares Rückschlagventil 36a, 36b, also ein Rückschlagventil, das sich unter bestimmten Umständen entsperren läßt, so dass es auch in der normalerweise gesperrten Durchflussrichtung einen Fluiddurchlass ermöglicht.Both hydraulic circuits expediently each contain an unlockable check valve 36a, 36b, that is Check valve that unlock under certain circumstances leaves so that it is also in the normally locked Flow direction allows a fluid passage.

Die entsperrbaren Rückschlagventile 36a, 36b sind so in die jeweilige Hydraulikschaltung 26, 27 eingegliedert, dass sie normalerweise eine Fluidströmung von der Hydraulikpumpe 22 zur jeweils angeschlossenen Arbeitskammer 17, 18 zulassen und in Gegenrichtung verhindern. Das entsperrbare Rückschlagventil 36a, 36b einer jeweiligen Hydraulikschaltung 26, 27 steht allerdings über einen in Figur 3 gestrichelt angedeuteten Entsperrkanal 37a, 37b mit demjenigen Kanalabschnitt der jeweils anderen Hydraulikschaltung 27, 26 in Fluidverbindung, der sich zwischen der Hydraulikpumpe 22 und dem dortigen entsperrbaren Rückschlagventil befindet. Auf diese Weise wird in einer jeweiligen Hydraulikschaltung 26, 27 der von der Hydraulikpumpe aufrecht erhaltenden Druck abgegriffen und dem in der anderen Hydraulikschaltung platzierten entsperrbaren Rückschlagventil als Entsperrsignal zugeleitet. Wird also die Hydraulikpumpe 22 beispielsweise so betrieben, dass in der ersten Hydraulikschaltung 26 ein Druckaufbau stattfindet und durch das sich dabei öffnende zugeordnete entsperrbare Rückschlagventil 36a ein Einspeisen von Hydraulikfluid in die erste Arbeitskammer 17 erfolgt, bewirkt der aufgebaute Druck gleichzeitig eine Entsperren und Öffnen des entsperrbaren Rückschlagventils 36b der zweiten Hydraulikschaltung 27, so dass aus der zweiten Arbeitskammer 18 verdrängtes Hydraulikmedium zur Hydraulikpumpe 22 zurückströmen kann. Der entsprechende Ablauf ergibt sich bei umgekehrter Förderrichtung der Hydraulikpumpe 22.The unlockable check valves 36a, 36b are thus in the respective hydraulic circuit 26, 27 incorporated that they typically fluid flow from hydraulic pump 22 to the connected working chamber 17, 18 and prevent in the opposite direction. The unlockable check valve 36a, 36b of a respective hydraulic circuit 26, 27 however via a dashed line in FIG Unlocking channel 37a, 37b with that channel section of each another hydraulic circuit 27, 26 in fluid communication, which can be unlocked between the hydraulic pump 22 and the one there Check valve is located. This way, in a respective hydraulic circuit 26, 27 of the hydraulic pump maintaining pressure tapped and the in of the other hydraulic circuit placed unlockable Check valve supplied as an unlock signal. So will that Hydraulic pump 22 operated, for example, that in the first hydraulic circuit 26, a pressure build-up takes place and through the associated releasable check valve that opens 36a feeding hydraulic fluid into the first working chamber 17 takes place, causes the pressure built up simultaneously unlocking and opening the unlockable Check valve 36b of the second hydraulic circuit 27, see above that hydraulic medium displaced from the second working chamber 18 can flow back to the hydraulic pump 22. The corresponding one The process results when the conveying direction is reversed Hydraulic pump 22.

Durch die entsperrbaren Rückschlagventile 36a, 36b ergibt sich der Vorteil, dass die Abtriebseinheit 13 bei deaktivierter Hydraulikpumpe 22 in ihrer momentanen Position festgehalten wird, weil das in den Arbeitskammern 17, 18 und in den sich daran anschließend bis hin zu den entsperrbaren Rückschlagventilen 36a und 36b in den Hydraulikschaltungen 26, 27 befindliche Fluid fest eingesperrt ist. Zum Halten einer bestimmten Position der Abtriebseinheit 13 wird somit keine Energie benötigt. By the 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 that in the working chambers 17, 18 and in the then go all the way to the unlockable check valves 36a and 36b in the hydraulic circuits 26, 27 fluid is firmly locked. To hold a specific one Position of the output unit 13 is therefore not Energy needed.

Die Realisierung eines weiteren Ausstattungsmerkmals der Antriebsvorrichtung 2 empfiehlt sich insbesondere bei Anwendungsfällen, die ein sehr dynamisches Bewegungsverhalten der Abtriebseinheit 13 erfordern, also abwechselnd hohe Beschleunigungen bzw. Geschwindigkeiten und starkes Abbremsen. Dieses Ausstattungsmerkmal besteht in einem zweckmäßigerweise in jede Hydraulikschaltung 26, 27 integrierten Vorspannventil 38a, 38b, das die Fluidverbindung von der zugeordneten Arbeitskammer 17, 18 hin zur Hydraulikpumpe 22 nur freigibt, wenn und solange sich in der momentan ausströmseitigen Arbeitskammer ein vorbestimmter Mindestdruck aufgebaut hat, der als Öffnungsdruck bezeichnet sei. Dieser Öffnungsdruck bewegt sich typischerweise im Bereich zwischen 10% und 90% und dabei vorzugsweise in einer Größenordnung zwischen 30% und 50% des von der Hydraulikpumpe 22 maximal erzeugbaren Betriebsdruckes. Beim Ausführungsbeispiel, bei dem der Arbeitsbereich der Hydraulikpumpe 22 zwischen 24 und 100 bar liegt, sind die beiden Vorspannventile 38a, 38b auf einen Öffnungsdruck von etwa 50 bar ausgelegt.The realization of a further equipment feature of the drive device 2 is particularly recommended for use cases which has a very dynamic movement behavior Output unit 13 require alternating high accelerations or speeds and heavy braking. This Equipment features in one suitably in each Hydraulic circuit 26, 27 integrated preload valve 38a, 38b, the fluid connection from the associated working chamber 17, 18 only releases to the hydraulic pump 22 if and as long as it is in the working chamber currently on the outlet side has built up a predetermined minimum pressure, the opening pressure be designated. This opening pressure is moving typically in the range between 10% and 90% and preferably in a range between 30% and 50% of that of the hydraulic pump 22 maximum operating pressure that can be generated. In the embodiment in which the working range of the hydraulic pump 22 are between 24 and 100 bar, are the two Preload valves 38a, 38b to an opening pressure of approximately 50 designed for bar.

