EP1244187A1 - Hydraulisches Pressgerät und Verfahren zum Betreiben desselben - Google Patents

Hydraulisches Pressgerät und Verfahren zum Betreiben desselben Download PDF

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Publication number
EP1244187A1
EP1244187A1 EP02000014A EP02000014A EP1244187A1 EP 1244187 A1 EP1244187 A1 EP 1244187A1 EP 02000014 A EP02000014 A EP 02000014A EP 02000014 A EP02000014 A EP 02000014A EP 1244187 A1 EP1244187 A1 EP 1244187A1
Authority
EP
European Patent Office
Prior art keywords
pressure
valve
return
piston
hydraulic
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.)
Withdrawn
Application number
EP02000014A
Other languages
German (de)
English (en)
French (fr)
Inventor
Egbert Frenken
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.)
Gustav Klauke GmbH
Original Assignee
Gustav Klauke GmbH
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
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Application filed by Gustav Klauke GmbH filed Critical Gustav Klauke GmbH
Priority claimed from EP98951524A external-priority patent/EP0944937B1/de
Publication of EP1244187A1 publication Critical patent/EP1244187A1/de
Withdrawn legal-status Critical Current

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Classifications

    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D39/00—Application of procedures in order to connect objects or parts, e.g. coating with sheet metal otherwise than by plating; Tube expanders
    • B21D39/04—Application of procedures in order to connect objects or parts, e.g. coating with sheet metal otherwise than by plating; Tube expanders of tubes with tubes; of tubes with rods
    • 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
    • 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
    • B21J15/26—Drives for riveting machines; Transmission means therefor operated by rotary drive, e.g. by electric motor
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25F—COMBINATION OR MULTI-PURPOSE TOOLS NOT OTHERWISE PROVIDED FOR; DETAILS OR COMPONENTS OF PORTABLE POWER-DRIVEN TOOLS NOT PARTICULARLY RELATED TO THE OPERATIONS PERFORMED AND NOT OTHERWISE PROVIDED FOR
    • B25F5/00—Details or components of portable power-driven tools not particularly related to the operations performed and not otherwise provided for
    • B25F5/005—Hydraulic driving means
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01R—ELECTRICALLY-CONDUCTIVE CONNECTIONS; STRUCTURAL ASSOCIATIONS OF A PLURALITY OF MUTUALLY-INSULATED ELECTRICAL CONNECTING ELEMENTS; COUPLING DEVICES; CURRENT COLLECTORS
    • H01R43/00—Apparatus or processes specially adapted for manufacturing, assembling, maintaining, or repairing of line connectors or current collectors or for joining electric conductors
    • H01R43/04—Apparatus or processes specially adapted for manufacturing, assembling, maintaining, or repairing of line connectors or current collectors or for joining electric conductors for forming connections by deformation, e.g. crimping tool
    • H01R43/042—Hand tools for crimping
    • H01R43/0427—Hand tools for crimping fluid actuated hand crimping tools

