FITTING

Description

[0001] The invention relates to a fitting for securing a threaded element to a wall section, having a base body through which a recess extends along a central axis, having a clamping ring which is rotatably mounted on an outer surface, in particular on a sleeve section arranged coaxially to the central axis, of the base body, wherein the outer surface, in particular the sleeve section, is assigned a first control cam and / or wherein the clamping ring is assigned a second control cam which is designed for an elastic or elastic and plastic change in the diameter of the clamping ring during a rotational movement of the clamping ring relative to the base body.

[0002] From DE 10 2004 045 675 B1 a clamping means is known which comprises a working part and a clamping part which can be connected to one another, wherein cams are arranged on the working part or the clamping part, by means of which cams the working part and the clamping part are clamped to one another.

[0003] EP 2 655 902 B1 discloses a cage nut with a holding device and a method for producing the same. The cage nut has a nut with a radially projecting square flange and a threaded sleeve-like receptacle for a screw. A holder with a through-opening through which the sleeve-like screw receptacle passes, engages like a bracket over the square flange of the nut. A holding collar, which encloses the sleeve-like screw receptacle of the nut, rests on the holder in the area of ​​the through-opening. The holding collar is one-piece and has first and second cover elements covering the through-opening of the holder on both sides. The cover elements are mechanically connected via a connecting bushing that lies concentrically on the screw receptacle. The connecting bushing is at a radial distance from the through-opening.

[0004] From EP 0 696 686 B1 it is known that a tubular shaft at one end of a nut cage is inserted into an opening in a wall and expanded to connect it to the wall and the wall material surrounding the opening is cold worked to improve fatigue strength. The nut cage includes a cage bottom area for receiving the central part of a nut. One end portion of the nut bottom is inserted into a bushing. A second end portion of the nut socket is pushed axially into a channel. A snap ring is then installed and moved so that a closed portion lies over the end portion of the nut base. The bushing and the channel hold the nut socket against rotation in the nut cage. The channel and a portion of the snap ring, which closes the channel and the axial boundaries of the socket, prevent the nut socket from moving axially out of the nut cage.

[0005] DE 10 2012 019 037 A1 discloses a cage nut arrangement for arrangement on a through-opening of a support component, comprising a cage section receiving a nut and an insert connected thereto, which insert is mechanically deformable in an installation position on the support component passing through the through-opening, forming a positive connection with the through-opening.

[0006] US 6 183 180 B1 discloses a tubular shaft which is inserted at one end of a nut holder into an opening in a wall and expanded to connect it to the wall. An annular collar or space contacts the wall and immediately surrounds the opening. A slip-on nut is clamped onto a nut receptacle, the end of which lies outside the collar. By a compressive movement on the slip-on nut, the locking tabs are moved past diametrically opposed edge portions of the nut receptacle and brought into positions below the edge portions of the nut receptor. When thus positioned, the drivers hold the slip-on nut on the nut receptacle. The slip-on nut can be a sealed nut.When this is the case, the locking tabs are positioned so that when they engage under portions of the rim of the nut receiver, a sealing ring at the base of the nut is compressed. This compression of the sealing ring causes the nut to be sealed before a bolt is connected to the nut.

[0007] US 2 820 499 A discloses a floating anchor nut for the blind fastening of conical parts.

[0008] KR 100 843 934 B1 discloses an angle-adjustable insert that ensures that a hanger bolt is always perpendicular to the ground surface, even when installed on a deck plate or an inclined surface. The angle-adjustable insert consists of a base, a housing, a spherical union nut, a cap, and a vibration-resistant material. The base consists of a circular mounting plate provided with a plurality of mounting holes at regular intervals, a conical insertion projection formed in the center of the upper surface of the mounting plate, and a projection that prevents rotation occurring on top of the insertion projection. The housing consists of an insertion tube containing the rotation-preventing projection and the insertion projection, and a cylindrical body formed in an upper end of the insertion tube.The coupling nut is inserted into the housing so that the lower end of a coupling hole is inserted into the anti-rotation projection. The cap is inserted into the upper end of the housing through a cylindrical coupling projection. The vibration-resistant material is installed between the lower end of the housing and the lower end of the union nut.