Die auch als Druckbegrenzungsventile bezeichenbaren, druckabhängig öffnenden Vorspannventile 38a, 38b bewirken, dass der Abtriebseinheit 13 zusätzlich zu der eigentlich zu bewegenden Last eine Bremslast auferlegt wird, die es erst durch entsprechende Druckerzeugung der Hydraulikpumpe 22 zu überwinden gilt, um die Abtriebseinheit 13 in Bewegung zu versetzen. Vernachlässigt man einmal die durch das Kraftabgriffsteil 14 zu betätigende externe Last und die auftretende Reibung, so würde sich beim geschilderten Ausführungsbeispiel erst dann eine Bewegung der Abtriebseinheit 13 einstellen, wenn durch das eingespeiste Hydraulikmedium ein über 50 bar liegender Druck aufgebaut wird.The pressure-dependent valves, which can also be referred to as pressure relief valves opening bias valves 38a, 38b cause the Output unit 13 in addition to that actually to be moved Last a braking load is imposed, which it can only by appropriate To overcome pressure generation of the hydraulic pump 22 applies in order to set the output unit 13 in motion. If one neglects the force tapping part 14 external load to be actuated and the friction that occurs, so would then only in the described embodiment set a movement of the output unit 13 when by the hydraulic medium fed is over 50 bar Pressure is built up.

Wird die Abtriebseinheit 13 durch entsprechenden Druckaufbau mit hoher Geschwindigkeit verlagert, so läßt sich der Abbremsvorgang durch Reduzieren der Pumpleistung sehr einfach beherrschen, weil der durch die Fluidvorspannung in der ausströmseitigen Arbeitskammer herrschende Öffnungsdruck eine als Bremskraft wirkende Gegenkraft zur Folge hat.The output unit 13 becomes by appropriate pressure build-up shifted at high speed, so the braking process very easy by reducing the pump power dominate because of the fluid bias in the outflow Working chamber prevailing opening pressure one counterforce acting as braking force.

Beim Ausführungsbeispiel enthalten die Vorspannventile jeweils ein bewegliches Absperrglied 42, das durch eine dem Öffnungsdruck entsprechende Federkraft in eine die Fluidverbindung normalerweise unterbrechende Schließstellung vorgespannt ist. Die Federkraft wird beispielsweise durch eine mechanische Federeinrichtung 43 und/oder durch eine Gasfeder geliefert. Durch schematisch angedeutete Einstellmittel 44 läßt sich die Federvorspannung zweckmäßigerweise variabel einstellen, um den Öffnungsdruck zu beeinflussen und dementsprechend eine Anpassung an den momentanen Einsatzfall der Antriebsvorrichtung 2 zu ermöglichen.In the embodiment, the bias valves each contain a movable shut-off member 42, which by a Opening pressure corresponding spring force into the fluid connection normally pre-tensioned closed position is. The spring force is, for example, by a mechanical Spring device 43 and / or by a gas spring delivered. By means of schematically indicated setting means 44 the spring preload can expediently be variable adjust to influence the opening pressure and accordingly an adaptation to the current application of the To enable drive device 2.

Das Absperrglied 42 wird vom Hydraulikfluid der aüsströmseitigen Arbeitskammer entgegen der Federkraft im Öffnungssinne beaufschlagt und verlagert das Absperrglied in die Offenstellung, wenn die aus dem Öffnungsdruck resultierende Stellkraft größer ist als die Federkraft. Die Auslegung ist dabei zweckmäßigerweise so getroffen, dass ein digitales Schaltverhalten vorliegt und das Vorspannventil schlagartig in die maximale Offenstellung umschaltet. The shutoff member 42 is the hydraulic fluid on the outflow side Working chamber against the spring force in the opening direction applies and shifts the shut-off element to the open position, if the actuating force resulting from the opening pressure is greater than the spring force. The interpretation is expedient taken so that a digital switching behavior is present and the preload valve suddenly reaches its maximum Open position switches.

Es versteht sich, dass auch lediglich eine der Hydraulikschaltungen mit einem Vorspannventil ausgestattet sein kann. Dies insbesondere dann, wenn nur in einer Bewegungsrichtung dynamische Bewegungen der geschilderten Art auftreten.It goes without saying that only one of the hydraulic circuits can be equipped with a preload valve. This is especially true if only in one direction of movement dynamic movements of the type described occur.

