Source: https://patents.google.com/patent/DE10049092A1/en
Timestamp: 2020-04-07 11:27:07
Document Index: 74295577

Matched Legal Cases: ['art 125', 'art 125', 'art 125', 'art 125', 'art 125', 'art 125', 'art 125', 'art 125', 'art 125']

DE10049092A1 - Secured screw connection - Google Patents
Secured screw connection
DE10049092A1
DE10049092A1 DE2000149092 DE10049092A DE10049092A1 DE 10049092 A1 DE10049092 A1 DE 10049092A1 DE 2000149092 DE2000149092 DE 2000149092 DE 10049092 A DE10049092 A DE 10049092A DE 10049092 A1 DE10049092 A1 DE 10049092A1
DE2000149092
Arno Giehl
2000-09-27 Application filed by Arno Giehl filed Critical Arno Giehl
2000-09-27 Priority to DE2000149092 priority Critical patent/DE10049092A1/en
2001-09-27 Priority claimed from AU1381602A external-priority patent/AU1381602A/en
2002-06-20 Publication of DE10049092A1 publication Critical patent/DE10049092A1/en
The invention relates to a secured screw connection. DOLLAR A It is an object of the invention to provide a screw connection which is reliably secured against unintentional loosening. DOLLAR A This task is solved according to a first variant by a secured screw connection, with: DOLLAR A - a threaded shaft (12); DOLLAR A - a threaded bore (11); DOLLAR A - at least one locking element (13, 13 ') which is attached to the threaded shaft (12) and projects radially outwards; and DOLLAR A - at least one locking recess (15) for receiving the locking element (13, 13 '), which is formed on the threaded bore (11). DOLLAR A This task is solved according to a second variant by a secured screw connection, with: DOLLAR A - a threaded shaft (12); DOLLAR A - a threaded bore (11); DOLLAR A - at least one locking element (13, 13 ') which is attached to the threaded bore (11) and projects radially inwards; and DOLLAR A - at least one locking recess (15) for receiving the locking element (13, 13 '), which is formed on the threaded shaft (12).
The present invention relates to a secured screw connection.
A correctly designed screw connection that reliably featured is generally not subject to additional screw locking. By Loosen as a result of setting or creeping of the connecting elements or by automatic loosening as a result of relative movements between the In some cases, however, contact surfaces can require the required preload be crossed. A creep can occur, for example, when tensioning down solid copper sheets or painted steel sheets even at room temperature be observed, while relative movements between the contact surfaces before al lem with thin clamped parts and loads perpendicular to the axial direction the screw occur with insufficient preload.
It is therefore an object of the invention to provide a screw connection places that are reliably secured against unintentional loosening.
According to a first variant, this task is solved 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 protrudes radially outward; and
- At least one locking recess for receiving the locking element, which on the Threaded bore is formed.
According to a second variant, this task is solved by a secured screw connection, with:
- At least one locking element which is attached to the threaded bore and protrudes radially inward; and
- At least one locking recess for receiving the locking element the threaded shaft is formed.
The threaded shaft can, for example, the shaft carrying an external thread ner screw, and the threaded hole can be on a workpiece, as in provided for example an engine block or carrying an internal thread Bore a nut.
If the locking element in the locking recess when tightening the screw connection protrudes into it, then the screw connection can only be overcome by overcoming the Release detent force can be released again. Locking element and recess can be con structurally be designed such that the tightening detent force required for further tightening must be overcome, is less than the release locking force.
A threaded shaft is also used for the purposes of the present invention stood, which carries only on part of its length an external thread. In the sem case the locking element of the first variant or the Rastver The second variant is also deepened on a section of the threaded shaft be brought, which carries no external thread.
Under tapping in the sense of the present invention, a Boh tion understood that only has an internal thread over part of its length. In In this case, the recess of the first variant or the rest element of the second variant is also attached to a section of the threaded bore be brought that has no internal thread.
