EP0009814A2 - Dispositif extensible d'équilibrage d'un outil, en particulier d'un outil d'assemblage - Google Patents

Dispositif extensible d'équilibrage d'un outil, en particulier d'un outil d'assemblage Download PDF

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Publication number
EP0009814A2
EP0009814A2 EP79103795A EP79103795A EP0009814A2 EP 0009814 A2 EP0009814 A2 EP 0009814A2 EP 79103795 A EP79103795 A EP 79103795A EP 79103795 A EP79103795 A EP 79103795A EP 0009814 A2 EP0009814 A2 EP 0009814A2
Authority
EP
European Patent Office
Prior art keywords
piston
tool
weight compensation
cylinder
compensation device
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.)
Granted
Application number
EP79103795A
Other languages
German (de)
English (en)
Other versions
EP0009814B1 (fr
EP0009814A3 (en
Inventor
Günter Otto
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.)
Willy Traub & Co GmbH
Original Assignee
Willy Traub & Co 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
Application filed by Willy Traub & Co GmbH filed Critical Willy Traub & Co GmbH
Priority to AT79103795T priority Critical patent/ATE395T1/de
Publication of EP0009814A2 publication Critical patent/EP0009814A2/fr
Publication of EP0009814A3 publication Critical patent/EP0009814A3/xx
Application granted granted Critical
Publication of EP0009814B1 publication Critical patent/EP0009814B1/fr
Expired legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25H—WORKSHOP EQUIPMENT, e.g. FOR MARKING-OUT WORK; STORAGE MEANS FOR WORKSHOPS
    • B25H1/00—Work benches; Portable stands or supports for positioning portable tools or work to be operated on thereby
    • B25H1/0021—Stands, supports or guiding devices for positioning portable tools or for securing them to the work