Da die Vorspannventile 38a, 38b in der betreffenden Hydraulikschaltung 26, 27 eine Fluidströmung von der Hydraulikpumpe 22 zum Hydraulikantrieb 5 nicht zulassen, ist ihnen jeweils ein Rückschlagventil 45a, 45b parallel geschaltet, das in der genannten Richtung eine Fluidströmung zulässt und in Gegenrichtung, hin zur Hydraulikpumpe 22, absperrt.Since the bias valves 38a, 38b in the hydraulic circuit in question 26, 27 a fluid flow from the hydraulic pump 22 to the hydraulic drive 5 is not allowed a check valve 45a, 45b connected in parallel, which in the allows fluid flow and in the opposite direction, towards the hydraulic pump 22, shut off.

Innerhalb einer jeweiligen Hydraulikschaltung 26, 27 ist das entsperrbare Rückschlagventil 36a, 36b mit den parallel geschalteten Vorspann- und Rückschlagventilen 38a, 45a; 38b, 45b in Reihe geschaltet. Dabei befindet sich das Vorspannventil 38a, 38b zweckmäßigerweise in demjenigen Kanalabschnitt, der sich zwischen dem entsperrbaren Rückschlagventil 36a, 36b und dem Hydraulikantrieb 5 erstreckt.This is within a respective hydraulic circuit 26, 27 unlockable check valve 36a, 36b with the parallel connected Bias and check valves 38a, 45a; 38b, 45b connected in series. The preload valve is located here 38a, 38b expediently in that channel section, which is between the unlockable check valve 36a, 36b and the hydraulic drive 5 extends.

Wie eingangs schon erwähnt, sind der Hydraulikantrieb 5, die Hydraulikpumpe 22, die Hydraulikschaltungen 26, 27, der Elektromotor 23 und das gegebenenfalls vorhandene Hydraulikfluid-Ausgleichsbehältnis 32 zu der Antriebseinheit 3 zusammengefasst. Dabei können die rückseitig an das Gehäuse 6 angesetzten Komponenten durch ein am Gehäuse 6 fixiertes Schutzgehäuse 46 abgedeckt sein, das vor Eindringen von Verunreinigungen und Feuchtigkeit abschirmt. As already mentioned at the beginning, the hydraulic drive 5 are the Hydraulic pump 22, the hydraulic circuits 26, 27, the Electric motor 23 and the hydraulic fluid reservoir, if any 32 combined to form the drive unit 3. The back of the housing 6 attached components by a fixed to the housing 6 Protective housing 46 must be covered, which prevents the ingress of contaminants and shields moisture.

Es wäre auch möglich, den Hydraulikantrieb 5, den Ausgleichs-bzw. Vorratsbehälter 32, die Hydraulikpumpe 22, den Elektromotor 23 mit Einstellmitteln 24, sowie die hydraulischen Schaltungen 26, 27 in ein gemeinsames Gehäuse zu integrieren.It would also be possible to use the hydraulic drive 5, the compensating or. Reservoir 32, the hydraulic pump 22, the electric motor 23 with adjusting means 24, as well as the hydraulic Integrate circuits 26, 27 into a common housing.

Die Antriebsvorrichtung 2 läßt sich prinzipiell zu beliebigen Antriebszwecken einsetzen, wobei auch unterschiedliche Bauarten des Hydraulikantriebes 5 denkbar wären, beispielsweise auch kolbenstangenlose Ausführungsformen. Besonders vorteilhaft gestaltet sich der Einsatz der Antriebsvorrichtung 2 in einer zu einer Antriebseinheit 3 zusammengefassten Bauform in Verbindung mit einer Spannvorrichtung 1, wobei an die vordere Stirnseite 15 des Gehäuses 6 die oben erwähnte Spanneinheit 4 angesetzt ist. Letztere kann wie abgebildet einen an das Gehäuse 6 angeflanschten Lagerungskopf 47 enthalten, in den das aus dem Gehäuse 6 herausragende Ende der Abtriebseinheit 13 eintaucht und der einen schwenkbeweglichen Spannarm 48 trägt. Dabei sind die Kraftabgriffsmittel 16 der Abtriebseinheit 13 über einen Kniehebelmechanismus 49 derart mit dem Spannarm 48 bewegungsgekoppelt, dass aus der Linearbewegung der Abtriebseinheit 13 eine Dreh- bzw. Schwenkbewegung des Spannarmes 48 abgeleitet wird. Dieser verfügt beim Ausführungsbeispiel über einen drehfest verbundenen Schwenkhebel 50, an dem an einer zur Schwenkachse 52 des Spannarmes 48 beabstandeten Lagerstelle 53 ein laschenartiges Zwischenglied 54 angelenkt ist, das über eine weitere Lagerstelle 55 mit den Kraftabgriffsmitteln 16 gelenkig gekoppelt ist. The drive device 2 can in principle be any Use drive purposes, with different types of the hydraulic drive 5 would be conceivable, for example also rodless designs. Particularly advantageous is the use of the drive device 2 in a design combined into a drive unit 3 in Connection with a tensioning device 1, being on the front Face 15 of the housing 6, the clamping unit 4 mentioned above is scheduled. The latter can be attached to the housing as shown 6 flanged bearing head 47 included, in which the end of the output unit 13 protruding from the housing 6 immersed and which carries a pivotable clamping arm 48. The force tapping means 16 are the output unit 13 via a toggle lever mechanism 49 with the tension arm 48 motion-coupled that from the linear movement of the output unit 13 a rotating or swiveling movement of the clamping arm 48 is derived. This has in the embodiment a rotatably connected pivot lever 50, on which at a to the pivot axis 52 of the clamping arm 48 spaced bearing 53 a tab-like intermediate member 54 is articulated, that via a further bearing 55 with the force tapping means 16 is articulated.

