EP1400313B1 - Clé à cliquet hydraulique avec entraínement hydraulique à piston-cylindre à double effet - Google Patents

Clé à cliquet hydraulique avec entraínement hydraulique à piston-cylindre à double effet Download PDF

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Publication number
EP1400313B1
EP1400313B1 EP02020916A EP02020916A EP1400313B1 EP 1400313 B1 EP1400313 B1 EP 1400313B1 EP 02020916 A EP02020916 A EP 02020916A EP 02020916 A EP02020916 A EP 02020916A EP 1400313 B1 EP1400313 B1 EP 1400313B1
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EP
European Patent Office
Prior art keywords
pump
hydraulic
stroke
piston
chamber
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Expired - Lifetime
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EP02020916A
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German (de)
English (en)
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EP1400313A1 (fr
Inventor
Alexander Kipfelsberger
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Individual
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Individual
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Priority to EP02020916A priority Critical patent/EP1400313B1/fr
Priority to DE50203771T priority patent/DE50203771D1/de
Priority to AT02020916T priority patent/ATE300396T1/de
Priority to US10/666,943 priority patent/US6966240B2/en
Publication of EP1400313A1 publication Critical patent/EP1400313A1/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
    • B25B23/00—Details of, or accessories for, spanners, wrenches, screwdrivers
    • B25B23/14—Arrangement of torque limiters or torque indicators in wrenches or screwdrivers
    • B25B23/145—Arrangement of torque limiters or torque indicators in wrenches or screwdrivers specially adapted for fluid operated wrenches or screwdrivers
    • 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
    • B25B21/00—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose
    • B25B21/004—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose of the ratchet type
    • B25B21/005—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose of the ratchet type driven by a radially acting hydraulic or pneumatic piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
    • F15B7/001—With multiple inputs, e.g. for dual control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
    • F15B7/005—With rotary or crank input
    • F15B7/006—Rotary pump input
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
    • F15B7/04—In which the ratio between pump stroke and motor stroke varies with the resistance against the motor

