WO2006056256A2 - Unite hydraulique et procede pour mettre a disposition un fluide hydraulique sous pression - Google Patents

Unite hydraulique et procede pour mettre a disposition un fluide hydraulique sous pression Download PDF

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Publication number
WO2006056256A2
WO2006056256A2 PCT/EP2005/010208 EP2005010208W WO2006056256A2 WO 2006056256 A2 WO2006056256 A2 WO 2006056256A2 EP 2005010208 W EP2005010208 W EP 2005010208W WO 2006056256 A2 WO2006056256 A2 WO 2006056256A2
Authority
WO
WIPO (PCT)
Prior art keywords
hydraulic
pressure
hydraulic unit
hydraulic fluid
electric motor
Prior art date
Application number
PCT/EP2005/010208
Other languages
German (de)
English (en)
Other versions
WO2006056256A8 (fr
WO2006056256A3 (fr
Inventor
Gerd Hartrampf
Christian Böhner
Klaus Dehlke
Original Assignee
Richard Bergner Verbindungstechnik Gmbh & 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 Richard Bergner Verbindungstechnik Gmbh & Co Kg filed Critical Richard Bergner Verbindungstechnik Gmbh & Co Kg
Priority to PCT/EP2005/010208 priority Critical patent/WO2006056256A2/fr
Priority to DE112005002804.6T priority patent/DE112005002804B4/de
Publication of WO2006056256A2 publication Critical patent/WO2006056256A2/fr
Publication of WO2006056256A3 publication Critical patent/WO2006056256A3/fr
Priority to US11/804,853 priority patent/US20070286740A1/en
Publication of WO2006056256A8 publication Critical patent/WO2006056256A8/fr

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J15/00—Riveting
    • B21J15/10—Riveting machines
    • B21J15/14—Riveting machines specially adapted for riveting specific articles, e.g. brake lining machines
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J15/00—Riveting
    • B21J15/02—Riveting procedures
    • B21J15/04—Riveting hollow rivets mechanically
    • B21J15/043—Riveting hollow rivets mechanically by pulling a mandrel
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J15/00—Riveting
    • B21J15/10—Riveting machines
    • B21J15/14—Riveting machines specially adapted for riveting specific articles, e.g. brake lining machines
    • B21J15/142—Aerospace structures
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J15/00—Riveting
    • B21J15/10—Riveting machines
    • B21J15/30—Particular elements, e.g. supports; Suspension equipment specially adapted for portable riveters
    • B21J15/32—Devices for inserting or holding rivets in position with or without feeding arrangements
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25J—MANIPULATORS; CHAMBERS PROVIDED WITH MANIPULATION DEVICES
    • B25J15/00—Gripping heads and other end effectors
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25J—MANIPULATORS; CHAMBERS PROVIDED WITH MANIPULATION DEVICES
    • B25J9/00—Programme-controlled manipulators
    • B25J9/10—Programme-controlled manipulators characterised by positioning means for manipulator elements
    • B25J9/14—Programme-controlled manipulators characterised by positioning means for manipulator elements fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/16—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by adjusting the capacity of dead spaces of working chambers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/26—Supply reservoir or sump assemblies
    • F15B1/265—Supply reservoir or sump assemblies with pressurised main reservoir

