EP2448720B1 - Dispositif de pressage hydraulique - Google Patents

Dispositif de pressage hydraulique Download PDF

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Publication number
EP2448720B1
EP2448720B1 EP10727433A EP10727433A EP2448720B1 EP 2448720 B1 EP2448720 B1 EP 2448720B1 EP 10727433 A EP10727433 A EP 10727433A EP 10727433 A EP10727433 A EP 10727433A EP 2448720 B1 EP2448720 B1 EP 2448720B1
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EP
European Patent Office
Prior art keywords
hydraulic
control valve
valve
return
medium
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Active
Application number
EP10727433A
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German (de)
English (en)
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EP2448720A1 (fr
Inventor
Egbert Frenken
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Gustav Klauke GmbH
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Gustav Klauke GmbH
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Application filed by Gustav Klauke GmbH filed Critical Gustav Klauke GmbH
Priority to PL10727433T priority Critical patent/PL2448720T3/pl
Publication of EP2448720A1 publication Critical patent/EP2448720A1/fr
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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
    • B21D22/00—Shaping without cutting, by stamping, spinning, or deep-drawing
    • B21D22/02—Stamping using rigid devices or tools
    • 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
    • B21D39/048—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 using presses for radially crimping tubular elements
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/20—Other details, e.g. assembly with regulating devices

