EP1260320B1 - Tournevis motorisé avec ACCOUPLEMENT LIMITEUR DE COUPLE - Google Patents

Tournevis motorisé avec ACCOUPLEMENT LIMITEUR DE COUPLE Download PDF

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Publication number
EP1260320B1
EP1260320B1 EP02010517A EP02010517A EP1260320B1 EP 1260320 B1 EP1260320 B1 EP 1260320B1 EP 02010517 A EP02010517 A EP 02010517A EP 02010517 A EP02010517 A EP 02010517A EP 1260320 B1 EP1260320 B1 EP 1260320B1
Authority
EP
European Patent Office
Prior art keywords
screwdriver
roller
clutch
ring
clutch part
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.)
Expired - Lifetime
Application number
EP02010517A
Other languages
German (de)
English (en)
Other versions
EP1260320A1 (fr
Inventor
Holger Listl
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.)
C&E Fein GmbH and Co
Original Assignee
C&E Fein GmbH and Co
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 C&E Fein GmbH and Co filed Critical C&E Fein GmbH and Co
Publication of EP1260320A1 publication Critical patent/EP1260320A1/fr
Application granted granted Critical
Publication of EP1260320B1 publication Critical patent/EP1260320B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • B25B23/00—Details of, or accessories for, spanners, wrenches, screwdrivers
    • B25B23/14—Arrangement of torque limiters or torque indicators in wrenches or screwdrivers
    • B25B23/141—Mechanical overload release couplings
    • 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
    • B25B23/147—Arrangement of torque limiters or torque indicators in wrenches or screwdrivers specially adapted for electrically operated wrenches or screwdrivers

