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WO2002027199A1 - Assemblage par boulons securise - Google Patents

Assemblage par boulons securise Download PDF

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Publication number
WO2002027199A1
WO2002027199A1 PCT/DE2001/003704 DE0103704W WO0227199A1 WO 2002027199 A1 WO2002027199 A1 WO 2002027199A1 DE 0103704 W DE0103704 W DE 0103704W WO 0227199 A1 WO0227199 A1 WO 0227199A1
Authority
WO
WIPO (PCT)
Prior art keywords
screw connection
inner body
locking
threaded shaft
threaded
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/DE2001/003704
Other languages
German (de)
English (en)
Inventor
Arno Giehl
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.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Priority to AU2002213817A priority Critical patent/AU2002213817A1/en
Priority to DE10194133T priority patent/DE10194133D2/de
Publication of WO2002027199A1 publication Critical patent/WO2002027199A1/fr
Anticipated expiration legal-status Critical
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
    • F16B39/00—Locking of screws, bolts or nuts
    • F16B39/22—Locking of screws, bolts or nuts in which the locking takes place during screwing down or tightening
    • F16B39/28—Locking of screws, bolts or nuts in which the locking takes place during screwing down or tightening by special members on, or shape of, the nut or bolt
    • F16B39/32—Locking by means of a pawl or pawl-like tongue

