EP4669871A1 - Moyen de liaison, ébauche de moyen de liaison et procédé de fabrication d'un moyen de liaison - Google Patents

Moyen de liaison, ébauche de moyen de liaison et procédé de fabrication d'un moyen de liaison

Info

Publication number
EP4669871A1
EP4669871A1 EP23833464.3A EP23833464A EP4669871A1 EP 4669871 A1 EP4669871 A1 EP 4669871A1 EP 23833464 A EP23833464 A EP 23833464A EP 4669871 A1 EP4669871 A1 EP 4669871A1
Authority
EP
European Patent Office
Prior art keywords
connecting means
longitudinal direction
region
blank
reduction structure
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.)
Pending
Application number
EP23833464.3A
Other languages
German (de)
English (en)
Inventor
Thorsten Schmitt
Stefan Wallmeier
Frank Wagner
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.)
Kamax Holding GmbH and Co KG
Original Assignee
Kamax Holding GmbH and Co KG
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 Kamax Holding GmbH and Co KG filed Critical Kamax Holding GmbH and Co KG
Publication of EP4669871A1 publication Critical patent/EP4669871A1/fr
Pending 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
    • F16B35/00—Screw-bolts; Stay-bolts; Screw-threaded studs; Screws; Set screws
    • F16B35/04—Screw-bolts; Stay-bolts; Screw-threaded studs; Screws; Set screws with specially-shaped head or shaft in order to fix the bolt on or in an object
    • F16B35/041—Specially-shaped shafts
    • F16B35/044—Specially-shaped ends
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21H—MAKING PARTICULAR METAL OBJECTS BY ROLLING, e.g. SCREWS, WHEELS, RINGS, BARRELS, BALLS
    • B21H3/00—Making helical bodies or bodies having parts of helical shape
    • B21H3/02—Making helical bodies or bodies having parts of helical shape external screw-threads ; Making dies for thread rolling
    • B21H3/06—Making by means of profiled members other than rolls, e.g. reciprocating flat dies or jaws, moved longitudinally or curvilinearly with respect to each other
    • 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
    • F16B35/00—Screw-bolts; Stay-bolts; Screw-threaded studs; Screws; Set screws
    • F16B35/04—Screw-bolts; Stay-bolts; Screw-threaded studs; Screws; Set screws with specially-shaped head or shaft in order to fix the bolt on or in an object
    • F16B35/041—Specially-shaped shafts
    • F16B35/048—Specially-shaped necks
    • 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
    • F16B37/00—Nuts or like thread-engaging members
    • F16B37/08—Quickly-detachable or mountable nuts, e.g. consisting of two or more parts; Nuts movable along the bolt after tilting the nut
    • F16B37/0807—Nuts engaged from the end of the bolt, e.g. axially slidable nuts
    • F16B37/085—Nuts engaged from the end of the bolt, e.g. axially slidable nuts with at least one unthreaded portion in both the nut and the bolt