Definitions

  • the invention relates to a power-driven screwdriver having a torque-dependent triggering torque limiting clutch, which has a first coupling part, a second coupling part, a spring element for axial clamping of the first coupling part against the second coupling part and at least one rolling element running in the form of a roller between the two coupling parts the two coupling parts are coupled together in a drive of the screwdriver until reaching a preset triggering torque, wherein the roller is rotatably mounted on an axis held on the first coupling part axis.
  • Such a screwdriver is from the US-A-2052152 known.
  • Power-driven screwdrivers for screwing in and loosening screws have increasingly replaced conventional manual screwdrivers in the past.
  • power-driven screwdrivers are used with a torque-dependent triggering torque limiting clutch, since there screws are usually screwed with well-defined torques.
  • torque-dependent triggering torque limiting clutch since there screws are usually screwed with well-defined torques.
  • Under screws are understood in the broadest sense, all types of threaded fasteners, ie in particular also nuts.
  • Torque limiting clutches are placed in a drive train between a driver of the screwdriver and a tool holder.
  • the torque limiting clutch breaks the connection between the drive and the tool holder as soon as a screwed-in screw is clamped with the desired force in a screw-receiving thread.
  • the torque with which the drive of the screwdriver then acts on the stuck screw is called the tripping torque and can usually be set on the torque limiting clutch. So that the drive does not idle after loosening the torque limiting clutch, the torque limiting clutch usually acts on an additional switch, upon actuation of the drive is turned off.
  • rollers along the axes on which they are held can migrate and thus subject to appropriate wear.
  • the invention is therefore an object of the invention to improve a power screwdriver according to the type mentioned in such a way that the operation is as reliable as possible.
  • the axis of rotation of the roller thus does not extend through a radius of the first coupling part, but at an angle thereto. Accordingly, the direction of the roller is not tangential, but set at an angle to the tangent. As a result, in one of the two possible directions of rotation, which is preferably the working direction for screwing in, the roller performs a self-centering movement. Therefore, the roller does not move when rolling outward and thus can not dig into surrounding housing parts.
  • roller is mounted on the axis flying.
  • This flying bearing which is made possible by the self-centering of the roller due to the axis of rotation, which does not extend through the longitudinal axis of the first coupling part, is simplified the bearing of the roller on the axis and reduces the size, since fasteners omitted.
  • the shortest distance between the axis of rotation of the roller and the longitudinal axis of the first coupling part is between 5% and 15%, preferably between 9% and 11%, of the distance between the center of the roller and the longitudinal axis.
  • a circumferentially extending cam track is formed on the second coupling part, which is composed of a plurality, preferably three, identically designed track sections.
  • each track section has a cam whose flanks form a run-up side and a discharge side for the roller, which can have different inclinations.
  • the reaction part is a ring gear of a planetary gear which receives a plurality of planetary gears.
  • planetary gearboxes Due to their distribution of forces, planetary gearboxes are particularly reliable and long-lasting, making them particularly suitable for power-driven screwdrivers in the commercial sector.
  • the coupling part rotatably connected to the housing of the screwdriver is arranged to be displaceable in the axial direction.
  • a switch is provided for switching off the screwdriver, which is actuated by the axially displaceable arranged in the coupling part.
  • latching elements are formed on the two coupling parts, via which engage in a drive of the screwdriver in a release direction, the two coupling parts directly to each other.
  • latching is understood here to mean, in each case, any production of a positive connection between the two coupling parts.
  • the locking elements surface in abutment, so that can be transferred without deformation and larger torques between the coupling parts.
  • FIG. 1 an inventive screwdriver is shown in a side view with partially removed housing part and designated 10 in total.
  • the screwdriver 10 has a housing 11 with a main housing part 12 on which a handle portion 16 is formed. From there, a main switch 18 is conveniently operated by an operator.
  • a main switch 18 is conveniently operated by an operator.
  • an angle head housing 19 of an angle head 20 is rotatably mounted, from which a tool holder 22 protrudes at right angles to a longitudinal axis of the screwdriver 10.
  • Such screwdrivers are commonly referred to as rod angle screwdrivers and have the advantage over conventional power driven screwdrivers that the torque absorbed by the screwdriver when screwing screws not to a twisting of the screwdriver about its longitudinal axis, but to a pivoting of the screwdriver at right angles angled, through the tool holder 22 fixed axis leads. Such pivotal movements can be more easily absorbed by an operator than rotations of the screwdriver about its longitudinal axis.
  • a rotary ring 28 is arranged rotatable relative to the main housing part 12.
  • the screwdriver 10 has an example designed as an electric motor drive 32 which is rotatably attached to a fixed relative to the main housing part 12 support sleeve 34.
  • the drive 32 drives via an intermediate shaft 36 to a reduction gear in the form of a planetary gear 38, which on the output side, a spindle 40 is rotated.
  • the spindle 40 drives a tool spindle 44 via a bevel gear arrangement 46 arranged in the angle head 20, which tool holder carries the tool holder 22 at its free end.
