EP2024112B1 - Verfahren zum betreiben eines hydraulischen verpressgerätes sowie hydraulisches verpressgerät - Google Patents

Verfahren zum betreiben eines hydraulischen verpressgerätes sowie hydraulisches verpressgerät Download PDF

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Publication number
EP2024112B1
EP2024112B1 EP07729579.8A EP07729579A EP2024112B1 EP 2024112 B1 EP2024112 B1 EP 2024112B1 EP 07729579 A EP07729579 A EP 07729579A EP 2024112 B1 EP2024112 B1 EP 2024112B1
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EP
European Patent Office
Prior art keywords
hydraulic
piston
pressing unit
line
chamber
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Active
Application number
EP07729579.8A
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German (de)
English (en)
French (fr)
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EP2024112A1 (de
Inventor
Egbert Frenken
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Gustav Klauke GmbH
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Gustav Klauke GmbH
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/16—Control arrangements for fluid-driven presses
    • 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
    • B21J15/16—Drives for riveting machines; Transmission means therefor
    • B21J15/20—Drives for riveting machines; Transmission means therefor operated by hydraulic or liquid pressure
    • 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
    • B25B27/00—Hand tools, specially adapted for fitting together or separating parts or objects whether or not involving some deformation, not otherwise provided for
    • B25B27/02—Hand tools, specially adapted for fitting together or separating parts or objects whether or not involving some deformation, not otherwise provided for for connecting objects by press fit or detaching same
    • B25B27/10—Hand tools, specially adapted for fitting together or separating parts or objects whether or not involving some deformation, not otherwise provided for for connecting objects by press fit or detaching same inserting fittings into hoses

Definitions

  • the invention relates first to a method according to the preamble of claim 1 for operating a hydraulic Verpresseurs, in particular hand-pressing device, wherein the pressing device comprises a hydraulic pump, a moving part, a fixed part and a return valve, wherein further the moving part by the construction of a hydraulic pressure, the itself by filling a hydraulic space with hydraulic fluid from a storage space using the hydraulic pump is moved into an injection position, wherein further the moving part is designed to automatically return under the action of a return spring of the injection position in an end position and the return valve is designed to only to close after a certain, acting on the return valve by the running back of the hydraulic fluid pressure falls below.
  • the invention further relates to a hydraulic compression device according to the preamble of claim 4.
  • Hydraulic compression devices and methods for operating the same are known. It is in this regard, for example, on the DE 198 25 160 A1 directed.
  • a hand-operated pressing device is described, which is provided with a return valve, which is triggered upon reaching or exceeding a predetermined pressure on the moving part. After opening the return valve, the moving part moves back spring-assisted, this by pressing back the hydraulic fluid acting on the moving part via the return valve in the reservoir.
  • a force acting on the return valve pressure corresponding to only a fraction of the return valve release pressure is achieved, which holds the return valve in the open position. Falling below this predetermined return pressure leads to the closing of the return valve, after which the pressing device is ready again for the next pressing operation.
  • a technical problem of the invention is seen as providing a method for operating a hydraulic pressing device, which allows an optional stopping of the moving part in one position.
  • means are provided which influence the return flow of the hydraulic fluid in front of the return valve, ie between the moving part and the return valve such that an optionally only short-term pressure drop is established, which is sufficient to cancel the preferably provided latching of the return valve in the open position.
  • the holding pressure of the return valve is lowered, after which the return valve falls into the closed position. Accordingly, no hydraulic fluid flows from the storage room.
  • the remaining hydraulic fluid cushion in front of the moving part causes it to stop.
  • the means acting on the return flow of the hydraulic means to stop the moving member may be purely mechanical means which are deliberately actuated by the user when needed.
  • the return line between the moving part and the return valve can be closed by a slide, whereby the desired pressure drop is achieved at the return valve.
  • This slider closure can be carried out, for example, electromechanically, so on, for example, triggered by a pulse to start a new injection process, ie a pulse to start the hydraulic pump. Also, a separate button or the like.
  • On the hydraulic Verpress réelle for stopping the return movement of the moving member may be provided, via which switch can be acted mechanically or electrically on the flow-influencing means.
  • the effect on the backflow is preferably only for a short time. The immediately adjusting pressure drop leads to an almost sudden closing of the valve, after which a further influence by the means is not necessary.
  • decoupling is achieved by moving a switching piston arranged in the flow path counter to the flow direction.
