EP1175284B1 - Embouts de tournevis - Google Patents

Embouts de tournevis

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Publication number
EP1175284B1
EP1175284B1 EP01923507A EP01923507A EP1175284B1 EP 1175284 B1 EP1175284 B1 EP 1175284B1 EP 01923507 A EP01923507 A EP 01923507A EP 01923507 A EP01923507 A EP 01923507A EP 1175284 B1 EP1175284 B1 EP 1175284B1
Authority
EP
European Patent Office
Prior art keywords
section
length
screwdriver bit
profile
bit according
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
EP01923507A
Other languages
German (de)
English (en)
Other versions
EP1175284A1 (fr
Inventor
Horst Holland-Letz
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.)
Felo Werkzeugfabrik Holland Letz GmbH
Original Assignee
Felo Werkzeugfabrik Holland Letz 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 Felo Werkzeugfabrik Holland Letz GmbH filed Critical Felo Werkzeugfabrik Holland Letz GmbH
Publication of EP1175284A1 publication Critical patent/EP1175284A1/fr
Application granted granted Critical
Publication of EP1175284B1 publication Critical patent/EP1175284B1/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
    • B25B15/00—Screwdrivers
    • B25B15/001—Screwdrivers characterised by material or shape of the tool bit
    • B25B15/002—Screwdrivers characterised by material or shape of the tool bit characterised by material used or surface finishing
    • 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
    • B25B15/00—Screwdrivers
    • B25B15/001—Screwdrivers characterised by material or shape of the tool bit
    • B25B15/004—Screwdrivers characterised by material or shape of the tool bit characterised by cross-section
    • B25B15/005—Screwdrivers characterised by material or shape of the tool bit characterised by cross-section with cross- or star-shaped cross-section

Definitions

  • the invention relates to screwdriver inserts of the type specified in the preamble of claim 1, in particular for use in power wrenches.
  • Screwdriver bits of this type have heretofore been made from alloyed tool steels, usually containing carbon content and alloying additives such as silicon, manganese, chromium, molybdenum and vanadium in proportions of less than 1%. After tempering, these steels reach a working hardness of approximately 60 to 64 HRC. When used in power wrenches made of tool steel er juenenburnereinsaeae at the top function of a relatively high wear, because the stress is higher than a hand screwdriver. When using the screwdriver in the industrial sector, especially in the screw assembly in an automated manufacturing, it is desirable to achieve a longer service life of erbcarder-inserts. Therefore, such inserts contain z. B. cylindrical intermediate portions which lie between the screwdriver tips and the present in hexagonal drive portions, the cushioning of load peaks serve and for this purpose a ratio diameter to length of 0.2 to 0.5 (EP 0 336 136 B1).
  • a screwdriver for Phillips screws is described in US 3,393,722, which consists of a shaft made of relatively soft steel and a tip part of an extremely hard material.
  • the tip part made of hard metal has on its rear side a pin which engages in a bore in the end face of the shank. Both parts are connected by welding together.
  • the tip part is preferably made of hard metal (tungsten carbide).
  • the cross profile of the tip part is formed relatively long, about as it is in the usual manufacturing method to produce the cross profile by milling the grooves, results.
  • a screwdriver insert of the type described at the outset is known (FR 2 469 250 A1), which contains a cross point made of metal powder by pressing and subsequent sintering.
  • the cross profile of the penetrating portion rises, without any clear, shaped as a radius or slope transition, from a plane which is perpendicular to the longitudinal axis of the Spitzenenközpers.
  • On the back of the tip body has a prismatic notch on for attachment to the corresponding end of the ffertechnikmaschinectiones (-schaftes), wherein the attachment is preferably carried out by brazing.
  • the length of the crossbars should correspond to approximately half the length of the tip body.
  • the starting material is steel or hard metal powder.
  • the disadvantage of such an embodiment is that the crossbars pass without defined radii or bevels in the base plane. Especially with hard materials, such as carbide, edged, not gradual transitions have a notch effect, which greatly reduces the load capacity at this point, especially at a torsional load.
  • Another disadvantage is the intended mounting method. In the cross-cutting incision self-centering of the two connecting parts is not given. It must be achieved by an auxiliary device, such as a fixed ring applied to the joint, which must not be displaced during brazing.