  • a torque limiting clutch 50 is shown schematically, which couples a reaction torque with respect to the spindle 40 receiving reaction part of the planetary gear 38 with a control sleeve 52.
  • the adjusting sleeve 52 is integrally formed with an angle head housing 19 or rotatably connected via one or more intermediate parts with this.
  • the angle head 20 for example in the in Fig. 1 Dashed position shown, the entire angle head 20, ie, the angle head housing 19 with housed bearings 55 and 56 for the spindles 40 and 44 and the adjusting sleeve 52, relative to the housing-fixed support sleeve 34 along a running here as a screw adjustment device 58 is rotated.
  • the torque limiting clutch 50 is closed, the reaction part of the planetary gear 38 is fixed against rotation relative to the angle head 20 and coupled to the drive 32 via the adjusting device 58.
  • Fig. 2 shows in an axial section details of in Fig. 1 only schematically illustrated parts in the interior of the screwdriver 10th
  • first sun gear 64 On a rotor neck 60 of in Fig. 2 only indicated drive 32 is an intermediate shaft 62 rotatably pushed, which is integrally formed with a first sun gear 64 of the two-stage planetary gear 38.
  • the first sun gear 64 meshes with three first planetary gears 66 of a first planetary gear stage, of which in Fig. 2 only two are recognizable.
  • the first planetary gears 66 are rotatably mounted on a first planet carrier 68 and mesh simultaneously with a ring gear 70 which extends over the entire axial length of the planetary gear 38.
  • the first planet carrier 68 is integrally formed with a second sun gear 72 or rotatably connected, which meshes with second planetary gears 74.
  • the second planetary gears 74 are in turn rotatably mounted on a second planet carrier 76 and also mesh with the ring gear 70.
  • Planetenradachsen 82 on which the second planetary gears 74 are guided, enforce the second planet 76 and form on the gear side facing away from neck 80th These engage on wings of a driving gear 84, which drives the spindle designed as a hexagon 40 and is supported in the axial direction on a ring 87 held by a snap ring 85.
  • the nozzle 80 and the driving wheel 84 together form a clearance clutch 86th
  • the ring gear 70 which assumes a reaction torque relative to the intermediate shaft 62 and the spindle 40 and thus represents the reaction part of the planetary gear 38, is rotatable via a bearing 88 in the carrier sleeve 34 bolted to the drive 32 and the adjusting sleeve 52 connected thereto via the adjusting device 58 added.
  • the ring gear 70 is fixed to the adjusting sleeve 52 (or a part rotatably connected thereto) via the torque limiting clutch 50.
  • the switching ring 96 is axially, ie in the longitudinal direction 95 of the spindle 40, slidably, but rotatably received in an associated with the adjusting sleeve 52 intermediate sleeve 98.
  • the rotationally fixed, but axially displaceable arrangement of the switching ring 96 is achieved by means of first and second longitudinal grooves 100 and 102, which are arranged on a peripheral surface of the switching ring 96 and the inside of the intermediate sleeve 98 and cooperate with guide balls 102.
  • first and second longitudinal grooves 100 and 101 guide balls 102
  • the switching ring 96 and the intermediate sleeve 98 can be moved to each other in the axial direction, wherein a snap ring inserted into the intermediate sleeve 98 105 prevents falling out of the guide balls 102.
  • rollers 104 are rotatably mounted on axles 106 circumferentially.
  • the rollers 104 can roll on a cam track 108, which is formed on a switching ring 96 facing the end face of the cam ring 90.
  • a cam track 108 which is formed on a switching ring 96 facing the end face of the cam ring 90.
  • three projections 109 are formed, the function of the Fig. 3 to 8 will be explained in more detail.
  • the compression spring 94 is supported on a clamping plate 110, which is accommodated in the intermediate sleeve 98 so as to be displaceable in the axial direction.
  • a clamping plate 110 On the clamping disk 110 act four circumferentially uniformly distributed clamping bolt 112, which are guided in holes 114 which are mounted in a shoulder of the intermediate sleeve 98, and are supported on a collar 116.
  • the adjusting ring 116 can be displaced by turning on a threaded portion 118 applied externally to the intermediate sleeve 98 in the longitudinal direction 95.
  • a longitudinal displacement of the adjusting ring 116 on the threaded portion 118 of the intermediate sleeve 98 is transmitted via the clamping bolt 112 and the clamping plate 110 to the compression spring 94, so that in this way the bias between the switching ring 96 and the cam ring 90 can be changed.
  • a tool such as a screwdriver
  • one of the slots 30 in the rotary ring 28 is inserted into one of a plurality of receptacles 122 formed on the adjusting ring 116.
  • the adjusting ring 116 can be rotated together with the rotary ring 28 until the desired tension of the compression spring 94 and thus the triggering torque of the torque limiting clutch 50 is reached.
  • the rollers 104 are formed on the cam track 108 cams such that the force exerted on the ring gear 70 reaction torque on the cam, the rollers 104 and the switching ring 96 on the intermediate sleeve 98 and thereby on the rotatably associated adjusting sleeve 52 is transmitted, so that the ring gear 70 rests during the screwing of a screw.
  • the torque acting on the cam ring 90 increases until, finally, the cam ring 90 begins to rotate, lifting the rollers 104 and thus the switching ring 96 counter to the force of the compression spring 94 with its cams.
  • this runs with its cams under the rollers 104 away, so that the rollers 104 with the Shifting ring 96 finally lower again under the pressure of the compression spring 94.
  • the planetary gear 38 is no longer fixed against rotation, so that the torque exerted by the drive 32 on the spindle 40 is reduced to virtually zero.
  • a switch 124 which protrudes through the intermediate sleeve 98 in a above the switching ring 96 remaining space 128.