  • This working against the return flow control piston causes a brief suction of the returning hydraulic fluid, which, although only a small amount, is entrained in hydraulic fluid. Again, this effect on the return flow causes a pressure drop, which has the closing of the return valve result.
  • the pressure drop to achieve the return valve closure position is on the order of about 0.5 to 1 bar.
  • the latching of the return valve in the course of the movement part return is achieved at a pressure of about 0.5 to 2.5 bar, so on, in particular at 1.5 bar, while the first opening of the return valve to complete the compression process at a pressure of about 400 to 800 bar, so on, in particular at 500 or 700, preferably at 600 bar, after which a return spring, which acts on the moving part in the return directly in the region of the moving part, a pressure of about 1.5 to 5 bar, preferably 2, 5 bar is present.
  • the pressure difference of at least one bar between the area acted upon by the returning moving part and the area of the return valve is consumed mainly as it flows through smaller, in the closed position with smaller part piston surfaces cooperating holes of the sealing seat as a throttle loss.
  • the switching piston is preferably held solely by the return flow in a non-actuated drain position, wherein the control piston in this flow position a flow passage for the returning hydraulic fluid leaves.
  • This flow passage is further dimensioned so large that this results in no negative impact on the self-retention of the return valve pressure losses.
  • the switching piston leads to a shut-off of the flow, ie the return flow thus triggering a pressing operation immediately causes the displacement of the switching piston in a shut-off position.
  • this barrier leads to a pressure drop at the return valve, according to which this closes.
  • the displacement of the control piston due to the startup of the pressing device against the flow direction of the returning hydraulic fluid further causes a suction of a subset of the hydraulic fluid, which further supports the desired pressure drop to close the return valve.
  • the switching piston can be spent in triggering a re-pressing process, for example by mechanical means in the pumping position.
  • the switching piston is arranged with its piston surface in the flow path of the hydraulic fluid such that by commissioning the hydraulic pump, the pumped hydraulic fluid first via the control piston surface causes a displacement of the control piston from the discharge position to the pumping position, this to produce a pressure drop to close the return valve.
  • the invention further relates to a hydraulic compression device with a hydraulic pump, a moving part, a fixed part and a return valve, wherein the moving part moves from a starting position into a Verpress too due to filling a hydraulic space with hydraulic fluid from a storage container by means of the hydraulic pump, wherein the return valve is automatically in Dependence of one of the Verpressgna corresponding hydraulic pressure moves into an open position and the moving part moves back under the action of a return spring.
  • a pressing device of the type in question is from the cited above DE 198 25 160 A1 known.
  • the invention has for its object to design a hydraulic compression device of the type in question in particular handling technology improved.
  • the return movement after exceeding the pressure threshold reached in the course of the pressing process or triggered by a manual intervention in the course of the forward displacement of the moving part can be stopped at any time according to the present invention, including means are provided for the self-retention of the retaining valve reduce pressure required in the open position such that a drop in the return valve is achieved.
  • the means engage in the return flow of the hydraulic medium between the movement part and the return valve.
  • the pressure drop achieved by the means moves in this case in the order of 0.5 to 5 bar, preferably 1 to 1.5 bar, wherein further acting on the return valve pressure for latching the valve in the open position between 0.5 and 5 bar , preferably 1.5 bar.
  • the hydraulic chamber has a first subspace in which moves the moving part and a second subspace, which is designed as a line section, in which the hydraulic fluid for filling or emptying of the first subspace flows and that the means are arranged in the second subspace.
  • the movement part is of a piston-like design for direct application to a piston or piston rod assigned to the tool that can be assigned to the pressing device.
  • the first subspace which comprises this movement part, in particular cylindrically, is essentially separated from the second subspace upstream in the inflow direction, with a fluid connection of the subspaces initially being achieved by means of an inflow channel.
  • a return channel through which the hydraulic fluid flows after triggering the return valve and corresponding displacement of the same in the open position according to the spring-loaded return displacement of the moving member is optionally switchable formed the two sub-spaces connecting.
  • the means may be designed for the short-term decoupling of a subset of the hydraulic medium.
  • a pressure reduction can be achieved by a slider-like member in the simplest way, which is inserted in the flow path between the moving part and return valve, the flow interrupting.
  • a brief negative pressure effect on this flow path lead to a corresponding uncoupling of a subset of the return flow, which has a corresponding decrease in pressure at the return valve result.
  • a transverse channel opening into the return flow channel can be provided in this case, in which a piston-like means for triggering the return stop acts in an absorbent manner on the returning hydraulic medium.