Definitions

  • the invention relates to a hydraulic ratchet wrench with a double-acting Hydraulic cylinder-piston drive according to the preamble of the claim 1, which is known from the document DE 37 19 893 A.
  • a well-known hydraulic ratchet wrench with a double acting hydraulic cylinder piston drive is a piston as Disk piston slidably guided in the hydraulic cylinder, the one tight the hydraulic cylinder led out piston rod for ratchet operation having.
  • In the hydraulic cylinder is a working stroke by the displaceable piston as a high pressure chamber on a piston side of the piston and a remindhubhunt as a low pressure chamber on the piston side with the piston rod educated.
  • the well-known hydraulic ratchet wrench also includes a two-stage Hydraulic pump assembly with a gear pump and a piston pump.
  • the gear pump and the piston pump are by means of a via a Pump motor control controllable pump motor through its output shaft drivable, the gear pump due to their construction a relative large flow hydraulic oil per engine revolution up to a pressure of can pump about 100 bar and the piston pump in contrast, a relative small flow per engine revolution, however, up to much higher Press to pump is able.
  • the pump assembly is via a hydraulic control unit connected to the working stroke chamber and the gearhubsch.
  • This known pump arrangement is via the hydraulic control unit so controlled that in a first phase of a screwing process, in which in the Ratchet unit still no or only a small torque is applied the working stroke chamber pumping over the fast and with large delivery volume Gear pump is filled.
  • a second phase at the end of the screwing process if a high screw-on torque is to be applied, is decoupled by the hydraulic control unit, the gear pump and the Piston pump switched on, which then with this in the Hähubhunt pumped with high pressure.
  • the necessary switches in the hydraulic lines in particular also the switching from Vor- Return to the hydraulic cylinder lifting chambers follows through expensive, susceptible to interference Valves, in particular by solenoid valves, which have their own power supply need.
  • the object of the invention is a generic hydraulic ratchet wrench with a double-acting hydraulic cylinder-piston drive so educate that a cheaper, more reliable and easier Construction in combination with low weight and small dimensions with low energy consumption is possible.
  • a first gear pump port is provided with a working-stroke chamber hydraulic oil passage with the working chamber and a second Gear pump connection with a return stroke hydraulic oil pipe with connected to the remindhubsch.
  • the working-stroke chamber hydraulic oil passage is at a first intake port via a first intake manifold with a first intake check valve and the return stroke hydraulic oil passage at a second Intake connection point via a second intake manifold with a second suction check valve with the hydraulic oil volume of an oil tank connected.
  • a high-pressure check valve with a blocking action in the direction of the first Intake connection point arranged in the working stroke chamber hydraulic oil line.
  • the piston pump is designed as a radial piston pump, possibly also different constructed piston pumps can be used with appropriate effect.
  • Preferred is an embodiment of a radial piston pump with three against each other staggered small pump cylinders, the pistons be driven for example via an eccentric disc.
  • the radial piston pump is at a piston pump suction inlet through a piston pump suction line connected to the hydraulic oil volume and to a piston pump delivery outlet through a piston pump delivery line between the high pressure check valve and the working stroke chamber with the working stroke chamber hydraulic oil passage connected.
  • a hydraulic oil return line leading into the oil tank is provided.
  • This hydraulic oil return line is via a pressure-controlled low-pressure limiting valve between the first intake connection point and the high pressure check valve with the working stroke chamber hydraulic oil line connected, wherein a return flow of hydraulic oil from the working-stroke chamber hydraulic oil line to the oil tank when reaching a certain low pressure is releasable.
  • the hydraulic return line is also over by a function of a pressure in the return stroke hydraulic oil pipe pressure-controlled Entsperr-check valve with reverse direction in the backflow between the High-pressure check valve and the working stroke chamber with the working-stroke chamber hydraulic oil line connected.
  • the pump motor is equipped with the pump motor control for a working stroke
  • a direction of rotation can be controlled, so that at the first gear pump connection the delivery outlet and at the second gear pump connection the suction inlet lies.
  • the pump motor For a return stroke, however, the pump motor to a reverse direction controllable, so that then at the first gear pump connection the suction inlet and at the second gear pump connection the delivery outlet lies.
  • Due to the structure of the radial piston pump promotes this in each of the driving directions in the same conveying direction. Possibly. are also in the direction of rotation and conveying direction reversible rotary element pumps with used other rotary elements than in a gear pump, provided they have a corresponding effect.
  • the gear pump with a large flow of, for example up to 6 liters per minute causes a fast piston feed, wherein also the delivery volume of the radial piston pump is switched on. to required associated emptying the return stroke this is fluid with the other acting as a suction port gear pump port connected. Because of the volume of the piston rod, the in the working stroke chamber inflowing hydraulic oil volume greater than that the return stroke chamber displaced hydraulic oil volume is can the gear pump the differential volume across the second intake manifold and the second Suction check valve still suck.
  • Low pressure for example, of 70 bar opens this, causing the Gear pump then promotes via the hydraulic oil return line into the oil tank.
  • the high pressure check valve and the radial piston pump closes promotes with smaller flow of, for example, up to 0.6 liters per minute in a second screw phase in the working stroke chamber after for a high screwing torque high pressures of for example up to 700 bar are reachable.