  • the switch 124 interrupts the power supply for the drive 32 and thus ensures that after exceeding the triggering torque of the cam ring 90 does not turn away repeatedly under the switching ring 96.
  • Fig. 3 shows the switching ring 96 in a perspective view.
  • the switching ring 96 is divided into three sections 136, 138 and 140 of different diameters.
  • the longitudinal grooves 100 are distributed on the circumference at equal angular intervals.
  • the first section 136 is followed by the second section 138 and the third section 140 thereafter.
  • This third section 140 is peripherally provided with three holes 142 which serve to receive the axles 106 and of which in Fig. 3 only the bore pointing to the viewer is recognizable.
  • the mouths of the bores 142 surrounding region of the second portion 138 and the third section 140 is just milled to create a contact surface for the rollers 104.
  • end face 143 of the switching ring 96 On the mounted in the mounted state to the cam ring 90 end face 143 of the switching ring 96 is a flat end surface 144, which forms a sliding surface of the switching ring 96. From the end face 144 are the three projections 109, which also form sliding surfaces of the switching ring 96. Through the entire switching ring 96 extends centrally a bore 148 through which the spindle 40 rotates freely in the mounted state.
  • Fig. 4 shows a plan view of the end face 143 of in Fig. 3 shown switching rings 96.
  • 96 fixed rollers 104 are shown on the switching ring.
  • the longitudinal grooves 100 and the projections 109 recognizable.
  • Dashed lines indicate the axes of rotation 152 of the rollers 104 provided by the position of the axles 106.
  • the axes of rotation 152 extend at a distance to the longitudinal axis of the switching ring 96 arranged perpendicular to the end face 144.
  • the axes of rotation 152 therefore do not meet in a common point on this longitudinal axis, but are each arranged offset to a radius connecting the circumference and the longitudinal axis ,
  • Dashed lines are shown in Fig. 5 a vectorial decomposition of the direction 160 in a tangential component of motion 163 and a radially inward movement component 164.
  • the tangential component of motion 163 corresponds to the direction of a roller whose axis is not spaced from the longitudinal axis 154, but passes therethrough. In such a direction, therefore, no radial movement component would be present.
  • the distance 156 between the axis of rotation 152 and the longitudinal axis 154 and thus also the radially inward movement component 164 is different from zero, which leads to a self-centering of the rollers 104.
  • the inwardly directed component of movement 164 causes the rollers 104 to move radially outward when the cam ring 90 moves beneath them, or not to migrate slightly radially, and thus not dig into the surrounding support sleeve 34. Therefore, the rollers 104 can be cantilevered on the axles 106.
  • signs of wear on the rollers 104 and the surrounding carrier sleeve 34 are reduced and a reliable function ensured, since problems caused by friction are avoided.
  • the cam ring 90 in a perspective view and in a plan view of a mounted in the State to the switching ring 96 facing end face 165 shown.
  • an external thread 166 can be seen, with which the cam ring 90 is screwed into the ring gear 70.
  • On the outer cam track 108 three cams 168 are formed, each having a steeper casserole side 170 and a flatter running drain side 172.
  • the cam track 108 is thus composed of three identically formed track sections, the boundaries of which are naturally determined arbitrarily due to the periodic arrangement. In Fig. 7 these limits are set so that they coincide with the ends of the casserole sides 170 facing away from the cams 168 and thereby form a first, a second and a third track section 176, 178 and 180, respectively.
  • the cam track 108 encloses three spaced-apart steps 184 which are bounded on one side by shoulders 196 and on the opposite sides by the casserole sides 170 of the cams 168 extending there over the entire ring width.
  • the steps 184 are in this case in a radial plane extending sliding surfaces of the cam ring 90 on which the switching ring 96 with its end face 144 or its projections 109 come into contact and can slide along.
  • locking elements are further formed, on which, when the end face 144 rests on the steps 184, the projections 109 can strike at a relative rotation between the cam ring 90 and the switching ring 96. In this way, a locking between the cam ring 90 and the switching ring 96 is achieved, which prevents further relative movement in this direction of rotation.
  • Fig. 8a to 8h a section of the switching ring 96 shown in which one of the rollers 104 and one of the projections 109 below the end face 144 can be seen. Since the arrangement of the rollers 104 and projections 109 repeats in the same way periodically as the contour of the cam track 108, only one of the rollers 104 and one of the projections 109 is reproduced on the switching ring 96.
  • the in the Fig. 8a to 8h shown relative movement between the switching ring 96 and the cam track 108 shown for reasons of clarity, as the switching ring 96 moves over the fixed cam track 108 away. Actually, however, moves, as already explained above was, the cam ring 90 under the switching ring 96 away. Thus, for example, when it is said in the following that the rollers 104 move beyond the cams 168, this actually means that the cams 168 move under the fixed rollers 104.
  • Fig. 8a shows the mutual arrangement of the cam ring 90 and the switching ring 96 at a time when the Drehmomentbegrenzungskupplung 50 has just been released, so that the rollers 104 are already rolled over the cam 168 away.
  • the rollers 104 rest on the discharge sides 172 of the cams 168, while both the end surface 144 and the projections 109 move away from the underlying steps 184 over the cam ring 90.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Details Of Spanners, Wrenches, And Screw Drivers And Accessories (AREA)
  • Transmission Devices (AREA)
  • One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)