In both variants it can be provided that the secured screw connection has a nut with:
- An outer body which has an axial through opening;
- An inner body in the through opening in the axial direction is slidably received, the threaded bore and in axial Direction is divided into at least two jaws, each radially on their inside Ren area carry a segment of the internal thread and such in the through are guided that they when the outer body relative to the In body is moved in an axial direction, be moved apart and when the outer body is relative to the inner body in the opposite Axial direction is shifted, closed.
Such a shared mother is, for example, from the published French rule patent application FR 2 640 336, the published German patent application report DE 40 24 784 or the as yet unpublished German patent application dung DE 100 23 675 known, reference being made to the content of these three documents is taken. This split nut enables quick and easy loosening the screw connection without having to loosen against the release latching force is such. If the jaws are moved apart, then not only the Engagement between the internal thread segments and the external thread of the Ge windeschaftes reduced, but also the engagement between the locking element and Locking recess, whereby the release locking force is reduced. The cheeks can do that be moved far apart, that neither internal thread segments nor external thread still locking element and locking recess are in engagement with each other, so that in this state the nut can be moved axially on the threaded shaft can.
In this case it can be provided in a first alternative that the jaws, if the outer body is displaced in the release direction relative to the inner body, be moved radially outward and when the outer body relative to the inside body is moved in the tightening direction, moved radially inwards.
This first alternative is described in the above-mentioned DE 10 02 3675.
In a second alternative it can be provided that:
- The jaws each have a front section that the respective internal thread segment carries, and a one-piece adjoining rear section have, which is shaped similar to the front section, but relative to the sem is angled slightly outwards and instead of the internal thread segment has a threadless recess, the inner dimensions is larger than the internal thread segment; and
- The jaws at the transition point between the front sections and the Rear sections are pivotally mounted to each other so that the front derabschnitte 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, zuge be working.
This second alternative is described in the above-mentioned DE 40 24 784.
In both variants, it can also be provided that the secured screw connection has a screw with:
- An outer body that includes the threaded shaft and in the axial direction is divided into at least two legs, each a shaft section, the carries a segment of the external thread, and radially in front are excited; and
- An inner body ver between the legs in the axial direction is slidably disposed, the legs when the inner body in release direction of the screw between the legs is pulled out radially can be moved inwards.
Such a split screw is for example from the as yet unpublished German patent application DE 100 36 194 known, the content of this Document is referenced. Similar to the ge described above shared nut enables this split screw to be quick and easy Loosen the screw connection without loosening against the release latch force is required. If the legs are moved inwards, then not only that Engagement between the male thread segments and the female thread of the Ge reduced wind bore, but also the engagement between the locking element and Locking recess, whereby the release locking force is reduced. The legs can do this be moved far inward that neither male thread segments nor female threads winch still locking element and locking recess are in engagement with each other, so that in In this state, the screw is moved axially in the threaded hole can.
In addition, it can be provided that the locking recess is an axial groove.
Further features and designs of the invention are in the subclaims described.
In the following, preferred exemplary embodiments are described with reference to the attached Drawings described in more detail:
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 two-th 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 four-th embodiment according to the second variant;
Fig. 5 is a sectional side view of a secured screw connec tion in a fifth embodiment according to the first variant with a split nut, in which the jaws are open;
Fig. 6 is a cross section along the line VI-VI of Fig. 6;
Fig. 7 shows the screw connection of Figure 5, in which the jaws are closed.
Figure 9 is a side view of a jaw for the nut of Figures 5 to 8;
Fig. 10 is a sectional side view of a secured screw connec tion 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 XI-XI of Fig. 10;
Fig. 12 shows the screw connection of Figure 10, in which the legs are ge spread.
Fig. 13 is a cross section along the line XIII-XIII of Fig. 12;
Fig. 14 is a top view of the inner body of the screw of Figs. 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 be, in which the legs are spread; and
Fig. 17 is a plan view of the inner body of the screw of Fig. 16.
In Fig. 1, a secured screw connection is shown 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.