Definitions

  • the present invention relates to a secured screw connection.
  • a correctly designed screw connection that is reliably preloaded generally does not require additional screw locking.
  • the required pretensioning force can be fallen below in some cases. Creep can be observed, for example, when tensioning low-strength copper sheets or painted steel sheets even at room temperature, while relative movements between the contact surfaces occur, especially with thin tensioned parts and loads perpendicular to the axial direction of the screw with insufficient pre-tensioning force.
  • this object is achieved by a secured screw connection, with: a threaded shaft; a threaded hole; at least one locking element which is attached to the threaded shaft and projects radially outwards; and at least one locking recess for receiving the locking element, which on the
  • Threaded bore is formed.
  • this object is achieved by a secured screw connection, with: - a threaded shaft; a threaded hole; at least one locking element which is attached to the threaded bore and projects radially inwards; and at least one locking recess for receiving the locking element, which is formed on the threaded shaft.
  • the threaded shank can, for example, be the shank of a screw carrying an external thread, and the threaded bore can be provided on a workpiece, such as an engine block, or the bore of a nut carrying an internal thread.
  • the locking element and locking recess can be designed such that the tightening locking force that has to be overcome for further tightening is less than the releasing locking force.
  • a threaded shaft in the sense of the present invention is also understood to mean a shaft which has an external thread only over part of its length.
  • the latching element of the first variant or the latching recess of the second variant can also be attached to a section of the threaded shaft that does not have an external thread.
  • Threaded bore in the sense of the present invention is also understood to mean a bore which has an internal thread only over part of its length.
  • the locking recess of the first variant or the locking element of the second variant can also be attached to a section of the threaded bore that does not have an internal thread.
  • the secured screw connection has a nut with: an outer body which has an axial through opening; - An inner body which is slidably received in the through opening in the axial direction, has a threaded bore and is divided in the axial direction into at least two jaws, each of which carries a segment of the internal thread on its radially inner surface and are guided in the through opening such that they are moved apart when the outer body is displaced in an axial direction relative to the inner body and when the outer body is displaced relative to the inner body in the opposite axial direction, are closed.
  • the jaws are displaced radially outward when the outer body is displaced relative to the inner body in the release direction and are displaced radially inward when the outer body is displaced relative to the inner body in the tightening direction.
  • the jaws each have a front section which carries the respective internal thread segment and an integral rear section which is shaped like the front section, but is slightly angled outwards relative to this and instead of the Internal thread segment has a non-threaded recess, the internal dimensions of which is larger than the internal thread segment; and the jaws at the transition point between the front sections and the rear sections are pivotably mounted to one another in such a way that the front sections, when the outer body relative to the inner body in the release direction the mother is moved, opened and, when the outer body is moved relative to the inner body in the tightening direction of the mother, closed.
  • the secured screw connection has a screw with: an outer body, which encompasses the threaded shaft and is divided in the axial direction into at least two legs, each having a shaft section which carries a segment of the external thread, and are biased radially inward; and an inner body which is arranged between the legs so as to be displaceable in the axial direction, the legs being able to be moved radially inward when the inner body is pulled out between the legs in the loosening direction of the screw.
  • Such a split screw is known, for example, from the as yet unpublished German patent application DE 100 36 194, reference being made to the content of this document. Similar to the split nut described above, this split screw also enables quick and easy loosening of the screw connection without having to unscrew it against the release latching force. If the legs are moved inwards, not only the engagement between the external thread segments and the internal thread of the threaded bore is reduced, but also the engagement between the latching element and the latching recess, whereby the release latching force is reduced. The legs can be moved so far inward that neither external thread segments and internal threads nor the locking element and locking recess are in engagement with one another, so that in this state the screw can be moved axially in the threaded bore.
  • the latching element is anchored in a side surface of the inner body, which forms a section of the peripheral surface of the threaded shaft that does not have an external thread.
  • the locking recess is an axial groove.
  • the latching depressions and / or the latching elements are designed asymmetrically to the longitudinal axis of the screw connection in such a way that the release latching force is greater than the tightening latching force.
  • each latching recess has an oblique right flank that moves radially inward from the left, radially extending flank.
  • each locking element is inclined to the left when it is in a locking recess.