Definitions

  • the invention initially relates to a method for operating a hydraulic pressing device with a fixed part and a moving part, the moving part relative to the fixed part until it is reached a predetermined pressure is moved.
  • a method of operating a hydraulic Pressing device of the type in question such as for example a cable lug (connector) or riveting tool pressing device, specify which, in particular, in terms of handling is improved.
  • the invention further relates to a method for Operating a hydraulic press, such as. a pipe clamping device, with a fixed part and a Moving part and an automatically triggering return valve, the moving part by means of a return spring is biased into its initial position.
  • a hydraulic press such as. a pipe clamping device
  • a fixed part and a Moving part and an automatically triggering return valve the moving part by means of a return spring is biased into its initial position.
  • the invention further relates to a hydraulic pressing device with a fixed part and a moving part, wherein the moving part by a hydraulic piston relative is moved to the fixed part and by means of a return spring can be moved back to a starting position, the return movement depending on a predetermined Press pressure can be triggered by addressing a Return valve.
  • a hydraulic press device in The type in question is more reliable and easy to handle to improve it is proposed that the automatically responsive return valve through the pressure of the returning oil over the entire Return stroke of the hydraulic piston in the open position is held. This configuration can to a mechanical locking of the return valve in the In the course of resetting the hydraulic piston or Movement part can be dispensed with, in particular offers functional advantages.
  • Known constructive Solutions consist, for example, of a pressure relief valve to be used, which after being triggered by a mechanical Locking mechanism is locked and so a complete Retraction of the spring-loaded piston allows.
  • the press tool is actuated again, For example, when the motor is switched on, the lock mechanically canceled and the pressure relief valve goes in the closed position back.
  • the pressure of the returning oil which is present anyway after a response of the return valve used to to keep it in the open position.
  • the return valve speaks automatically when one is exceeded predetermined oil pressure. The one in the course of the resetting of the hydraulic piston decreasing pressure of the returning Oil is sufficient over the entire return path high to the return valve in the open position to keep.
  • the return valve as a valve piston is formed, an effective in the locked state Partial cup area with regard to the desired Maximum pressure is designed.
  • the return valve is there preferably from a valve piston with, for example. a needle tip, which is connected to the pressure chamber Hole closes.
  • The, through the bore diameter effective smaller piston area is in the course pressing by means of the hydraulic pressing device acted upon by the oil. If the oil pressure exceeds one height predefined by the bore diameter, see above the valve piston of the Return valve raised from the sealing seat, after which a much larger piston area comes into effect.
  • the return valve works in this position a much lower limiting pressure than in the closed position.
  • the limit pressure is in this Position no longer due to the smaller piston area defined, but rather by the total surface of the valve piston designed as a longitudinal slide piston.
  • a ratio of the total piston area to smaller, interacting with the sealing seat Partial piston area of 400: 1 can be given.
  • the limiting pressure in the open position of the Valve piston 400 times lower than the trigger pressure in the sitting position, i.e. in the initial locking position.
  • a return valve is included large hysteresis formed, with the valve piston over the entire return stroke of the hydraulic piston as a result of the oil pressure acting on the valve piston in the The open position remains, even though the oil pressure in the In the course of the return movement decreases steadily.
  • the valve piston only falls back to the initial closure position, if the oil pressure falls below a predetermined minimum level.
  • This very low oil pressure is synonymous with the position of the Hydraulic piston.
  • can trigger i.e. an opening of the return valve at 600 bar and an independent return process the same in the initial closed position at 1.5 bar respectively.
  • the oil flows Exceeded by the force of the pressure spring and defined the smaller partial piston area of the valve piston Release pressure not directly in the oil reservoir from. Rather, the oil only gets through the Drain opening in the oil reservoir, which drain opening only becomes free when the valve piston is one Overlap length has shifted.
  • the valve piston can be fitted with little play, so that relatively little oil can flow past it.
  • To one To design damping of the return valve is in an advantageous development of the subject of the invention provided that on the back of the Valve piston one that penetrates the cylinder wall Relief bore is formed. This hole serves to relieve the pressure on the back of the piston, using the Size and location of the relief bore damping the Valve can be influenced.
  • the desired automatic Return of the hydraulic piston is easy acting cylinders with a return spring enables this return spring to be dimensioned in this way will that by pressure on the hydraulic piston causes an oil pressure that is above the limit pressure of the return valve in the longitudinal slide position lies. This keeps the valve open and the Hydraulic piston moved back.