Um das Kraftabgriffsteil 14 und die diesem zugeordnete, im Bereich einer vorderen Abschlusswand 59 des Kolbenaufnahmeraums 7 platzierte Dichtung 58 vor zu starkem Verschleiß zu schützen, ist das Kraftabgriffsteil 14 mit seinem äußeren Endabschnitt an Führungsmitteln 56 längsverschiebbar geführt und zugleich in Querrichtung bezüglich der Schwenkachse 52 abgestützt. Die Führungsmittel 56 können beispielsweise von einer oder mehreren, insbesondere nutartig ausgebildeten Führungsbahnen gebildet sein.To the force tapping part 14 and the associated, in Area of a front end wall 59 of the piston receiving space 7 placed seal 58 against excessive wear protect, the force tapping part 14 is with its outer End section on guide means 56 guided longitudinally and at the same time in the transverse direction with respect to the pivot axis 52 supported. The guide means 56 can, for example, from one or more, in particular groove-like guideways be educated.

Durch Betätigung des Hydraulikantriebs 5 kann der Schwenkarm 48 gemäß Doppelpfeil 57 zu einer Schwenkbewegung um die Schwenkachse 52 veranlasst werden, um ihn wahlweise in einer Spannstellung oder einer Freigabestellung zu positionieren. In der Spannstellung kann er auf ein nicht näher dargestelltes Werkstück einwirken, um dieses so fest zu spannen, dass es bearbeitet werden kann. Die Spannvorrichtung 1 eignet sich besonders zum Zusammenspannen von zu verschweißenden Werkstücken.By actuating the hydraulic drive 5, the swivel arm 48 according to double arrow 57 for a pivoting movement around the Swivel axis 52 are caused to selectively in a To position the clamping position or a release position. In the clamping position, he can on a not shown Work in the workpiece in order to clamp it so tight that it can be edited. The tensioning device 1 is suitable especially for clamping workpieces to be welded.

Wie auch aus der Rückansicht der Figur 2 ersichtlich ist, ermöglicht die Antriebseinheit 3 eine besonders schmale Bauweise. Es ist insbesondere möglich, die Querschnittsabmessungen der Antriebseinheit 3 so zu wählen, dass sie gleich oder geringer sind als diejenigen, des Lagerungskopfes 47.As can also be seen from the rear view in FIG. 2, this is made possible the drive unit 3 has a particularly narrow design. It is possible in particular the cross-sectional dimensions to select the drive unit 3 so that it is equal to or less are those of the bearing head 47.

Da die Antriebsvorrichtung 2 weder servobetätigte Steuerventile bzw. Proportionalventile noch Drosselventile benötigt, sind an das verwendete Hydraulikmedium keine besonders hohen Qualitätsanforderungen gestellt, was die zur Aufbereitung notwendigen Maßnahmen auf ein Minimum reduziert. Häufiges Auswechseln des Hydraulikmediums und Reinigen von Filtereinrichtungen erübrigt sich. Die Bewegungsrichtung der Abtriebseinheit 13 wird allein durch die Drehrichtung des Gleichstrommotors vorgegeben, wie auch die Hubgeschwindigkeit der Abtriebseinheit 13 eine Funktion der Geschwindigkeit des Gleichstrommotors bzw. der Pumpendrehzahl ist. Die einzige Variable während des Betriebes der Antriebsvorrichtung 2 ist beim Ausführungsbeispiel der Betriebszustand der Hydraulikpumpe bzw. deren Drehzahl.Since the drive device 2 neither servo-operated control valves or proportional valves still require throttle valves, are not particularly high in the hydraulic medium used Quality requirements, what the preparation necessary measures reduced to a minimum. Frequent Exchange of the hydraulic medium and cleaning of filter devices is unnecessary. The direction of movement of the output unit 13 is determined solely by the direction of rotation of the DC motor specified, as well as the lifting speed of the Output unit 13 a function of the speed of the DC motor or the pump speed is. The only Variable during the operation of the drive device 2 is in the embodiment, the operating state of the hydraulic pump or their speed.

Zum Ausführungsbeispiel kann nochmals zusammengefasst werden, dass es sich vorzugsweise um eine Antriebsvorrichtung mit einem durch ein hydraulisches Medium betätigbaren Hydraulikantrieb 5 handelt, dem eine Hydraulikpumpe 22 zur Zufuhr des hydraulischen Mediums zugeordnet ist. Der Druckaufbau im aktivierten Hydraulikantrieb 5 wird durch einstellbare Druckbegrenzungsventile (Vorspannventile 38a, 38b), die druckabhängig öffnend ausgebildet sind, sowie zu diesen parallelgeschaltete Rückschlagventile 45a, 45b, gesteuert. Die Geschwindigkeit des Antriebskolbens 8 des aktivierten Hydraulikantriebes 5 wird ausschließlich vom Volumenstrom des hydraulischen Mediums in den hydraulischen Schaltungen 26, 27 bestimmt.The embodiment can be summarized again that it is preferably a drive device with a hydraulic drive operated by a hydraulic medium 5, which is a hydraulic pump 22 for supplying the hydraulic medium is assigned. The pressure build-up in the activated Hydraulic drive 5 is through adjustable pressure relief valves (Preload valves 38a, 38b), which are pressure-dependent are designed to be opening, as well as parallel to these Check valves 45a, 45b controlled. The speed of the drive piston 8 of the activated hydraulic drive 5 is determined exclusively by the volume flow of the hydraulic Medium in the hydraulic circuits 26, 27 certainly.