Definitions

  • the invention relates to a hydraulic unit and a method for providing a pressurized hydraulic fluid.
  • Hydraulic power units are used in various technical fields.
  • the hydraulic unit is also used in a machining tool, which must perform an axial movement with high force in a machining operation.
  • a machining tool is, for example, a press or punch in which a hole is stamped out or a stamped element punched by means of an axially displaceable punch.
  • the hydraulic unit also serves, in particular in the area of riveting technology, for connection to a setting device for setting a rivet, in particular a blind rivet.
  • a setting device for setting a rivet in particular a blind rivet.
  • this is inserted into a bore of two components to be connected with its rivet sleeve in advance from one side until its setting head comes to rest on the upper component.
  • a rivet mandrel is arranged, which is pulled in the axial direction by means of the setting device.
  • the rivet sleeve deforms and forms a closing head, so that the components to be connected between the closing head and setting head are clamped.
  • a certain tensile force is exceeded, the mandrel breaks off and the setting operation of the blind rivet is completed.
  • the invention has for its object to specify a compact hydraulic unit, which can be used in particular in combination with an industrial robot.
  • the invention is further based on the object of specifying a method for providing a pressurized hydraulic fluid.
  • a hydraulic unit for providing a pressurized hydraulic fluid at an outlet of the unit, which is an electric motor and at least one operated via the electric motor and in particular Having trained as a piston pump pump to generate pressure.
  • a storage space with a variable compensation volume is provided, in which the hydraulic fluid is stored gas-free.
  • the invention is based on the consideration that due to the problem of the leadership of the hydraulic lines on the robot along an immediate arrangement of the hydraulic unit on the robot, in particular on the robot hand, so that no hydraulic lines is guided over a movable robot axis, is advantageous.
  • this raises the problem that in a conventional Hydraulikaggre ⁇ gat due to the acceleration air or gas would get into the hydraulic fluid, so that a secure and defined hydraulic actuation of a machining tool, such as a blind rivet setting head, would not be possible.
  • the hydraulic unit proposed here is therefore arranged, in particular, on machine parts which are accelerated during operation. These are, in particular, the robot hand of an industrial robot, crane or gripper devices, motor vehicles, in particular trucks, and, for example, fairground rides for amusement parks. In an industrial robot, accelerations of, for example, 20 times the gravitational acceleration and more may occur.
  • the mobile hydraulic unit is able to carry out such high accelerations without impairing its functionality.
  • the hydraulic fluid in the storage space on an overpressure over an ambient pressure.
  • This overpressure is preferably in the range of a few 10 5 Pa, in particular between 3 and 50 ⁇ 10 5 Pa.
  • a compensation wall of the storage space in the manner of a piston is arranged displaceably and sealed to a stationary housing wall of the storage space.
  • the preferred embodiment as a piston also has the advantage of a simple construction.
  • the pressure generating unit is therefore designed in the manner of a piston accumulator.
  • the compensation wall is designed, for example, as an elastic membrane.
  • the compensation wall can expediently be acted upon by a counterforce or a counterpressure.
  • a pressure chamber is provided on the outside facing away from the storage space, to which a pressure line can be connected.
  • the generation of the counterforce therefore takes place in particular in a pneumatic or hydraulic manner.
  • the advantage of a pneumatic or hydraulic pressure application lies in the simple controllability of the level of the backpressure.
  • the pressure unit for generating the counter-pressure is therefore designed in the manner of a media converter in the case of pneumatic pressure generation, ie converts pneumatic pressure into hydraulic pressure.
  • the printing unit is designed such that a pressure gain is achieved.
  • a safety spring is additionally provided in a preferred embodiment for generating the backpressure.
  • a securing spring is generally understood to mean an elastic element which exerts a fixed elastic restoring force.
  • a spring element in the actual sense for example a compression spring, is used in this case.
  • this is provided instead of the pressure chamber.
  • the electric motor and the pump are arranged in a housing of the unit, and the interior surrounded by the housing forms the storage space, ie is filled with hydraulic fluid.
  • the electric motor and the pump are therefore arranged in the hydraulic fluid, in particular hydraulic oil.
  • the housing is hermetically sealed to the outside. Due to this configuration, a separate Ausretesbe ⁇ container is not required. Furthermore, no supply lines from expansion tank to a suction side of the pump are required.
  • the housing is preferably closed by a particular frontal functional block, in which several hydraulic components are integrated.
  • hydraulic components are, for example, hydraulic lines and valves.