  • the return spring is preferred designed so that the hydraulic piston up moved back to the stop. In this end position the reflux ends and the valve piston sinks into its Starting position, the sitting position back, after which the hydraulic press is ready for the next one Duty cycle. For example, a desired one Maximum pressure in the pressure chamber of 600 bar may be desired. If this is exceeded, the reset valve is triggered and the limiting pressure drops to about 1.5 bar.
  • the Return spring is designed so that the Pressure in the pressure chamber when retracting the hydraulic piston is always at least 2.5 bar.
  • the pressure difference of at least 1 bar is predominantly when flowing through the small one, in the locked position with the smaller one Partial piston surface interacting bore of Sealing seat consumed as throttle loss and determined the oil flow and thus the retraction speed of the hydraulic piston.
  • valve piston moved into an open position, whereby the drain opening to the oil reservoir is released becomes.
  • This has a drop in oil pressure and thus a displacement of the hydraulic piston.
  • a train part is advantageous, which with the Valve piston, connected through the cylinder is.
  • This pull part is in a preferred embodiment Can be moved by hand using an operating rocker.
  • This rocker switch forms one for the user favorable lever arm, over which the valve piston against the force of the pressure spring acting on it can be lifted from the valve seat.
  • the traction part has a driving head has that with a driving lug of the valve piston is engaged.
  • the driving head having traction part moved away from the valve seat.
  • the pressure spring that also defines the trigger pressure can directly on the pot-like valve piston act.
  • the pressure spring by means of the tension member acts on the valve piston.
  • Another advantage, especially during assembly or repair, is given by the fact that the driving nose in the Snap ring arranged in the cup wall of the valve piston is.
  • the Driver nose in the cup wall of the valve piston is preferably a radial collar formed on the inside wall, which also centers the pulling part in the valve piston.
  • the seat disc and the one arranged over the snap ring on the pulling part Valve piston can be replaced in the simplest way. It is also conceivable to act on the valve piston Pressure spring against a screw elsewhere support over which the desired preload of the Pressure spring can be adjusted, this is an adjustment of the limit pressure enables.
  • the driving head by a circumferential flange formed on the cylindrical tension member is. Furthermore, it proves particularly in With regard to high functional reliability, it is advantageous that the pulling part over one, in the middle of the driving head arranged, reduced-diameter pin acts on the valve piston.
  • the driving head in Open state of the return valve an effective piston area formed.
  • the driving head in the open state of the return valve one in the effective Valve piston surface of the valve piston integrated partial piston surface formed.
  • the driving head or its effective piston surface integral part of the total piston area whereby it is further preferred that the now ring-shaped Valve piston surface at least in the active state the driving head piston surface is aligned.
  • valve piston hollow cylindrical with a circular cross-section is, the ring-shaped formed thereby End face forms the valve piston surface.
  • the driving head in the locked state is a designed with regard to the desired maximum pressure Partial piston surface forms.
  • the Carrying head with a closure body for example one Provide needle tip, which one with the pressure chamber connected hole closes. Exceeds the oil pressure one predefined by the bore diameter Height, so it is about that formed by the needle tip Partial piston surface of the driving head of the tension member and the valve piston is lifted out of the sealing seat, after which the valve piston and driving head of the Traction part formed much larger piston area in Effect occurs.
  • the diameter of the drain opening is smaller than the height a closed circumference of the valve piston.
  • Prefers is the diameter of the drain opening smaller than the height of one, the valve piston surface facing closed circumference of the valve piston, whereby the drain opening only after a first lifting of the valve piston is initially opened like a gap becomes.
  • the rear Valve piston surface one open to the outer shell of the pot Ring groove is provided. The latter is preferred in Closed state of the valve at least partially in Connection to the drain opening. The arrangement is chosen so that when lifting the valve piston opening the drain opening to drain the oil at the same time the separation of the open ring groove to the drain opening he follows. This is achieved in that the distance between the valve piston surface and the annular groove is larger than the diameter of the drain opening.
  • valve piston surface an axially directed passage opening goes out for Connection of the valve piston surface with the ring groove.
  • This passage opening serves on the one hand to closed operation the inevitable residual oil to let it run without causing an increase in pressure in the remaining gap results.
  • the passage opening is so small held that a shift when opening the valve of the piston because this is the escaping oil due to the amount also to a closure of the Lead opening leads.
  • the diameter of the flow opening is smaller than the diameter of an oil inlet bore of the valve.
  • the annular groove in the outer wall of the pot is trained at essentially planner Formation of the cylinder bore.
  • the annular groove in the cylinder bore is formed and the valve piston is assigned Has radial bore. The latter stands above the axially directed Flow opening with the valve piston surface in Connection.
  • the one trained in the cylinder bore The annular groove is preferably at the level of the drain opening intended.