Definitions

  • Fasteners fastener blanks and methods for producing fasteners
  • the invention relates to a connecting means, a connecting means blank and a method for producing a connecting means.
  • Fasteners are already known from the state of the art. They are used to connect components or sections to one another, usually using a thread on the fastener. Fasteners are also often used to allow adjustment. In order to provide a high level of precision, fasteners often have a groove that allows adjustment, particularly in chassis systems, in a form-fitting manner. However, this groove is designed in such a way that if the thread is formed by reshaping on the side opposite the groove, a poor thread design results. This usually means that the fastener is difficult to install.
  • a connecting means in particular a bolt or a screw, is advantageously provided.
  • the connecting means comprises a head region and/or a threaded region, the head region having actuating surfaces, the threaded region extending along and around a longitudinal direction, the threaded region having a thread whose center line lies in the longitudinal direction, the threaded region having a groove introduced in a radial direction, which extends in particular parallel to the longitudinal direction, the radial direction being perpendicular to the longitudinal direction, a stiffness reduction structure, in particular a recess or an underfill, being provided in the threaded region opposite the groove or opposite +/- 60° to the groove.
  • the connecting means serves to mechanically connect a wide variety of components and/or sections to one another, in particular within the framework of a force-locking connection.
  • the connecting means can also be a form-locking connecting means.
  • the connecting means is also particularly suitable and/or intended for adjustment, in particular of a chassis.
  • the connecting means comprises a head region. This head region forms in particular a distal end in the longitudinal direction of the connecting means.
  • the head region can have actuating surfaces. These actuating surfaces expediently have a normal which is directed in or parallel to the radial direction.
  • the radial direction is in particular the direction which is expediently perpendicular to the longitudinal direction.
  • the longitudinal direction is in particular the direction in which the length of the thread region and/or the connecting means is determined.
  • the thread region can also form a distal end of the connecting means in the longitudinal direction.
  • one distal end in the longitudinal direction of the connecting means can be formed by the head region and the other distal end of the connecting means by the thread region.
  • the center line of the thread provided in the thread region lies on the longitudinal direction or this center line can be congruent with the longitudinal direction at least in sections.
  • a center line is the line from which the core radius or the flank radius of the thread is determined.
  • the center line is the central axis, around which the thread is formed.
  • the longitudinal direction, the radial direction and a circumferential direction can form a cylinder coordinate system, with the longitudinal direction in particular forming the height direction, the radial direction, the radial coordinate, and the circumferential direction forming the angular coordinate.
  • a groove is formed in the thread area, which is radially introduced into the thread areas.
  • the groove can therefore be formed in a plane perpendicular to the longitudinal direction or to the center line in such a way that it is introduced into the thread in the radial direction from the outside to the inside.
  • the longitudinal extent of the groove is in particular formed parallel to the longitudinal direction.
  • the groove can therefore be formed in a straight line and/or parallel to the longitudinal direction.
  • the groove serves in particular to be able to achieve a form-fitting anti-twisting lock of an eccentric element. In other words, when the connecting means is used as an adjustment means - by introducing an eccentric element into the groove - an adjustment option can therefore be achieved.
  • the invention can also relate to an adjustment system comprising a connecting means and a separate eccentric element, wherein the eccentric element in particular has an externally running surface whose center of gravity is spaced from the longitudinal direction or the center line in order to achieve eccentricity.
  • the eccentric element engages at least partially, in particular by means of a projection, in the groove and/or surrounds the connecting means, in particular in the threaded area in which the groove is also present.
  • the threaded area also has a stiffness reduction structure opposite the groove or opposite +/- 60° to the groove, in particular in the form of a recess or an underfill.
  • Opposite is to be understood in particular as meaning that in a cutting plane perpendicular to the longitudinal direction, which intersects the groove and the stiffness reduction structure, there is a connecting line between the stiffness reduction structure and the groove, which runs through the longitudinal direction or intersects it.
  • the intersection point of this connecting line with the longitudinal direction is arranged between the stiffness reduction structure and the groove.
  • Opposite can also be understood in particular to mean that the stiffness reduction structure is arranged 180° offset from the groove in the circumferential direction. is arranged.
  • An opposite +/- 60°, in particular to the groove can be understood to mean that there can also be a deviation of up to +/- 60° from the opposite.
  • the stiffness reduction structure is in particular a structure which causes the contact pressure on the other opposite plane to be locally increased when the threaded area is arranged between two ideal planes and when the groove comes into contact with one of these planes. However, this simultaneously causes an increase in the contact pressure with the same contact force, so that a greater deformation is achieved. Therefore, this type of structure is also referred to as a stiffness reduction structure in the context of the invention.
  • This stiffness reduction structure can in particular be an underfill or also a groove, wherein the stiffness reduction structure in particular has its largest main dimension in the longitudinal direction or parallel to the longitudinal direction.