  • the resulting flow path switches take advantage of automatic, so that no externally controlled solenoid valves required are.
  • Gear pumps with the features of claim 4 with a maximum Delivery pressure of about 100 bar and, for example, a flow rate of 0-6 Liters per minute are commercially available.
  • a gear pump is an operation of the arrangement in the low pressure range of up to 70 bar expedient and has proven to be suitable in practical testing.
  • radial piston pump with the features according to claim 5 with a maximum discharge pressure of about 700 bar are commercially available and for the proposed arrangement well suited.
  • the Pump motor control in particular the right-left rotation control can be manually or automatically activated, the screwing manually, time-dependent or working pressure-dependent as well as torque-dependent controllable can be executed.
  • a current screwing torque as control parameter can in a conventional manner directly via a torque transducer or indirectly over the current assigned working pressure or the current power consumption of the pump motor can be determined.
  • the pump motor can after Claim 8 be an electric motor, an air motor or a hydraulic motor.
  • FIG. 1 the structure of a hydraulic pump assembly 1 of a hydraulic ratchet wrench shown.
  • An oil tank 2 for hydraulic oil is through a cover plate 3, on which a pump motor 4 with a vertical motor output shaft is mounted.
  • a gear pump and a radial piston pump disposed from the engine output shaft are driven.
  • On the cover plate 3 is also a hydraulic control unit 5, the circuit configuration explained in connection with FIG becomes.
  • To the hydraulic control unit 5 is a high pressure gauge. 6 connected. There are also actuations for shut-off valves and control valves recognizable. From the hydraulic control unit 5, a power stroke hydraulic oil pipe lead 7 and a return stroke hydraulic oil passage 8 to a not shown hydraulic cylinder 9.
  • a tank level indicator 10 and a tank vent 11 are shown.
  • a hydraulic ratchet wrench 12 is shown in a hydraulic cylinder 13 .
  • a hydraulic cylinder 13 is a piston slidably received as a disc piston 14, wherein a Piston rod 15 or possibly an extension in a only schematically indicated Screw ratchet 16 engages the actuation.
  • a Hähubhunt in the hydraulic cylinder 13 and on the right Piston side formed a return stroke chamber 18, in which also the piston rod 15 is guided displaceably.
  • the hydraulic cylinder 13 with the associated Divide and the screw ratchet 16 form a unit 19 via flexible Hydraulic lines connected to the hydraulic pump assembly 1 shown in FIG is.
  • the gear pump 20 and the radial piston pump 21 are added, driven jointly by the output shaft of the pump motor 4 become.
  • the pump motor 4 is powered by a pump motor controller 22 operated to the example of a manual actuation unit 23 and a working pressure line 24 are connected for input of control parameters.
  • the hydraulic circuit for the hydraulic control unit 5 is from the frame 25th framed, from which the high-pressure gauge 6 protrudes.
  • a first gear pump port 26 is via the working-stroke chamber hydraulic oil passage connected to the Hähubsch 17 in the end region.
  • a second gear pump port 27 is connected to the return stroke hydraulic oil passage 8 is connected to an end portion of the return stroke chamber 18.
  • the working-stroke chamber hydraulic oil passage 7 is at a first suction port point 28 via a first intake manifold 29 with a first intake check valve 30 connected to the hydraulic oil volume of the oil tank 2.
  • the return stroke hydraulic oil passage 8 is at a second intake port 31 via a second intake manifold 32 via a second intake check valve 33 is connected to the hydraulic oil volume of the oil tank 2.
  • a high pressure check valve 34 having a blocking action in the direction of the first intake port 28 in the working-stroke chamber hydraulic oil passage 7 arranged.
  • the radial piston pump 21 has a piston pump suction inlet 35, with a piston pump suction line 36 with the hydraulic oil volume of the Oil tanks 2 is connected. From a piston pump delivery outlet 37 leads a piston pump delivery line 38 to a port with the working-displacement hydraulic oil passage 7 between the high pressure check valve 34th and the working stroke chamber 17. In the oil tank 2 also performs a hydraulic oil return line 39. This hydraulic oil return line is via a low pressure relief valve 40 with the working-stroke chamber hydraulic oil pipe 7 between the high pressure check valve 34 and the first intake port 28 connected.
  • a high pressure relief safety valve 43 is connected between the working-stroke chamber hydraulic oil passage 7 and the hydraulic oil return passage 39. Accordingly, between the gearboxhunt hydraulic oil line. 8 and the hydraulic oil return line 39, a low pressure limiting safety valve 44 switched.
  • FIG. 3 the hydraulic circuit of FIG. 2 (without screw ratchet 16 and engine control unit 22) shown with drawn volume flows in a first phase of a workhub.
  • the pump motor 4 with a clockwise rotation (arrow 45), whereby at the first gear pump connection 26 the delivery outlet and the second gear pump connection 27, the suction inlet of the gear pump 20 are formed.
  • This sucks the Gear pump 20 with high capacity hydraulic oil from the remindhubhunt 18 via the remindhubhunt hydraulic oil line 8 and pumps this in the Hähubhunt 17.
  • Fig. 4 the second phase of a power stroke is shown, in which the Ulhubhunt 17 already largely filled with hydraulic oil and accordingly the Piston rod 15 is extended far.
  • a low-pressure relief valve 40 set low pressure of 70 bar in the connected Working stroke chamber hydraulic oil line 7 below the reverse direction of the high pressure check valve 34 opens the low pressure relief valve and the gear pump 20 runs without further connection to the working stroke chamber 17, the line with the low pressure relief valve 40 acts as a short-circuit line to the hydraulic oil return line 39.
  • the radial piston pump 21 works due to the construction, even with the left-hand rotation of the pump motor 4 in the same conveying direction, so that via the piston pump delivery line 38 the piston pump delivery is promoted. There but this is low compared to the flow rate of the gear pump 20 this easily without disturbing the return stroke from the Ulhubhunt 17th added flowing hydraulic oil and also via the hydraulic oil return line 39 fed to the oil tank 2.