  • the means are formed in the line section for switching between a first and second conduction path, wherein the decoupling takes place in the course of the switching.
  • the means switch in the line section between the line paths for the flow of the moving part in the course of a pressing operation and the conduction path for the return flow of the hydraulic fluid in the course of the return displacement of the moving means.
  • the decoupling of a subset of the hydraulic medium in the course of the return is preferably derived from the movement of the means resulting from the switching over of the means between the first and second conduction paths. Accordingly, the movement of the means and the decoupling is coupled to the pressure reduction before the return valve.
  • the means consist of a movable in the second compartment switching piston. This is displaceable in the second subspace along a piston body axis displaceable between two end positions, which end positions on the one hand, the flow position of the hydraulic means for acting on the moving part and the other the return position of the hydraulic fluid with the return valve open.
  • the switching piston has an effective piston surface and a piston stem. The latter is for releasing or closing a hydraulic line connected downstream of the hydraulic pump, in particular the first flow line connecting the first subspace to the second subspace.
  • the switching piston is in this case preferably positioned and designed such that in the usual operating position, in which hydraulic medium is pumped into the hydraulic space via the hydraulic pump, the latter remains in a predisplaced position, in which the aforementioned hydraulic line is unlocked.
  • the piston head for releasing or closing a return line leading to the drain line is formed such that in the vorverlagerten pumping position, in which the hydraulic line between the first and second subspace is unlocked, leading to the return valve drain line is blocked by the piston head.
  • the switching piston In the return position, ie after exceeding the maximum pressure in the hydraulic chamber - possibly manually triggered by opening the return valve - the switching piston falls into a retracted position in which this first closes the flow hydraulic line and at the same time opens the return line leading drain line between the hydraulic chamber and return valve.
  • the switching piston is used accordingly in a figurative sense as a pressure-dependent two-way valve for the alternate release / closure of flow line and return line.
  • the switching piston has three mutually separate loading surfaces. These extend in a plane perpendicular to the displacement direction of the control piston and are preferably formed circular-disk-shaped or annular.
  • a first contiguous loading surface of the switching piston is preferably associated with the first subspace, so according to the hydraulic space receiving the moving part.
  • This contiguous loading surface is preferably circular disk-shaped, further formed approximately flat surface.
  • a second opposite to the first loading area arranged Beaufschlagungsthesis is assigned to the drain line, has accordingly in the direction of the second subspace.
  • This second loading surface is preferably formed annularly with an outer diameter which substantially corresponds to the outer diameter of the first opposing loading surface.
  • the inner diameter of the second loading surface is defined in a preferred embodiment by the outer diameter of the piston skirt.
  • a third, likewise opposite to the first loading surface arranged loading surface is associated with the hydraulic pump, is accordingly acted upon in a direct manner by the hydraulic means in the course of advancement of the moving part in the context of a pressing operation.
  • This third loading surface is formed substantially circular disk-shaped, with an outer diameter which substantially corresponds to the outer diameter of the piston skirt.
  • the second and third loading areas are summarized in terms of size of the first loading area.
  • both further loading surfaces lie within the first loading surface.
  • the switching piston is preferably movable between a drainage position and a pumping position.
  • the switching piston is moved by Hydraulikstoffschbeaufschlagung particular the third loading surface in the pumping position.
  • the switching piston is displaced in the opposite direction into the expiration position.
  • the piston head is received in an enlarged diameter relative to the piston head annulus, which annulus merges into the drain line. This annular space is not necessarily provided over the entire circumference of the piston head.
  • the piston closes in the pumping position in which the aforementioned hydraulic line is released, the drain line like a slide, wherein further the slide-like closing movements of the switching piston are synchronized so that no simultaneous opening of drain line and hydraulic line (flow line) can be achieved.
  • the slide-like closure of the hydraulic line preferably prefers the slide-like opening of the drain line.
  • the switching piston has an integrated pressure relief valve.
  • This is preferably formed the first and the opposite third loading surface of the switching piston line connecting, which opens the integrated line of the control piston at overpressure valve controlled.
  • the pressure relief valve is formed by a held by a pin, plate spring-like valve disc. This is preferably on the side of the first loading surface, the associated opening edge of the pressure line overlapping.
  • the central holding the valve disc spigot is in one another embodiment surrounded by the valve disc covered by the overpressure line, which pin is also centrally preferably coaxially positioned to the switching piston axis.