  • FIG. 1 is a cross section of a secured screw connection in a first embodiment according to the first variant
  • FIG. 2 is a cross section of a secured screw connection in a second embodiment according to the first variant
  • FIG. 3 is a cross section of a secured screw connection in a third embodiment according to the first variant
  • FIG. 4 is a cross section of a secured screw connection in a fourth embodiment according to the second variant
  • FIG. 5 is a sectional side view of a secured screw connection in a fifth embodiment according to the first variant with a split nut with the jaws open;
  • FIG. 6 is a cross section along the line VI-VI of FIG. 6;
  • FIG. 7 shows the screw connection of FIG. 5 with the jaws closed
  • FIG. 8 is a cross section along the line VIII-VIII from FIG. 7;
  • FIG. 9 is a side view of a jaw for the nut of FIG. 5 to 8;
  • FIG. 10 is a sectional side view of a secured screw connection in a sixth embodiment according to the second variant with a split screw in which the legs are closed;
  • FIG. 11 is a cross section along the line Xl-Xl from FIG. 10;
  • FIG. 12 shows the screw connection of FIG. 10 with the legs spread apart
  • FIG. 13 is a cross section taken along the line Xlll-Xlll from FIG. 12;
  • FIG. 14 is a top view of the inner body of the screw of FIG. 10 to 13;
  • FIG. 15 is a side view of the inner body of FIG. 14;
  • FIG. 16 is a cross section of a secured screw connection in a seventh embodiment according to the first variant with a split screw in which the legs are spread apart;
  • FIG. 17 is a top view of the inner body of the screw of FIG. 16th
  • FIG. 1 shows a secured screw connection in a first embodiment. It has a nut 10 with a threaded bore 11 and a threaded shaft 12. In the lower half of FIG. 1, the nut 10 and the threaded shaft 12 are shown separately.
  • a locking element 13 is attached to the threaded shaft 12 and projects radially outwards.
  • the locking element 13 here consists of a spring plate which is anchored with an edge in the threaded shaft 12 and whose opposite free edge runs parallel to the longitudinal axis A of the screw connection.
  • On the threaded bore 11 four locking recesses 15 are formed, which have the same
  • Each locking recess 15 is an axial groove here, which extends over the length of the threaded bore 11.
  • FIG. 1 is the free edge of the locking element 13 in the upper locking recess 15, so that the screw connection is secured against unintentional loosening. Because to loosen the threaded shaft 12 must rotate from the position shown relative to the nut 10 to the left, so that the locking element 13 first comes into contact with the left flank of the upper locking recess 15 and thereby hampers a further left turn. This is only possible if the torque is so large that the locking element is bent from the adjacent left flank to the right and its free edge slips out of the locking recess. The force required for this torque is also referred to here as release detent force.
  • the threaded shaft 12 must rotate from the position shown relative to the nut 10 to the right, so that the latching element 13 initially comes into contact with the right flank of the upper latching recess 15 and thereby hinders a further clockwise rotation. As before, this is only possible if the torque is so large that the locking element 13 is bent to the left by the adjacent right flank and slips out of the locking recess 15 with its free edge. The force required for this torque is also referred to here as the pull-in locking force. Now the threaded shaft 12 can be turned further to the right with less torque, since the bent locking element 13 can be pulled relatively easily over the internal thread until after 90 ° the right locking recess is reached, into which the locking element 13 can snap again.
  • the external thread has a recess tion 17 on, in which the locking element 13 sits and which offers him enough space to evade.
  • the release locking force is equal to the pull-on locking force, since the locking element 13 and the locking recesses 15 are symmetrical to the longitudinal axis A.
  • the release latching force is greater than the tightening latching force, so that the screw connection can be loosened more difficult and / or tightened more easily.
  • FIG. 2 shows a secured screw connection in a second embodiment.
  • the nut 10 is shown alone.
  • the locking recesses 15 are not symmetrical here, but each have an oblique right flank, which moves radially inward from the left, radially extending flank. If the threaded shaft 12 is now turned to the right to tighten the screw connection, the latching element 13 initially comes into contact with the right flank only with its free edge, so that it can be bent more easily to the left and as on a wedge surface slips out of the locking recess 15. As a result, the locking force is smaller than in the first embodiment.
  • FIG. 3 shows a secured screw connection in a third embodiment.
  • the threaded shaft 12 is shown alone.
  • the locking element 13 is not symmetrical here, but rather is inclined to the left when it is located in a locking recess 15. If the threaded shaft 12 rotates to the left to loosen the screw connection from the position shown, then the latching element 13 initially comes into contact only with its free edge in contact with the left flank, so that it is more difficult to bend to the right, since it has only just been set up who- that must and only then can be bent further. As a result, the release latch force is larger than in the first embodiment.
  • the second embodiment can of course also be combined with the third embodiment.
  • FIG. 4 shows a secured screw connection in a fourth embodiment.
  • the nut 10 and the threaded shaft 12 are shown separately.