  • the functional block therefore forms a cover of the housing and thus of the unit. Due to the integration of the hydraulic components in the cover, no separate space requirement for these components is required and the aggregate as a whole can be constructed very compactly.
  • the functional block is designed to control and guide the hydraulic fluid provided at the outlet.
  • a multiplicity of lines and also hydraulic control elements, such as valves, are arranged in the functional block.
  • the function block is therefore used, for example, to block or release the hydraulic fluid generated and pressurized by the pump.
  • the pressure side of the pump is connected via a line to the function block. All other hydraulic components downstream of the pump on the pressure side are integrated in the function block.
  • the arrangement of all hydraulic functional elements within the functional block, the structure of the remaining Aggre ⁇ gats is kept relatively simple and robust.
  • At least two pumps are provided on the one hand to provide a low-pressure substream and on the other hand to provide a high-pressure substream of the hydraulic fluid. So there is a two-stage hydraulic unit provided. This has the advantage that, depending on the particular application, different pressure stages are provided with a low expenditure of energy. Thus, different printing requirements are operated in a simple manner energy-saving. Especially in a Blindnietsetzvorgang at the beginning of the setting process, no high pressure to be provided.
  • the at least two different pumps are actuated together by the electric motor. Therefore, a plurality of hydraulic partial flows of different pressures and / or different delivery rates are generated via the single and identical electric motor, so that the most different pressure requirements can be met with only one electric motor and thus very space-saving. par- This is particularly advantageous in the case of two-stage or multi-stage machining operations in which different pressure requirements are set within one work process. For example, long axial strokes must be performed at low pressure and short axial strokes at high pressure, such as in a blind rivet setting process.
  • the pumps are actuated together via an eccentric shaft of the electric motor and therefore angeord ⁇ net in an annular manner around the eccentric shaft.
  • the pumps are therefore operated directly without the interposition of a transmission from the electric motor.
  • a plurality of pumps for generating the low-pressure and multiple pumps for generating the high-pressure partial flow are expediently provided, preferably alternately one pump for the high-pressure partial flow and one for the low-pressure partial flow being adjacent to one another ,
  • a valve arrangement for controlling the at least two partial flows, which is designed such that in each case only a partial flow is provided at the outlet of the hydraulic unit.
  • the valve arrangement is in particular designed in such a way that, as a function of the current pressure requirement, automatic switching between the partial flows takes place.
  • valve arrangement is in this case integrated in particular in the function block.
  • the valve arrangement has a pressure switching valve which automatically switches off the low pressure partial flow when a presettable pressure of the hydraulic fluid provided at the outlet is exceeded.
  • valve arrangement is furthermore preferably designed such that in each case one of the partial flows can be switched without pressure. It is therefore especially provided that in operation in each case one of the partial flows is depressurized.
  • the electric motor therefore only needs one Partial pressure build up and therefore can be less powerful and compact forms kept ⁇ .
  • the electric motor is controllable and in particular adjustable.
  • the electric motor is in this case only in case of need, so if there is a pressure request, started.
  • the pressure is therefore generated energy-saving without a pressure accumulator only when needed.
  • the electric motor is preferably regulated to a constant speed.
  • This provides a constant flow of hydraulic fluid.
  • the electric motor is regulated to a constant torque, so that a certain pressure, for example, a limited maximum pressure is generated and maintained.
  • the torque control is particularly advantageous in the case of an O-way stroke, that is to say when, for example, during the setting process of a blind rivet, a setting or forming force must be maintained without or with virtually no movement of the blind rivet.
  • the electric motor is expediently designed, in particular, as a servomotor.
  • the object is further achieved according to the invention by a method for providing a pressurized hydraulic fluid according to claim 20.
  • the advantages and preferred embodiments stated with regard to the hydraulic unit are to be applied correspondingly to the method.
  • the hydraulic unit described here is characterized on the one hand by its mobility, that is to say the hydraulic unit can be moved and accelerated very quickly without impairing its functional capability and is therefore able to function, in particular, also independently of position.
  • the hydraulic unit is particularly suitable for being arranged on an industrial robot and is there, in particular, a part of an exchangeable robot hand.
  • the hydraulic unit described here is characterized on the other hand by its very compact design while generating very high pressures.
  • the hydraulic unit has an approximately cylindrical housing, which has a length of only about 30-40 cm with a diameter of about 12 cm.