  • the pin is designed as a screw, the screw head of the valve disc displaceable acts against the peripheral edge of the associated opening of the pressure relief line.
  • an unillustrated electric motor is arranged in the pressing device 1.
  • the drive of this electric motor via a, integrated in a handle 2 accumulator 3.
  • a finger-operable switch 4 is pumped from a reservoir 5 hydraulic fluid (oil) in a hydraulic chamber 6, whereby a slidably received in the hydraulic chamber 5, piston-like movement part 7 is moved in the direction of a working end position.
  • the replaceable device head 10 can be fixed externally on the hydraulic cylinder 9 via a threaded connection 13 on the outside.
  • the piston-like movement part 7 facing away from the tool carrier 11 is fixed to the device head 10, d. H. not displaceable executed.
  • the tool carrier 12 lying opposite this tool carrier 11, assigned to the movement part 7, can be displaced in the movement part displacement direction, for which purpose furthermore the displaceable tool carrier 12 is provided rearwardly with a piston shaft 14. This is surrounded by a return spring 15, which further loads the piston skirt 14 in contact with the device-side movement part 7.
  • the return displacement of the moving part 7 takes place solely as a result of the restoring force of the spring 15, which via the piston shaft 14 and an end
  • the radial part associated with the movement part 7 acts on the movement part 7, the hydraulic medium from the hydraulic space 6 being pressed further back into the storage space 5 via the movement part 7.
  • a triggering of a return valve 16 is sought, which ensures that the full pressing force was effective.
  • a return valve 16 is from the above-mentioned DE 198 25 160 A1 known.
  • the content of this patent application is hereby incorporated in full in the disclosure of the present invention, also for the purpose of including features of this patent application in claims of the present invention.
  • the return valve 16 consists essentially of a valve piston 17 with a frontally centrally arranged, pointed conical needle tip 18, to form a, relative to the entire piston surface 19 substantially smaller and defined by the diameter of a connected to the hydraulic chamber 6 bore 20 partial piston surface (poppet valve active surface) , The latter is in one, as in Fig. 2 illustrated exit closure layer closed by the needle tip 18.
  • valve piston 17 is acted upon by a pressure spring 21, whereby the needle tip 18 is pressed against the bore 20 with a co-determining a maximum release pressure force.
  • a pressure relief valve in seat type is essentially given.
  • the return valve 16 opens at a force acting on the hydraulic piston surface 22 of the moving member 7 maximum pressure of 600 bar.
  • cut-off pressures between 400 and 700 bar for example 500, 550 or even 650 bar, can open the return valve 16 lead.
  • the maximum pressure is defined by the projected onto the bore 20, very small part piston area of the needle tip 18 and by the cross-sectional area of the bore 20 and by the contact pressure of the pressure spring 21 on the valve piston 17th
  • valve piston 17 If the pressure of the hydraulic fluid exceeds the predefined maximum value of, for example, 600 bar, then the valve piston 17 is moved out of its seat 20 sealing against the force of the pressure spring 21, after which the substantially larger piston area 18 of the valve piston 17 comes into effect. As a result of the backward displacement of the valve piston 17, a drain opening 24 arranged in the cylinder 23 receiving the valve piston 17 is at least partially exposed, for the return flow of the hydraulic fluid into the reservoir 5.
  • the return valve 16 acts as a pressure relief valve, but this in Lekssschieberbauart with a much lower limiting pressure, since the latter is now defined by the much larger piston surface 19 of the valve piston 17.
  • a diameter ratio of smaller effective partial piston tip (needle tip 18 in bore 20) to the total piston surface 19 of 1: 400 given with the result that the limiting pressure in the open position of the return valve 16 is 400 times smaller as the trigger pressure.
  • the restoring spring 15 acting on the moving part 7 is designed with regard to its restoring force so that the pressure in the hydraulic chamber 6 during retraction of the moving part 7 is always at least 2.5 bar.
  • the pressure difference of at least 1 bar is consumed mainly as it flows through the small bore 20 of the return valve 16 as a throttle loss and determines the oil flow and thus the retraction speed of the moving part 7th
  • the pressing device 1 is hereafter in an automatic, purely spring-loaded return.
  • means 25 are provided, which at least temporarily lower the return valve 16 in the open position retaining pressure in the course of the hydraulic fluid return, that the latching of the return valve 16 is released and the valve piston 17 for closing the bore 20 by means of the needle tip 18 moves back.
