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WO2000045057A1 - Systeme de cle a couple eleve - Google Patents

Systeme de cle a couple eleve Download PDF

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Publication number
WO2000045057A1
WO2000045057A1 PCT/US2000/002147 US0002147W WO0045057A1 WO 2000045057 A1 WO2000045057 A1 WO 2000045057A1 US 0002147 W US0002147 W US 0002147W WO 0045057 A1 WO0045057 A1 WO 0045057A1
Authority
WO
WIPO (PCT)
Prior art keywords
tightening
loosening
fastener
wrench
central axis
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.)
Ceased
Application number
PCT/US2000/002147
Other languages
English (en)
Other versions
WO2000045057A9 (fr
Inventor
Richard B. Wright
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.)
Wright Tool Co
Original Assignee
Wright Tool 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
Priority claimed from US09/240,313 external-priority patent/US6725746B1/en
Application filed by Wright Tool Co filed Critical Wright Tool Co
Publication of WO2000045057A1 publication Critical patent/WO2000045057A1/fr
Anticipated expiration legal-status Critical
Publication of WO2000045057A9 publication Critical patent/WO2000045057A9/fr
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
    • F16B23/00—Specially shaped nuts or heads of bolts or screws for rotations by a tool
    • F16B23/0061—Specially shaped nuts or heads of bolts or screws for rotations by a tool with grooves, notches or splines on the external peripheral surface designed for tools engaging in radial direction
    • 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
    • B25B13/00—Spanners; Wrenches
    • B25B13/02—Spanners; Wrenches with rigid jaws
    • B25B13/06—Spanners; Wrenches with rigid jaws of socket type
    • B25B13/065—Spanners; Wrenches with rigid jaws of socket type characterised by the cross-section of the socket
    • 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 generally to a wrench and fastener arrangement and more particularly to a wrench and fastener arrangement with driving surfaces that generate a higher torque in the loosening direction than in the tightening direction or higher torque in the tightening direction than in the loosening direction.
  • FIG. 1-3 shows a 1 1/2" Hex socket
  • FIG. 2 shows a 1" 12 point socket
  • FIG. 3 shows a 1" 12 point spline.
  • the torque required for loosening a fastener that has been tightened is several times more than the torque required for tightening a fastener. This is because metal surfaces in contact with one another for an extended period of time tend to seize and resist separation.
  • fastener heads are typically forged. High strength fasteners are typically made from material that is difficult to forge. This material tends not to fill out the outer corners of the fastener, or the inner corners of wrenches. Other fastening arrangements require using fasteners that will never be removed for security reasons. Systems currently in use include fasteners having two heads where the top head is twisted off during tightening. However, these systems do not have the high torque capability of the present invention.
  • a high torque wrenching system having a wrench with asymmetrical torque transmission capability.
  • the system further provides a fastener that can mate with the asymmetrical wrench so that the fastener can be axially rotated to a loosened or tightened state.
  • the wrench can be a socket type, an open end type, a closed end type wrench or an internal wrench type.
  • the wrench includes a plurality of protuberances and a plurality of recesses around a central axis. The protuberances and recesses form a saw tooth shape. Each tooth or protuberance is formed by a first wrenching surface for loosening a fastener and a second wrenching surface for tightening a fastener.
  • the wrenching surface carrying the loosening load will be at a much smaller angle, with respect to a radial vector extending from the wrench's central axis, than the wrenching surface carrying the tightening load.
  • the result is that the loosening torque vector will have a much greater moment arm.
  • the mating relationship will be less sensitive to dimensional variations of the fastener and wrench, because a better distribution of load can be accomplished on the loosening surface than on the tightening surface, even though the tightening surface is much larger.
  • the load transmission increases proportionally to the number of protuberances or teeth. Therefore, the number of teeth can vary depending on the application or particular torque requirements. Additionally, more teeth will allow the use of a smaller head diameter for a given fastener' s size because the difference between the major and minor diameters is less.
  • the invention also provides a fastener that is easier to forge because the outer connecting surface of the protuberances is smaller in cross-sectional area than the inner connecting surface of the recesses. This tends to squeeze the metal to the corners during forging. Additionally, the greater slope on the loosening surface than on the tightening surface tends to move the metal toward the tightening surface, filling the right-hand corner of the outer connecting surface of the fastener and the left-hand corner of the outer connecting surface of the wrench. These are on the portions of the wrench that carry the loosening load, which is the greater load. Therefore, it is desirable to have only a small radius in the corner to make the load carrying surface as large as possible.
  • An example of a mating fastener type could be a typical hexagonal head with a cross flats dimension of approximately one and a half times the bolt diameter.