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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)
  • Reciprocating Pumps (AREA)
  • Details Of Spanners, Wrenches, And Screw Drivers And Accessories (AREA)
  • Actuator (AREA)

Claims (8)

  1. Clé visseuse à cliquet hydraulique (12) avec entraínement hydraulique à piston-cylindre à double effet,
    avec un piston (14), guidé coulissant dans un cylindre hydraulique (13), piston présentant une tige de piston (15) étanche sortant du cylindre hydraulique, pour l'actionnement par cliquet,
    avec une chambre de course de travail (17) dans le cylindre hydraulique, réalisée en tant que chambre haute pression, sur un côté de piston, et avec une chambre de course de retour (18), réalisée en tant que chambre basse pression sur le côté de piston portant la tige de piston,
    avec un agencement de pompage hydraulique (1) muni d'une pompe à roue dentée (20) et d'une pompe à piston (21), où
    la pompe à roue dentée (20) et la pompe à piston (21) sont susceptibles d'être entraínées au moyen d'un moteur de pompe (4) pouvant être commandé avec une commande pour moteur de pompe (22), l'entraínement se faisant par son arbre mené et la pompe à roue dentée pompant une quantité de refoulement relativement grande d'huile hydraulique par tour de rotation du moteur, et la pompe à piston pompant une quantité de refoulement relativement petite par rapport à celle-ci par tour de rotation du moteur, et
    l'agencement de pompe (1) est relié, par l'intermédiaire d'une unité de commande hydraulique (5), à la chambre de course de travail (17) et à la chambre de course de retour (18)
       caractérisé
    en ce qu'un premier raccordement de pompe à roue dentée (26) est relié, par une conduite (7) d'huile hydraulique de chambre de course de travail, à la chambre de course de travail (17), et un deuxième raccordement de pompe à roue dentée (27) est relié, par une conduite (8) d'huile hydraulique de chambre de course de retour , à la chambre de course de retour (18),
    en ce que la conduite (7) hydraulique de chambre de course de travail est reliée, en un premier point de raccordement d'aspiration (28), par l'intermédiaire d'une première tubulure d'aspiration (29) munie d'un premier clapet anti-retour d'aspiration (30), et la conduite (18) d'huile hydraulique de chambre de course de retour est reliée, en un deuxième point de raccordement d'aspiration (31) par l'intermédiaire d'une deuxième tubulure d'aspiration (32) munie d'un deuxième clapet anti-retour d'aspiration (33), au volume d'huile hydraulique d'un réservoir d'huile (2)
    en ce que, entre le premier point de raccordement d'aspiration (28) et la chambre de course de travail (17) est disposé un clapet anti-retour haute pression (34), ayant un effet de blocage en direction du premier point de raccordement d'aspiration (28) dans la conduite (7) d'huile hydraulique de chambre de course de travail.
    en ce que la pompe à piston, réalisée à la manière d'une pompe à piston radiale (21), est reliée à une entrée d'aspiration de la pompe à piston (35), au moyen d'une conduite d'aspiration de pompe à piston (36), au volume d'huile hydraulique et est relié, à une sortie de refoulement de la pompe à piston (37), au moyen d'une conduite de refoulement de pompe à piston (38) entre le clapet anti-retour haute pression (34) et la chambre de course de travail (17), à la conduite (7) d'huile hydraulique de chambre de course de travail,
    en ce qu'une conduite de retour d'écoulement d'huile hydraulique (39), menant au réservoir d'huile (2), est prévue,
    en ce que la conduite de retour d'écoulement d'huile hydraulique est reliée, par l'intermédiaire d'une soupape de limitation basse pression (40), entre le premier point de raccordement d'aspiration (28) et le clapet anti-retour haute pression (34), à la conduite (7) d'huile hydraulique de chambre de course de travail, la soupape de limitation basse pression (40) étant susceptible de libérer un écoulement de retour à l'atteinte d'une basse pression déterminée,
    en ce que la conduite d'écoulement de retour hydraulique (39), de plus, est reliée à la conduite d'huile (7) hydraulique de chambre de course de travail, au moyen d'un clapet anti-retour de déblocage (41), pouvant être piloté par pression en fonction d'une pression régnant dans la conduite (8) d'huile hydraulique de chambre de course de retour, le clapet (41) ayant un effet de blocage dans la direction d'écoulement de retour entre le clapet anti-retour haute pression (34) et la chambre de course de travail (17), et