  • both the cylinder bore and the outer wall of the pot each with an annular groove to accommodate residual oil to provide.
  • the return spring must be designed so that their strength in a certain position within the Working stroke of the hydraulic piston is no longer sufficient, keep the reset valve open.
  • Fig. 1 shows a return valve 1, for example for a hydraulic Press device 2.
  • This return valve 1 can be used can be found in manual or motor-operated hydraulic tools.
  • the return valve 1 consists essentially of a Valve piston 3 with a centrally arranged end face tapered needle tip 4, to form a, compared to the entire piston surface 5 much smaller and by the diameter of one with a pressure chamber 6 connected bore 7 defined piston area (Poppet valve effective area). The latter is in one, as in Fig. 1 illustrated output closure position by the Needle tip 4 closed.
  • the valve piston 3 is at the rear by a pressure spring 8 acted upon, whereby the needle tip 4 with a a maximum trigger pressure with a determining force is pressed against the bore 7. This is in essentially a pressure relief valve in seat design given.
  • the pressing device 2 For actuating the pressing device 2, for example for pressing on from cable lugs or connectors to electrical conductors or also for rivet connection or pipe pressing Hand or motor operated oil pumped into the pressure chamber 6.
  • the increasing oil pressure shifts one, in the pressure chamber 6 arranged hydraulic pistons 9 counter the force of a return spring 10 in the direction the workpiece to be pressed (see arrow a in Fig. 1).
  • valve piston 3 If the oil pressure now exceeds the predefined maximum value of, for example, 600 bar, the valve piston 3 is switched off his seat to bore 7 sealing against the force the pressure spring 8 moves, after which a sudden much larger piston area, namely the total piston area 5 of the valve piston 3 comes into effect.
  • the valve piston 3 receiving cylinder Discharge opening 12 By the return movement of the valve piston 3 is one in the arranged 11, the valve piston 3 receiving cylinder Discharge opening 12 at least partially exposed, for the backflow of the oil into the oil reservoir 13. (see Arrow x in Fig. 2.
  • the valve piston 3 can do this be fitted with little play, so that relatively little oil past this through a relief opening 14 can flow into the oil reservoir 13.
  • a desired automatic return of the hydraulic piston 9 is by means of the return spring 10 enables the latter to be dimensioned such that it by pressure on the hydraulic piston 9 in the pressure chamber 6 causes an oil pressure which is above the limit pressure of the return valve 1 in the longitudinal slide position 2 lies. This will make the return valve 1 kept open and the hydraulic piston 9 moved back (see arrow b in Fig. 2).
  • the return spring 10 is designed so that the hydraulic piston 9 completely up to the stop withdrawal begins. In this end position the oil reflux ends, what a lowering of the valve piston 3 in its Output lock position causes. The pressing device 2 is thereafter for the next work cycle without further mechanical preparatory work, such as lifting an mechanical lock ready.
  • the return valve releases 1 off and the limiting pressure drops conditionally by the area ratio of the piston areas to each other from 1: 400 to about 1.5 bar.
  • the return spring 10 is designed so that the pressure in the pressure chamber 6 when retracting the hydraulic piston 10 always at least Is 2.5 bar. The pressure difference of at least 1 bar becomes predominantly when the small ones flow through Bore 7 consumed as throttle loss and determined the oil flow and thus the retraction speed of the hydraulic piston 9.
  • valve 1 The advantage of such a return valve 1 is in that compared to the pressure relief valve to be provided anyway no additional parts, e.g. mechanical Locking elements are needed. Moreover valve 1 turns itself on without any required manual release back to its original state after falling below that which keeps the valve piston 3 open Limiting pressure according to FIG. 1 back.
  • Fig. 3 is an electromotive hand-held pressing device 2, with one as previously described Return valve.
  • a pressing device 2 is for example from the unpublished German patent application known with the file number 197 31 054.
  • the content of this patent application is hereby fully in the disclosure of the present invention included, also for the purpose, features of this patent application to be included in claims of the present invention.
  • An electric motor 15 is arranged in this pressing device 2, which has a reduction gear 16.
  • the latter acts on an eccentric via a shaft 17 18, which in turn has a roller bearing 19 on one High-pressure delivery piston 20 acts.
  • the electric motor 15 is driven by a Battery or one, integrated in a handle 21 Accumulator 22.
  • the hydraulic piston 9 is moved back via the return spring 10 as soon as - as described above - the return valve 1 due to exceeding the predetermined maximum pressure opens.
  • valve piston 3 of the return valve 1 on the back i.e. from his Piston surface 5 facing away, pot-shaped.
  • the inner pot protrudes axially aligned with the valve piston 3 Pull part 27 a, with a driving head 28, which by a circumferential flange on the cylindrical Train part 27 is formed.
  • the sealing seat can also be used in the simplest way Exchange way if necessary.
  • Valve piston 3 and seat disk 29 are in a transverse bore 30 of the pump cylinder 31 arranged and through this centered.
  • a snap ring 33 rear of the driving head 28 arranged to the valve piston 3 positively on the Holding the tension member 27 is inside the pot wall 32 .
  • the pressure spring 8 acts via the tension member 27 in the area of a centrally on the driving head 28 arranged, diameter-reduced pin 40 the valve piston 3 in the direction of the seat disk 29 on.