  • a 12-point fastener version with a cross flats of one times the diameter could be provided.
  • Standard 12-point fasteners depending on the details of their construction, including head height and material hardness, may not have sufficient wrenchability to fully utilize the properties of the fastener.
  • Using asymmetrical surfaces increases the torque ability while still preserving the small 12-point heads. Additionally, 15-point variations could increase torque requirements while allowing smaller heads.
  • the wrenching surfaces may be straight or have some curvature or tilt. In particular, it could be beneficial for the tightening surface to have some curvature or tilt to help control and improve the contact pattern despite variations in fastener and wrench dimensions.
  • the fastener also includes a plurality of protuberances and a plurality of recesses.
  • the protuberances of the wrench mate with the recesses of the fastener, and the protuberances of the fastener mate with the recesses of the wrench.
  • This arrangement is beneficial because it precludes the use of common wrench and fastener types outside this system, which could result in the risk of injury because of failure of lesser strength tool types.
  • the fastener and wrench could be comprised of a special material and hardness, such as a pressed-on ring, to further increase its ability to transmit a higher torque than a standard socket.
  • a wrenching system wherein the wrenching surface carrying the tightening load is at a much smaller angle, with respect to a radial vector extending from the wrench's central axis, than the wrenching surface carrying the loosening load.
  • the wrench and fastener tightening surfaces are nearly radial.
  • the loosening surface would be at a greater angle than as previously discussed above for a high torque loosening system because the loosening surface would not be used for transmitting torque, but rather would be provided for backside support and support for the torque transmitting surfaces.
  • a two headed fastener having an upper head connected to a lower head by a neck portion.
  • the upper head is a twist off head that breaks away from the fastener when a predetermined torque is reached.
  • the upper head has a diameter that is as small or preferably smaller than the diameter of the lower head.
  • the upper head has a tightening surface that is at a much smaller angle than the loosening surface.
  • the lower head has preferably a nearly rounded surface so that once the fastener is tightened and the upper head twisted off when the appropriate torque is reached, the lower head cannot be loosened and removed.
  • An object of the present invention is to provide a high torque wrenching system. Another object of the invention is to provide a wrenching system that transmits more torque when loosening a fastener than when tightening a fastener. Another object of the present invention is to provide a high torque wrenching system that can be used on heads having larger and smaller diameters. A further object of the present invention is to provide a wrenching system that transmits higher torque with minimum sized fasteners and wrenches.
  • Another object of the invention is to provide a high torque wrenching system that cannot mate with members outside the system having lesser strength tools that may result in the risk of injury.
  • Another object is to provide high strength fasteners that are easier to forge than conventional high strength fasteners.
  • a further object of the invention is to provide a high torque two headed twist off fastener.
  • FIGURE 1 is a front view of a 1 1/2" Hex wrench socket according to the prior art
  • FIGURE 2 is a is a front view of a 1" 12-point wrench socket according to the prior art
  • FIGURE 3 is a front view of a 1 " 12-point wrench socket spline according to the prior art
  • FIGURE 4 is an enlarged view of a wrench and fastener represented in outline form
  • FIGURE 5 is a cross-sectional handle-end view of the preferred embodiment as a 15-point wrench socket
  • FIGURE 6 is a top or socket-end view of the preferred embodiment as a 15-point fastener mate for the wrench socket shown in FIG. 5 ;
  • FIGURE 7 is a cross-sectional handle-end view of the preferred embodiment as a 8-point internal wrench
  • FIGURE 8 is a top or handle-end view of the preferred embodiment as a 8-point internal fastener mate for the internal wrench shown in FIG. 7;
  • FIGURE 9 is a top or socket-end view of the preferred embodiment as a 15-point fastener for a high torque tightening
  • FIGURE 10 is a top or socket-end view of the preferred embodiment as a 15-point two headed fastener for high torque tightening;
  • FIGURE 11 is an enlarged top or socket-end view of the preferred embodiment of FIG. 9 including ridges on the tightening surface.
  • FIG. 4 shows the invention in a modification of one of its preferred forms.
  • FIG. 4 shows a high torque system 10 comprised of an asymmetrical wrench 20 and a mating asymmetrical fastener 30 presented in an outline type form which could be an open or closed end wrench type.
  • Standard wrenches and fasteners have a minimum and maximum cross flats dimension established by industry standards. These minimum and maximum dimensions require a maximum and minimum material.
  • Wrench 20 has a maximum material 60 and a minimum required material 62.
  • Fastener 30 has a maximum material 64 and a minimum material 66. The wrench and fastener must be within the minimum and maximum tolerances to be categorized within a specified head size.