Definitions

  • the invention relates to an extendable weight compensation device according to the preamble of claim 1.
  • weight balancers work in such a way that a spring biased according to the weight of the tool, in particular a spiral spring, keeps the load hanging on a rope and acting on a rope drum in balance.
  • the tools should be made practically weightless by attaching them to such a weight balancer.
  • the weightlessness results only within a certain extension distance within which the weight of the tool is in equilibrium with the spring force acting on the corresponding extension distance.
  • the spring force of the spiral spring or the mechanical spring changes, so that perfect weight compensation is achieved only within a relatively small range.
  • the known weight balancers must therefore be adapted to the tool to be suspended.
  • Tools especially tools with different weights, therefore require a large number of differently designed weight compensators.
  • the extension length is limited depending on the spring used.
  • hand-operated tools for example screwdrivers, generate forces during operation which, in the known weight balancers, have to be absorbed by the muscular strength of the operator. In this respect, the known weight balancers do not eliminate all difficulties with regard to the provision of work.
  • the object is therefore achieved to provide a weight compensation device in which the handling of the tool makes work much easier in that a constant weight compensation is achieved practically over the entire extension length and, if necessary, by the tool in the Handling outgoing forces can be absorbed by the weight compensation device.
  • the fact that the spring properties of a hydropneumatic piston-cylinder arrangement can be kept constant practically over the entire stroke of the piston is advantageously used. In this way, despite a long extension of the weight balancer over the entire extension distance, a constant weight balance is obtained. Furthermore, due to the rigid support connected to the outer cylinder of the piston-cylinder arrangement, forces exerted by the tool, which are effective, for example, in the form of torques, can be absorbed perfectly, so that the handling of the tool, apart from the weight compensation, for the operator is still significantly improved. Although it is known in the field of screwdrivers to reduce the tightening torque by using impact wrenches when tightening screws, these impact wrenches produce considerable noises which considerably impair the working conditions.
  • the configuration of claim 4 gives a piston-cylinder arrangement in which the piston rod can be replaced.
  • piston rods with different diameters can be used in constant piston-cylinder arrangements.
  • the ratio of the inner cylinder diameter to the piston diameter and thus the load-bearing capacity of the weight balancer can be adjusted with simple means. It also makes maintenance easy. guaranteed.
  • From US-PS 33 26 546 a similar hydropneumatic piston cylinder arrangement with inner cylinder and outer cylinder is known, but in the known arrangement the interchangeability of the piston rod and thus the possibility of adjusting the load capacity of the weight balancer is not available.
  • the configuration of claim 9 provides a compact arrangement of the individual components of the weight balancer.
  • the embodiment of claim 11 also ensures the collection of high torques emanating from the tool. These arise in particular in screwdrivers which are guided and handled in the axial direction of the weight balancer or in the vertical direction.
  • the configuration of claim 23 results in control of the commissioning of the tool in such a way that the tool itself is only put into operation when all the operating conditions necessary to absorb the forces exerted by the tool have been created.
  • Fig. 1 shows an embodiment of the invention, in which a clamping tube 1 with a circular cross section is used as a rigid support, which can be non-positively connected with the help of a collet 3 with an outer cylinder 4 of a piston-cylinder arrangement.
  • the tension tube 1 is on a trolley 5, for example, by screwing, which in turn has a locking device in the form of clamping jaws 6 with which the carriage can be moved on a rail 7 on the ceiling.
  • a filling head 5 At the lower end of the extendable outer cylinder 4 of the piston cylinder arrangement there is a filling head 5, the individual parts of which are explained in connection with FIGS. 4 and 5.
  • the tool 9 is rigidly fastened to the outer cylinder 4 of the piston-cylinder arrangement by means of a fixed connection 10 via a fastening rod 8.
  • the outer cylinder 4 of the piston-cylinder arrangement arranged in the clamping tube 1 is pulled down or raised up.
  • the effective load capacities or spring forces remain essentially constant over the entire extension length or lifting height.
  • the collet 3 is tightened by corresponding actuation of a valve 11, which is connected via a connection P to a pressure source, so that the clamping tube 1 is non-positively connected the outer cylinder 4 is connected.