Claims (10)

  1. Visseuse dynamométrique (10) comportant un dispositif d'accouplement limiteur de couple (50) se déclenchant en fonction du couple, qui présente un premier élément de couplage (96), un deuxième élément de couplage (90), un élément formant ressort (94) permettant la tension axiale du premier élément de couplage (96) contre le deuxième élément de couplage (90) et au moins un corps de roulement (104) sous forme de rouleau roulant entre les deux éléments de couplage (90, 96), par le biais duquel les deux éléments de couplage (90, 96) sont couplés l'un à l'autre lors d'un entraînement de la visseuse (10) jusqu'à ce que le moment de déclenchement préréglé soit atteint, le rouleau (104) étant logé de manière rotative sur un axe (106) maintenu au niveau du premier élément de couplage (96), caractérisée en ce que l'axe de rotation (152) du rouleau (104) déterminé par l'axe (106) est espacé d'un axe de rotation et longitudinal (154) du premier élément de couplage (96).
  2. Visseuse selon la revendication 1, caractérisée en ce que le rouleau (104) est disposé en porte-à-faux sur l'axe (106).
  3. Visseuse selon la revendication 1 ou 2,
    caractérisée en ce que la distance la plus courte (156) entre l'axe de rotation (152) du rouleau (104) et l'axe longitudinal (154) du premier élément de couplage (96) est compris entre 5 % et 15 %, de préférence entre 9 % et 11 %, de la distance entre le milieu (158) du rouleau (104) et l'axe longitudinal (154).
  4. Visseuse selon l'une quelconque des revendications précédentes, caractérisée en ce qu'une piste de came (108) s'étendant dans la direction périphérique, qui se compose de plusieurs, de préférence trois, sections de piste (176, 178, 180) de même construction, est réalisée sur le deuxième élément de couplage (90).
  5. Visseuse selon la revendication 4, caractérisée en ce que chaque section de piste (176, 178, 180) présente une came (168), dont les flancs forment un côté ascendant (170) et un côté descendant (172) pour le rouleau (104).
  6. Visseuse selon l'une quelconque des revendications précédentes, caractérisée en ce qu'un des deux éléments de couplage (96) est relié de manière solidaire en rotation à un boîtier (11) de la visseuse (10) et l'autre élément de couplage (90) est relié de manière solidaire en rotation à un élément de réaction (70) d'une transmission (38) pouvant tourner librement par rapport au boîtier (11) et absorbant un moment de réaction par rapport à une broche (40).
  7. Visseuse selon la revendication 6, caractérisée en ce que l'élément de réaction est une couronne (70), recevant plusieurs roues planétaires (66, 74), d'un engrenage de roue planétaire (38).
  8. Visseuse selon la revendication 6 ou 7, caractérisée en ce que l'élément de couplage (96) relié de manière solidaire en rotation au boîtier (11) de la visseuse (10) est disposé de manière mobile dans la direction axiale (95).
  9. Visseuse selon la revendication 8, caractérisée par un interrupteur (124) permettant de mettre hors circuit la visseuse (10), qui peut être actionné par l'élément de couplage (96) disposé de manière mobile dans la direction axiale.
  10. Visseuse selon l'une quelconque des revendications précédentes, caractérisée en ce que des éléments d'encliquetage (109, 196) sont réalisés au niveau des deux éléments de couplage (90, 96), par le biais desquels les deux éléments de couplage (90, 96) s'enclenchent directement l'un avec l'autre lors d'un entraînement de la visseuse (10) dans une direction de libération.
EP02010517A 2001-05-14 2002-05-10 Tournevis motorisé avec ACCOUPLEMENT LIMITEUR DE COUPLE Expired - Lifetime EP1260320B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10124573A DE10124573A1 (de) 2001-05-14 2001-05-14 Kraftgetriebener Schrauber mit Drehmomentbegrenzungskupplung
DE10124573 2001-05-14