    en ce que le moteur de pompe (4) est susceptible d'être commandé à l'aide de la commande pour moteur de pompe (22) pour effectuer une course de travail avec un premier sens de rotation, de la manière que, au raccordement de pompe à roue dentée (26), la sortie de refoulement et, au deuxième raccordement pour pompe à roue dentée (27), l'entrée d'aspiration, soient formées, et en ce que le moteur pour pompe (4) est susceptible d'être commandé en un sens de rotation inverse, pour effectuer une course de retour de manière qu'alors, au premier raccordement pour pompe à roue dentée (26), l'entrée d'aspiration et, au deuxième raccordement pour pompe à roue dentée (27), la sortie de refoulement soient formées, sachant que la pompe à piston radiale (21) refoule dans le même sens de refoulement pour les deux sens de rotation du moteur de pompe (4).
  2. Clé visseuse à cliquet hydraulique avec entraínement hydraulique à piston-cylindre à double effet selon la revendication 1, caractérisé en ce que, entre la conduite (7) d'huile hydraulique pour chambre de course de travail et la conduite d'écoulement de retour d'huile hydraulique (39), est branchée une soupape de sécurité de limitation de haute pression (43).
  3. Clé visseuse à cliquet hydraulique avec entraínement hydraulique à piston-cylindre à double effet selon la revendication 1 ou la revendication 2, caractérisé en ce que, entre la conduite d'huile hydraulique de chambre de course de retour et la conduite d'écoulement de retour d'huile hydraulique (39), est branchée une soupape de sécurité de limitation de basse pression (44).
  4. Clé visseuse à cliquet hydraulique avec entraínement hydraulique à piston-cylindre à double effet selon l'une des revendications 1 à 3, caractérisé en ce que la pompe à roue dentée (20) permet une pression de refoulement maximale d'environ 100 bar, et la soupape de limitation basse pression (40) et, le cas échéant, la soupape de sécurité de limitation basse pression (44), sont réglées à environ 70 bar.
  5. Clé visseuse à cliquet hydraulique avec entraínement hydraulique à piston-cylindre à double effet selon l'une des revendications 1 à 4, caractérisé en ce que la pompe à piston radiale (20) permet une pression de refoulement maximale d'environ 700 bar, et la soupape de limitation de haute pression (43) est susceptible d'être réglée dans une plage de commutation entre la basse pression et environ 700 bar.
  6. Clé visseuse à cliquet hydraulique avec entraínement hydraulique à piston-cylindre à double effet selon l'une des revendications 1 à 5, caractérisé en ce que le volume maximal de la chambre de course de travail, du fait de la présence de la tige de piston (15), est supérieur au volume maximal de chambre de course de retour, le rapport étant d'environ 3:1.
  7. Clé visseuse à cliquet hydraulique avec entraínement hydraulique à piston-cylindre à double effet selon l'une des revendications 1 à 6, caractérisé en ce que la commande pour moteur de pompe (22) peut être activée manuellement ou automatiquement, et le processus de vissage peut être commandé manuellement et/ou en fonction du temps et/ou en fonction de la pression de travail et/ou en fonction du couple de rotation.
  8. Clé visseuse à cliquet hydraulique avec entraínement hydraulique à piston-cylindre à double effet selon l'une des revendications 1 à 7, caractérisé en ce que le moteur pour pompe (4) est un moteur électrique ou un moteur pneumatique ou un moteur hydraulique.
EP02020916A 2002-09-19 2002-09-19 Clé à cliquet hydraulique avec entraínement hydraulique à piston-cylindre à double effet Expired - Lifetime EP1400313B1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP02020916A EP1400313B1 (fr) 2002-09-19 2002-09-19 Clé à cliquet hydraulique avec entraínement hydraulique à piston-cylindre à double effet
DE50203771T DE50203771D1 (de) 2002-09-19 2002-09-19 Hydraulik-Ratschenschrauber mit einem doppeltwirkenden Hydraulik-Zylinder-Kolben-Antrieb
AT02020916T ATE300396T1 (de) 2002-09-19 2002-09-19 Hydraulik-ratschenschrauber mit einem doppeltwirkenden hydraulik-zylinder-kolben- antrieb
US10/666,943 US6966240B2 (en) 2002-09-19 2003-09-19 Hydraulic ratchet wrench with double-action hydraulic cylinder piston drive