  • the screwdriver inserts not in one piece as in DE 92 11 907 U1, DE 42 41 005 A1 and DE 43 00 446 A1, but in two parts with a possible short front part made of carbide and a drive part made of steel.
  • the front part consisting of hard metal is given a total length, which is determined essentially by the length of a penetrating part, which is dimensioned so that it assumes the maximum penetration depth of the inner profile in screw heads of the associated screw size and / or type ,
  • relatively short length is added the length of a base part and an anchoring part, via which the front part is connected to a drive part of the screwdriver bit.
  • the invention achieves two major advantages. On the one hand, a uniform, accurate and good compression when pressing the blanks and thus a good stability in the region of the Eindringabitess the front part relative to the bending moments acting on the crossbars when transmitting a torque is achieved. A suitable Komissenzusammen applicant the selected metal powder mixture according to claim 4 can contribute to this. Such a good, uniform compression has been difficult to achieve, especially in cross tips, since the crimp die is similarly filled with metal powder, as it is also required for the production of one-piece screwdriver inserts.
  • the high specific load of the tip and the in The ejector force acting on the crossbars can lead to the formation of fine cracks, which are not even compensated during sintering and disturb the homogeneity of the microstructure. Due to the short design of the carbide front part according to the invention, however, the required ejector force is substantially reduced, so that z. B. a complicated, expensive mold can be avoided, in which the lower punch not only the profile of the central tip, but also the profile of the conical tip extending back of the cross bars, as in the above-described known method [VDI journal no. 7 - 9 (1999), pp. 42 to 45].
  • a feature of the invention is also that in variants, the anchoring elements, by which the front part are connected to the shaft part, are formed so that a solid, suitable for the transmission of torque connection alone by pressing, optionally using adhesive, is achieved.
  • Fig. 1 shows a front part 1 of a screwdriver insert according to the invention.
  • the front part 1 is provided at its front end with a penetration portion 2 in the form of a conventional cross tip, which serves to penetrate into the corresponding inner profile of a Phillips screw.
  • the cross point comprises four cross-shaped ribs or webs 3 with upper edges 4, which taper towards each other towards the front and terminate at a for the purposes of the invention insignificant, flattened end portion 5.
  • cross grooves or grooves with groove bottoms 6, which are also conical up to the end section 5 and which, on the side remote from the end section 5, bulge radially outwards or bevelled, starting at a point 7 which defines the rear end of the penetrating section 2 and thereby form a subsequently designated as outlet 8 section.
  • anchoring portion 12 in the form of a pin from behind, which has a reduced compared to the construction section 9 cross-section, wherein the penetration portion 2, the base portion 9 and the anchoring portion 12 are arranged coaxially to the axis 11.
  • This basic shape of the front part 1 is essentially the same in all screwdriver inserts of the invention, but the outer design and dimensions of the different sections 2, 4 and 6 in particular are adapted to the inner profile of the respectively assigned screw and the sections 12 to the selected ones Anchoring must be adapted, as explained below.
  • Fig. 2 shows an analogous to Fig. 1 front part 1 and its essential for the invention dimensions.
  • Front part 1 (Fig. 4 to 6) and a likewise separately produced drive member 14 (Fig. 7) composed, the z. B. is used to attach the insert in the lining of a motor screwdriver.
  • the front part 1 made of hard metal
  • the drive member 14 made of a usual for this purpose tool steel.
  • the drive part 14 is provided on a front side facing the front part 1 with a surface incorporated in its, adapted with its inner cross section to the outer cross section of the anchoring part 12 recess 15 ,
  • the connection then takes place in that the anchoring part 12 is inserted into the recess 15 and pressed in this way, soldered or fastened in any other way that the drive member 14 can transmit the required torques on the front part 1.
  • the recess 15 in a z. B. cylindrical or slightly conical transition portion 16 may be formed, which adjoins a portion 17 with a conventional hexagonal outer profile of the drive member 14 and causes a flush transition from the section 17 to the base portion 9.
  • the preparation of the front part 1 is effected by means of a in Fig. 8 and 9 schematically indicated pressing tool 19.
  • This contains a press bushing 20, which at one end with a z. B. cylindrical receiving opening 21 for a z. B. also cylindrical ram 22 and at the other end is provided with a Preßmatrize 23 inserted into it, which at one of the receiving opening 21 coaxial opposite side as a negative mold 24 for the front part 1 to be produced, d. H. is formed in the embodiment as a negative mold for a cross point.