Claims (26)

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.Drive device, with a closed hydraulic circuit, a hydraulic drive that can be actuated by hydraulic medium (5) and the supply and discharge of the hydraulic Medium causing the hydraulic drive (5) Hydraulic pump (22) contains, wherein for actuating the Hydraulic pump (22) an electric motor (23) is provided and the activation of the hydraulic drive (5) by the operating state the hydraulic pump (22) is determined. Antriebsvorrichtung nach Anspruch 1, gekennzeichnet durch einen allein in Abhängigkeit von der Drehzahl der Hydraulikpumpe (22) erfolgenden Druckaufbau unterschiedlicher Betätigungsdrücke im Hydraulikantrieb (5).Drive device according to claim 1, characterized by a pressure build-up in the hydraulic drive (5) which occurs solely as a function of the speed of the hydraulic pump (22). Antriebsvorrichtung nach Anspruch 1 oder 2, gekennzeichnet durch Einstellmittel (24) zur variablen Vorgabe der die Pumpendrehzahl der Hydraulikpumpe (22) bestimmenden Motordrehzahl des Elektromotors (23).Drive device according to claim 1 or 2, characterized by setting means (24) for variably specifying the motor speed of the electric motor (23) which determines the pump speed of the hydraulic pump (22). Antriebsvorrichtung nach Anspruch 3, dadurch gekennzeichnet, dass durch die Einstellmittel (24) Drehzahlrampen erzeugbar sind, die eine gleichförmige Antriebsbewegung des Hydraulikantriebes (5) hervorrufen.Drive device according to claim 3, characterized in that speed ramps can be generated by the setting means (24), which cause a uniform drive movement of the hydraulic drive (5). 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.Drive device according to claim 3 or 4, characterized in that the hydraulic drive (5) is assigned a position measuring system, the signals of which are fed to the setting means (24), which in this case expediently contain a position controller. Antriebsvorrichtung nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass der Elektromotor (23) als drehzahlgesteuerter oder drehzahlgeregelter Antriebsmotor ausgebildet ist.Drive device according to one of claims 1 to 5, characterized in that the electric motor (23) is designed as a speed-controlled or speed-controlled drive motor. Antriebsvorrichtung nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass die Drehzahl der Hydraulikpumpe (22) die Bewegungsgeschwindigkeit des Antriebskolbens (8) des Hydraulikantriebes bestimmt.Drive device according to one of claims 1 to 6, characterized in that the speed of the hydraulic pump (22) determines the speed of movement of the drive piston (8) of the hydraulic drive. Antriebsvorrichtung nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, dass die Hydraulikpumpe als reversierbare Volumenstrompumpe ausgebildet ist.Drive device according to one of claims 1 to 7, characterized in that the hydraulic pump is designed as a reversible volume flow pump. Antriebsvorrichtung nach einem der Ansprüche 1 bis 8, dadurch gekennzeichnet, dass 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.Drive device according to one of Claims 1 to 8, characterized in that the hydraulic drive (5) has at least one drive piston (8) which is motion-coupled to a force-tapping part (14) and which divides two working chambers (17, 18) from one another in a fluid-tight manner, both of which are each via one Hydraulic circuit (26, 27) are connected to the hydraulic pump (22), the feeding of hydraulic fluid into one working chamber (17, 18) being accompanied by the simultaneous outflow of hydraulic fluid from the other working chamber (18, 17). Antriebsvorrichtung nach Anspruch 9, dadurch gekennzeichnet, dass 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.Drive device according to claim 9, characterized in that the hydraulic pump (22) can be driven either for a left-hand or a right-hand rotary movement in order to selectively feed hydraulic medium into one or the other of the two working chambers (17, 18) and accordingly the direction of movement of the drive piston (8 ) to specify. Antriebsvorrichtung nach Anspruch 9 oder 10, 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.Drive device according to claim 9 or 10, characterized in that both hydraulic circuits (26, 27) contain an unlockable check valve (36a, 36b) which normally allows fluid flow from the hydraulic pump (22) to the hydraulic drive (5) and prevents it in the opposite direction, whereby each check valve (36a, 36b) can be unlocked by the pressure maintained in the respective other hydraulic circuit by the hydraulic pump (22) in order to allow fluid flow from the hydraulic drive (5) back to the hydraulic pump (22). Antriebsvorrichtung nach einem der Ansprüche 9 bis 11, 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. Drive device according to one of claims 9 to 11, characterized in that at least one hydraulic circuit (26, 27) contains a biasing valve (38a, 38b) which only releases the fluid connection from the relevant working chamber (17, 18) to the hydraulic pump (22) if and as long as a predetermined opening pressure has built up in the outflow-side working chamber. Antriebsvorrichtung nach Anspruch 12, 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.Drive device according to claim 12, characterized in that the design is such that the opening pressure is in the range between 10% and 90% and preferably in the range between 30% and 50% of the maximum operating pressure that can be generated by the hydraulic pump (22). Antriebsvorrichtung nach Anspruch 12 oder 13, gekennzeichnet durch Einstellmittel (44) zur veränderlichen Vorgabe des Öffnungsdruckes.Drive device according to claim 12 or 13, characterized by adjusting means (44) for variably specifying the opening pressure. Antriebsvorrichtung nach einem der Ansprüche 12 bis 14, 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 ausströmseitigen Arbeitskammer entgegen der Federkraft im Öffnungssinne beaufschlagt wird.Drive device according to one of claims 12 to 14, characterized in that the biasing valve (38a, 38b) has a movable shut-off member (42) which is biased by a spring force corresponding to the opening pressure into a closed position interrupting the fluid connection and which is from the hydraulic fluid of the outflow-side working chamber is applied against the spring force in the opening direction. Antriebsvorrichtung nach einem der Ansprüche 12 bis 15, dadurch gekennzeichnet, dass jede Hydraulikschaltung (26, 27) ein Vorspannventil (36a, 36b) enthält.Drive device according to one of claims 12 to 15, characterized in that each hydraulic circuit (26, 27) contains a biasing valve (36a, 36b). Antriebsvorrichtung nach einem der Ansprüche 12 bis 16 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. Drive device according to one of claims 12 to 16 in connection with claim 11, characterized in that in a relevant hydraulic circuit (26, 27) the unlockable check valve (36a, 36b) and the biasing valve (38a, 38b) are connected in series. Antriebsvorrichtung nach einem der Ansprüche 12 bis 17, dadurch gekennzeichnet, dass jedem Vorspannventil (38a, 38b) ein in Richtung zum Hydraulikantrieb (5) öffnendes und in Gegenrichtung sperrendes Rückschlagventil (45a, 45b) parallel geschaltet ist.Drive device according to one of claims 12 to 17, characterized in that each preload valve (38a, 38b) is connected in parallel with a non-return valve (45a, 45b) opening in the direction of the hydraulic drive (5) and blocking in the opposite direction. Antriebsvorrichtung nach einem der Ansprüche 9 bis 18, dadurch gekennzeichnet, dass jede Hydraulikschaltung (26, 27) mit einem Hydraulikfluid-Ausgleichsbehältnis (33) verbunden ist.Drive device according to one of claims 9 to 18, characterized in that each hydraulic circuit (26, 27) is connected to a hydraulic fluid compensation container (33). Antriebsvorrichtung nach einem der Ansprüche 1 bis 19, dadurch gekennzeichnet, dass zumindest der Hydraulikantrieb (5), die Hydraulikpumpe (22), die gegebenenfalls vorhandene Hydraulikschaltungen (26, 27) und der Elektromotor (23) zu einer Antriebseinheit (3) zusammengefasst sind.Drive device according to one of claims 1 to 19, characterized in that at least the hydraulic drive (5), the hydraulic pump (22), any hydraulic circuits (26, 27) and the electric motor (23) are combined to form a drive unit (3). Antriebsvorrichtung nach Anspruch 20, dadurch gekennzeichnet, dass die Antriebseinheit (3) zur Energieeinspeisung ausschließlich über elektrische Anschlussmittel (35) verfügt.Drive device according to claim 20, characterized in that the drive unit (3) has only electrical connection means (35) for feeding in energy. Antriebsvorrichtung nach einem der Ansprüche 1 bis 21, 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.Drive device according to one of claims 1 to 21, as part of a toggle clamp device in particular trained clamping device (1), wherein the force tapping part (14) of the hydraulic drive (5) with a pivotable clamping arm (48) is in drive connection. Antriebsvorrichtung nach Anspruch 22 in Verbindung mit Anspruch 20 oder 21, dadurch gekennzeichnet, dass stirnseitig an der Antriebseinheit (3) ein den Schwenkarm (48) tragender Lagerungskopf (47) angeordnet ist.Drive device according to claim 22 in connection with claim 20 or 21, characterized in that a bearing head (47) carrying the swivel arm (48) is arranged on the end face of the drive unit (3). Antriebsvorrichtung nach Anspruch 23, dadurch gekennzeichnet, dass die Querschnittsabmessungen der Antriebseinheit (3) gleich oder geringer sind als diejenigen des Lagerungskopfes (47).Drive device according to claim 23, characterized in that the cross-sectional dimensions of the drive unit (3) are equal to or less than those of the bearing head (47). Antriebsvorrichtung nach einem der Ansprüche 1 bis 24, dadurch gekennzeichnet, dass der Hydraulikantrieb (5) ein Drehantrieb ist.Drive device according to one of claims 1 to 24, characterized in that the hydraulic drive (5) is a rotary drive. Antriebsvorrichtung nach einem der Ansprüche 1 bis 25, dadurch gekennzeichnet, dass der Hydraulikantrieb (5) ein Linearantrieb ist.Drive device according to one of claims 1 to 25, characterized in that the hydraulic drive (5) is a linear drive.
EP01105621A 2000-03-17 2001-03-07 Transmission installation Expired - Lifetime EP1134431B1 (en)