  • the stiffness reduction structure is preferably designed to be straight or unchanged in the longitudinal direction. This makes it particularly easy to manufacture. As already mentioned, these stiffness reduction structures can increase the local surface pressure in particular, so that thread forming can be carried out in a simple manner.
  • the stiffness reduction structure is, as already explained, in particular a recess or an underfill.
  • An underfill is characterized in particular by the fact that it is arranged on the outside and, although basically in the thread area, the underfill does not have any threads, in particular thread peaks, but at most thread valleys. This can also increase the local surface pressure during the thread forming of the thread in the thread area.
  • a recess is present in particular when it is completely surrounded by surrounding materials except in its direction of extension or perpendicular to its direction of extension.
  • the stiffness reduction structure can also preferably be a groove.
  • a further aspect of the invention may relate to a fastener blank.
  • the fastener blank is used in a production in order to form a connecting means as described above and/or below.
  • the elements already set out for the connecting means can also exist in the connecting means blank, but instead of the threaded area in the connecting means blank there is a shaft area which serves in particular to provide a thread by means of a thread forming process or to form a thread in the shaft area in order to thus provide a threaded area.
  • the transformation from the connecting means blank to the connecting means therefore takes place in particular exclusively by forming the shaft area in such a way that a threaded area is created.
  • the shaft area of the connecting means blank is therefore thread-free and can otherwise have the same or the same features as the threaded area.
  • the invention can advantageously also relate to a fastener blank, in particular for producing a bolt or a screw, comprising a head region and a shaft region, wherein the head region can have actuating surfaces, wherein the shaft region extends along and/or around the longitudinal direction, wherein the shaft region is cylindrical or at least substantially cylindrical and its cylinder axis lies in the longitudinal direction, wherein the shaft region has a groove introduced in a radial direction or in the radial direction, which extends in particular parallel to the longitudinal direction, wherein the radial direction is perpendicular to the longitudinal direction, wherein a stiffness reduction structure, in particular a recess or an underfill, is provided in the shaft region opposite the groove or opposite +/- 60° to the groove.
  • the features already set out with regard to the fastener in particular relating to the head region, the actuating surfaces, the longitudinal direction, the radial direction, the groove and the stiffness reduction structure, can be provided in the same or equivalent manner in the fastener blank.
  • the features that are set out for the fastener with regard to the thread area can apply in an equivalent manner to the shaft area of the fastener blank. This naturally also applies in reverse order, so that the features, advantages and design of the fastener blank can also be applied in an equivalent manner in the connecting means, unless this is excluded due to the missing thread in the connecting means blank.
  • the shaft region of the connecting means blank can be cylindrical or at least essentially cylindrical.
  • Essentially cylindrical can be understood to mean that the basic geometry is almost exclusively rotationally symmetrical about the cylinder axis.
  • Almost exclusive rotational symmetry exists in particular when, in a cross-section perpendicular to the cylinder axis, which may run parallel to the longitudinal direction, the shaft region always has the same width or the same distance, but without taking the groove and/or the stiffness reduction structure into account in this consideration. Cylinders or cones in particular are therefore to be regarded as an almost exclusively rotationally symmetrical design.
  • a local surface load of the shaft area can also be increased during the forming of a thread, so that the decisive contact pressure between a thread forming device, in particular a rolling die, and the shaft area is increased during thread forming, so that the plastic deformation levels can be increased in order to achieve a better or more defined thread design opposite or opposite +/- 60° to the groove.
  • this can increase the load-bearing capacity of the thread and/or the gaugeability of the thread. This can also make screwing in the thread easier.
  • the connecting means and/or the connecting means blank are in particular formed as one piece. This allows a particularly high level of mechanical strength to be achieved.
  • the term "one piece” means in particular that the means/component is not created by joining several components.
  • the connecting means and/or the connecting means blank are made in particular from a high-strength or an ultra-high-strength material.
  • a high-strength material is in particular a material whose tensile limit or sen tensile strength is at least 800 N/mm 2 , preferably at least 1000 N/mm 2 .
  • An ultra-high-strength material has a tensile limit or a tensile strength of at least 1200 N/mm 2 , preferably of at least 1400 N/mm 2 .
  • the fastener can be grouped in the strength classes 8.8, 10.9, 12.9 or even 14.8 or 14.9, 15.8U, 15.9U or higher. In other words, the fastener can therefore be in these strength classes or have them.
  • the stiffness reduction structure is a female structure.
  • a female structure means that material is removed or is not present in order to form the structure.
  • a female stiffness reduction structure or structures cannot be characterized by projections, but only by recesses, recesses and/or underfills.
  • the stiffness reduction structure advantageously limits the thread area and/or the shaft area in the radial direction.
  • the stiffness reduction structure can therefore be introduced radially from the outside into the thread area or the shaft area.
  • the stiffness reduction structure can therefore interrupt thread turns in the thread area and/or disrupt and/or interrupt their continuous course, in particular in the continuous course of the thread peaks and/or the thread valleys. This makes it possible to achieve a particularly simple and effective design of the stiffness reduction structure.