Definitions

  • the invention relates to a hydraulic pressing device with a fixed part and a moving part, wherein the moving part is moved by a hydraulic piston relative to the fixed part and by means of a return spring in an initial position réellebewegbar, wherein further the return movement in response to a predetermined pressing pressure can be triggered by addressing a Return valve, wherein, in addition, a control valve is provided which, in addition to the return valve in the open state, a hydraulic fluid discharge free and, based on a state when conveying hydraulic fluid, a hydraulic fluid inflow and outflow side has
  • Such pressing devices are known in many embodiments WO 99/19947 to refer.
  • the WO 98/24570 relating to an application as a punching device
  • the WO 02/062504 concerning an application as expansion tool
  • the WO 02/00368 concerning an application as a riveting tool
  • Such a pressing device is also for example from the DE 20 2004 000 215 U1
  • the control valve arranged in a hydraulic line leading from the hydraulic fluid pump to the hydraulic piston leading hydraulic cylinder is penetrated by the hydraulic fluid delivered by the pump according to a design as a check valve from the inflow side to the outflow side.
  • the hydraulic fluid pump is switched off, the fluid pressure acting on the downstream side, together with a biasing spring acting in the same direction, causes the control valve to move to the open position, thus releasing the hydraulic fluid discharge associated with the downstream side.
  • the control valve does not open at higher system pressure, there is still no opening of the control valve at the beginning of the hydraulic fluid return when the return valve has opened after the pressing operation has been completed.
  • the invention is concerned with the task of making such a hydraulic pressing device with regard to the response of the control valve advantageous.
  • a hydraulic pump is provided, from which pump a (first) hydraulic fluid flow path leads to the control valve and a further (second) hydraulic fluid flow path leads directly to the return valve.
  • the from the hydraulic pump to the control valve and preferably also to a return piston receiving Hydraulic cylinder leading hydraulic fluid supply line is also given directly from the hydraulic fluid pump to the control valve.
  • the said hydraulic fluid flow paths can also partially coincide. It is essential that due to the direct connection, the hydraulic fluid flows through the supply line to the control valve or to the return valve, without first, about to flow with respect to the return valve, via the control valve. As a result, with respect to the two valves, a parallel circuit is provided starting from the hydraulic fluid pump.
  • Hydraulic fluid inlet (from the pump) and hydraulic fluid drain through the (open) return valve are located hydraulically on the same side of the control valve.
  • the connection to the cylinder chamber (moving part) is located hydraulically on the other side of the control valve (or in the bypass for this purpose).
  • the return valve Seen from the moving part, the return valve may be arranged hydraulically after the control valve or, at least in addition, in parallel with the control valve. Essential is the possible compact arrangement of said valves and the hydraulic lines.
  • the biasing the control valve in the open position spring can be formed with a relatively low spring force.
  • no opening of the control valve is given even when stopping the pump in the course of the initiation of the compression process or in an already more advanced compression.
  • the control valve moves only in its open position, if in addition, according to open return valve, a negative pressure of the control valve or a pressurization pressure difference sets
  • a hydraulic hand press which is preferred here, the compression by a manual actuation of the pump, which is preferably driven by an electric motor achieved. If the depression of a corresponding switch is interrupted, the pump also stops running. Press jaws of a pressing device remain in a certain position.
  • control valve is chosen for clear conceptual separation. You can also call this valve as another return valve, for example.
  • control valve is designed as a seat valve.
  • the valve By driving against a seat stop, the valve closes the hydraulic fluid drain.
  • the closed by the seat valve opening extends (relative to an axis of the opening) in the direction of displacement of the control valve.
  • the closed control valve is acted upon by a differential force formed by the pressure in the hydraulic medium reservoir and the pressure in the hydraulic fluid supply line. Since in almost all operating conditions, the pressure in the hydraulic fluid supply line is higher than the pressure in the hydraulic fluid reservoir, this results in a locking force of the control valve when it is in the closed position. Although initially a higher pressure is required to move the control valve in the closed position, then, when it is in the closed position, also a lower pressure in the hydraulic medium supply line, as long as this pressure is still sufficiently higher than that Pressure in the hydraulic fluid reservoir.
  • the pressure in the hydraulic fluid reservoir can correspond to the ambient pressure or even be lower than the ambient pressure, so be a negative pressure. The latter especially if the pump with high flow rate works.
  • the higher pressure which serves to displace the control valve into the closed position arises due to the pressure loss of the flowing hydraulic fluid via the control valve, as seen from the inflow side to the outflow side. It is, as it were, a dynamic pressure due to the movement of the hydraulic fluid or the pressure difference resulting from the control valve.
  • the control valve responds to the direction of flow of the hydraulic fluid.
  • the pressure in the hydraulic fluid supply line accordingly increases upon initiation of a squeeze operation from ambient pressure (or slightly above) to the squeeze trigger pressure.
  • a trigger pressure can for example be between 300 and 700 bar.
  • the pressure in the hydraulic fluid supply line which then depending on the configuration, as described below, hydraulic fluid runs back into the storage room, for example, 10 and 0.5 bar (pressure) , In this case, all intermediate values, in particular in steps of 0.1 bar, are included in the disclosure.