  • the pressure spring 8 is supported on a floor 34 of a likewise pot-like, screwed into the bore 30 Screw body 35 from.
  • the latter is penetrated in the axial direction by the Traction part 27, at its free, from the pump cylinder 31st protruding end of a lever arm 36 of an operating rocker 37 is articulated.
  • the latter is based approximately in the middle in the longitudinal direction over a cross section circular segment-shaped cams 38 on the From the outer surface of the pump cylinder 31 and forms on it free end of an actuation button that is led outwards 39 out.
  • valve piston 3 sits in this initial locking position axial distance to the screw body 35 in order to be exceeded of the maximum pressure an axial displacement of the To ensure valve piston 3.
  • adjusting gap is also to the oil reservoir 13 open relief bore 14 positioned.
  • valve piston 3 After falling below the piston surface 5 and defined by the force of the pressure spring 8 limiting pressure the valve piston 3 falls in automatically its initial lock position back.
  • the screw body 35 also serves to adjust the desired bias of the pressure spring and thus to Adjustment of the limit pressure.
  • FIG. 7 is an alternative embodiment of the Return valve 1 shown. Contrary to the previously described The exemplary embodiment is the valve piston 3 of the return valve 1 not pot-like, but hollow cylindrical with essentially constant strength the pot wall 32 is formed.
  • the valve piston thus formed 3 is penetrated by the axially aligned to this Switzerlandteil 27, its plate-like driving head 28 is caught by one, a driving nose forming radial collar 40 of the valve piston 3.
  • the latter protrudes from the pot wall 32 into the interior of the valve piston 3, the radial extent of this collar 40 is dimensioned such that this is also a centering of the tension member 27 causes.
  • the pressure spring 8 comprising the tension part 27 supports one end on the floor 34 of the screw body 35 and otherwise rearward of the radial collar 40 of the valve piston 3, to act on the valve piston 3 and also over the radial collar 40 of the tension member 27 in the valve closure position.
  • the distance b of the annular groove 42 to the piston surface 5 is dimensioned larger than the diameter c of the drain opening 12. It follows that in the locked state of the return valve 1 a closed scope of the valve piston 3, the drain opening 12 relative to the formed between piston surface 5 and seat disc 29 Gap closes.
  • the annular groove 42 stands over an axially directed passage opening 44 in connection with the valve piston surface 5.
  • the diameter of this passage opening 44 is kept low. In the embodiment shown corresponds to the flow opening diameter about half the diameter of the oil inlet bore 7.
  • the passage opening 44 mentioned serves in the stationary, closed operation, inevitable residual oil quantities in the annular groove 42 to drain what residual amounts over the gap 42 formed through the drain opening 12 can run without this an increase in pressure in the remaining gap between Piston surface 5 and seat disc 29 results.
  • the flow opening 44 is however kept so small that at one Opening the return valve 1 of the valve piston 3 without any problems is shifted to the open position, because the here in the space between piston surface 5 and Seat disc 29 entering oil due to the amount also leads to a closure of the passage opening 44.
  • the passage opening 44 therefore has no effect disadvantageous on the opening properties of the valve out.
  • valve piston 3 After falling below the piston surface 5 and the partial piston surface 41 of the driving head 28 and through the force of the pressure spring 8 defined limiting pressure the valve piston 3 falls automatically into its Exit closure position back, with residual quantities between Piston surface 5 and seat disc 29 through the passage opening 44 are passed into the annular groove 42, resulting in a faster pressure reduction and thus a faster Closing the valve leads.
  • the in the annular groove 42nd The residual oil quantity collected can be closed in accordance with Fig. 7 through the gap 43 through the drain opening 12 in drain the oil reservoir 13.
  • annular groove 42 in the cylinder bore 30 of the pump cylinder 31 provided at the level of the drain opening 12, wherein the ring groove height corresponds to the drain opening diameter.
  • the passage opening 44 opens in this embodiment in a radial bore 45 of the valve piston 3. This is spaced from the piston surface 5 by a dimension b, which dimension b is chosen larger than the diameter c of the drain opening 12.
  • the radial bore 45 is therefore largely covered radially through the bore wall of the pump cylinder 31 under Leaving a gap 43 to the annular groove 42, over which Gap 43 residual oil can run off.
  • This radial bore 45 is also preferably opposite arranged to the drain opening 12.
  • Fig. 8 1 The operation of the return valve shown in Fig. 8 1 corresponds to that described with reference to FIG. 7 Embodiment, being in both embodiments also a manual displacement of the valve piston 3 take place via the tension member 37 in the open position can.
  • one with an arm 36 is on the end the tension member 27 acting via a pump cylinder side stored pivot 46 or the like Schmdkewegliche Actuator rocker 37 provided.
  • used return valve 1 can also in hand or foot operated press tools use Find.
EP02000014A 1997-10-15 1998-10-15 Hydraulisches Pressgerät und Verfahren zum Betreiben desselben Withdrawn EP1244187A1 (de)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE19745483 1997-10-15
DE19745483 1997-10-15
DE19825160A DE19825160A1 (de) 1997-10-15 1998-06-05 Hydraulisches Preßgerät und Verfahren zum Betreiben desselben
DE19825160 1998-06-05
EP98951524A EP0944937B1 (de) 1997-10-15 1998-10-15 Hydraulisches pressgerät