On the threaded shaft 12 , a locking element 13 is attached, which projects radially outwards. The locking element 13 here consists of a spring plate, which is anchored with egg ner edge in the threaded shaft 12 and whose opposite free edge runs parallel to the longitudinal axis A of the screw connection. Four locking recesses 15 are formed on the threaded bore 11 and are arranged at the same angular distance of 90 ° around the longitudinal axis A. Each recess 15 is an axial groove here, which extends over the length of the threaded bore 11 .
According to FIG. 1, the free edge of the locking element 13 is in the upper locking recess 15 , so that the screw connection is secured against unintentional loosening. Because to release the threaded shaft 12 must rotate relative to the nut 10 to the left from the shown position, so that the latching element 13 first comes into contact with the left flank of the upper latching recess 15 and thereby hinders 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 as Lö serastkraft.
If, on the other hand, the screw connection is to be tightened further, then the threaded shaft 12 must rotate from the position shown relative to the nut 10 to the right, so that the latching element 13 first comes into contact with the right flank of the upper latching recess 15 and thereby a further right rotation with special needs. 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 as the locking force. Now the threaded shaft 12 can be turned 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.
So that the bent locking element 13 can not clamp between the internal thread and the external thread, the external thread has a recess 17 in which the locking element 13 sits and which offers him sufficient space for evasion.
In this first embodiment, 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. In FIGS. 2 and 3 show two variations of the first exporting the other hand, are shown approximately form in which the release locking force is greater than the Anziehrastkraft so that the screw connection heavy dissolved and / or can be more easily attracted.
In FIG. 2 is a secured screw connection is shown approximate shape in a second exporting. In the right half of FIG. 2, the nut 10 is Darge alone.
In contrast to the first embodiment, 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 recess 15 . As a result, the tightening detent force is smaller than that of the first embodiment.
In Fig. 3, a secured screw connection is shown in a third embodiment. In the right half of FIG. 3, the threaded shaft 12 is Darge alone.
In contrast to the first embodiment, the locking element 13 is not symmetrical here, but 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 first 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 because it is just now who has to be set up and only then can be bent further. As a result, the detachment force is larger than in the first embodiment.
The second embodiment can of course also with the third embodiment be combined.
In FIG. 4 is a secured screw joint is shown in a fourth form of execution. In the lower half of Fig. 4, the nut 10 and the threaded shaft 12 are shown separately.
In contrast to the three previous embodiments, 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.
In Figs. 5 to 8, a secured screw connection is shown in approximate shape of a fifth embodiment. This fifth embodiment corresponds to the first embodiment, but has a split nut 10 , as described in DE 100 23 675.
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 slidably received 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 qua-shaped blocks, the length of which corresponds to the length of the outer body 16 and the width is slightly smaller than the width of the through opening 22 , as can be clearly seen in FIG. 6, so that they rotate in the Through opening 22 sit. 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 . Consequently, the upper jaw 18 in FIGS. 5 and 6 carries its internally threaded segment 24 on its underside, while the lower jaw 20 carries its internally threaded segment 24 on its upper side.
As can be clearly seen in FIG. 6, 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. This arrangement also applies accordingly to other embodiments of the nut 10 (not shown) in which more than two jaws are provided: in the case of three jaws, these are then preferably arranged at an angular distance of 120 ° from one another around the longitudinal axis A.
According to FIG. 6, first guide means are provided on the outer body 16 , which here comprise four lugs 26 which protrude from the through opening 22 . In this case, two lugs 26 are arranged at the same distance above and below the longitudinal axis A on the left and on the right side of the passage opening 22 in FIG. 6. 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 .