  • the hydraulic fluid pump delivers via a delivery line into a first branch line leading to the control valve and a second branch line leading to the return valve.
  • the return valve is closed or is closed, for example, by releasing an opening detent in the course of this triggering.
  • the hydraulic fluid is therefore only in this branch line, but does not flow. However, it flows through the control valve and the hydraulic fluid supply line then into the cylinder chamber.
  • a bypass can be provided directly in the cylinder chamber.
  • the promotion to the return valve is carried out according to line or not only via the control valve, but, if appropriate, in parallel thereto.
  • the return valve is related to the hydraulic fluid delivery hydraulically connected in parallel to the control valve.
  • the return valve when the return valve is opened via the return valve, the hydraulic fluid flowing out initially, preferably as a whole, flows via the control valve.
  • the return valve is hydraulically connected downstream of the control valve at draining hydraulic fluid. But it can also be provided that it flows only partially through the control valve. On the other hand, it can flow through a line leading directly from the cylinder to the return valve, this line furthermore preferably having a throttle point. It may also flow in total via said separate line from the cylinder space to the return valve. Even in the latter case, however, it is provided that this leading to the return valve line is in line connection with the control valve, and to the upstream side of the control valve. Also in this structural design, therefore, in the case of the return of hydraulic fluid, the respective pressurization is given on the upstream side of the control valve.
  • the control valve may be biased by a spring in its open position.
  • This bias is preferably chosen to be lower in this case than corresponds to a force acting on the control valve by a spring action of the return piston force.
  • the caused by the spring action of the return piston in the case of the return in the hydraulic medium supply line pressure, which, as stated, for example, between 0.5 and 5 bar may be, corresponding to the hydraulically effective surface of the control valve to a force acting thereon.
  • the said force exerted by the spring action of the return piston force is greater than that corresponding to the force acting on the control valve in the opening direction spring force.
  • a realistic one Size for the force of this acting on the control valve in the opening direction spring is for example between 0.1 and 1 Newton, more preferably between 0.2 and 0.4 Newton, in which range also all intermediate values, in particular in 1/10 Newton Steps are included.
  • hydraulic fluid at least partially flows via the control valve to the return valve
  • the control valve in its open position at the same time the hydraulic fluid supply line, via which otherwise hydraulic fluid to the return valve can flow, blocked.
  • this blocking may preferably also be given in the sense of a seat valve.
  • the outflow can then be given via an example provided direct line connection from the hydraulic cylinder to the return valve, as already mentioned.
  • the outflow via the return valve can thereby be completely interrupted. The return valve goes in this case, because of the associated pressure drop, immediately in its closed position.
  • the return valve is set to the highest pressure, the pressure to be achieved.
  • the control valve allows due to the (further) pressure drop resulting from its opening an automatic control of the return valve in the closed position, with simultaneous opening of a (further) discharge path for the hydraulic fluid. This can be achieved in the desired manner in the course of carrying out a pressing process first, take each intermediate position and then continue the pressing process. After carrying out the pressing operation can be achieved by simply re-actuation of the pump stopping the moving part, ie usually the return piston, and made from this position from the next pressing.
  • the control valve consists in detail of a valve closure body, which cooperates with a - fixed to the housing - valve seat.
  • the valve closure body passes through a compensating part which also follows the movement of the valve closure body.
  • the compensation part thus moves with the valve closure body from the closed position to the open position and vice versa.
  • the compensating part is designed such that the valve closure body can move transversely to its direction of movement when moving from the closed position to the open position or vice versa.
  • the valve closure body is also preferably received in the hydraulic medium supply line with a corresponding play. This mobility of the valve closure body ensures that even with not exactly aligned alignment of the valve seat with the valve closure body results in a reliable closure of the control valve.
  • the valve closure body accordingly has sufficient movement possibility with respect to possible manufacturing tolerances.
  • the compensating part may be formed, for example, in the form of a washer.
  • the compensation part for example, specifically the washer, is preferably not sealingly fitted in the more preferably at least in this area cylindrically shaped hydraulic fluid supply line. Rather, here also a suitable, albeit very small, radial gap can remain, which allows a certain flow of hydraulic fluid. In any case, such a gap in the idle state allows the pressure equalization via the compensating part.
  • a realistic size for such a gap is about 1/100 to 2/100 mm.
  • the possibility of movement of the valve closure part transverse to its direction of movement with respect to an opening or closing operation can be 2/100 to 10/100 or more hundredths of a millimeter, for example up to a 1/2 mm.
  • Fig. 1 Shown and described, first with reference to Fig. 1
  • the moving part 3 is moved by means of a hydraulic piston 4 relative to the fixed part 2, which can also be considered as the entire housing, the hydraulic piston 4 is moved back by means of a return spring 5 in its initial position and biased in the non-use state to the starting position thereby.