  • a displaceable in the same direction as the moving part 7 switching piston 26 is provided. This is held in an insert 27, which is received in a bore-like continuation 28 of the hydraulic chamber 6 is substantially cylindrical. Cloak outside the insert 27 is provided with a circumferential ring seal 29, for sealing against the wall of the bore-like continuation 28th
  • the insert part 27 is fixed by a screw 30 which engages in the bottom of the bore-like continuation 28 facing away from the movement part 7 and whose screw head rests in a line section 31 which essentially passes through the insert part 27.
  • the line section 31 is aligned corresponding to coaxial with the body axis of the insert member 27.
  • the switching piston 26 which is also formed as a rotary member.
  • the switching piston 26 has a piston shaft 32 with an outer diameter which corresponds to the inner diameter of the line section 31.
  • the piston head is enlarged in diameter.
  • the head diameter corresponds approximately to twice the shaft diameter, wherein further measured in the axial direction thickness of the collar-like projecting piston head 33 corresponds approximately to a quarter of the free axial extension length of the piston shaft 32.
  • the line section 31 is at one end, the switching piston 26 facing away from the flow connected to a Hydraulik.-supply line 34 of the pressing device 1, through which the latter by means of a pump, not shown, hydraulic fluid from the reservoir 5 with the interposition of a check valve 35 is promoted.
  • the insert 27 is correspondingly connected in the supply line between the storage space 5 and the hydraulic chamber 6.
  • the insert member 27 is also connected between the hydraulic chamber 6 and the return valve 16, to which the insert member 27 is arranged eccentrically to the body axis of the insert member 27, i. W. axially parallel drain line 37 which opens at one end in a device housing-side return line 38.
  • the latter is connected to the return valve 16, specifically with the valve seat side bore 20th
  • the switching piston 26 is aligned in the insert member 27 coaxially with the insert part axis and held stop-end slidably on both sides in the axial direction.
  • the piston shaft 32 is in this case in the line section 31 of the insert member 27, while the diameter-enlarged piston head 33 rests in a correspondingly enlarged diameter, the hydraulic chamber 6 out open bore portion 39 is guided.
  • a rear the movement of the control piston 26 in the direction of the line section 31 limiting abutment surface is given by the penetrated by the line section 31 bore portion bottom 40.
  • the head of an end face of the insert part 27 has a stop-limiting screw 41 screwed in, the head of which protrudes radially inwards over the associated bore-cut edge.
  • the insert part-side drain line 37 opens approximately with half the opening cross section in which the switching piston 26 leading bore portion 39. Accordingly, the axis of the drain line 37 is positioned so that it enters approximately in the outer wall of the bore portion 39.
  • the associated transition region from the bore section wall to the bore section bottom 40 is enlarged in diameter relative to the further bore section 39 and the outside diameter of the piston head 33, so that when the control piston 26, d. H. in stop position of the same against the bore portion bottom 40, a free flow area in the form of an annular space 50 for connecting the drain line 37 to the hydraulic chamber 6 sets.
  • the axial length of the piston shaft 32 and the axial travel of the switching piston 26 and the positioning of the radially aligned hydraulic line 36 are selected so that in a pumping position as shown in FIG Fig. 3 and associated advancement of the control piston 26, in which this limited stop occurs against the screw 41, the hydraulic line 36 is in flow communication with the central line section 31st
  • a first loading surface 42 which faces the hydraulic chamber 6 and is defined by the corresponding transversely to the axis aligned piston head surface.
  • the third loading surface 43 is defined by the end surface of the piston skirt 32 facing away from the first loading surface 42 and aligned transversely with respect to the axis. This third loading surface 43 is offset parallel to the first loading surface 42.
  • the second loading surface is 44 annularly formed by the surface of the piston head 33 facing away from the first loading surface 42, which second loading surface 44 is also at the same time the counter stop surface cooperating with the stop surface formed by the bore portion bottom 40.
  • a loading area ratio of the third loading surface 43 to the first loading surface 42 is from 1: 2 to 1: 4, preferably 1: 3, while the Ratio of second loading surface 44 to the first loading surface 42 1: 2 to 3: 4, preferably 2: 3.
  • the insert part 27 or the line paths provided in the insert part 27 are altogether part of the hydraulic chamber 6, wherein the control piston 26 subdivides these into two subspaces, thus into a first subspace 45, in which the movement part 7 moves and a second subspace 46, which moves the forms aforementioned line sections within the insert part 27.
  • the switching piston 26 further has an integrated pressure relief valve 47.
  • This is essentially formed by a plate-spring-like valve disc 49 supported by means of a pin 48 forming a journal.