  • the locking element 13 is not attached to the threaded shaft 12 but to the threaded bore 11 and projects radially inwards. Accordingly, the locking recesses 15 are not formed on the threaded bore 11, but on the threaded shaft 12. However, the mode of operation is the same in all embodiments.
  • FIG. 5 to 8 a secured screw connection is shown in a fifth embodiment.
  • This fifth embodiment corresponds to the first embodiment, but has a split nut 10, as described in DE 10023 675.
  • the nut 10 has an outer body 16 and two jaws 18, 20.
  • the outer body 16 has an axial through opening 22, in which the jaws 18, 20 are received so as to be displaceable in the axial direction, as will be explained in more detail below.
  • the through opening 22 here has a rectangular cross section and extends coaxially to the longitudinal axis A of the nut 10.
  • the jaws 18, 20 are here rectangular blocks, the length of which corresponds to the length of the outer body 16 and the width of which is slightly smaller than the width of the through opening 22 is, as in FIG. 6 is clearly visible, so that they sit in the through opening 22 in a rotationally fixed manner.
  • Each jaw 18, 20 has on its radially inner surface, that is to say on the surface which faces the threaded shaft 12, an internally threaded segment 24 which is designed to match the external thread of the threaded shaft 12.
  • upper jaw 18 has its internally threaded segment 24 on its underside
  • lower jaw 20 carries its internally threaded segment 24 on its upper side.
  • the two jaws 18, 20 are distributed symmetrically around the longitudinal axis A and thus also around the threaded shaft 12, that is to say they are at an angular distance of 180 ° to one another.
  • first guide means are provided on the outer body 16, which here comprise four lugs 26 which protrude from the through opening 22.
  • the lugs 26 are formed here by the inner end of pins which have been inserted from the outside into through holes 28 in the outer body 16.
  • first guide means on the outer body 16 are shown in FIG. 5, 6 and 9, second guide means are provided on the jaws 18, 20, which here comprise four grooves 30, in each of which one of the lugs 26 runs.
  • Each jaw 18, 20 has on its in the FIG. 6 left side surface a groove 30 and in its right side surface another groove 30 symmetrical to this.
  • Each groove 30 arises according to FIG. 5 and 9 in the tightening direction from the longitudinal axis A, so that their distance from the longitudinal axis A in FIG. 5 is larger on the left than on the right.
  • Each groove 30 thus extends essentially axially in a plane which is parallel and at a distance from the longitudinal axis A.
  • grooves are straight here, they can also be curved in the axial direction.
  • the split nut 10 has only two locking recesses 15 (indicated by a dotted line in FIGS. 5 and 7), which are formed on the internally threaded segments 24 of the upper jaw 18 and the lower jaw 20 and with the same angular distance 180 ° around the longitudinal axis A are arranged.
  • the threaded shaft 12 corresponds to that of the first to fourth embodiments, but according to FIGS. 6 and 8 a second locking element 13 ', which is offset by 90 ° to the first locking element 13 about the longitudinal axis A. As in the first to fourth embodiments, this results in the screw connection being in a locked, secured state again after a rotation of 90 °, since either the first locking element 13 or the second locking element 13 ′ is seated in one of the two locking recesses 15.
  • FIG. 5 to 8 the locking elements 13, 13 'are only shown schematically.
  • the nut 10 is shown in the open state, in which the jaws 18, 20 are so far apart that their internal thread segments 24 are not in engagement with the external thread of the threaded shaft 12 and also none of the locking elements 13, 13 'are in engagement with the recesses 15 is.
  • the nut 10 can therefore in this open state to the right in FIG. 5, that is to say in the release direction, are quickly removed from the threaded shaft 12 without having to be rotated about its longitudinal axis A, as is the case with a conventional one-piece nut.
  • This property is particularly advantageous when the release latching force is high.
  • the nut 10 can of course also be quickly pushed onto the threaded shaft 12 to the left, that is to say in the tightening direction, without having to be rotated.
  • the outer body 16 is displaced relative to the jaws 18, 20 in the release direction up to the stop of the lugs 26 at the right end of the grooves 30, so that the jaws 18, 20 are only about halfway in the through opening 22 stuck. Since each groove 30 lies with its right end closer to the longitudinal axis A than with its rest, the jaws 18, 20 are so far apart that their internal thread segments 24 are not in engagement with the threaded shaft 12 and neither is the first locking element 13 is in engagement with the upper locking recess 15.
  • the height of the jaws 18, 20 is selected so that with its radially outer surface 32, which is the upper side of the upper jaw 18 and the lower side of the lower jaw 20, in this opened state of the nut 10 on the top or the lower surface of the through opening 22 is prevented from tipping down around the lugs 30 and then the lower left edge of the upper jaw 18 and the upper right edge of the lower jaw 20 from resting against the threaded shaft 12.
  • the jaws 18, 20 thus together form an inner body which is accommodated in the through opening 22 in a rotationally fixed manner and displaceably in the axial direction and has an axial internal thread, as is required by a nut 10. Conversely, it can be said that the inner body is divided into two jaws 18, 20 in the axial direction. If the nut 10 in the in the FIG. 7 and 8 is shown closed state, then it can be tightened like a conventional one-piece nut, since the inner body 18, 20 sits in the through opening 22 in a rotationally fixed manner.