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
EP98951524A Division EP0944937B1 (de) 1997-10-15 1998-10-15 Hydraulisches pressgerät

Publications (1)

Publication Number Publication Date
EP1244187A1 true EP1244187A1 (de) 2002-09-25

Family

ID=7845577

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02000014A Withdrawn EP1244187A1 (de) 1997-10-15 1998-10-15 Hydraulisches Pressgerät und Verfahren zum Betreiben desselben

Country Status (3)

Country Link
EP (1) EP1244187A1 (ja)
CH (1) CH0944937H2 (ja)
DE (3) DE19825160A1 (ja)

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ITBZ20100027A1 (it) * 2010-07-13 2012-01-14 Intercable Srl Attrezzo per l'azionamento di teste per lavorazioni da taglio o da compressione e procedimento per il comando della corsa di apertura delle stesse
WO2012055901A1 (de) * 2010-10-28 2012-05-03 Novopress Gmbh Pressen Und Presswerkzeuge & Co. Kg Hydraulik-presswerkzeug sowie verfahren zum steuern eines hydraulik-presswerkzeugs
US9242422B2 (en) 2011-06-16 2016-01-26 Von Arx Ag Quick-connect coupling
US9434119B2 (en) 2011-06-16 2016-09-06 Von Arx Ag Quick-connect coupling
US9573263B2 (en) 2012-04-18 2017-02-21 Ridge Tool Company Work tools having interchangeable work heads