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Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1355030A2 (en) * 2002-04-16 2003-10-22 DORMA GmbH + Co. KG Hydraulic drive for a turning sash
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EP2503086A3 (en) * 2011-03-22 2014-07-16 Reinhold Schulte Drive circuit sub-assembly for a vehicle door
DE202014006621U1 (en) * 2014-08-19 2015-11-20 Deutsches Zentrum für Luft- und Raumfahrt e.V. actuator system
CN105849421A (en) * 2013-11-14 2016-08-10 伊顿公司 Pilot control mechanism for boom bounce reduction
CN109366385A (en) * 2018-10-18 2019-02-22 九江精密测试技术研究所 A kind of electro-hydraulic five axis composite turntable of combination drive of big unbalance loading shafting
US11028861B2 (en) 2013-05-31 2021-06-08 Eaton Intelligent Power Limited Hydraulic system and method for reducing boom bounce with counter-balance protection
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Families Citing this family (43)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2831226B1 (en) * 2001-10-24 2005-09-23 Snecma Moteurs AUTONOMOUS ELECTROHYDRAULIC ACTUATOR
US7111835B2 (en) 2002-10-10 2006-09-26 Smc Kabushiki Kaisha Clamp apparatus
FR2845628B1 (en) * 2002-10-10 2006-02-24 Smc Kk CLAMPING DEVICE
GB0329243D0 (en) * 2003-12-17 2004-01-21 Thales Plc Apparatus and methods for actuation
DE102004029409A1 (en) * 2004-06-18 2006-01-05 Jungheinrich Ag Pressure-medium-actuated actuating device, in particular for a vehicle steering device
DE102004061559A1 (en) 2004-12-21 2006-06-29 Brueninghaus Hydromatik Gmbh Hydraulic drive
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 (en) * 2006-03-07 2008-10-08 太原理工大学 Closed electrohydraulic controlling system
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
EP2126372B1 (en) * 2007-03-05 2012-02-29 Contour Aerospace Limited Hydraulic actuator
GB2454908B (en) * 2007-11-23 2012-04-11 Schlumberger Holdings Hydraulic manifold pump
DE102010020132A1 (en) * 2010-05-11 2011-11-17 Hydac Electronic Gmbh Drive system with at least one hydraulic actuator
PL225323B1 (en) * 2010-08-20 2017-03-31 Nowak Wiesław Przedsiębiorstwo Innowacyjno Wdrożeniowo Handlowe Telescopic servomotor
CN102140807B (en) * 2011-01-11 2012-05-23 徐州徐工挖掘机械有限公司 Method for improving excavating control characteristic and leveling operation characteristic of excavator
CN102200151B (en) * 2011-06-14 2013-10-30 赵铁栓 Method for controlling hydraulic pump to output constant flow according to flow control device
CN102588358B (en) * 2012-02-20 2015-01-21 北京理工大学 High-performance energy saving type electro-hydraulic servo control oil line
US10138908B2 (en) 2013-08-19 2018-11-27 Purdue Research Foundation Miniature high pressure pump and electrical hydraulic actuation system
WO2015031821A1 (en) 2013-08-30 2015-03-05 Eaton Corporation Control method and system for using a pair of independent hydraulic metering valves to reduce boom oscillations
US10316929B2 (en) 2013-11-14 2019-06-11 Eaton Intelligent Power Limited Control strategy for reducing boom oscillation
EP3111092B1 (en) 2014-02-28 2021-04-21 Project Phoenix LLC Pump integrated with two independently driven prime movers
US10465721B2 (en) 2014-03-25 2019-11-05 Project Phoenix, LLC System to pump fluid and control thereof
US10294936B2 (en) 2014-04-22 2019-05-21 Project Phoenix, Llc. Fluid delivery system with a shaft having a through-passage
US10544861B2 (en) 2014-06-02 2020-01-28 Project Phoenix, LLC Hydrostatic transmission assembly and system
EP3957853A1 (en) 2014-06-02 2022-02-23 Project Phoenix LLC Linear actuator assembly and system
EP3169858B1 (en) 2014-07-15 2021-02-17 Eaton Intelligent Power Limited Methods and apparatus to enable boom bounce reduction and prevent un-commanded motion in hydraulic systems
SG11201700472XA (en) 2014-07-22 2017-02-27 Project Phoenix Llc External gear pump integrated with two independently driven prime movers
US10072676B2 (en) 2014-09-23 2018-09-11 Project Phoenix, LLC System to pump fluid and control thereof
EP3204647B1 (en) 2014-10-06 2021-05-26 Project Phoenix LLC Linear actuator assembly and system
US11137000B2 (en) * 2014-10-10 2021-10-05 MEA Inc. Self-contained energy efficient hydraulic actuator system
WO2016064569A1 (en) 2014-10-20 2016-04-28 Afshari Thomas Hydrostatic transmission assembly and system
US20160221171A1 (en) * 2015-02-02 2016-08-04 Caterpillar Inc. Hydraulic hammer having dual valve acceleration control system
EP3109488B1 (en) * 2015-06-25 2017-12-13 MOOG GmbH Safe-to-operate hydraulic drive
TWI712744B (en) 2015-09-02 2020-12-11 美商鳳凰計劃股份有限公司 System to pump fluid and control thereof
EP3779122A1 (en) 2015-09-02 2021-02-17 Project Phoenix LLC System to pump fluid and control thereof
US10871174B2 (en) 2015-10-23 2020-12-22 Aol Prime mover system and methods utilizing balanced flow within bi-directional power units
DE102016109103A1 (en) 2016-05-18 2017-11-23 Hoerbiger Automatisierungstechnik Holding Gmbh Electrohydraulic linear actuator
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
CN112901474B (en) * 2019-11-19 2023-03-31 科颉工业股份有限公司 Piston pump and clamping device with same
TWI717112B (en) * 2019-11-19 2021-01-21 科頡工業股份有限公司 Piston pump and clamping device with the piston pump
US11441583B2 (en) * 2020-07-15 2022-09-13 Coretrax Americas Limited Hydraulic thruster
DE102022204211A1 (en) * 2022-04-29 2023-11-02 Robert Bosch Gesellschaft mit beschränkter Haftung Method for operating a hydraulic system with at least one hydraulically actuated actuator