  • the or a stiffness reduction structure can be a structure extending in the longitudinal direction. This is to be understood in particular that the main extension direction of the stiffness reduction structure runs in the longitudinal direction or parallel to the longitudinal direction. This allows a particularly simple and quick design of the stiffness reduction structure. In addition, this type can also ensure that, especially when the groove runs along the longitudinal direction or parallel to the longitudinal direction, the stiffness reduction structure is always formed opposite the groove.
  • the stiffness reduction structure is designed in such a way that a part of the groove always runs opposite it along its course.
  • the stiffness reduction structure is designed in such a way that the groove is also cut in all planes that the stiffness reduction structure intersects and which run perpendicular to the longitudinal direction.
  • the stiffness reduction structure is a recess, in particular a bore, made in an end face, wherein the end face delimits the connecting means or the connecting means blank in the longitudinal direction.
  • the or one of the stiffness reduction structures can be a recess made in the longitudinal direction of the connecting means or the connecting means blank.
  • This recess is advantageously provided with a round, in particular circular, cross-section in a plane perpendicular to the longitudinal direction.
  • This recess advantageously extends in a direction parallel or congruent with the longitudinal direction. This makes it possible to achieve particularly simple production and also a particularly uniform reduction in stiffness through the stiffness reduction structure.
  • the stiffness reduction structure is advantageously surrounded in the longitudinal direction by the threaded region and/or the shaft region.
  • parts of the threaded region or the shaft region extend in the longitudinal direction above or below the stiffness reduction structure. Consequently, there are distal end regions of the threaded region and the shaft region in the longitudinal direction which are designed to be free of stiffness reduction structures.
  • the notch effect factor caused by the stiffness reduction structure can also be reduced.
  • an unfavorable encounter between two influences that increase the notch effect factor, namely the distal ends and the stiffness reduction structures can be avoided or reduced.
  • the stiffness reduction structure advantageously has a rectangular, round, in particular circular, or elliptical cross-section.
  • the cross-section is understood to mean the base area and/or the wall areas of the stiffness reduction structure that is open on one side, in particular the groove or the recess.
  • a geometry that is particularly easy to produce can be achieved by means of a rectangular or flat design, in particular of the base area. If, on the other hand, the base and/or the cross-section and/or the transition between the wall area and the base area or even the entire wall and base area are round, in particular circular, or elliptical, a design with a particularly low notch effect can be achieved in this way.
  • the stiffness reduction structure advantageously extends to a distal end of the threaded region or the shaft region in the longitudinal direction.
  • a stiffness reduction structure can also be provided directly from a distal end of the shaft region or the threaded region. This makes it possible to later achieve particularly simple threading into the groove opposite the stiffness reduction structure using an eccentric element or an adjusting element. Alternatively or additionally preferably, this can simplify or improve the subsequent threading of the thread, in particular into a nut thread.
  • the extension of the stiffness reduction structure in the longitudinal direction is a maximum of 3.2 times, preferably a maximum of 2 times, and particularly preferably a maximum of 1.7 times, the diameter of the threaded area or the shaft area.
  • This allows a particularly gentle thread production for the forming tool, while at the same time a nut can be mounted on the particularly well-formed threaded area by the stiffness reduction structure, in particular a nut in combination with a lock nut.
  • the ratio of the extension of the stiffness reduction structure in the radial direction to the diameter of the shaft region or to the diameter of the threaded region is in a ratio of 0.01 to 0.1, preferably in a range of 0.012 to 0.06 and particularly preferably in a range of 0.013 to 0.04.
  • the extension of the stiffness reduction structure in the radial direction is in particular the depth of the stiffness reduction structure in the radial direction or the height. These can in particular be the maximum or minimum depth or height, which is advantageously measured from a circle around the center line or the circle congruent with the diameter of the shaft region. With a ratio in the range of 0.01 to 0.1, particularly simple production can be achieved.
  • the ratio is in a range of 0.012 to 0.06, this can achieve an advantageous design with a low notch effect factor.
  • the ratio is in a range of 0.013 to 0.14, this can achieve an advantageous design of the thread, while at the same time resulting in a particularly low mechanical load or overload due to the notch effect factor.
  • the extension of the stiffness reduction structure in the longitudinal direction to the diameter of the shaft region or the diameter of the threaded region is in a ratio of 1.0 to 3.2, preferably in a range of 1.5 to 2 and, particularly preferably, in a range of 1.5 to 1.75.
  • the length of the stiffness reduction structure is in particular the length of the outer contours of the stiffness reduction structure on the shaft region, which precisely characterizes the outer dimensions of the stiffness reduction structure.
  • the length is in particular the main dimension of this contour in the longitudinal direction. If the ratio is in a range of 1.0 to 3.2, this can result in particularly simple production.
  • the ratio is in a range of 1.5 to 2, this can result in particularly little mechanical weakening of the shaft region or the subsequent threaded region. If the ratio However, if the diameter is in a range of 1.5 to 1.75, a particularly mechanically resilient thread design can be achieved.