  • the hydraulic unit is provided for providing, in particular, the two partial pressure streams, the low-pressure substream being provided, for example, for about 200 ⁇ 10 5 Pa and the high-pressure partial stream preferably for 500 ⁇ 10 5 Pa.
  • a mobile hydraulic unit is created, which allows two hydraulic streams with 100 to 300 bar and 300 to 700 bar pressure.
  • the total volume of Hydraulik ⁇ liquid within the hydraulic unit is in this case preferably only about 500 ml.
  • the hydraulic unit is therefore characterized by a high power density with low energy consumption. Since no pressure relief valves are provided and the hydraulic unit is operated in the shutdown, so only if there is actually a pressure requirement, only small energy losses occur and the necessary energy use is low. This allows the use of a ver ⁇ comparatively low-power and compact electric motor.
  • Fig. 3 is a view of the rear end side of the hydraulic unit and Fig. 4 is a hydraulic plan of the hydraulic unit.
  • the hydraulic unit 2 shown in FIGS. 1 to 3 has a generally cylindrical housing 4, the interior of which forms a storage space 5 for the hydraulic fluid and is hermetically sealed.
  • the housing 4 is closed on its left front side by a control or functional block 6 designed in the manner of a housing cover.
  • the hydraulic unit 2 has a compensation block 8, which closes the housing 4 at the rear end side.
  • a pressure generating block 10 is arranged between these two blocks 6,8 .
  • the individual housing components of the hydraulic unit 2 are - as shown in the figure - fastened together by screw.
  • each sealing elements 12 are provided so that a hermetic seal of the entire réelle ⁇ space 5 is achieved with respect to the environment.
  • the pressure generating block 10 is essentially formed by a lower oil electric motor 14 designed as an alternating current servomotor and a plurality of pumps 16 designed as piston pumps.
  • the electric motor 14 has a stator 14A with a stator winding and a rotor 14B with a permanent magnet.
  • an eccentric shaft 18 is provided at the end, whose axis is arranged offset radially to the rotor axis 20.
  • the pumps 16 which are arranged annularly around the eccentric shaft 18 are actuated alternately.
  • the piston of the respective piston pump 16 is actuated for sucking and discharging the hydraulic oil via the eccentric shaft 18.
  • a bearing 22 is arranged between the rotating in operation eccentric shaft 18 and the fixed pump 16.
  • Each of the pumps 16 is followed by a pressure line 24 on the pressure side, which leads to the function block 6.
  • the pressure line 24 is in this case formed by a channel incorporated into the housing wall.
  • the suction side of the pumps 16 is in each case connected to the inner space 5, in which the hydraulic oil is located.
  • a total of annularly arranged wherein alternately adjacent pumps 16 supply for the Erzeu ⁇ two different pressures are provided, namely a low pressure of approximately 200 x 10 -5 Pa, and a high pressure in the amount of about 500 x 10 ⁇ 5 Pa.
  • the trained as solid metal lid function block 6 has a thickness d, which is for example about 10% of the total length I of the hydraulic unit 2.
  • a plurality of channels for forming Hydrauliklei ⁇ lines 28 and holes 30 are introduced for the arrangement of hydraulic valves, so that the functional block forms a valve block.
  • the arrangement of the individual hydraulic lines 28 and of the bores 30 and of the valves results in particular also from the end view according to FIG. 2, from which the hydraulic lines 28 and the bores 30 are shown by dashed lines.
  • a plurality of bores 30 and thus hydraulic valves are provided.
  • a directional seat valve 32A and a pressure switching valve 32B can be seen in FIG.
  • a further refill or Nach ⁇ filling valve 32C is provided, via which the storage space 5 can be filled.
  • a vent valve 32 D is further arranged.
  • Another opening 34 which is open only when filling with the hydraulic fluid, is used to equalize the pressure during filling.
  • All hydraulic controls are therefore integrated in the function block 6.
  • the hydraulic oil provided at an output 36A, B (see Fig. 4) is controlled via the function block 6, that is, via the function block 6, the hydraulic pressure at the output 36A, B is controlled.
  • a hydraulic line can be connected directly at the outlet 36 and connected to a corresponding hydraulic input on a processing line.
  • Tool for example, a blind rivet setting tool 38 (see Fig. 4) connect.
  • the mode of operation of the functional block 6 and the meaning of the individual valves are in particular also given in the description of the hydraulic diagram according to FIG. 4.
  • the compensation block 8 comprises an annular or cylindrical housing wall formed by the housing 4, which forms a cylinder 40 which is open to the interior.
  • a piston 42 forming a balance wall is arranged with an accurate fit.
  • the piston 42 is sealed to the inner wall of the cylinder 40 by sealing elements 12 and arranged displaceably in the longitudinal direction relative to the cylinder 40.
  • the piston 42 is designed as a hollow piston, which, as seen in the cross-section of the cylinder 40 extends stepwise.
  • the cavity of the piston 42 forms a pressure chamber 44, which can be acted upon by a presettable pressure via a pneumatic connection 46 (see FIG.
  • the pressure chamber 54 is bounded on the back by a fixed end wall 48 of the housing.