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP02020916A EP1400313B1 (fr) 2002-09-19 2002-09-19 Clé à cliquet hydraulique avec entraínement hydraulique à piston-cylindre à double effet

Publications (2)

Publication Number Publication Date
EP1400313A1 EP1400313A1 (fr) 2004-03-24
EP1400313B1 true EP1400313B1 (fr) 2005-07-27

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EP02020916A Expired - Lifetime EP1400313B1 (fr) 2002-09-19 2002-09-19 Clé à cliquet hydraulique avec entraínement hydraulique à piston-cylindre à double effet

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Country Link
US (1) US6966240B2 (fr)
EP (1) EP1400313B1 (fr)
AT (1) ATE300396T1 (fr)
DE (1) DE50203771D1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2147750A1 (fr) 2008-07-24 2010-01-27 Alexander Kipfelsberger Dispositif équipé d'un tournevis doté d'une limitation de couple électronique et procédé de fonctionnement du dispositif
DE202008018265U1 (de) 2008-07-24 2012-06-26 Alexander Kipfelsberger Vorrichtung mit einem Schraubwerkzeug mit elektronischer Drehmomentbegrenzung
EP3501739A1 (fr) 2017-12-21 2019-06-26 Aliki Technik GmbH Schraubsysteme Entwicklung- Produktion-Vertrieb Procédé d'étalonnage et de commande d'un dispositif de vissage et dispositif destiné à la mise en uvre dudit procédé

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EA030037B1 (ru) * 2010-11-15 2018-06-29 Хайторк Дивижн Юнекс Корпорейшн Приводной агрегат для инструмента с силовым приводом
US20150316919A1 (en) * 2013-05-16 2015-11-05 HYTORC Division Unex Corporation Multifunctional Hydraulic Drive Unit
CN106168201A (zh) * 2016-08-18 2016-11-30 福建省农业机械化研究所 一种多排量往复液压泵
DE102018111652A1 (de) * 2018-05-15 2019-11-21 STAHLWILLE Eduard Wille GmbH & Co. KG Werkzeug und Verfahren zum Betätigen eines Werkzeuges
DE102019112022A1 (de) * 2019-05-08 2020-11-12 Moog Gmbh Motorkühlung via Hydraulikfluid

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DE3719893A1 (de) * 1987-06-13 1988-12-29 Wagner Paul Heinz Hydraulischer kraftschrauber
US5617771A (en) * 1996-01-11 1997-04-08 Power Team Div. Of Spx Corp. Auto cycle pump
FR2745216B1 (fr) * 1996-02-23 1998-05-22 Turripinoise De Mecanique Sa S Machine de vissage et de devissage de boulons ou de tire-fonds
US5782158A (en) * 1996-09-20 1998-07-21 Applied Power Inc. Air operated hydraulic torque wrench pump
US6029546A (en) * 1997-06-13 2000-02-29 Parker-Hannifin Corporation Reaction member system for rotary fluid-operated wrenches
DE19813900A1 (de) * 1998-03-28 1999-09-30 Frank Hohmann Hydraulisch betriebener Kraftschrauber und Verfahren zu seiner Herstellung
US6012360A (en) * 1998-07-13 2000-01-11 Olaya Saavedra Santana Hydraulic wrench with gripping force proportional to applied torque
US6553873B2 (en) * 2000-05-03 2003-04-29 Power Tork Hydraulics, Inc. Hydraulic wrench control valve systems

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2147750A1 (fr) 2008-07-24 2010-01-27 Alexander Kipfelsberger Dispositif équipé d'un tournevis doté d'une limitation de couple électronique et procédé de fonctionnement du dispositif
DE202008018265U1 (de) 2008-07-24 2012-06-26 Alexander Kipfelsberger Vorrichtung mit einem Schraubwerkzeug mit elektronischer Drehmomentbegrenzung
EP3501739A1 (fr) 2017-12-21 2019-06-26 Aliki Technik GmbH Schraubsysteme Entwicklung- Produktion-Vertrieb Procédé d'étalonnage et de commande d'un dispositif de vissage et dispositif destiné à la mise en uvre dudit procédé

Also Published As

Publication number Publication date
US6966240B2 (en) 2005-11-22
EP1400313A1 (fr) 2004-03-24
DE50203771D1 (de) 2005-09-01
ATE300396T1 (de) 2005-08-15
US20040103762A1 (en) 2004-06-03

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