  • Wrench 20 is a 15-point wrench comprised of fifteen uniformly spaced peripherally and fifteen radially disposed protuberances 32 and fifteen uniformly spaced peripherally and radially disposed recesses 50.
  • Each protuberance 32 is located equidistant from a central axis A and each recess 50 is located equidistant from the central axis A.
  • Fastener 30 is a 15-point fastener and is also composed of fifteen uniformly spaced peripherally and fifteen radially disposed protuberances 33 and a plurality of uniformly spaced peripherally and radially disposed recesses 51, having the same shape as the protuberances and recesses of the wrench.
  • Each protuberance of the fastener is located equidistant from the central axis A and each recess of the fastener is located equidistant from the central axis A.
  • the protuberances of the wrench mates with the recess of the fastener and the protuberances of the fastener mates with the recesses of the wrench.
  • the protuberances are slightly smaller than the recesses to make mating possible.
  • the protuberances are essentially identical for both the wrench and the fastener and only one of the protuberances of the wrench needs to be described in detail, since all of the wrench protuberances are identical.
  • Protuberance 32 has an inner generally circumferential joining surface 34 that connects a loosening wrenching surface 36 and a tightening wrenching surface 38.
  • Loosening wrenching surface 36 and tightening wrenching surface 38 interface with a loosening engagement surface 70 and a tightening engagement surface 72, respectively, on fastener 30.
  • Loosening engagement surface 70 is connected to tightening engagement surface 72 by an outer fastener engagement surface 74.
  • Inner joining surface 34 of wrench 20 extends equidistantly between a given radius from a first point 39 at loosening wrenching surface 36 to a second point 41 at tightening wrenching surface 38.
  • Dashed line B-B extends circumferentially through approximately the center of the joining surfaces of the maximum and minimum material requirements.
  • the ends of inner joining surface 34 converge with the wrenching surfaces 36 and 38, and are joined together by a pair of arches 40 and 42.
  • Loosening wrenching surface 36 forms a 15° angle with respect to radius R.
  • Tightening wrenching surface 38 forms a 60° angle with respect to radius R. The result is that the torque vector of the loosening surface is much larger than the torque vector of the tightening surface, even though the length of the loosening surface is much longer.
  • the recesses are essentially identical for both the wrench and the fastener and only one of the recesses of the wrench will be described in detail. It should be understood that the recesses 50 of the wrench extend outwardly, while the recesses 51 of the fastener extend inwardly so that the surfaces described for the wrench will be diametrically opposed, with respect to the fastener. Recess 50 has an outer circumferential joining surface 52 that connects tightening wrenching surface 38, which is part of protuberance 32, with a second loosening wrenching surface 36 of an adjoining protuberance.
  • Outer circumferential joining surface 52 extends equidistantly along a given circumference from a first point 55 where it intersects the tightening wrenching surface 38 to a second point 57, where it is joined at second loosening wrenching surface 36.
  • the ends of outer radial joining surface 52 converge with wrenching surfaces 38 and 36, and are joined by a pair of arches 56 and 58.
  • Loosening wrenching surface 36 forms a 15° angle with respect to radius R".
  • Tightening wrenching surface 38 forms a 60° angle with respect to radius R' as previously discussed.
  • protuberance 32 and adjoining recess 50 form a complete section for mating with a point on a fastener. These sections are repeated radially and equal the number of points of the mating fastener forming a saw tooth typeshape. In this embodiment there are 15 points but the invention could have 8, 12 or a different number of points depending on the application, head size and torque requirements. It should also be understood, that the invention is not limited to a loosening surface having an angle 15° away from a radii extending from the central axis of the wrench or fastener, and is not limited to a tightening surface having an angle of 60° away from a radii extending from the central axis of the wrench or fastener. It should be understood that different angles could be chosen according to desired head size, number of points and torque requirements. In all cases the loosening surface would require a smaller angle than the tightening surface.
  • FIG. 5 shows a socket type wrench 100 having 15 points and a mating fastener head 110 shown in FIG. 6.
  • socket head 100 is comprised of a plurality of protuberances 32 and recesses 50, as described previously, having a tightening wrenching surfaces 36 and loosening wrenching surfaces 38.
  • the tightening wrenching surfaces 36 have an angle of 60° away from a radii extending from a central axis, like the previously described embodiment, however the loosening surfaces 38 are at a 22 25° angle with a radii extending from the central axis The steeper angle increases the torque transmission capability in the loosening direction of this embodiment, with respect to the previously described embodiment
  • Each protuberance 32 is spaced apart at 24° angles from each adjoining protuberance
  • inner joining surface 34 extends circumferentially from points 39 to 41 over an angle of 5 2°