  • the first latching element 13 is also seated in the upper latching recess 15, so that the screw connection is secured.
  • This fifth embodiment can of course also be varied so that, similarly to the fourth embodiment, the two locking elements 13 are attached to the internal thread segments 24 and the two locking recesses 15 are formed on the threaded shaft 12 for this purpose.
  • the snap-in elements 13 are then at an angular distance of 180 ° and the snap-in depressions 15 are at an angular distance of 90 ° to one another.
  • FIG. 10 to 13 a secured screw connection is shown in a sixth embodiment.
  • This sixth embodiment corresponds to the fourth embodiment, but has a split screw 110, as described in DE 100 36 194.
  • the screw 110 has an inner body 113 and an outer body which is divided into two legs 114, 115 in the axial direction.
  • Each leg 114, 115 has a shaft section 116, which carries a segment of the external thread of the screw 110, and a head section 117, which corresponds to that shown in FIG. 10 and 12 left end of the shaft portion 116 is connected.
  • the divided screw 12 has only two latching depressions 15 (indicated by a dotted line in FIGS. 10 and 12), which are formed on the external thread segments of the upper leg 114 or of the lower leg 115 and with the same Angular distance of 180 ° around the longitudinal axis A are arranged.
  • the nut 10 corresponds here to that of the first to fourth embodiments, but according to FIG. 11 and 13 have a second locking element 13 ', which is offset by 90 ° to the first locking element 13 about the longitudinal axis A. As in the first to fourth embodiments, this ensures that the screw connection after a rotation of 90 ° is again in a locked, secured state, since either the first locking element 13 or the second locking element 13 'is seated in one of the two locking recesses 15.
  • the legs 114, 115 are radially inward, that is, in the in the FIG. 10 and 11 biased closed position shown.
  • the shaft sections 116 have an annular groove 118 in which a snap ring 119 is seated. Additional ring grooves with a snap ring can be provided as required.
  • the annular groove 118 can also be provided at another location on the shaft sections 116.
  • a first bore 120 is formed in the head section 117 of the upper leg 114 and runs from top to bottom at right angles to the longitudinal axis A of the screw 110.
  • a corresponding second bore 121 is formed in the head section 117 of the lower leg 115 in alignment with the first bore 120.
  • a guide pin 122 is seated with its upper end in the first bore 120 and with its lower end in the second bore 121, so that the two legs 114, 115 can be displaced radially but not axially relative to one another.
  • the two bores 120, 121 are designed here as through bores and each have a diameter in the radially outer section that is larger than the diameter of the guide pin 122.
  • the two head ends of the guide pin 122 which have a larger diameter than the rest of the guide pin 122, lie in these radially outer sections. Thus, the guide pin 122 cannot slip out of the bores 120, 121.
  • Each head section 117 has a radially inner surface 123 which, starting from the left end face of the head section 117, initially runs parallel to the longitudinal axis A and then diagonally radially inwards to the longitudinal axis A.
  • the inner body 113 essentially has the shape of a rod with a rectangular cross section. Its tip end (right in FIGS. 10 and 12) is wedge-shaped to match the radially inner surfaces 123. In the in the FIG. 10 closed state, therefore, the upper and lower wedge surfaces 124 of the tip end of the inner body 113 abut the inclined portion of the radially inner surface 123 of the upper and lower head portions 117, respectively.
  • the middle part 125 of the inner body 113 adjoining the tip end has a height which corresponds to the distance between the parallel sections of the radially inner surfaces 123 of the two head sections 117 in the position shown in FIG. 12 corresponds to the closed state shown. Therefore, these parallel sections rest on the top or bottom of the central part 125.
  • the length of the middle part 125 corresponds to the length of the shaft sections 116.
  • the head end 126 of the inner body 113 adjoining the middle part 125 has an upper side and a lower side which are designed to match the radially inner surfaces 123 of the two head sections 117.
  • the head end 126 therefore lies in the spread state with its top and bottom sides against the radially inner surfaces 123, and in this spread state the middle part 125 lies with its top and bottom sides on the underside of the upper shaft section 116 and on the top of the lower shaft section, respectively 116 at.
  • the inner body 113 is shown in top and side views. It has an axial slot 127 which extends over the entire length of the central part 125 into the head end 126 and opens into the top and the bottom of the inner body 113.
  • the guide pin 122 is shown in FIG. 10 and 12 through the slot 127, so that the inner body 113 is captively connected to the legs 114, 115.
  • the shaft sections 116 have a cross-sectional area in the form of a circular segment, the radius of which corresponds to the radius of the external thread of the screw 110 and the radius of the internal thread 111 of the nut 10, and the central angle of which is less than 180 °.
  • This central angle is selected so that in the closed state with the coaxial alignment of nut 10 and screw 110, no shaft section 116 with its external thread segment is in engagement with the internal thread 111, that is to say that the width of the shaft section 116 is smaller than the internal diameter of the internal thread 111 and the The height of the shaft section 116 is smaller than the inner radius of the internal thread 111.