  • the press bush 20 has a cavity 26.
  • the Preßmatrize 20 is provided with a central passage into which an ejector 25 is inserted.
  • the ram 22 is provided on its side facing the Preßmatrize 22 end face with a recess 27 which is formed as a negative mold of the anchoring part 12.
  • the cavity 26 is first filled with the desired cemented carbide powder when the ejector 25 has been inserted and pushed up to the die 24, as indicated in FIG. 8 by the reference numeral 28.
  • the ram 22 is inserted into the receiving opening 21 and pre-pressed with the pressure required for the compression of the hard metal powder 28 in the direction of the Preßmatrize 23, whereby the hard metal powder 28 is compressed and brought into the shape of the front part 2 (Fig. 9).
  • the ram 22 is removed, the ejector 25 is advanced to eject the front part 2 of the Preßmatrize 22 and the Preßbuchse 20, and the front part 2 obtained in such conventional pressing method, for. B.
  • the hard metal powder mixture contains z. B. cobalt, molybdenum, and tungsten carbide and optionally iron and leads through the pressing and sintering process to an extremely hard and wear-resistant front part. 2
  • the screwdriver inserts 2, 14 Due to the two-part design of the screwdriver inserts 2, 14 according to the invention, it is achieved that the actual functional or active zone, which is contained in the front part 1, is produced with a comparatively simple, cost-effective method, but nevertheless achieves optimum pressing conditions become. After the connection of the front part 1 with the drive member 14 then creates a screwdriver insert which also withstands high loads.
  • the front part 1 it is considered necessary in the context of the invention to form the front part 1 as small as possible in order to cause the lowest possible friction losses in the tool 19. Since the shape and the size of the actual penetration section 2 depends on the internal profiling in the head of the respective associated screw, the following considerations are used to achieve this objective:
  • Fig. 10 shows a front part 1 according to FIGS. 1 to 7, which dips into the profiled opening of a screw head 29 having a penetration depth T, which is smaller than the length L0 of the penetrating portion 2 corresponds.
  • the length L0 on the basis of that screw head one of Profile size of the Eindringabiteses assigned screw series, which has the largest penetration depth T according to the relevant standard or other rule.
  • the screw type, through whose head shape, the largest penetration depth T results. These are in the case of Phillips screws z.
  • the screw that has the greatest penetration depth T is selected to design L0.
  • the largest occurring area of the largest screw head shape is used for the design of L0 by L0 is 3.35 mm. This ensures that the front part 1 can dive into all screw heads with full penetration depth T.
  • An advantage of this L0 design is that L0 is not made larger than required for the desired function.
  • the size of L1 in cross-hatch profiles depends on how large the values for LP and LB should be (FIG. 2).
  • LP has proved to be expedient to choose the outlet 8 significantly smaller than that in conventional Bits is possible.
  • the base portion 9 consists of a short, plate-shaped portion, which serves mainly for Anformung the anchoring elements 12. These may consist of convex, protruding from the end face 10 (FIG. 1) or concave, sunken into the end face 10 form elements.
  • FIGS. 11 to 24 some exemplary embodiments are explained in more detail below, in which the front parts 1 substantially correspond to the front part 1 according to FIGS. 1 to 9 except for partially different base sections.
  • the drive parts 14 substantially correspond to the drive part 14 according to FIG. 7, for which reason only the different parts are denoted by different reference numbers than before. While, as anchoring element 12 of FIG. 1 to 9 is a Cylindrical pin, the front part 1 of FIG.
  • FIG. 13 shows a concave anchoring element 33 in the base section 9 and a corresponding but convex anchoring element 34 on the drive part 14. B. by gluing or soldering.
  • Fig. 14 shows two anchoring elements in the form of flat surfaces on the underside of the base portion 9 and at the top of the transition portion 16 of the drive member 14.
  • the two anchoring parts are here along an interface 35 by welding firmly connected.
  • the front part 1 is provided with an anchoring element 36 in the form of a raised from the base portion 9 V-rib, while a drive member 37 is provided on its base portion 9 facing end face with an anchoring element 38 in the form of a corresponding, concave keyway.
  • the embodiment of FIG. 15 also differs from those of FIG. 7 to 14, that the drive member 37 is cylindrical.
  • the cylindrical drive part 37 is connected to the front part 1 analogously to FIG. 14 by welding along a weld seam 40.