  • This valve disc 49 covers a substantially the switching piston 26 centrally in the axial direction passing through pressure line 51, which faces the hydraulic chamber 6 in the middle of the piston head 33 passes.
  • a radial jump of the line is provided to further centrally provide a threaded mounting portion for the screw 48, the screw head pushes the valve disc 49 against the facing peripheral edge of the pressure line 51.
  • a pressure-unaffected position as shown in FIG Fig. 3 is the valve disc 49 in a loaded by the screw 48 rest position in which it closes the pressure line 51.
  • the hydraulic medium is pumped into the hydraulic chamber 6 via the hydraulic line 36, which causes an axial displacement of the movement part 7 displaceably held in this hydraulic chamber 6 and, via this, of the device head side piston shaft 14 for obtaining the injection position.
  • the return valve Upon reaching the maximum injection pressure of, for example, 600 bar, which is also constructed in the line section 31 and also conditioned by the non-pressure seal between piston skirt 32 and associated wall of the line section 31 in the drain line 37 and return line 38, the return valve lifts 16 as described and releases the return path via the drain opening 24.
  • the adjusting pressure difference of the switching piston 26 is rearranged in the axial direction, which may further be constructed by the before the third Beauftschungs constitutional 43 in the line section 31 still existing hydraulic fluid cushion a significant overpressure, in this case by automatic, spring-like lifting of the valve disc 49 as shown in FIG Fig. 4 is reduced.
  • the switching piston 26 has the hydraulic line 36 closed like a slide and hereafter the drain line 37 is also opened like a slide.
  • the hydraulic means can thereafter be expressed in a spring-loaded manner via the movement part 7 from the hydraulic space 6, with the flow around the piston head 33.
  • the piston head 33 in this case leaves the diameter-enlarged annulus area of the bore section 39; Accordingly, a short-term decoupling of a subset of located in the drain line 37 hydraulic means is achieved, so in particular by generating a short-term suction effect in the region of the second, annular and the discharge line 37 facing loading surface 44. This causes an at least short-term pressure drop in the drain line 37 and correspondingly in the return line 38, which pressure drop due to the spring load on the valve piston 17 has an immediate closing of the return valve 16 result.
  • the drain of the hydraulic fluid is interrupted accordingly.
  • the switching piston 26 is pressurized by the hydraulic means in the stop limited by the screw 41 position as shown in FIG Fig. 3 urged, after which the advancement of the moving part 7 and according to the pressing operation is performed.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Check Valves (AREA)
  • Press Drives And Press Lines (AREA)
  • Fluid-Pressure Circuits (AREA)
EP07729579.8A 2006-06-08 2007-05-29 Verfahren zum betreiben eines hydraulischen verpressgerätes sowie hydraulisches verpressgerät Active EP2024112B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006026552A DE102006026552A1 (de) 2006-06-08 2006-06-08 Verfahren zum Betreiben eines hydraulischen Verpressgerätes sowie hydraulisches Verpressgerät mit einer Hydraulikpumpe
PCT/EP2007/055156 WO2007141156A1 (de) 2006-06-08 2007-05-29 Verfahren zum betreiben eines hydraulischen verpressgerätes sowie hydraulisches verpressgerät mit einer hydraulikpumpe

Publications (2)

Publication Number Publication Date
EP2024112A1 EP2024112A1 (de) 2009-02-18
EP2024112B1 true EP2024112B1 (de) 2017-06-14

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US (1) US7908963B2 (es)
EP (1) EP2024112B1 (es)
KR (1) KR101469451B1 (es)
CN (1) CN101500728B (es)
DE (1) DE102006026552A1 (es)
ES (1) ES2633924T3 (es)
RU (1) RU2428301C2 (es)
WO (1) WO2007141156A1 (es)

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EP2070660B1 (de) 2007-12-14 2012-09-26 Gustav Klauke GmbH Hydraulisches Pressgerät
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ES2633924T3 (es) 2017-09-26
CN101500728A (zh) 2009-08-05
DE102006026552A1 (de) 2007-12-13
KR20090017697A (ko) 2009-02-18
EP2024112A1 (de) 2009-02-18
US20090133591A1 (en) 2009-05-28
CN101500728B (zh) 2013-06-12
KR101469451B1 (ko) 2014-12-05
US7908963B2 (en) 2011-03-22
RU2428301C2 (ru) 2011-09-10
RU2008152791A (ru) 2010-07-20

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