  • the return movement of the hydraulic piston 4 can be triggered by the response of a return valve 6 at the end of a pressing operation.
  • This return valve 6 is formed in the embodiment and operates as described in the EP 0 944 937 B1
  • the disclosure content of this document is hereby incorporated in full in the disclosure with regard to the design of this return valve and the corresponding mode of operation Application, also to include one or more of the features known there in claims of this application.
  • a control valve 7 which influences the closure characteristic of the return valve 6. Because preferably, the return valve 6 is no longer open until complete return of the hydraulic piston 4. According to the control valve 7 results in the opening state of this control valve 7 such a strong pressure drop before the return valve 6, that it prematurely in this sense, before the hydraulic piston 4 reaches its end-return position closes. A further return movement of the hydraulic piston 4 then takes place only by outflow of hydraulic fluid via the discharge opening 8 released by the control valve 7 in the opening state into the hydraulic fluid reservoir 9.
  • control valve 7 has an inflow side 10 and an outflow side 11.
  • the inflow side 10 refers to the fact that the control valve 7 is acted upon by the hydraulic medium on this side during the delivery of hydraulic fluid by means of the hydraulic fluid pump 12. Via the outflow side 11, the hydraulic fluid flows through the hydraulic medium line 13 into the hydraulic cylinder 14, in which the hydraulic piston 4 is accommodated.
  • the hydraulic pump 12 may be a piston pump as shown. But it may also be, for example, a screw pump. The latter has the advantage that it is pumped with a continuous pressure. When pumping hydraulic fluid through the open control valve 7, which is associated with this, but also practically immediately displaced into the closed position, resulting throttling effect, a pressure drop of, for example, 1 bar, which causes said shift to the closed position
  • the open position according to Fig. 3 on the one hand can be provided so that a dense or nearly dense valve seat 17 results
  • An opening seat portion 18 of the control valve 7 sealingly cooperates with the housing 36, which has a valve seat with ausformende constriction in this area.
  • the design can also be provided so that in the opening state of the control valve 7 according to Fig. 3 still a flow of hydraulic fluid to the return valve 6 remains.
  • the spring 5 relaxes and the pressure exerted on the hydraulic fluid pressure is reduced. Accordingly, the return valve 6 can then be moved into a closed position, if a required critical pressure, which is required to maintain the opening state of the return valve 6, is exceeded.
  • the closed position of the return valve 6 is reached before the hydraulic piston 4 is completely moved back to its final position.
  • the setting can also be made so that, approximately to achieve the fastest possible retraction of the hydraulic piston, the control valve 7, as well as Return valve 6, remain in the open position until reaching the end position.
  • the setting is provided so that the return valve 6 immediately moves into its closed position when the control valve 7 opens.
  • Fig. 4 . 5 be trained. This is preferably designed as a throttle point. According to Fig. 5 it may also be closed by a check valve 20, so that only when pumping hydraulic fluid through the pump 12 hydraulic fluid flows through the delivery path 19.
  • control valve 7 is made so that the pressure drop described in the case that the return valve 6 triggers, each shift the control valve 7 in the open position. Due to the bias by means of the spring 16, the control valve then remains in this open position.
  • the pump 12 can be actuated again at any time by a switch actuation.
  • the control valve 7 moves in the closed position, whereby the hydraulic piston 4 is stopped at the then reached position in the hydraulic cylinder 14. Without a complete retraction is required, then from this position, the next compression can be performed.
  • the control valve 7 is seen to be formed in further detail with a front cone-shaped seating area 22, which merges via a cylinder portion 23 into an enlarged flange area 24. At the end of this flange region 24, a throttling region 25 adjoins.
  • a throttling region 25 adjoins.
  • an elongate shaft 27 is formed, which extends with an extension 29 into an inlet bore 28 of the return valve 6
  • the inlet bore 28 continues in a perpendicular thereto extending continuation 30, in which the return valve 6 is arranged
  • the shaft 27 passes through the room 21, which is first reached by funded by the pump 12 hydraulic fluid.
  • This space 21 is clearly branched into an inlet to the control valve 7 and an inlet to the return valve 6.
  • bypass line 19 if this is provided.
  • a baffle 31 is provided on the supply chamber side. Even with a small diameter of the drain opening 8, a thin, strong hydraulic fluid jet caused thereby can not lead to damage of the opposite wall 32 of the storage space 9. Especially since the wall 32 is preferably formed by a resilient rubber material.
  • the baffle 31 is formed in detail by a T-tube, wherein a portion of the T-tube is formed as Einschraubabites, the end forms the seat for the control valve 7 and the other portion of the T-tube forms said baffle.
  • the compensation part 33 is designed as an annular body, with an inner diameter Di, which is smaller than an outer diameter Da of the flange portion 24.
  • the compensating part 33 is seat area side of the flange portion 24, so in the embodiment of the cylinder portion 23, of the valve closure body interspersed by the inner diameter Di of the compensating part 33 leaves a gap s with respect to said cylinder portion 23. This gap s allows the valve closure body to move transversely to its longitudinal extent. This automatically results in a certain transverse displacement when, for example, the counter-valve seat forming bore 34 of the here formed by the T-tube valve seat portion 34 should not be aligned with a longitudinal center axis of the valve body.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Check Valves (AREA)
  • Safety Valves (AREA)
  • Press Drives And Press Lines (AREA)
  • Fluid-Driven Valves (AREA)