  • the diameter of the shaft area is in particular the nominal diameter of the same without taking into account the stiffness reduction structure and/or the groove.
  • the extension of the stiffness reduction structure in the longitudinal direction to the length of the shaft region or the thread region in the longitudinal direction is in a ratio of 0.1 to 0.5, preferably in a range of 0.15 to 0.4, and particularly preferably in a range of 0.2 to 0.3. If the ratio is in a range of 0.1 to 0.5, this can result in particularly simple production. If, on the other hand, the ratio is in a range of 0.15 to 0.4, this can result in a particularly low mechanical weakening of the shaft region or the subsequent thread region. If, however, the ratio is in a range of 0.2 to 0.3, this can result in a particularly mechanically resilient design of the thread.
  • the diameter of the shaft area is in particular the nominal diameter of the same without taking into account the stiffness reduction structure and/or the groove.
  • the connecting means is advantageously an eccentric screw and/or the connecting means blank is an eccentric screw blank.
  • An eccentric screw or an eccentric screw blank is understood to mean that it has an eccentric structure which has a circular or elliptical outer region, the center of which is eccentrically displaced to the longitudinal direction, in particular in the radial direction.
  • This eccentric structure can advantageously be formed in one piece with the connecting means or with the connecting means blank.
  • the eccentric structure is advantageously arranged between the head region and the thread region or the shaft region.
  • the stiffness reduction structure does not penetrate the connecting means or the connecting means blank. In other words, the stiffness reduction structure does not extend completely to an opposite side. This can prevent or at least reduce mechanical weakening. Therefore, the stiffness reduction structure is in particular a recess or an underfill.
  • a further aspect of the invention can relate to a connecting means system comprising a connecting means blank or a connecting means and an eccentric element, wherein the eccentric element can have an eccentric structure and/or wherein the eccentric element engages or can engage with a projection in the groove of the connecting means or the connecting means blank.
  • the eccentric element can thus be secured in a form-fitting manner in the circumferential direction against rotation by the groove and this projection.
  • the connecting means or the connecting means blank can have the features, configurations or advantages or embodiments described above and/or below.
  • a further aspect of the invention may relate to a method for producing a connecting means.
  • this method comprises the steps:
  • the process described here can be used to transform a fastener blank into a fastener in a simple and effective manner. Rethinking the groove means in particular that the rolling tools are one side of the connecting means is in contact with the edge areas of the groove and on the other side exerts a force and/or a deformation effect on parts and/or edge areas of the stiffness reduction structure.
  • the stiffness reduction structure in the connecting means blank in particular opposite the groove or opposite +/- 60° to the groove, a locally increased surface pressure can be achieved when forming the thread, so that the formation of the thread is positively supported and/or improved.
  • Figure 1 shows a method for producing a connecting means
  • Figure 2 shows a fastener blank in isometric view
  • Figure 3 is a detailed view of a threaded area of a fastener
  • Figure 4 shows a further detailed view of a threaded area of a connecting means
  • Figure 5 shows an alternative detailed view of a threaded area of a fastener.
  • Figure 1 shows a situation during a method for producing a connecting means 1.
  • the right-hand rolling tool 100 covers the groove 44, wherein a stiffness reduction structure is introduced opposite this groove 44, which is simultaneously covered by the rolling tool 100 arranged on the left side.
  • Figure 1 shows a situation in which the introduction a thread in the fastener blank 2, a fastener 1 is created or manufactured.
  • Figure 2 shows a connecting means blank 2 which has a head region 10.
  • This head region 10 has actuating surfaces 12, each of which has a normal which is parallel to the radial direction R.
  • the connecting means blank 2 also has a shaft region 40, with the eccentric structure 39 being arranged between the shaft region 40 and the head region 10.
  • the shaft region 40 is cylindrical.
  • the shaft region 40 has a groove 44, with a stiffness reduction structure in the form of a recess 46 or an underfill 48 being provided opposite.
  • Figure 3 shows a detailed view of a threaded area 30 of a connecting means 1.
  • the connecting means 1 has a thread 32 in the threaded area 30.
  • the threaded area 30 can be formed by the part in which the thread 32 is present.
  • the thread 32 or the threaded area 30 has numerous underfills 38, which each interrupt the course of the thread crests of the thread 32.
  • the threaded area 30 also has a groove 34.
  • Figure 4 shows a further embodiment of a threaded region 30 of a connecting means 1.
  • the stiffness reduction structure which in the example presented is designed as an underfill 38, can have a depth in the radial direction R or a thickness in the radial direction R which is less than the height difference between the thread peak and the thread valley. Such an embodiment can be independent of the actual embodiment of the underfill 38 presented here.
  • the stiffness reduction structure is surrounded in the longitudinal direction L by the threaded region 30. In the longitudinal direction L, the threaded region 30 is bordered by the end face 60.
  • Figure 5 shows a further alternative embodiment of a connecting means 1.
  • the threaded region 30 also has a thread 32, wherein the stiffness reduction structure is formed as a recess 36 in the longitudinal direction L or by a recess 36 running parallel to the longitudinal direction L.
  • the center line of the recess 36 in the radial direction R is spaced from the longitudinal direction L. This also makes it possible in particular to use the recess 36 for a positive rotary drive during the formation of the thread.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Forging (AREA)
  • Connection Of Plates (AREA)
  • Mutual Connection Of Rods And Tubes (AREA)