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DE19926481B4 (de) * 1999-06-10 2013-09-12 Gustav Klauke Gmbh Hydraulisches Arbeitsgerät
DE19944229B4 (de) * 1999-09-15 2016-07-28 Gustav Klauke Gmbh Hydraulisches Handpressgerät und auswechselbarer Gerätekopf hierfür
IT1316351B1 (it) * 2000-02-07 2003-04-10 Cbc Spa Dispositivo strozzatubi a trasmissione idraulica automatico
DE10031073B4 (de) * 2000-06-30 2016-11-24 Gustav Klauke Gmbh Verfahren zum Vernieten
DE10124267B4 (de) * 2001-05-18 2014-04-10 Gustav Klauke Gmbh Hydraulisches Pressgerät
DE102006003044B4 (de) 2006-01-23 2015-10-08 Gustav Klauke Gmbh Hydraulisch angetriebenes Verpressgerät sowie Verfahren zum Verpressen eines Fittings
DE102006026552A1 (de) * 2006-06-08 2007-12-13 Gustav Klauke Gmbh Verfahren zum Betreiben eines hydraulischen Verpressgerätes sowie hydraulisches Verpressgerät mit einer Hydraulikpumpe
DE102007007294B3 (de) * 2007-02-14 2008-07-10 Rothenberger Ag Antriebsgerät mit einer Kupplung für Werkzeugköpfe
AU2008249954B2 (en) * 2007-05-16 2013-07-04 Gustav Klauke Gmbh Method for the operation of a motor-driven hand-held pressing apparatus, and hand-held pressing apparatus
DE202007009629U1 (de) 2007-07-10 2007-10-11 Joiner's Bench Ag Hydraulisches Pressgerät, insbesondere zum Verbinden von Werkstücken
DE102008028957A1 (de) 2008-06-18 2009-12-24 Gustav Klauke Gmbh Verfahren zum Betreiben eines hydraulischen Verpressgerätes und hydraulisches Verpressgerät
DE102011011742A1 (de) * 2011-02-18 2012-08-23 Novopress Gmbh Pressen Und Presswerkzeuge & Co. Kg Verfahren zum automatischen Steuern eines elektro-hydraulischen Presswerkzeuges
DE202011109251U1 (de) 2011-12-17 2013-03-18 Novopress Gmbh Pressen Und Presswerkzeuge & Co. Kg Elektrohydraulisches Pressgerät
DE202012003758U1 (de) * 2012-04-13 2013-07-17 Novopress Gmbh Pressen Und Presswerkzeuge & Co. Kg Antriebseinrichtung für ein Hydraulik-Presswerkzeug
EP3078456B1 (de) * 2015-04-10 2017-12-06 HAWE Hydraulik SE Hydraulikantrieb
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ITBZ20100027A1 (it) * 2010-07-13 2012-01-14 Intercable Srl Attrezzo per l'azionamento di teste per lavorazioni da taglio o da compressione e procedimento per il comando della corsa di apertura delle stesse
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US9873187B2 (en) 2010-10-28 2018-01-23 Novopress Gmbh Pressen Und Presswerkzeuge & Co. Kg Hydraulic pressing tool and method for controlling a hydraulic pressing tool
US9242422B2 (en) 2011-06-16 2016-01-26 Von Arx Ag Quick-connect coupling
US9434119B2 (en) 2011-06-16 2016-09-06 Von Arx Ag Quick-connect coupling
US9573263B2 (en) 2012-04-18 2017-02-21 Ridge Tool Company Work tools having interchangeable work heads

Also Published As

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DE19825160A1 (de) 1999-04-22
DE29824642U1 (de) 2002-01-10
DE59803508D1 (de) 2002-05-02
DE59803508C5 (de) 2018-10-04
CH0944937H2 (ja) 2016-01-15

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