Claims (10)

  1. Dispositif de compression hydraulique (1) avec une partie fixe (2) et une partie mobile (3), la partie mobile étant déplacée par un piston hydraulique (4) par rapport à la partie fixe (2) et replaçable dans une position de départ au moyen d'un ressort de rappel (5), le mouvement de recul étant en outre déclenchable en fonction d'une compression prédéterminée par la sollicitation d'un clapet antiretour (6), une soupape de commande (7) étant en outre prévue qui libère en outre un écoulement d'agent hydraulique (8) vers le clapet antiretour (6) dans la position d'ouverture et, par rapport à un état pour le transport d'agents hydrauliques, présente un côté entrée et sortie de l'agent hydraulique, caractérisé en ce que la soupape de commande (7) lors de l'ouverture du clapet antiretour (6) est alimentée par la pression de l'agent hydraulique refluant côté entrée et sortie, la pression côté entrée étant inférieure en raison de l'étranglement.
  2. Dispositif de compression hydraulique selon la revendication 1, caractérisé en ce qu'une pompe d'agent hydraulique (12) est prévue, une voie d'écoulement de l'agent hydraulique conduisant, à partir de ladite pompe, vers la soupape de commande et en ce qu'une voie d'écoulement de l'agent hydraulique conduit directement, depuis la pompe d'agent hydraulique, jusqu'au clapet antiretour (6).
  3. Dispositif de compression selon l'une des revendications qui précèdent, caractérisé en ce que la soupape de commande (7) a la forme d'une soupape à siège.
  4. Dispositif de compression selon l'une des revendications qui précèdent, caractérisé en ce que la soupape de commande (7) est disposée dans une conduite d'amenée menant à un cylindre hydraulique (14) comprenant l'un des pistons hydrauliques (4).
  5. Dispositif de compression selon l'une des revendications qui précèdent, caractérisé en ce que la soupape de commande fermée est alimentée par une force différentielle formée par la pression dans la chambre de réserve de l'agent hydraulique et la conduite d'amenée de l'agent hydraulique.
  6. Dispositif de compression selon l'une des revendications qui précèdent, caractérisé en ce que la conduite d'amenée de l'agent hydraulique menant de la pompe au cylindre présente une liaison immédiate tant avec le clapet antiretour qu'avec la soupape de commande.
  7. Dispositif de compression selon l'une des revendications qui précèdent, caractérisé en ce que l'agent hydraulique sortant via le clapet antiretour s'écoule d'abord via la soupape de commande.
  8. Dispositif de compression selon l'une des revendications qui précèdent, caractérisé en ce qu'une force de précompression agissant sur la soupape de commande est plus réduite dans la position d'ouverture que ce qui correspond à une force agissant sur la soupape de commande par une alimentation à ressort du piston de retour.
  9. Dispositif de compression selon l'une des revendications qui précèdent, caractérisé en ce que la soupape de commande, en position d'ouverture, bloque un reflux de l'agent hydraulique en direction du clapet antiretour.
  10. Dispositif de compression selon l'une des revendications qui précèdent, caractérisé en ce que la soupape de commande présente un corps de fermeture qui traverse une partie d'égalisation accomplissant également le mouvement du corps de fermeture de la soupape.
EP10727433A 2009-07-02 2010-07-01 Dispositif de pressage hydraulique Active EP2448720B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL10727433T PL2448720T3 (pl) 2009-07-02 2010-07-01 Prasa hydrauliczna