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1776139A1 (en) * 1968-09-27 1971-09-30 Tullio Levrini Hydraulic drive device
DE2929442A1 (en) * 1979-07-20 1981-01-29 Elmeg Electrohydraulic servo with centrifugal pump - has elastic components separating hydraulic liq. from air
DE3637404A1 (en) * 1986-11-03 1987-11-26 Bornemann & Haller Kg ACTUATOR
US5125324A (en) * 1988-02-10 1992-06-30 Daia Industry Co. Ltd. Portable hydraulically operated device incorporating automatic drain valve
DE4137103A1 (en) * 1991-11-12 1993-05-13 Elmeg ELECTROHYDRAULIC DEVICE
DE4207764A1 (en) * 1992-03-11 1993-09-16 Hugo Junkers Werke Gmbh Hydraulic machine with interchangeable tools - comprises high pressure hydraulic pump driven by electric motor and coaxial working cylinder to drive tool and all contained in portable unit
DE4302889A1 (en) * 1993-02-02 1994-08-04 Emg Eltma Hebezeuge Oschersleb Electrohydraulic actuator in housing with deformable wall sections
DE19535691C1 (en) * 1995-09-26 1997-01-23 Rothenberger Werkzeuge Masch Hydraulically driven hand tool
JPH09170601A (en) * 1995-12-20 1997-06-30 Tokimec Inc Hydraulic closed circuit
FR2752446A1 (en) * 1996-08-13 1998-02-20 Thomson Csf OPTIMIZED CONTROL METHOD FOR AN ELECTROFLUIDIC ACTUATOR AND ACTUATOR USING THE SAME
DE29903281U1 (en) * 1999-02-24 1999-07-01 Festo AG & Co, 73734 Esslingen Toggle clamp device