Usable for the first guide means on the outer body 16 are shown in FIGS. 5, 6 and 9 second guide means on the jaws 18, 20 which here comprise four grooves 30, in each of which one of the lugs 26 is running. Each jaw 18 , 20 has on its left side surface in FIG. 6 a groove 30 and in its right side surface another groove 30 symmetrical to this. Each groove 30 ent removed thereby as shown in FIGS. 5 and 9, so that their distance to the longitudinal axis A in Fig. 5 on the left is greater than in the tightening direction of the longitudinal axis A than the right. Thus, each groove 30 extends substantially axially in a plane which was parallel to and in the longitudinal axis A.
Although the grooves are straight here, they can also be curved in the axial direction his.
In contrast to the first embodiment, 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 has a second locking element 13 'which is offset by 90 ° to the first locking element 13 about the longitudinal axis A. As a result, as in the first to fourth embodiments, the screw connection is again in a locked, secured state after a rotation of 90 °, since either the first locking element 13 or the second locking element 13 'in one of the two locking grooves 15 sitting.
To simplify the drawings, the locking elements 13 , 13 'are only shown schematically in FIGS . 5 to 8.
The operation of the split nut 10 is described below with reference to FIGS. 5 to 8. In FIGS. 5 and 6, the nut 10 is ge in the open state, in which the jaws 18, 20 moved so far apart are that their inner 24 are not thread segments in engagement with the external thread of the threaded shaft 12, and also none of the latching elements 13 , 13 'engages with the locking recesses 15 . The nut 10 can therefore in this open state to the right in FIG. 5, that is to say in the release direction, be quickly pulled off the threaded shaft 12 without having to be rotated about its longitudinal axis A, as is the case with a conventional one-piece nut is. This property is particularly advantageous when the release latching force is high. The nut 10 can of course also be pushed to the left, that is to say in the tightening direction, onto the threaded shaft 12 without having to be rotated.
As can be clearly seen in FIG. 5, 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 hole 22 . 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 .
Since the height of the jaws 18 , 20 is selected so that with its radially outer surface 32 , the upper side of the upper jaw 18 and the lower side of the lower jaw 20 is in this opened state of the nut 10 on the upper or The bottom surface of the through opening 22 is prevented from tilting downward around the lugs 30 and then the left lower edge of the upper jaw 18 and the right upper edge of the lower jaw 20 from resting against the threaded shaft 12 .
To close the nut 10 , it is pushed from the position shown in FIG. 5 to the left until the jaws 18 , 20 abut the objects 14 to be connected with their left end faces. If the outer body 16 is pushed further to the left relative to the threaded shaft 12 , it is now also displaced to the left relative to the jaws 18 , 20 and thus, since these can no longer deflect to the left, pushed onto them. Now that the outer body 16 is displaced relative to the jaws 18 , 20 in the tightening direction, the lugs 26 in the grooves 30 also run in the tightening direction, so that the jaws 18 , 20 are pushed radially inward and are thus closed. Since the jaws 18 , 20 are moved radially inward, that is to say toward the threaded shaft 12 , their internally threaded segments 24 come evenly into engagement with the external thread of the threaded shaft 12 over their entire length. This prevents jamming and jamming of the internal thread desegmente 24 with the external thread by an oblique seat of the jaws 18 , 20 on the threaded shaft 12 . Otherwise there would be a risk that the nut 10 cannot be closed completely or, if this should be achieved with excessive force, the threads of the threaded shaft 12 and / or the jaws 18 , 20 will be damaged.
If the outer body 16 is completely pushed onto the jaws 18 , 20 , then the nut 10 is in the closed state, which is shown in FIGS. 7 and 8. In Fig. 7 is easily seen that then the lugs 26 sit in the left En de of the grooves 30 so that the internal thread segments 24 along a portion of a female thread form that fits the external thread of the threaded shaft 12, as shown in Fig. 8 is clearly visible. The jaws 18 , 20 thus form together 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 is in the closed state shown in FIGS . 7 and 8, then it can be tightened like a conventional one-piece nut who, since the inner body 18 , 20 is non-rotatably seated in the through hole 22 .