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102009031678 2009-07-02
DE102009026273A DE102009026273A1 (de) 2009-07-02 2009-07-29 Hydraulisches Pressgerät
PCT/EP2010/059356 WO2011000907A1 (fr) 2009-07-02 2010-07-01 Presse hydraulique

Publications (2)

Publication Number Publication Date
EP2448720A1 EP2448720A1 (fr) 2012-05-09
EP2448720B1 true EP2448720B1 (fr) 2013-03-20

Family

ID=43298832

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10727433A Active EP2448720B1 (fr) 2009-07-02 2010-07-01 Dispositif de pressage hydraulique

Country Status (12)

Country Link
US (1) US8844436B2 (fr)
EP (1) EP2448720B1 (fr)
KR (1) KR101821238B1 (fr)
CN (1) CN102481689B (fr)
AU (1) AU2010268021B2 (fr)
BR (1) BRPI1015945A2 (fr)
DE (1) DE102009026273A1 (fr)
ES (1) ES2411881T3 (fr)
MX (1) MX2012000079A (fr)
PL (1) PL2448720T3 (fr)
RU (1) RU2532224C2 (fr)
WO (1) WO2011000907A1 (fr)

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DE102012105383A1 (de) * 2012-06-21 2013-12-24 Gustav Klauke Gmbh Schneidgerät
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CN103072124B (zh) * 2012-12-27 2015-11-18 台州巨力工具有限公司 一种电动液压工具
DE102013107294A1 (de) 2013-07-10 2015-01-15 Gustav Klauke Gmbh Handarbeitsgerät und Hand-Aufweitgerät
EP2835540B1 (fr) 2013-08-08 2016-04-27 HAWE Hydraulik SE Entraînement hydraulique
US10226826B2 (en) 2013-10-22 2019-03-12 Milwaukee Electric Tool Corporation Hydraulic power tool
CN107107317B (zh) 2014-10-06 2019-09-17 米沃奇电动工具公司 液压电动工具
US10312653B2 (en) 2015-05-06 2019-06-04 Milwaukee Electric Tool Corporation Hydraulic tool
DE102016102960A1 (de) * 2016-02-19 2017-08-24 Viega Technology Gmbh & Co. Kg Vorrichtung und Verfahren zum Übersetzen einer mechanischen Kraft zum Antreiben einer Pressvorrichtung für Pressfittings
US10967442B2 (en) 2016-06-08 2021-04-06 Milwaukee Electric Tool Corporation Tool head
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US20120160065A1 (en) 2012-06-28
KR20120052957A (ko) 2012-05-24
RU2012103481A (ru) 2013-08-10
EP2448720A1 (fr) 2012-05-09
CN102481689A (zh) 2012-05-30
WO2011000907A1 (fr) 2011-01-06
RU2532224C2 (ru) 2014-10-27
AU2010268021B2 (en) 2014-07-10
PL2448720T3 (pl) 2013-07-31
BRPI1015945A2 (pt) 2016-04-19
ES2411881T3 (es) 2013-07-09
CN102481689B (zh) 2014-12-10
MX2012000079A (es) 2012-02-29
DE102009026273A1 (de) 2011-01-05
AU2010268021A1 (en) 2012-02-02
KR101821238B1 (ko) 2018-01-23
US8844436B2 (en) 2014-09-30

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