  • the pressure medium is introduced via the valve 11, which also has the pressure medium outlet A, into the collet via a pressure line 12.
  • Pressure medium is also conveyed through the pressure line 12 to the pneumatically actuated locking device 6 of the trolley 5, so that the clamping jaws are placed on the rail 7 and the trolley 5 is blocked.
  • the tool 9 is then put into operation by further actuation of the valve 11 in the same direction.
  • a hand lever 13 is used, through which a valve piston 14, which will be explained in more detail in connection with FIGS. 6 and 7, is inserted into the valve for actuating the collet 3 and the clamping device 6 and the tool 9.
  • the devices mentioned are then operated in the order described above.
  • FIG. 2 shows an exemplary embodiment in which the tensioning tube 1 has a hexagonal cross section.
  • This embodiment is suitable for collecting high torques which are exerted by the tool. This is particularly the case if the tool is a screwdriver that is guided vertically. Such a tool is shown in FIG. 2.
  • equivalent means are provided with the same reference numerals as in FIG. 1.
  • the tool 9 is also connected to the lower end of a torsion bar via a screwdriver holder plate 18.
  • This torsion bar can be moved in the vertical direction together with the tool.
  • a force transmission device 15 connected to the torsion bar 16, which comprises the tensioning tube and has a sleeve shape, the inner wall of which is adapted to the cross section of the jacket of the tensioning tube 1, is also shifted.
  • the inner wall has a hexagonal cross section like the jacket of the tensioning tube 1. This can also be seen from the sectional illustration along the section AA in FIG. 2.
  • the torsion bar 16 is connected to the force transmission sleeve 15 via a holding plate 20. During the axial displacement of the tool 9, the outer cylinder 4 is either inserted into the clamping tube 1 or pushed out of it.
  • the torsion bar 16 slides in a guide sleeve 21 which is rigidly attached to the tensioning tube 1 via a connecting support.
  • the torsion bar 16 is also connected via a connection carrier 19 to the lower end of the outer cylinder of the piston-cylinder arrangement, in particular to the filling head 5.
  • the tool is connected to the lower end of the outer cylinder 4 via the connection carrier 8.
  • the pressure medium through which the tool is started is also introduced into the tool 6 through this connection carrier. Before the tool is put into operation, however, the pressure medium is first introduced into the pneumatically actuated locking device of the trolley 5 via the pressure line 12 by appropriate control by the valve 11. In this way, the trolley 5 is blocked on the rail 7.
  • FIG. 3 An exemplary embodiment is described in FIG. 3, in which the weight compensation device is arranged on a carriage 30 which can be moved on the floor.
  • the embodiment shown in FIG. 2 has proven to be advantageous for the weight compensation device to which the tool 9 is attached. This is mounted on the tensioning tube 1 "in such a way that it can be pivoted through 360 °.
  • a lockable cylinder arrangement 22 serves as the bearing, by means of which the weight balancer can be pivoted together with the tool into the corresponding operating position.
  • the guide shafts 23 are fastened to the cross plate 25, while the guide shafts 24 are fastened to the carriage, for example to the frame 27.
  • the cross plate 25 is guided on the guide shafts 24 so as to be displaceable in the vertical direction.
  • the guide shafts 23 are also attached, which are used for the horizontal guidance of the weight balance with the tool 9.
  • the tension tube 1 is supported on the guide shafts 24 via a carrier plate 26.
  • the hydropneumatic piston-cylinder arrangement is arranged in the tensioning tube 1.
  • the tensioning tube 1 and the hydropneumatic piston-cylinder arrangement arranged therein can have the same embodiment as the exemplary embodiment in FIG. 1.
  • the bearing block 31 can be rigidly connected via a rigid connecting rod 32 to the outer cylinder of the piston cylinder arrangement, which is arranged in the tension tube 1 '.
  • a collet 3 or 3' is provided in order to establish a frictional connection between the tensioning tube 1 or 1 'and the outer cylinder of the piston cylinder arrangement in the tensioning tube.
  • the control for blocking the cylinder 22 for actuating the collets 3 and 3 'and lifting devices 28, with which the carriage -30 can be supported on the floor by means of a punch 29, takes place via the valve 11.
  • This valve 11 can, as in the case of the embodiment Game shown in Fig. 1, operated.
  • the valve piston 14 when the valve piston 14 is inserted into the valve, the cylinder bearing 22 is blocked and the collets 3 and 3 'are tightened.
  • the carriage 30 is raised by the lifting devices 28 so that it is supported on the ground by the stem 129.