Abstract

L'invention concerne une ébauche de moyen de liaison (2), en particulier pour la fabrication d'un boulon ou d'une vis, comprenant une région de tête (10) et une région de tige (40), la région de tête (10) comprenant des surfaces d'actionnement (12) ; la région de tige (40) s'étend le long et autour d'une direction longitudinale (L) ; la région de tige (40) est cylindrique et son axe de cylindre se trouve dans la direction longitudinale (L) ; la région de tige (30) présente une rainure (44) qui est introduite dans une direction radiale (R) et qui s'étend en particulier parallèlement à la direction longitudinale ; la direction radiale (R) est perpendiculaire à la direction longitudinale (L) ; une structure de réduction de rigidité, en particulier une découpe (46) ou un sous-remplissage (48), est disposée à l'opposé de la rainure (44) ou +/- 60° opposée à la rainure dans la région de tige (40).
EP23833464.3A 2023-02-21 2023-12-18 Moyen de liaison, ébauche de moyen de liaison et procédé de fabrication d'un moyen de liaison Pending EP4669871A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102023104264.5A DE102023104264A1 (de) 2023-02-21 2023-02-21 Verbindungsmittel, Verbindungsmittelrohling und Verfahren zum Herstellen eines Verbindungsmittels
PCT/EP2023/086436 WO2024175241A1 (fr) 2023-02-21 2023-12-18 Moyen de liaison, ébauche de moyen de liaison et procédé de fabrication d'un moyen de liaison

Publications (1)

Publication Number Publication Date
EP4669871A1 true EP4669871A1 (fr) 2025-12-31

Family

ID=89430003

Family Applications (1)

Application Number Title Priority Date Filing Date
EP23833464.3A Pending EP4669871A1 (fr) 2023-02-21 2023-12-18 Moyen de liaison, ébauche de moyen de liaison et procédé de fabrication d'un moyen de liaison

Country Status (5)

Country Link
EP (1) EP4669871A1 (fr)
CN (1) CN120712419A (fr)
DE (1) DE102023104264A1 (fr)
MX (1) MX2025009822A (fr)
WO (1) WO2024175241A1 (fr)

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KR102256916B1 (ko) * 2019-09-27 2021-05-27 한국안전기술주식회사 티볼트 조립체
DE202019106653U1 (de) * 2019-11-29 2021-03-02 Rehau Ag + Co Trägervorrichtung für ein Außenverkleidungsteil eines Kraftfahrzeugs

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