  • the cross section of the drive part 37 according to FIGS. 13 and 14 is slightly larger than that of the base section 9 or the diameter D1 in FIG. 2.
  • FIGS. 17 and 18 show in a direct comparison two screwdriver inserts according to the invention, which differ in the region of a base section 9 and 41, respectively. While the base portion 9 in Fig. 17 is formed as shown in Figs. 1 to 9, the base portion 41 immediately adjacent to a spout 42 has a radially expanding zone 43 which then merges into a zone 44 corresponding to the base portion 9.
  • the embodiment shown in direct comparison with Fig. 17 and 18 of FIG. 19 differs from the embodiments of FIGS. 7 to 14 in that a drive member 45 is connected via a transition section 46 with a base portion 47 of a front part 48.
  • the base portion 47 here has a dimension D1 (FIG. 2) which, in contrast to FIG.
  • the anchoring element is exemplified here as described for FIGS. 22 to 24.
  • FIGS. 20 and 21 show an anchoring element 48 projecting from the upper end face of the drive part 14 and inserted in a corresponding anchoring element 49 incorporated in the end face of the base section 9 in the form of a recess.
  • the anchoring elements 48 and 49 have a bow star profile analogous to FIG. 12.
  • the connection of the two anchoring elements 48, 49 takes place, for example, in FIG. B. by soldering along a solder seam 50th
  • a raised protruding anchoring element 52 having a cross-shaped profile is formed on the base portion 9 of the front part 1, which is in a corresponding anchoring element 53 in the form of a Phillips, which is formed in the upper end face of the transition portion 16 of the drive member 14 ,
  • the attachment is z. B. by gluing or soldering. This embodiment is currently considered the best variant of anchoring elements.
  • FIG. 25 shows an exemplary embodiment analogous to FIG. 17, in which a front part 1a is provided with a penetration section 2a with a Pozidriv profile, which is designed as in FIGS. 22 to 24.
  • a base portion 9a is provided with a projecting anchoring element 12a which projects into a corresponding anchoring element 15a in the form of a recess which is machined into the upper end face of the transitional section 16 of the drive part 14.
  • the connection of the two anchoring elements 12a, 15a takes place by soldering in the region of the contact surfaces.
  • L0 is the length of the penetrating portion 2a extending to a spout 8a
  • L1 is the total length of the front portion 1a except for the length of the anchoring member 12a.
  • measures of L0 and L1 of the Pozidriv bets as for the Phillips bets, ie. H. it is L1 ⁇ 2.5 ⁇ L0, preferably L1 ⁇ 2.2 ⁇ L0 and with very particular advantage L1 ⁇ 2 ⁇ L0, wherein L0 is determined analogously to the above description.
  • L0 may also be chosen equal to ET MAX plus a small allowance for tolerance compensation, since in this case length L0 will always be would be suitable.
  • the length of the anchoring elements in the direction of the axis 11 (Fig. 2) measured, should be as small as possible, so as not to hinder the homogeneous pressure distribution during the pressing process.
  • the anchoring elements are arranged on the side of the front parts 1, 1a facing the ram, their length is less critical than that for the lengths L0 and L1. Apart from this, it can be provided if necessary to include the anchoring elements in the measure L1.
  • the minimum lengths L0 of the penetration section are also specified by the manufacturer's standards or other regulations, such as: B. an associated data sheet.
  • the function lengths for the different profile sizes are derived from this, if necessary with a surcharge.
  • B. hexagonal or Robertson profiles in this case, the penetration sections with outlet can pass into a base section in accordance with the outlet 8, 8a (eg, FIGS.
  • FIGS. 26 and 27 show, analogously to FIGS. 1 and 2, a front part 58 of a screwdriver insert according to the invention intended for TORX® screws on a much larger scale.
  • the front part 58 is arranged coaxially to a longitudinal or rotational axis 59 and provided at its front end with a penetration portion 60 having a conventional TORX® profile whose wave-shaped course is shown in particular in FIG. 27, and for penetrating into the corresponding Internal profile of a TORX® screw is used.
  • the TORX® profile is characterized by webs 61 and grooves 62 (FIG.
  • the TORX® profile is the same throughout the penetration section 60 in the direction of the axis 59 and terminates at a conical, for the purposes of the invention insignificant, flattened end portion 63.