  • the pneumatically operated tool 9 which can be a drill, is then put into operation. This ensures that forces exerted by the tool from the device shown in FIG. 3 are safely introduced into the ground.
  • FIG. 4 shows an embodiment for the hydropneumatic piston-cylinder arrangement which can be used in the invention.
  • This hydropneumatic piston-cylinder arrangement has the outer cylinder 4 and an inner cylinder 33.
  • An inner cylinder piston 34 is arranged displaceably in the inner cylinder 33.
  • a piston rod 35 is connected to the inner cylinder piston 34, for example, by screwing.
  • the piston rod 35 is guided in a piston rod guide 36 which is provided with a seal 37.
  • the piston rod guide 36 is inserted into a connecting piece 38 with the outer cylinder 4 and screwed, for example.
  • a thread 39 is provided. In this way, the piston rod can be removed from the inner cylinder 33 together with the piston rod guide.
  • piston rods with different diameters can be used in cylinder arrangements in which the inner cylinder and the outer cylinder have the same dimensions, in particular the same diameter. In this way, the ratio between the inner diameter of the inner cylinder 33 and the diameter can be water of the piston rod 35 vary.
  • a stop neck 40 which is at a certain distance from the piston rod. The space between the stop neck 40 and the piston rod 35 forms an overflow channel, which connects the interior above the piston 34 in the inner cylinder with the space between the inner cylinder 33 and the outer cylinder 4 above a separating or compensating piston 41.
  • the overflow channel 42 continues between the seal 37 and the upper part of the stop neck in a horizontal direction and has a further vertically extending channel part between the connecting piece 38 and the stop neck 40, which opens into the space between the inner cylinder 33 and the outer cylinder 4.
  • the space above the piston 34 in the inner cylinder 33 and the space above the separating piston 41 between the inner cylinder 33 and the outer cylinder 4, which are connected to one another by the overflow channel 42, are filled with a hydraulic fluid, for example oil.
  • the space below the separating piston 41 between the inner cylinder 33 and the outer cylinder 4 is filled with compressed gas.
  • This compressed gas can be filled in via a valve 45.
  • the inner cylinder 33 is supported against a base piece 44, which seals the space between the inner cylinder 33 and the outer cylinder 4.
  • Atmospheric pressure prevails in the space below the inner cylinder piston 34.
  • a ventilation hole 48 is provided in the base piece 44.
  • a stop neck 49 is also attached to the upper part of the outer cylinder. The stroke distance of the outer cylinder in the tensioning tube 1 is limited by this.
  • the piston rod 35 can be connected at its upper end via a ball joint 50 to a stationary articulation point or to the trolley 5. Forces that come from the tool, however, are not transmitted to the trolley via this ball joint, but, as has already been explained in connection with the exemplary embodiments in FIGS. 1 to 3, via the tensioning tube 1, which bridges this ball joint. In this respect, no forces act on this ball joint during the operation of the tool.
  • the collet 3 of the outer cylinder 4 of the piston-cylinder arrangement can be non-positively connected to the clamping tube 1.
  • the collet 3 which is fastened to the clamping tube 1 essentially has a collet head 51 which can be displaced in the radial direction by axially displacing a pneumatically actuated slide 52.
  • the collet head and the slide have two contacting conical surfaces which are aligned with one another in such a way that when a pressure medium is introduced through the pressure line 12, the slide 52 is displaced upwards in FIG. 5, so that the collet head 51 is pressed against the outer cylinder 4 .
  • a retaining ring 53 is also provided in the collet for guiding the slide 52. ''
  • the movable parts are sealed against each other by appropriate seals.
  • the filling head 5 is configured differently in the exemplary embodiment in FIG. 5 than in the exemplary embodiment in FIG. 4, but pressure gas between the outer cylinder 4 and the inner cylinder 33 below the separating piston (not shown in more detail) is also introduced via an adjusting valve 45 ' can. Furthermore, in the bottom piece 44 there is the ventilation bore 48 ', through which atmospheric pressure 33 can be set in the inner cylinder below the inner cylinder piston. The base piece 44 is screwed into a block 54, on which the tool 9 is pivoted. The swivel axis is horizontal.
  • the supply of compressed air into the tool 9 is controlled in this embodiment via a switch 55 which can be actuated by the valve 11 as soon as the valve piston 14 has been inserted into the valve by a certain distance by means of the handle 13; however, the locking device 6 for the trolley 5 and the collet 3 have been actuated beforehand.
  • valve 11 is shown in detail. 6A to 6C, the valve is shown alone, the rest position of the valve being shown in FIG. 6A.