  • socket fastener 110 is comprised of a plurality of protuberances 33 and recesses 51, as described previously, having tightening engagement surfaces 70 and loosening engagement surfaces 72
  • the tightening engagement surfaces 70 have an angle of 60° away from a radii extending from a central axis, and loosening surfaces 72 are at a 22 25° angle with a radu extending from the central axis, as described in mating wrench 100
  • the number of points or teeth of the wrench and number of points on the fasteners can vary depending on the shape, size, hardness of the fastener, and the application being facilitated Smaller heads can be used as the number of points increase because more teeth will allow for a smaller diameter head However, smaller teeth require more precise manufacturing Increasing the number of teeth can increase the amount of torque because the load transmission increases with the number of teeth
  • this high torque wrenching system could be applied to internal wrenching systems such as that found in hollow head cap screws such as "Allen" fasteners This could be possible by interchanging the wrench and the fastener so that the wrench element is inside the hollow head of the fastener In this configuration, the number of points on the fastener and wrench are likely to be smaller to facilitate manufacturing, because the wrenching surfaces are toward the center of the fastener rather than on the outside, and because there is no need in this design to consider a nut A nut cannot be made with an internal wrenching configuration, whereas a nut must be considered in the design of an external wrenching configuration, and space must be left for the tapped hole in the nut In the internal wrenching configuration larger teeth can be used that will not be limited by the internal space
  • FIG 7 shows an internal wrench 120 used for mating a hollow head cap screw 140 shown in FIG 8 internal wrench 120 and mating hollow head cap screw 140 each have 8 points
  • Internal wrench 120 is comprised of a plurality of outwardly directed protuberances 122 and inwardly directed recesses 124, each having a tightening wrenching surface 126 and a loosening wrenching surface 128
  • Tightening wrenching surfaces 126 have an angle of 60° away from a radii extending from a central axis, and the loosening wrenching surfaces 128 are at a 22 25° angle with a radii extending from the central axis, like the previously described embodiment
  • Each protuberance 122 is spaced apart at 45° angles from each adjoining protuberance
  • inner joining surface 130 extends circumferentially from points 132 to 134 over an angle of 10 8°
  • mating hollow head cap 140 shown in FIG 8, it is comprised of a plurality of inwardly directed protuberances 142 and outwardly directed recesses 144, as described previously, having tightening engagement surfaces 146 and loosening engagement surfaces 148
  • the tightening engagement surfaces 146 have an angle of 60° away from a radii extending from a central axis, and loosening engagement surfaces 148 are at a 22 25° angle with a radii extending from the central axis, as described in mating wrench 120
  • General tolerances with respect to the 60° and 22 25° angle would of course apply
  • a fastener 150 is comprised of a plurality of protuberances 152 and recesses 154, having tightening engagement surfaces 156 and loosening engagement surfaces 158
  • the tightening engagement surfaces 156 each have an angle of 22 25° away from radii extending respectively from a central axis, and loosening surfaces 158 are at a 60° angle with radii extending respectively from the central axis
  • fastener 150 is
  • a plurality of ridges or projections 160 may be formed on tightening surface 156 of fastener 150. Ridges 160 deform when sufficient load is applied during the tightening process. Determining whether sufficient load has been applied can be done by visual inspection for large fasteners, or by use of a gage (not shown) for small fasteners that would only fit on the fastener if the projections were properly deformed. Such ridges or protrusions could also be formed in the corresponding surfaces of fasteners disclosed earlier where a higher torque is necessary in the loosening direction than in the tightening direction.
  • a two headed fastener 170 is provided having an upper head 172 and a lower head 174 attached to one another by a neck 175 (shown by dashed lines).
  • Upper head 172 is a high torque configuration head essentially identical to fastener 150 depicted in FIG. 9.
  • Upper head 172 includes a plurality of protuberances 176 and a plurality of recesses 178, having tightening engagement surfaces 180 and loosening surfaces 182.
  • tightening surfaces 180 are at a much smaller angle than loosening surfaces 182.
  • Lower head 174 has a round circumference such that it can engage with the surface it is tightened on, but cannot be removed.
  • a head can be used similar to the head of fastener 1 10 of FIG. 6.
  • the lower head could also be shaped in a configuration specifically adapted to a special removal tool.
  • a matching wrench is placed over fastener head 172 and turned in the tightening direction. Once lower head 174 engages with the surface that fastener 170 is being fastened to and sufficient torque is applied, upper head 172 and neck 175 are severed from lower head 174.
  • the security of fastener 170 can be further enhanced by enclosing lower head 174.
  • the security of fastener 170 can be further enhanced by enclosing lower head 174 in a countersunk hole.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Spanners, Wrenches, And Screw Drivers And Accessories (AREA)