  • a locking spring 50 designed as a compression spring is supported, which exerts a compressive force on the piston 42.
  • the illustrated embodiment is a pressure booster and media wall ler created.
  • the interior 5 is completely filled with a hydraulic fluid, in particular hydraulic oil, so that the electric motor 14 and with it the pumps 16 are mounted in the hydraulic oil.
  • a hydraulic fluid in particular hydraulic oil
  • the vent valve 32 D is a complete vent, so that the entire inner space 5 is free of gas and air.
  • the electric motor 14 is started as needed. That is, the hydraulic pressure is generated only when there is actually a need, so if the blind rivet is already introduced into the Blindnietloch and the setting process begins by pulling the rivet mandrel. It no pressure vessel is provided.
  • the eccentric shaft 18 is set in rotational motion, so that alternately and circumferentially the individual Pum ⁇ pen 16 are actuated, each promoting a predefined amount of hydraulic fluid in the pressure line 24 and thus to the function block 6.
  • the volume of the interior 5 can be varied in order to avoid the formation of gas bubbles in the hydraulic fluid.
  • the volume of the interior 5 therefore forms a Ausretes ⁇ volume and the interior 5 forms a storage space.
  • To vary the volume of the piston 42 moves automatically within the cylinder 40 according to the respective aktu ⁇ ellen requirements.
  • the operation of the setting tool 38 via the hydraulic unit 2 is apparent from the hydraulic plan of FIG. 4.
  • the compensation block 8 is shown on the right-hand side of the image, and subsequently the pressure-generating block 10 and, in turn, the function block 6 are shown thereon.
  • the setting tool 38 is charged with the pressurized hydraulic oil.
  • the pumps 16 are arranged, in which case three of the pumps 16 for forming a high-pressure partial flow 54 and three further Pum ⁇ pen 16 for forming a low-pressure partial flow 56 are summarized. From the hydraulic plan several check valves 58 are to be taken, which allow the flow of hydraulic oil only in the direction of the arrow. Furthermore, the already mentioned for Fig. 1 pressure switching valve 32B 1 two controllable directional seat valves 33A, B and two safety valves 60A, B are arranged.
  • the electric motor 14 is turned on, so that a hydraulic pressure is provided both in the high-pressure partial flow 54 and in the low-pressure partial flow 56.
  • the high-pressure partial flow 54 is guided via the safety valves 6OA as well as via the directional seat valves 33A, which are shown on the right-hand half of the figure.
  • the directional seat valve 33A is in this case activated in such a way that the flow for the high-pressure substream 54 is opened as long as a flow is predetermined at the outlets 36A.B. rer pressure is not exceeded.
  • the directional seat valve 33A is open, the high-pressure partial flow 54 immediately opens into the interior of the housing 5, so that high pressure can not be built up at the rear and the partial flow 54 is switched without pressure.
  • the low pressure partial stream 56 is supplied to the setting tool 38 via the check valve 58 and via the supply line 52A.
  • This has an axially movable Kol ⁇ benelement 62, which moves by the application of the low pressure partial flow 54 at the beginning of the setting process to the right.
  • this first phase of the setting process comparatively long paths are covered at only low pressures.
  • the blind rivet is aligned in the blind rivet hole and a first forming.
  • the directional seat valve 33A is activated and closed, so that in the ms range the high pressure at the output 36A to the supply line 52A builds up successively.
  • the pressure switching valve 32B is now designed such that it automatically switches at ei ⁇ nem predetermined pressure, for example at a pressure of 80 bar, so that the low pressure partial flow 54 is released to the interior 5 and thus switched off without pressure ge.
  • the pressure supply now takes place via the high-pressure partial flow 54. Via the check valve 58 in the high-pressure partial flow 54, this is provided at the outlet 36 to the supply line 52A.
  • the further directional seat valve 33B which is connected to the second supply line 52B via the second output 36B, is in the state shown in FIG. That is, the supply line 52B is connected via the directional seat valve 33B with the interior 5 in the manner of a return line verbun ⁇ the.
  • the high-pressure partial flow 54 is switched back to pressure by switching the directional seat valve 33A. Due to the pressure drop caused thereby, the pressure switching valve 32B automatically switches back to the low-pressure partial flow 56.
  • the directional seat valve 33B is switched so that, as shown, the pumps 16 provide sub-streams 54,56, in particular the low-pressure partial flow 54 now rests both on the right side of the piston member 62 as well as on the left side. Due to the selected larger cross-sectional area on the right side of the Kol ⁇ benelements 62 this is pushed back to the left back to the starting position.
  • the high-pressure partial flow 54 is also connected to the housing interior 5 via the safety valves 6OA.
  • This safety valve 6OA switches, for example when exceeding a pressure of 400 x 10 -5 Pa.
  • the safety valve 6OB shown on the left is provided to secure the pressure prevailing in the interior 5. This safety valve 6OB switches, for example, when a pressure of 25 ⁇ 10 5 Pa is exceeded.
  • Electric motor 46 Pneumatic connection A Stator 48 End wall B Rotor 50 Safety spring