  • FIG. 6B shows a view of the valve from above
  • FIG. 6A shows a sectional illustration along the section line BB.
  • 6C shows a sectional representation along the section line CC.
  • the valve has a channel P which is connected to the Compressed air source is connected. At the lower end of this channel, a drain valve 56 for condensed water is provided.
  • three valve chambers 57, 58, 59 are arranged one above the other in the axial direction.
  • the valve piston 14 is guided in these valve chambers.
  • the valve piston has valve beads 60, 61, 62.
  • Valve grooves 63 and 64 are located between the valve beads.
  • the groove width is dimensioned such that when the compressed air is introduced, there is no nozzle effect, but that the compressed air can pass through smoothly. This means that sufficiently wide passage gaps are formed between the valve grooves and the valve chamber walls.
  • a compressed air outlet channel P 1 is also provided in the valve body. This is located diametrically to the compressed air inlet channel P with respect to the valve chambers 57, 58, 59 and the piston 14 arranged one above the other in the middle. As can be seen from FIG. 6c, the valve also has a ventilation channel 65 which is connected via a cross connection is connected to a vent hole R. Furthermore, a further compressed gas outlet channel A is provided in the valve body. This is located diametrically with respect to the piston 14 to the ventilation channel.
  • valve or the valve piston 14 the rest position of the valve or the valve piston 14 is shown.
  • the valve piston is pushed into its lowest position by a compression spring 66.
  • the compressed air supply from the compressed air duct P is blocked in relation to the two compressed air outlet ducts P 1 and A by the corresponding position of the valve beads, in particular the valve bead 61.
  • the compressed air outlet channel P is connected to the lower valve chamber 59.
  • the compressed air outlet channel A is connected to the upper valve chamber 57.
  • the pressure Air inlet duct P is connected to the central valve chamber 58.
  • the compressed air supply to the lower chamber 59 is blocked by the valve bead 61, while the compressed air supply to the upper chamber 57 is blocked by the valve bead 60.
  • valve piston 14 If the valve piston 14 is pushed into the valve block by a certain amount, as shown in FIG. 6c, a connection between the central valve chamber 58 and the upper valve chamber 57 results via the valve groove 63. Compressed air can then be drawn from the compressed air channel P, which is connected to the compressed air source, flows into the compressed air outlet channel A via the upper valve chamber 57.
  • This compressed air outlet duct A is, as can be seen from the exemplary embodiments of FIGS. 1, 2 and 3, connected to the locking device 6 of the trolley 5, the collet 3 or 3 ', the lockable cylinder 22 and the lifting devices 28. 6C, these devices are therefore actuated.
  • FIGS. 7A and 7C The second operating position of the valve is shown in FIGS. 7A and 7C.
  • the valve piston 14 is shifted a further distance into the valve block, so that a connection is also established between the central valve chamber 58 and the lower valve chamber 59 via the valve groove 64.
  • the compressed air can then also flow via this lower valve chamber 59 into the compressed air outlet channel P 1 , which, as can be seen in particular from FIG. 7A, is connected to the pneumatically actuated tool 9.
  • the compressed air outlet channel is via a Boh-E 92 provided in a holding plate 67 tion 68 connected to a corresponding compressed air duct in the tool 9.
  • FIG. 7A is a sectional illustration along the section line D-D in FIG. 7B, which shows a top view of the valve with the holding plate 67.
  • FIG. 7C shows a sectional illustration along the section line E-E in FIG. 7B.
  • annular spaces 71 and 72 which are connected to the vent hole R.
  • the annular space 72 is connected to the ventilation bore R via the ventilation channel 65, as can be seen from FIGS. 6C and 7C. Damage to the seals cannot have an adverse effect, since the compressed air can then escape through these ventilation channels and bores. In this way, the pneumatic control is additionally secured.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Actuator (AREA)
  • Earth Drilling (AREA)
  • Testing Of Balance (AREA)
  • Jigs For Machine Tools (AREA)
  • Machine Tool Units (AREA)
  • Finish Polishing, Edge Sharpening, And Grinding By Specific Grinding Devices (AREA)
  • Golf Clubs (AREA)
EP79103795A 1978-10-06 1979-10-04 Dispositif extensible d'équilibrage d'un outil, en particulier d'un outil d'assemblage Expired EP0009814B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT79103795T ATE395T1 (de) 1978-10-06 1979-10-04 Ausziehbare gewichtsausgleichseinrichtung fuer ein werkzeug, insbesondere montagewerkzeug.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2843727 1978-10-06
DE2843727A DE2843727C2 (de) 1978-10-06 1978-10-06 Ausziehbare Haltevorrichtung für ein Werkzeug, insbesondere Montagewerkzeug