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1916266A1 (en) * 1968-05-21 1970-10-08 Bbc Brown Boveri & Cie Electrohydraulic actuator
US4696163A (en) * 1983-03-28 1987-09-29 Rexa Corporation Control valve and hydraulic system employing same
DE3919823C3 (en) * 1989-06-14 1998-04-09 Mannesmann Ag Injection molding machine with hydraulic consumers
DE4335328A1 (en) * 1993-10-18 1995-04-20 Battenfeld Gmbh Hydraulic operating system for injection molding machines
DE19517582C2 (en) * 1995-05-05 1998-08-20 Mannesmann Ag Drive for the injection and plasticizing unit of a plastic injection molding machine
JP3668543B2 (en) * 1995-12-18 2005-07-06 株式会社トキメック Circuit pressure holding device in hydraulic closed circuit
DE19603012C1 (en) * 1996-01-18 1997-09-04 Mannesmann Ag Plasticizing and injection unit of a plastic injection molding machine
US6092290A (en) * 1996-12-24 2000-07-25 Rescue Technology, Inc. Rescue tool

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1776139A1 (en) * 1968-09-27 1971-09-30 Tullio Levrini Hydraulic drive device
DE2929442A1 (en) * 1979-07-20 1981-01-29 Elmeg Electrohydraulic servo with centrifugal pump - has elastic components separating hydraulic liq. from air
DE3637404A1 (en) * 1986-11-03 1987-11-26 Bornemann & Haller Kg ACTUATOR
US5125324A (en) * 1988-02-10 1992-06-30 Daia Industry Co. Ltd. Portable hydraulically operated device incorporating automatic drain valve
DE4137103A1 (en) * 1991-11-12 1993-05-13 Elmeg ELECTROHYDRAULIC DEVICE
DE4207764A1 (en) * 1992-03-11 1993-09-16 Hugo Junkers Werke Gmbh Hydraulic machine with interchangeable tools - comprises high pressure hydraulic pump driven by electric motor and coaxial working cylinder to drive tool and all contained in portable unit
DE4302889A1 (en) * 1993-02-02 1994-08-04 Emg Eltma Hebezeuge Oschersleb Electrohydraulic actuator in housing with deformable wall sections
DE19535691C1 (en) * 1995-09-26 1997-01-23 Rothenberger Werkzeuge Masch Hydraulically driven hand tool
JPH09170601A (en) * 1995-12-20 1997-06-30 Tokimec Inc Hydraulic closed circuit
FR2752446A1 (en) * 1996-08-13 1998-02-20 Thomson Csf OPTIMIZED CONTROL METHOD FOR AN ELECTROFLUIDIC ACTUATOR AND ACTUATOR USING THE SAME
DE29903281U1 (en) * 1999-02-24 1999-07-01 Festo AG & Co, 73734 Esslingen Toggle clamp device

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 1997, no. 10 31 October 1997 (1997-10-31) *

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1355030A2 (en) * 2002-04-16 2003-10-22 DORMA GmbH + Co. KG Hydraulic drive for a turning sash
EP1355030A3 (en) * 2002-04-16 2009-03-11 DORMA GmbH + Co. KG Hydraulic drive for a turning sash
EP2503086A3 (en) * 2011-03-22 2014-07-16 Reinhold Schulte Drive circuit sub-assembly for a vehicle door
US11028861B2 (en) 2013-05-31 2021-06-08 Eaton Intelligent Power Limited Hydraulic system and method for reducing boom bounce with counter-balance protection
CN103410808A (en) * 2013-07-17 2013-11-27 丽水中德石化设备有限公司 Intrinsic safety type fire-proof and explosion-proof electro-hydraulic actuator and control method thereof
CN103410808B (en) * 2013-07-17 2015-07-15 丽水中德石化设备有限公司 Intrinsic safety type fire-proof and explosion-proof electro-hydraulic actuator and control method thereof
CN105849421A (en) * 2013-11-14 2016-08-10 伊顿公司 Pilot control mechanism for boom bounce reduction
US10344783B2 (en) 2013-11-14 2019-07-09 Eaton Intelligent Power Limited Pilot control mechanism for boom bounce reduction
DE202014006621U1 (en) * 2014-08-19 2015-11-20 Deutsches Zentrum für Luft- und Raumfahrt e.V. actuator system
US11204048B2 (en) 2017-04-28 2021-12-21 Eaton Intelligent Power Limited System for damping mass-induced vibration in machines having hydraulically controlled booms or elongate members
US11209028B2 (en) 2017-04-28 2021-12-28 Eaton Intelligent Power Limited System with motion sensors for damping mass-induced vibration in machines
CN109366385A (en) * 2018-10-18 2019-02-22 九江精密测试技术研究所 A kind of electro-hydraulic five axis composite turntable of combination drive of big unbalance loading shafting

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DE50106158D1 (en) 2005-06-16
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US20010022083A1 (en) 2001-09-20
EP1134431B1 (en) 2005-05-11
DE10013194B4 (en) 2005-02-24
US6543223B2 (en) 2003-04-08

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