Abstract

L'invention concerne une unité hydraulique (2) qui sert à mettre à disposition un fluide hydraulique sous pression au niveau d'une sortie (36. 36A, B) et qui présente un moteur électrique (14) ainsi qu'une pompe (16) fonctionnant au moyen de ce dernier, servant à produire une pression. Une chambre de stockage (5) à volume de compensation variable sert au stockage, sans gaz, du fluide hydraulique aspiré par la pompe (16). Le fluide hydraulique présente notamment une surpression pour qu'il soit, de manière sûre et fiable, exempt de gaz. Cette conception permet d'assurer la fiabilité et la sécurité de fonctionnement de l'unité hydraulique (2) même en présence de valeurs d'accélération élevées. L'unité hydraulique (2) est destinée en particulier à être montée sur un robot industriel.
PCT/EP2005/010208 2004-11-19 2005-09-21 Unite hydraulique et procede pour mettre a disposition un fluide hydraulique sous pression WO2006056256A2 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
PCT/EP2005/010208 WO2006056256A2 (fr) 2004-11-19 2005-09-21 Unite hydraulique et procede pour mettre a disposition un fluide hydraulique sous pression
DE112005002804.6T DE112005002804B4 (de) 2004-11-19 2005-09-21 Hydraulikaggregat sowie Verfahren zur Bereitstellung einer unter Druck stehenden Hydraulikflüssigkeit
US11/804,853 US20070286740A1 (en) 2004-11-19 2007-05-21 Hydraulic unit and method for providing a pressurized hydraulic fluid

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE102004056046.3 2004-11-19
DE102004056046 2004-11-19
DE102004061164 2004-12-16
DE102005023099 2005-05-13
PCT/EP2005/010208 WO2006056256A2 (fr) 2004-11-19 2005-09-21 Unite hydraulique et procede pour mettre a disposition un fluide hydraulique sous pression

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US11/804,853 Continuation US20070286740A1 (en) 2004-11-19 2007-05-21 Hydraulic unit and method for providing a pressurized hydraulic fluid

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WO2006056256A2 true WO2006056256A2 (fr) 2006-06-01
WO2006056256A3 WO2006056256A3 (fr) 2006-06-29
WO2006056256A8 WO2006056256A8 (fr) 2007-12-13

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US (1) US20070286740A1 (fr)
DE (1) DE112005002804B4 (fr)
WO (1) WO2006056256A2 (fr)

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EP2128446A2 (fr) 2008-05-26 2009-12-02 Kai Böhner Unité hydraulique
GB2469016A (en) * 2009-02-26 2010-10-06 Ge Aviat Systems Ltd Electrically driven hydraulic actuator
DE102006013652B4 (de) * 2005-10-14 2010-12-16 Richard Bergner Verbindungstechnik Gmbh & Co. Kg Bearbeitungswerkzeug sowie Verfahren zum Bearbeiten eines Werkstücks
DE112005002827B4 (de) * 2004-11-19 2014-02-20 Richard Bergner Verbindungstechnik Gmbh & Co. Kg Roboterhand sowie Verfahren zum automatischen Setzen eines Elements
US20220081226A1 (en) * 2020-09-14 2022-03-17 Yamaha Hatsudoki Kabushiki Kaisha Movable harvesting apparatus and harvesting unit

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US20090191068A1 (en) * 2008-01-29 2009-07-30 Clark Equipment Company Variable volume reservoir
US10282285B2 (en) * 2008-09-30 2019-05-07 Rockwell Automation Technologies, Inc. Human interface module for motor drive
EP2642122B1 (fr) * 2012-03-21 2014-05-21 HAWE Hydraulik SE Groupe motopompe
DE102017106449A1 (de) 2017-03-24 2018-09-27 Böllhoff Verbindungstechnik GmbH Mehrstufige Fügevorrichtung und Fügeverfahren dafür
CN114434337B (zh) * 2020-11-03 2023-07-04 中国海洋石油集团有限公司 一种水力割刀导向装置及其导向方法

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US20070286740A1 (en) 2007-12-13
WO2006056256A3 (fr) 2006-06-29

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