Publications (3)

Publication Number Publication Date
EP0009814A2 true EP0009814A2 (fr) 1980-04-16
EP0009814A3 EP0009814A3 (en) 1980-04-30
EP0009814B1 EP0009814B1 (fr) 1981-10-28

Family

ID=6051621

Family Applications (1)

Application Number Title Priority Date Filing Date
EP79103795A Expired EP0009814B1 (fr) 1978-10-06 1979-10-04 Dispositif extensible d'équilibrage d'un outil, en particulier d'un outil d'assemblage

Country Status (4)

Country Link
US (1) US4274495A (fr)
EP (1) EP0009814B1 (fr)
AT (1) ATE395T1 (fr)
DE (1) DE2843727C2 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2986452A1 (fr) * 2012-02-06 2013-08-09 Asbe Engineering Systeme de compensation d'un effort de reaction produit par un outil mobile
FR3095361A1 (fr) * 2019-04-25 2020-10-30 Commissariat A L`Energie Atomique Et Aux Energies Alternatives Canne de port de charge et d’amplification d’effort

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DE3245131C1 (de) * 1982-12-07 1984-05-24 Dr.Ing.H.C. F. Porsche Ag, 7000 Stuttgart Einrichtung zum Bohren in untertägigen Grubenbauen
US4696351A (en) * 1983-08-26 1987-09-29 C O D Inter Techniques Sa Assembly robot with reaction absorbing platform
DE3331975C2 (de) * 1983-09-05 1987-04-30 Deutsche Gesellschaft für Wiederaufarbeitung von Kernbrennstoffen mbH, 3000 Hannover Vorrichtung zum fernhantierbaren Instandhalten von Werkstücken, Rohrleitungen od.dgl. in abgeschirmten Zellen
DE9402241U1 (de) * 1994-02-10 1995-06-14 LIKRATEC Drucklufttechnik GmbH, 80636 München Schrauberführung mit Bremse
DE19500320A1 (de) * 1995-01-07 1996-07-11 Hilti Ag Pulverkraftbetriebenes Bolzensetzgerät
US5779216A (en) * 1995-11-16 1998-07-14 Ohio Tool Systems, Inc Power tool torque and weight balancing apparatus
CN109682927A (zh) * 2017-10-19 2019-04-26 江苏骆驼环保科技有限公司 一种固定污染源监测设备用防护安装装置

Citations (5)

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US1617512A (en) * 1921-12-17 1927-02-15 George E Ruffner Power mechanism for driving tools
DE728400C (de) * 1940-11-05 1942-11-26 Bosch Gmbh Robert Federzugaufhaengevorrichtung fuer tragbare Elektrowerkzeugmaschinen
AU6247965A (en) * 1966-07-13 1966-01-18 Abily Germain Extensible prop forthe support of normally handheld tools
FR1472043A (fr) * 1964-07-10 1967-03-10 Dispositif hydropneumatique à cylindre et à piston
FR1501012A (fr) * 1965-11-11 1967-11-10 Kratzer F Mefa Duebel Gmbh Dispositif support d'outil, en particulier d'outils entraînés par des moteurs électriques

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US2176979A (en) * 1936-07-27 1939-10-24 Briggs Mfg Co Pneumatic counterbalancing fixture
US2212696A (en) * 1939-03-20 1940-08-27 Independent Pneumatic Tool Co Tool suspension
US2323321A (en) * 1940-12-26 1943-07-06 Samuel M Futral Hydraulic tubing foot
DE1012494B (de) * 1954-10-08 1957-07-18 Hemscheidt Maschf Hermann Hydraulisch betaetigte Feststellvorrichtung fuer hydraulische Stossdaempfer
DE1256960B (de) * 1964-07-10 1967-12-21 Wilde & Spieth Hydropneumatische Feder
US3647199A (en) * 1970-05-07 1972-03-07 Menasco Mfg Co Variable-damping liquid spring
DE2408052C3 (de) * 1974-02-20 1978-04-13 Suspa-Federungstechnik Fritz Bauer & Soehne Ohg, 8503 Altdorf Längenverstellbare Gasfeder
DE2830906C2 (de) * 1978-07-13 1985-03-28 M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 8000 München Schraubvorrichtung zum Einschrauben und Festziehen von Schrauben mit hohem Anzugsmoment

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1617512A (en) * 1921-12-17 1927-02-15 George E Ruffner Power mechanism for driving tools
DE728400C (de) * 1940-11-05 1942-11-26 Bosch Gmbh Robert Federzugaufhaengevorrichtung fuer tragbare Elektrowerkzeugmaschinen
FR1472043A (fr) * 1964-07-10 1967-03-10 Dispositif hydropneumatique à cylindre et à piston
FR1501012A (fr) * 1965-11-11 1967-11-10 Kratzer F Mefa Duebel Gmbh Dispositif support d'outil, en particulier d'outils entraînés par des moteurs électriques
AU6247965A (en) * 1966-07-13 1966-01-18 Abily Germain Extensible prop forthe support of normally handheld tools

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2986452A1 (fr) * 2012-02-06 2013-08-09 Asbe Engineering Systeme de compensation d'un effort de reaction produit par un outil mobile
WO2013117832A1 (fr) * 2012-02-06 2013-08-15 Asbee Engineering Systeme de compensation d'un effort de reaction produit par un outil mobile
FR3095361A1 (fr) * 2019-04-25 2020-10-30 Commissariat A L`Energie Atomique Et Aux Energies Alternatives Canne de port de charge et d’amplification d’effort

Also Published As

Publication number Publication date
US4274495A (en) 1981-06-23
EP0009814B1 (fr) 1981-10-28
EP0009814A3 (en) 1980-04-30
DE2843727C2 (de) 1986-02-06
ATE395T1 (de) 1981-11-15
DE2843727A1 (de) 1980-04-10

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