Publications (2)

Publication Number Publication Date
EP1260320A1 EP1260320A1 (fr) 2002-11-27
EP1260320B1 true EP1260320B1 (fr) 2008-02-27

Family

ID=7685486

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02010517A Expired - Lifetime EP1260320B1 (fr) 2001-05-14 2002-05-10 Tournevis motorisé avec ACCOUPLEMENT LIMITEUR DE COUPLE

Country Status (4)

Country Link
EP (1) EP1260320B1 (fr)
AT (1) ATE387291T1 (fr)
DE (2) DE10124573A1 (fr)
ES (1) ES2300401T3 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202013104656U1 (de) 2012-10-29 2013-10-28 Waldemar Link Gmbh & Co. Kg Werkzeug, insbesondere chirurgisches Instrument, mit einem Drehmomentbegrenzer

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2052152A (en) * 1932-05-19 1936-08-25 Arthur B Webb Torque transmission mechanism
DE683190C (de) * 1933-10-05 1939-11-01 Bosch Gmbh Robert Kraftbetriebene Werkzeugmaschine
US3419087A (en) * 1967-03-30 1968-12-31 Chicago Pneumatic Tool Co Torque controlled electric nut-runner with solenoid brake
US4215594A (en) * 1978-07-14 1980-08-05 Cooper Industries, Inc. Torque responsive speed shift mechanism for power tool
DE3831960A1 (de) * 1988-09-21 1990-03-22 Scintilla Ag Geraeuscharme schrauberkupplung
DE4038226A1 (de) * 1990-11-30 1992-06-04 Bosch Gmbh Robert Handgefuehrtes kraftdrehwerkzeug
DE4123349C1 (de) * 1991-07-15 1993-03-04 Fein C & E Schrauber mit variabler Drehmomenteinstellung
NL9101335A (nl) * 1991-08-02 1993-03-01 Emerson Electric Co Transmissie voor elektrisch aangedreven gereedschap.
DE19845018C1 (de) * 1998-09-30 1999-12-16 Fein C & E Kraftgetriebener Schrauber

Also Published As

Publication number Publication date
EP1260320A1 (fr) 2002-11-27
ATE387291T1 (de) 2008-03-15
ES2300401T3 (es) 2008-06-16
DE10124573A1 (de) 2002-11-21
DE50211765D1 (de) 2008-04-10

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