  • the screw 110 is shown in the closed state, in which the legs 114, 115 are so close to one another that their external thread segments are not in engagement with the internal thread 111 of the nut 10 and also none of the latching elements 13, 13 'in Engagement with the locking recesses 15 is.
  • the screw 110 can therefore in this closed state to the right in FIG. 10, ie in the tightening direction, can be quickly pushed into the nut 10 without having to be rotated about its longitudinal axis A, as is the case with a conventional one-piece screw. This property is particularly advantageous when the release latching force is high.
  • the screw 110 can of course also be quickly pulled out of the nut 10 to the left, that is to say in the release direction, without having to be rotated.
  • the inner body 113 is displaced relative to the legs 114, 115 in the release direction up to the stop of the guide pin 122 at the right end of the slot 127, so that its tip end is located between the head sections 117. Since the legs 114, 115 are prestressed radially inward with the aid of the snap ring 119, their radially inner surfaces, that is to say the underside of the upper leg 114, and the top of the lower leg 115 lie against one another.
  • the inner body 113 from the in FIG. 10 shown to the right relative to the legs 114, 115, which are initially pressed radially outward in the region of the head section 117 by the wedge action between the wedge surfaces 124 at the tip end of the inner body 113 and the inclined sections of the radially inner surfaces 123 of the head section 117 and come into engagement with the internal thread 111 with the regions of the shaft sections 116 adjoining the head section 117. If the inner body 113 is pushed so far to the right that its tip end lies between the shaft sections 116, then the legs 114, 115 are no longer spread in the area mentioned, but are held in the spread position reached.
  • the inner body 113 is further to the right between the legs 114, 115 which are now pressed radially outward in the regions of the shaft sections 116 lying further to the right and come into engagement with the internal thread 111. If the head end 126 lies between the head sections 117 and rests with its oblique sections on the oblique sections thereof, then the inner body 113 is pushed completely between the legs 114, 115, so that the screw 110 is in the spread state, which is shown in FIG the FIG. 12 and 13 is shown. In FIG. 12 that the guide pin 122 is then seated at the left end of the slot 127.
  • the legs 114, 115 thus together form an outer body which carries an external thread, as is required by a screw 110. Conversely, it can be said that the outer body is divided into two legs 114, 115 in the axial direction.
  • the shaft sections 116 of the legs 114, 115 together with the middle part 125 of the inner body 113 form the threaded shaft 12 of the screw 110, the outside diameter of which matches the outside diameter of the inside thread 111 of the nut 10 and the sum of the heights of the two shaft sections 116 and the Height of the middle part corresponds to 125.
  • the screw 110 can be tightened like a conventional one-piece screw. This is done with a conventional tool, such as a screwdriver or wrench, which engages the head of the screw 110, which in this spread state is formed by the head sections 117 of the legs 114, 115 and the head end 126 of the inner body 113.
  • a conventional tool such as a screwdriver or wrench
  • the first latching element 13 is also seated in the upper latching recess 15, so that the screw connection is secured.
  • this sixth embodiment can also be varied such that, like in the first embodiment, the two latching elements 13 are attached to the legs 114, 115 and the two latching depressions 15 are attached to the leg Threaded bore 11 are formed. In order to ensure a latching here after each rotation by 90 °, the latching elements 13 are then at an angular distance of 180 ° and the latching depressions 15 are at an angular distance of 90 ° to one another.
  • the guide pin 122 which is initially only on its in the FIG. 12 has an upper end a head end, in the spread state of the screw 110 with its lower end inserted into the second bore 121 and pushed through the slot 127 so far from below into the first bore 120 that its head end on the shoulder of the second bore 121 supports where its diameter decreases. Then the head end is pushed up and the upper end of the guide pin 122 is compressed so that, like the lower end, it becomes a head end which is supported on the shoulder of the first bore 120, where its diameter decreases.
  • the guide pin 122 In the spread state of the screw 110, the guide pin 122 is supported with its head ends on the shoulders of the two bores 120, 121 and is therefore under tension. Consequently, the two legs 114, 115 are pressed radially inwards against the inner body 113, so that the pulling out of the inner body 113 is made more difficult.
  • FIG. 16 shows a secured screw connection in a seventh embodiment.
  • This seventh embodiment corresponds to the first embodiment, but like the sixth embodiment has a split screw 110 as described in DE 100 36 194.
  • a locking element 13 is provided here, which is shown in FIG. 16 left side surface of the central part 125 of the inner body 113 is anchored.
  • this inner body 113 of the split screw 10 is shown in a top view. Since, as already mentioned previously, the central part 125 together with the shaft sections 116 of the legs 114, 115 form the threaded shaft 12 of the screw 110, the latching element 13 is, as in the first embodiment, attached to the threaded shaft 12, it lies here however, in a section of the threaded shaft 12 that does not have an external thread.
  • the locking recess 15 is an axial groove that extends over the length of the threaded bore 11, the inner body 113 can be pulled out in the axial direction between the two legs 114, 115 without the threaded shaft 12 having to be rotated in the threaded bore 11.