In this closed state, 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 such that, similarly to the fourth embodiment, the two locking elements 13 are attached to the inner thread segments 24 and the two locking recesses 15 are formed on the threaded shaft 12 . In order to ensure a snap-in here after each rotation by 90 °, 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.
In Figs. 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 portion 116 , which carries a segment of the external thread of the screw be 110 , and a head portion 117 , which is connected to the left end of FIGS . 10 and 12 of the shaft portion 116 .
In contrast to the fourth embodiment, the split screw 12 has only two locking recesses 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 Winkelab was arranged from 180 ° around the longitudinal axis A. The nut 10 corresponds here to that of the first to fourth embodiments, but has according to FIGS . 11 and 13 a second locking element 13 'which is offset by 90 ° to the first locking element 13 about the longitudinal axis A. As with 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 .
To simplify the drawings, the latching elements 13 , 13 'are only shown schematically in FIGS . 10 to 13.
The legs 114 , 115 are biased radially inward, that is, in the closed position shown in FIGS. 10 and 11. For this purpose it is provided here, for example, that 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. In addition, deviating from its position at the free end of the shaft sections 116 , the annular groove 118 can also be provided at another location on the shaft sections 116 .
Referring to FIGS. 10 and 12 of the upper leg 114 is formed a first bore 120 in the head section 117 which extends 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 formed here as through bores and each have a diameter in the radially outer section which 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 . The assembly of the guide pin 122 is described below.
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 closed state shown in FIG. 10, therefore, the upper and lower wedge surfaces 124 of the tip end of the inner body 113 bear against the oblique 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 closed state shown in FIG. 12. 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 central 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 . Therefore, the head end 126 lies in the spread state with its top and bottom on the radially inner surfaces 123 , and in this spread state the middle part 125 lies with its top and bottom on the bottom of the upper shaft portion 116 and on the top of the lower sheep section 116 .
In Figs. 14 and 15 of the inner body shows ge in plan view and side view of the 113th It has an axial slot 127 which extends over the entire length of the central part 125 to the head end 126 and opens into the top and bottom of the inner body 113 . The guide pin 122 is shown in FIGS. 10 and through the slot 127 12, so that the inner body 113 captive to the legs 114, 115 is connected.
As can be clearly seen in FIG. 11, 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 whose central angle is less than 180 ° is. 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 height of the shaft section 116 is smaller than the inner radius of the internal thread 111 .
The operation of the split screw 110 is described below with reference to FIGS. 10 to 13. In Figs. 10 and 11, the screw 110 is shown in ge closed state, in which the legs 114, 115 are so close to one another that their outer thread segments are not in engagement with the internal thread 111 of the nut 10 and also none of the latching elements 13, 13 'is in engagement with the locking recesses 15 . The screw 110 can therefore be quickly pushed into the nut 10 in this closed state to the right in FIG. 10, that is to say in the tightening direction, without having to be rotated about its longitudinal axis A, as is the case with a conventional one-piece screw Case is. 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.
As can be clearly seen in FIG. 10, 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 preloaded radially inwards with the aid of the snap ring 119 , their radially inner surfaces, ie the underside of the upper leg 114 , and the top of the lower leg 115 lie against one another.
To spread the screw 110 , the inner body 113 is pushed from the position shown in FIG. 10 to the right relative to the legs 114 , 115 , which is caused by the wedge action between the wedge surfaces 124 at the tip end of the inner body 113 and the oblique sections of the radially inner surfaces 123 of the Kopfab section 117 are initially pressed in the area of the head portion 117 radially outward and adjacent to the head portion 117 regions of the shaft portions 116 engage with the internal thread 111th If the inner body by 113 is pushed so far to the right that its tip end lies between the shaft sections 116 , then the legs 114 , 115 are not further spread in the above range, but are held in the spread position reached. The inner body 113 is pushed further to the right between the legs 114 , 115 , which are now pressed radially outward in the regions of the shaft sections 116 located further to the right and come into engagement with the internal thread 111. When the head end 126 lies between the head sections 117 and with its bevelled sections resting against its bevelled sections, 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 FIGS. 12 and 13. It can be clearly seen in FIG. 12 that the guide pin 122 then sits at the left end of the slot 127 .