  • the defined rearward end of the Eindringabitess 60 At its end remote from the end portion 63 back of the groove bottoms are from a point 64, the defined rearward end of the Eindringabitess 60, curved radially outwardly, whereby analogous to the spouts 8,8a an outlet 65 is formed which terminates at a base portion 66 which substantially corresponds to the base portion 9 of FIG. 1 and has a rear end face 67, which is usually perpendicular to the axis 59.
  • An anchoring element 68 projects backwards from the end face 67 in one embodiment, as described in relation to FIGS. 22 to 24.
  • the basic shape of the front part 58 substantially corresponds to that of the front part 1 according to FIG. 1, for which reason the same lengths L0, L1, LP and LB and the diameter D1 are assigned to it for the purposes of the present invention, as described in detail above with reference to FIG was explained.
  • a screwdriver insert for TORX® screws according to FIG. 28 from the separately and integrally manufactured front part 58 and a likewise separately produced drive member 69 composed, the z. B. in a section 70 has a conventional hexagonal profile and analogous to Fig. 1 to 27 by means of a Studentsgangsab-section 71 is connected to the front part 58.
  • the transition section 71 is provided for this purpose with a corresponding anchoring element 72 in the form of a recess formed in its front end surface.
  • the connection of the two anchoring elements 68, 72 is analogous to the above description by gluing, welding, soldering or other connection methods.
  • the production of the front part 58 is analogous to the Buchspitz front parts 1 from a hard metal powder and with the aid of a press tool according to Fig. 8 and 9, the press bushing 20 and optionally Preßmatrize 23 are adjusted accordingly.
  • the dimension L0 is again as short as possible and preferably measured according to those of the embrasures T which the supplier of the respective TORX® system specifies in a data sheet or the like.
  • the length L0 is preferably dimensioned at least equal to the predetermined penetration depth, wherein an additional addition for tolerance compensation is expediently added.
  • TORX® systems of sizes 15, 20, 30, 40 and 50, for which the manufacturer or supplier specifies minimum penetration depths of 2.16 mm, 2.29 mm, 3.18 mm , 3.30 mm and 4.57 mm, which are to guarantee a sufficiently deep penetration of the TORX® profiles into the screw heads and a transmission of the required torques.
  • Fig. 29 shows a screwdriver insert for screws with hexagon internal profiles. This differs from the screwdriver insert according to FIGS. 26 to 28 only in that it has a front part 74 with a penetration section 75, which is provided with a conventional hexagonal profile.
  • the various parts are the same, and therefore, in FIG. 29, like parts are provided with the same reference numerals as in FIGS. 26 to 28.
  • An outlet is provided with the reference numeral 76.
  • the sizes L0, L1, etc. the same applies as with screwdriver inserts for TORX® screws, and also with regard to the design of these sizes to achieve an optimum microstructure in the pressing process of FIG. 8 and 9.
  • FIG. 30 shows a two-part screwdriver insert having a Robertson-profile front part 77, which has a penetration section 78 with a quadratic square profile, which can be seen from the top view.
  • the front part 77 is connected along an arcuate radially outwardly curved outlet 79 with a base portion which is provided on its rear side with the anchoring element 68 which is inserted into the recess formed as an anchoring element 72 of the drive element 69 preferably made of normal tool steel and fixed therein becomes. Since the arrangement is the same as in FIGS. 28 and 29 except for the penetration section 78, the same reference numerals are again provided to simplify the illustration. It is clear that z. B. the transition portion 71 depending on the shape of the respective Eindringabites 60, 75 and 78 may have different shapes.
  • the described two-part design has the advantage that the small front part of carbide press technology and dimensionally accurate to produce and in the plane of the highest torsional stress, ie in the Plane of the front face of the Drive parts, no indentations, which increase the risk of breakage by notch stress.
  • the ratio L1 / d 0 (Fig. 2), ie L1 and d0 should be approximately the same size.
  • Ratios L1 / d0 ( Figures 26, 27) of about 0.9 to 1.4 have been found to be useful in TORX® spouted outlets, ie, L1 may generally be slightly larger than d0.
  • favorable ratios of L1 (FIG. 29) to d0 are approximately 1.4 to 1.9, where d0 is the angular dimension according to FIG. 29 in millimeters.
  • Robertson profiles result in favorable front parts with L1 / d0 ( Figure 30) from about 1.3 to 1.5, where d0 is again the girth in millimeters ( Figure 30).