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  • General Engineering & Computer Science (AREA)
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Abstract

L'invention concerne un assemblage par boulons sécurisé. L'invention vise à fournir un assemblage par boulons qui soit sécurisé de façon fiable contre tout desserrage involontaire. Selon une première variante, l'assemblage par boulons sécurisé comprend: une tige filetée (12); un orifice fileté (11); au moins un élément d'encliquetage (13, 13') qui est fixé à la tige filetée (12) et fait saillie radialement vers l'extérieur; et au moins une encoche (15) destinée à recevoir cet élément d'encliquetage (13, 13') et pratiquée sur l'orifice fileté (11). Selon une deuxième variante, un assemblage par boulons sécurisé comprend: une tige filetée (12); un orifice fileté (11); au moins un élément d'encliquetage (13, 13') qui est monté sur l'orifice fileté (11) et fait saille radialement vers l'intérieur; et au moins une encoche (15) destinée à recevoir l'élément d'encliquetage (13, 13') qui est réalisé sur la tige filetée (12).
PCT/DE2001/003704 2000-09-27 2001-09-27 Assemblage par boulons securise Ceased WO2002027199A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
AU2002213817A AU2002213817A1 (en) 2000-09-27 2001-09-27 Secured screw connection
DE10194133T DE10194133D2 (de) 2000-09-27 2001-09-27 Gesicherte Schraubenverbindung