In the Fig. 13 can be clearly seen that the external thread segments of the Schaftab sections 116 along the external thread of the screw 110 form that fits the internal thread 111 of the nut 10. 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 central part 125 of the inner body 113 form the threaded shaft 12 of the screw 110 , the outer diameter of which fits the outer diameter of the inner thread 111 of the nut 10 and the sum of the heights of the two shaft sections 116 and Height of the middle part speaks 125 ent.
When the screw 110 is in the expanded state shown in FIGS . 12 and 13, it can be tightened like a conventional one-piece screw. This is done with a conventional tool, such as a screwdriver or wrench that 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 .
In this spread state, the first locking element 13 also sits in the upper locking recess 15 , so that the screw connection is secured.
This sixth embodiment can of course also be varied so that Lich Lich as in the first embodiment, the two locking elements 13 on the legs 114 , 115 are attached and for this purpose the two locking recesses 15 are formed on the threaded bore 11 . In order to ensure a snap-in here after each rotation by 90 °, 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.
For assembly, the guide pin 122 , which initially only has a head end at its upper end in FIG. 12, is inserted with the lower end into the second bore 121 with the lower end in the spread state of the screw 110 and through the slot 127 so far from below into the first bore 120 pushed that his head de is supported on the shoulder of the second bore 121 , where its diameter decreases ver. 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.
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 inward against the inner body 113 , so that the pulling out of the inner body 113 is made more difficult.
In the Fig. 16 is a secured screw connection is shown in approximate shape of a seventh exporting. 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.
In contrast to the sixth embodiment, only a latching element 13 is provided here, which is anchored in the left side surface of the central part 125 of the inner body 113 in FIG. 16. In Fig. 17 this is the inner body geteil th screw 113 shown 10 in plan view. Since yes, as already mentioned above, the middle part 125 together with the shaft sections 116 of the legs 114 , 115 form the Ge threaded shaft 12 of the screw 110 , the locking element 13 , as in the first embodiment, is attached to the threaded shaft 12 , it is here, however, in a section of the threaded shaft 12 that does not have an external thread.
Since the locking recess 15 is an axial groove which extends over the length of the threaded hole 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 .
'' Locking element
objects to be screwed
Internal thread segment
radially outer surfaces of the jaws
inner wedge surfaces
radially inner surface of the head section
Wedge surface at the tip end of the inner body
Middle part of the inner body
Head end of the inner body
1. Secured screw connection, with:
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 is formed on the threaded bore.
2. Secured screw connection, with:
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.
3. Secure screw connection according to claim 1 or 2, characterized in that it has a nut with:
an outer body having an axial through hole;
an inner body which is slidably received in the through opening in the axial direction, has the 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 that they are moved apart when the outer body is displaced in an axial direction relative to the inner body, and are closed when the outer body is displaced in the opposite axial direction relative to the inner body.
4. Secured screw connection according to claim 3, characterized net that the jaws when the outer body relative to the inner body in Löserich tion of the nut is moved radially outward and when the Outer body is moved relative to the inner body in the tightening direction of the nut, be moved radially inwards.
5. Secured screw connection according to claim 3, characterized in that:
the jaws each have a front section that carries the respective internal thread segment, and an integrally adjoining rear section that is shaped similarly to the front section, but is slightly angled outwards relative to it and has a threadless recess instead of the internal thread segment, the Internal dimensions is larger than the internal thread segment; and
the jaws at the transition point between the front sections and the rear sections are pivotally mounted to one another in such a way that the front sections, when the outer body is displaced relative to the inner body in the loosening direction of the nut, are opened and when the outer body is displaced relative to the inner body in the tightening direction of the nut will be closed.