  • the invention is not limited to the described embodiments, which can be modified in many ways. This applies initially to the shape of the anchoring elements, whereby the application of two or more anchoring elements per bit would be conceivable if these z. B. would be formed as a plurality of pins.
  • the described quantities L0, L1, d0, etc. can be dimensioned differently than exemplified above.
  • the ratios of length to diameter should always be chosen so that the smallest possible circumferential or contact surfaces arise with the pressing tool, so favorable friction conditions and small Auswerfer kit be obtained.
  • the largest T MAX / T MIN range is used and the length L0 is chosen to be a value that is approximately in the middle of that range. Then penetrate the penetration of the largest screws, although not fully, but still sufficiently deep into the recesses of the screw heads to achieve a good fit.
  • the ratio L1 / d0 should preferably be less than 2.2 and with particular advantage less than 2.0.
  • the size d0 is bestimnit by the respective associated screw head.
  • the short length L1 according to the invention is advantageous not only in the case of pressing and immediately following sintering, but also in front parts produced by injection molding. As in the pressing process, demoulding by means of an ejector is usually also desired in injection molding, and therefore a reduction of the demolding resistance by reducing the length is expedient.
  • thermoplastic flux eg wax or plastic
  • the selected grain size composition of the cemented carbide powder mixture has also proved to be important. Grain gradations in the mixture of 0.5 ⁇ m to 8 ⁇ m are particularly advantageous.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Joining Of Building Structures In Genera (AREA)
  • Details Of Spanners, Wrenches, And Screw Drivers And Accessories (AREA)
  • Dowels (AREA)
  • Detergent Compositions (AREA)
  • Burglar Alarm Systems (AREA)
  • Control Of Stepping Motors (AREA)
  • Arrangement Of Elements, Cooling, Sealing, Or The Like Of Lighting Devices (AREA)
  • Mutual Connection Of Rods And Tubes (AREA)
  • Powder Metallurgy (AREA)
  • Portable Nailing Machines And Staplers (AREA)

Claims (12)

  1. Embout de tournevis, avec un élément d'entraînement (14, 37, 45, 69) et avec un élément avant (1, 1a, 58, 74, 77) de longueur (L1), fabriqué par formage ou par moulage par injection d'une poudre (28) de métal dur suivi d'un frittage, qui présente une partie de pénétration profilée (2, 2a, 60, 75, 78) de longueur de profil (LP) et, sur le côté arrière de cette dernière, une partie de base (9, 9a, 41, 47, 66) de longueur (LB) fixée à l'élément d'entraînement (14, 37, 45, 69), caractérisé en ce que les fonds de rainures de la partie de pénétration (2, 2a, 60, 75, 78) sont reliés à la partie de base (9, 41, 47, 60) par un débouché respectif (8, 8a, 42, 65, 76, 79) cintré radialement vers l'extérieur, destiné à éviter des répartitions de pression défavorables lors du formage, sachant que
    - une longueur (LA), mesurée dans la direction de l'axe longitudinal, du débouché s'obtient par la différence entre la longueur de profil (LP) et la longueur (LO), mesurée dans la direction de l'axe longitudinal (11) jusqu'au débouché, des fonds de rainures (6),
    - un diamètre ou surangle (dO) de la partie de pénétration est mesuré dans un plan perpendiculaire à l'axe longitudinal (11) qui se situe à l'extrémité de la longueur (LO) et contient un point (7, 7a ou 7b) où les fonds de rainures (6) se raccordent au débouché,
    - le rapport de (L1) à (LO) est compris entre 1,00 et 2,5,
    - le rapport de (L1) à (dO) est compris entre 0,9 et 2,2, et
    - la longueur (LB) de la partie de base est d'au plus 2,5 mm.
  2. Embout de tournevis selon la revendication 1, caractérisé en ce que la partie de base (9, 41, 47, 66) présente une longueur (LB) comprise entre 0,5 mm et 2,5 mm.
  3. Embout de tournevis selon la revendication 1 ou 2, caractérisé en ce que la partie de pénétration (2, 2a, 60, 75, 78) présente un profil cruciforme, TORX, hexagonal ou Robertson, et sa longueur (LO) mesurée jusqu'au débouché (8, 8a, 42, 65, 76, 79), si une taille de vis associée comprend des têtes (299) ayant des profondeurs de pénétration (T) requises ou souhaitées différentes, est choisie en fonction des plus grandes profondeurs de pénétration (T) minimales et maximales respectivement requises pour la taille de vis.