Abstract

L'invention concerne un système de clé à couple élevé, comprenant une clé (20) dotée d'une capacité de transmission asymétrique de couple. Cette clé comporte plusieurs protubérances (32) et évidements (50) autour d'un axe central. L'organe d'assemblage (30) comprend également plusieurs protubérances (33) et évidements (51) autour d'un axe central, lui permettant d'être couplée à la clé. Ces protubérances et évidements présentent une forme en dents de scie. Chaque dent ou protubérance est formée par une première surface d'entraînement (36) destinée à desserrer l'organe d'assemblage et par une seconde surface d'entraînement (38) destinée à serrer celui-ci. La surface d'entraînement portant la charge de desserrage forme, par rapport à un vecteur radial (R) s'étendant depuis l'axe central de la clé, un angle beaucoup plus petit que celui formé par la surface d'entraînement portant la charge de serrage. Il s'ensuit que le vecteur du couple de desserrage possède un bras de moment bien plus grand.
PCT/US2000/002147 1999-01-29 2000-01-27 Systeme de cle a couple eleve Ceased WO2000045057A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US09/240,313 US6725746B1 (en) 1998-04-13 1999-01-29 High torque wrenching system
US09/240,313 1999-01-29

Publications (2)

Publication Number Publication Date
WO2000045057A1 true WO2000045057A1 (fr) 2000-08-03
WO2000045057A9 WO2000045057A9 (fr) 2001-11-29

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PCT/US2000/002147 Ceased WO2000045057A1 (fr) 1999-01-29 2000-01-27 Systeme de cle a couple eleve

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1371453A2 (fr) 2002-06-12 2003-12-17 Wright Tool Company Système de clef et moyen de fixation asymétrique

Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE306294C (fr) *
US2685812A (en) * 1951-03-22 1954-08-10 George A Dmitroff Constant torque nut
US3425314A (en) * 1967-08-09 1969-02-04 John F Ohlson Spring beam load limiting nut
GB1204294A (en) * 1968-02-16 1970-09-03 Lockheed Aircraft Corp Nut formed with multiple torque-off collars
US3834269A (en) * 1972-10-24 1974-09-10 J Ohringer Stress indicating bolt
US3854372A (en) * 1972-10-20 1974-12-17 Elco Industries Inc Screw adapted for visible inspection of tightness
GB2060452A (en) * 1979-10-19 1981-05-07 Hilti Ag Tool for Applying Torque to Fastening Elements
GB2140523A (en) * 1983-05-17 1984-11-28 Hepworth Electrical Developmen Shear head screws or bolts, or shear head adapter
US4742735A (en) * 1977-11-09 1988-05-10 Vsi Corporation Driver for a lobed collar
WO1988009708A1 (fr) * 1987-06-01 1988-12-15 Sfs Stadler Ag Outil de vissage et vis utilisables avec cet outil
DE4022763A1 (de) * 1989-07-13 1991-01-17 Biotronik Mess & Therapieg Schraubwerkzeug
DE19610748A1 (de) * 1996-03-19 1997-01-02 Daimler Benz Ag Schraube oder Mutter mit Indikator bezüglich eines unbefugten Lösens der Verschraubung
WO1999052680A1 (fr) * 1998-04-13 1999-10-21 Wright Tool Company Systeme de cle a couple eleve

Patent Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE306294C (fr) *
US2685812A (en) * 1951-03-22 1954-08-10 George A Dmitroff Constant torque nut
US3425314A (en) * 1967-08-09 1969-02-04 John F Ohlson Spring beam load limiting nut
GB1204294A (en) * 1968-02-16 1970-09-03 Lockheed Aircraft Corp Nut formed with multiple torque-off collars
US3854372A (en) * 1972-10-20 1974-12-17 Elco Industries Inc Screw adapted for visible inspection of tightness
US3834269A (en) * 1972-10-24 1974-09-10 J Ohringer Stress indicating bolt
US4742735A (en) * 1977-11-09 1988-05-10 Vsi Corporation Driver for a lobed collar
GB2060452A (en) * 1979-10-19 1981-05-07 Hilti Ag Tool for Applying Torque to Fastening Elements
GB2140523A (en) * 1983-05-17 1984-11-28 Hepworth Electrical Developmen Shear head screws or bolts, or shear head adapter
WO1988009708A1 (fr) * 1987-06-01 1988-12-15 Sfs Stadler Ag Outil de vissage et vis utilisables avec cet outil
DE4022763A1 (de) * 1989-07-13 1991-01-17 Biotronik Mess & Therapieg Schraubwerkzeug
DE19610748A1 (de) * 1996-03-19 1997-01-02 Daimler Benz Ag Schraube oder Mutter mit Indikator bezüglich eines unbefugten Lösens der Verschraubung
WO1999052680A1 (fr) * 1998-04-13 1999-10-21 Wright Tool Company Systeme de cle a couple eleve

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
"Screws have automatic torque control", MACHINE DESIGN., vol. 54, no. 23, October 1982 (1982-10-01), PENTON,INC. CLEVELAND., US, pages 112, XP002139744, ISSN: 0024-9114 *
JOHN C. FORBIS: "Double-stage fracturable fastener for bondable elements", NAVY TECHNICAL DISCLOSURE BULLETIN., vol. 10, no. 3, March 1985 (1985-03-01), OFFICE OF NAVAL RESEARCH. ARLINGTON., US, pages 45 - 51, XP002139743 *

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1371453A2 (fr) 2002-06-12 2003-12-17 Wright Tool Company Système de clef et moyen de fixation asymétrique
EP1371453A3 (fr) * 2002-06-12 2007-03-14 Wright Tool Company Système de clef et moyen de fixation asymétrique

Also Published As

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