6. Secured screw connection according to one of the preceding claims, characterized in that it has a screw with:
an outer body which comprises the threaded shaft and is divided in the axial direction into at least two legs, each of which has a shaft section which carries a segment of the external thread and is stretched radially inwards; and
an inner body, which is slidably arranged between the legs in the axial direction, the legs, when the inner body is pulled out in the loosening direction of the screw between the legs, can be moved radially inward.
7. Secured screw connection according to one of the preceding claims che, characterized in that the locking recess is an axial groove.
DE2000149092 2000-09-27 2000-09-27 Secured screw connection Withdrawn DE10049092A1 (en)
DE2000149092 DE10049092A1 (en) 2000-09-27 2000-09-27 Secured screw connection
DE10066076A DE10066076A1 (en) 2000-09-27 2000-09-27 Secured screw connection
PCT/DE2001/003704 WO2002027199A1 (en) 2000-09-27 2001-09-27 Secured screw connection
PCT/DE2001/003703 WO2002027198A1 (en) 2000-09-27 2001-09-27 Secured screw connection
AU1381702A AU1381702A (en) 2000-09-27 2001-09-27 Secured screw connection
AU1381602A AU1381602A (en) 2000-09-27 2001-09-27 Secured screw connection
DE2001194132 DE10194132D2 (en) 2000-09-27 2001-09-27 Secured screw connection
DE2001194133 DE10194133D2 (en) 2000-09-27 2001-09-27 Secured screw connection
DE10049092A1 true DE10049092A1 (en) 2002-06-20
ID=7658625
DE2000149092 Withdrawn DE10049092A1 (en) 2000-09-27 2000-09-27 Secured screw connection
DE10066076A Withdrawn DE10066076A1 (en) 2000-09-27 2000-09-27 Secured screw connection
DE2001194133 Expired - Fee Related DE10194133D2 (en) 2000-09-27 2001-09-27 Secured screw connection
DE2001194132 Expired - Fee Related DE10194132D2 (en) 2000-09-27 2001-09-27 Secured screw connection
AU (1) AU1381702A (en)
DE (4) DE10049092A1 (en)
WO (2) WO2002027198A1 (en)
FR2640336A1 (en) * 1988-12-12 1990-06-15 Jouve Daniel Rapid nut
DE4024784A1 (en) * 1990-08-04 1992-02-13 Anton Woerndle Screw-nut device with outer element and two-segment inner section - has outer element slid forwards to lock pivoting segments, forming internal thread, and slid rearwards, to open thread
US1996727A (en) * 1934-01-20 1935-04-02 Gordon S Leslie Nut lock
DE10023675C2 (en) 2000-05-16 2003-04-17 Arno Giehl mother
DE10036194A1 (en) 2000-07-24 2002-02-21 Arno Giehl Screw
2000-09-27 DE DE2000149092 patent/DE10049092A1/en not_active Withdrawn
2000-09-27 DE DE10066076A patent/DE10066076A1/en not_active Withdrawn
2001-09-27 AU AU1381702A patent/AU1381702A/en active Pending
2001-09-27 WO PCT/DE2001/003703 patent/WO2002027198A1/en active Application Filing
2001-09-27 DE DE2001194133 patent/DE10194133D2/en not_active Expired - Fee Related
2001-09-27 WO PCT/DE2001/003704 patent/WO2002027199A1/en active Application Filing
2001-09-27 DE DE2001194132 patent/DE10194132D2/en not_active Expired - Fee Related
DE10194133D2 (en) 2003-09-04
AU1381702A (en) 2002-04-08
WO2002027199A1 (en) 2002-04-04
DE10194132D2 (en) 2003-08-07
DE10066076A1 (en) 2004-06-03
WO2002027198A1 (en) 2002-04-04
US7740427B2 (en) 2010-06-22 Drill plate with a clamping attachment in a base body
JP4431773B2 (en) 2010-03-17 Security nut fastening tool, security nut releasing tool and security nut fastening and releasing tool
2003-06-05 8143 Withdrawn due to claiming internal priority