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10049092.1 2000-09-27
DE2000149092 DE10049092A1 (de) 2000-09-27 2000-09-27 Gesicherte Schraubenverbindung

Publications (1)

Publication Number Publication Date
WO2002027199A1 true WO2002027199A1 (fr) 2002-04-04

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PCT/DE2001/003703 Ceased WO2002027198A1 (fr) 2000-09-27 2001-09-27 Assemblage par boulons securise
PCT/DE2001/003704 Ceased WO2002027199A1 (fr) 2000-09-27 2001-09-27 Assemblage par boulons securise

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Application Number Title Priority Date Filing Date
PCT/DE2001/003703 Ceased WO2002027198A1 (fr) 2000-09-27 2001-09-27 Assemblage par boulons securise

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AU (1) AU2002213817A1 (fr)
DE (4) DE10066076A1 (fr)
WO (2) WO2002027198A1 (fr)

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1996727A (en) * 1934-01-20 1935-04-02 Gordon S Leslie Nut lock
GB558302A (en) * 1942-07-22 1943-12-30 Albert Charles Hollis Screw fastening
US2834390A (en) * 1953-12-07 1958-05-13 Stevens Ludlow Resilient coil pawl and ratchet type nut and bolt lock
US4478546A (en) * 1981-12-21 1984-10-23 Mercer Mark J Quick insertion and release bolt system
FR2640336A1 (fr) 1988-12-12 1990-06-15 Jouve Daniel Ecrou rapide
DE4024784A1 (de) 1990-08-04 1992-02-13 Anton Woerndle Schnellmontagemutter
DE4340504A1 (de) * 1992-11-30 1994-06-01 Kai Corp Vorrichtung zur Verhinderung des Lösens einer Schraubanordnung
WO1997038231A1 (fr) * 1996-04-10 1997-10-16 Permanent Technologies, Inc. Systeme ecrou et boulon
DE19852100A1 (de) * 1998-11-12 2000-06-08 Phoenix Contact Gmbh & Co Kabelanschluß- oder -verbindungseinrichtung
DE10023675A1 (de) 2000-05-16 2002-01-03 Arno Giehl Mutter
DE10036194A1 (de) 2000-07-24 2002-02-21 Arno Giehl Schraube

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1996727A (en) * 1934-01-20 1935-04-02 Gordon S Leslie Nut lock
GB558302A (en) * 1942-07-22 1943-12-30 Albert Charles Hollis Screw fastening
US2834390A (en) * 1953-12-07 1958-05-13 Stevens Ludlow Resilient coil pawl and ratchet type nut and bolt lock
US4478546A (en) * 1981-12-21 1984-10-23 Mercer Mark J Quick insertion and release bolt system
FR2640336A1 (fr) 1988-12-12 1990-06-15 Jouve Daniel Ecrou rapide
DE4024784A1 (de) 1990-08-04 1992-02-13 Anton Woerndle Schnellmontagemutter
DE4340504A1 (de) * 1992-11-30 1994-06-01 Kai Corp Vorrichtung zur Verhinderung des Lösens einer Schraubanordnung
WO1997038231A1 (fr) * 1996-04-10 1997-10-16 Permanent Technologies, Inc. Systeme ecrou et boulon
DE19852100A1 (de) * 1998-11-12 2000-06-08 Phoenix Contact Gmbh & Co Kabelanschluß- oder -verbindungseinrichtung
DE10023675A1 (de) 2000-05-16 2002-01-03 Arno Giehl Mutter
DE10036194A1 (de) 2000-07-24 2002-02-21 Arno Giehl Schraube

Also Published As

Publication number Publication date
AU2002213817A1 (en) 2002-04-08
DE10194133D2 (de) 2003-09-04
DE10194132D2 (de) 2003-08-07
DE10049092A1 (de) 2002-06-20
DE10066076A1 (de) 2004-06-03
WO2002027198A1 (fr) 2002-04-04

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