  4. Embout de tournevis selon l'une des revendications 1 à 3, caractérisé en ce que le mélange (28) de poudre de métal dur possède une grosseur de grain de 0,5 µm à 8 µm.
  5. Embout de tournevis selon l'une des revendications 1 à 4, caractérisé en ce que l'élément avant (1, 1a, 58, 74, 77) et l'élément d'entraînement (14, 37, 45, 69) sont mutuellement assemblés par collage, brasage, pression ou soudage.
  6. Embout de tournevis selon l'une des revendications 1 à 5, caractérisé en ce que l'élément avant (1, 1a, 58, 74, 77) et l'élément d'entraînement (14, 37, 45, 69) sont pourvus, sur des côtés frontaux en vis-à-vis, d'éléments d'ancrage (12, 31 à 34, 36, 38, 49, 52, 53, 68, 72) s'engageant les uns dans les autres.
  7. Embout de tournevis selon la revendication 6, caractérisé en ce que les éléments d'ancrage (31 à 34, 36, 38, 49, 52, 53, 68, 72), en s'engageant positivement les uns dans les autres, fixent en position l'élément avant (1, 1a, 58, 74, 77) et l'élément d'entraînement (14, 37, 45, 69) sans possibilité de rotation relative.
  8. Embout de tournevis selon la revendication 6 ou 7, caractérisé en ce que les éléments d'ancrage (31 à 34, 36, 38, 49, 52, 53, 56, 68, 72) présentent des sections ovalisées.
  9. Embout de tournevis selon l'une des revendications 6 à 8, caractérisé en ce que les éléments d'ancrage sont constitués d'un élément (31, 36, 52) dépassant d'une face frontale de l'élément avant (1) et d'un évidement (32, 37, 53) formé dans une face frontale de l'élément d'entraînement (14).
  10. Embout de tournevis selon l'une des revendications 6 à 8, caractérisé en ce que les éléments d'ancrage sont constitués d'un élément (34, 48) dépassant d'une face frontale de l'élément d'entraînement (14) et d'un évidement (33, 49) formé dans une face frontale de l'élément avant (1, 1a).
  11. Embout de tournevis selon une ou plusieurs des revendications 1 à 10, caractérisé en ce que l'élément d'ancrage et l'évidement sont mutuellement adaptés dans leur forme et leurs dimensions de telle sorte qu'en assemblant par pression les deux éléments, on obtient un assemblage fixe par adhérence et/ou par engagement positif, centrant coaxialement les deux éléments et destiné à la transmission de couples de rotation.
  12. Embout de tournevis selon l'une des revendications 1 à 11, caractérisé en ce que l'élément avant (1, 1a, 1b, 58, 74, 77) est fabriqué par pressage.
EP01923507A 2000-03-06 2001-03-06 Embouts de tournevis Expired - Lifetime EP1175284B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10010311 2000-03-06
DE10010311 2000-03-06
PCT/DE2001/000852 WO2001066312A1 (fr) 2000-03-06 2001-03-06 Embouts de tournevis

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EP1175284A1 EP1175284A1 (fr) 2002-01-30
EP1175284B1 true EP1175284B1 (fr) 2006-08-16

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EP01923507A Expired - Lifetime EP1175284B1 (fr) 2000-03-06 2001-03-06 Embouts de tournevis

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US (2) US20020129680A1 (fr)
EP (1) EP1175284B1 (fr)
AT (1) ATE336334T1 (fr)
AU (1) AU5027601A (fr)
DE (2) DE10190814D2 (fr)
ES (1) ES2270999T3 (fr)
WO (1) WO2001066312A1 (fr)

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Also Published As

Publication number Publication date
ES2270999T3 (es) 2007-04-16
US20020129680A1 (en) 2002-09-19
DE10190814D2 (de) 2003-03-27
WO2001066312A1 (fr) 2001-09-13
AU5027601A (en) 2001-09-17
ATE336334T1 (de) 2006-09-15
EP1175284A1 (fr) 2002-01-30
US7168348B2 (en) 2007-01-30
US20040139829A1 (en) 2004-07-22
DE50110735D1 (de) 2006-09-28

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