[0009] WO 2020 / 055624 A1 discloses an installation system for a box profile for a motor vehicle. The installation system comprises at least one support bar that can be inserted into the box profile and at least one nut element for pre-positioning on the support bar, wherein the nut element is designed for releasable pre-positioning on the support bar.

[0010] DE 44 12 431 C1 discloses a device for the proper spacing of components provided with installation openings by means of a spacer, a connecting screw, and a counterbearing. The spacer consists of a holding body that can be attached to a component and a supporting body opposite it that can be moved relative to the longitudinal axis of the connecting screw. The holding body is a U-clip with mounting feet at one end and has an internal thread into which the holding body can engage with a corresponding thread. The supporting body is provided with a through-hole.

[0011] The object of the invention is to provide a fitting that can be used in a variety of ways.

[0012] This object is achieved for a fitting part of the type mentioned at the outset with the features of claim 1. It is provided that a coupling part is movably received in the recess and forms a play-related rotary coupling with the base body for transmitting a torque between the coupling part and the base body about the central axis, wherein a threaded portion of the coupling part determines a thread axis which is aligned with a variable orientation in a predeterminable angular interval and / or in a predeterminable distance interval from the central axis.

[0013] The fitting part is used to reliably fasten another component, such as a cladding part, to the wall section in a simple manner. It is assumed that the wall section is provided with a recess which enables at least partial accommodation of the clamping ring of the fitting part. The fitting part is fastened to the wall section by initiating a relative movement between the base body and the clamping ring, whereby at least elastic, and possibly also elastic and plastic deformation is caused when the clamping ring expands due to the interaction of the at least one first control cam of the sleeve section of the base body with the clamping ring or the second control cam of the clamping ring with the sleeve section of the base body. This enables a force-fitting coupling of the fitting part to the wall section.

[0014] To connect the component to be fixed, which may be a trim part, for example, to the fitting, a threaded section is formed on a coupling part belonging to the fitting, which can in particular be implemented as a stud bolt or as a threaded hole. The base body with the recess provided therein and the coupling part are coordinated with one another in such a way that during a screwing process with which, for example, a nut or a screw is to be fixed to the threaded section of the coupling part in order to fasten the other component, a torque is introduced around the central axis of the base body from the coupling part to the base body and, due to this torque, the desired rotational relative movement between the base body and the clamping ring is brought about in order to bring about the elastic or elastic and plastic expansion of the clamping ring.The threaded portion may comprise one or more threads and may, for example, be designed as a metric thread or an inch thread. It may also be provided that the thread of the threaded portion extends over an angular range of less than 360 degrees, thus enabling a locking connection between the coupling part and a corresponding locking element in the manner of a bayonet connection.

[0015] In principle, it is desirable that the recess in the wall section, which is intended to accommodate at least a portion of the clamping ring of the fitting, be formed in the wall section in such a way that the component to be secured can be secured without difficulty. Due to manufacturing tolerances, which must be taken into account both for the wall section and the recesses therein, as well as for the component to be secured, it may happen that a fastening area of ​​the component to be secured, which may, for example, be designed as a bore for accommodating a screw intended to engage the threaded portion of the coupling part, is not optimally aligned.Accordingly, either rework of the component to be fixed must be accepted to compensate for existing tolerances, or the component to be fixed is secured to the wall section using the fitting under a certain, usually undesirable, preload. To reduce the influence of such almost unavoidable manufacturing tolerances, the coupling part is designed to be movably mounted in the recess of the base body, thus ensuring tolerance compensation for positioning tolerances, at least within certain limits.In order to enable the desired force-locking fixing of the fitting part to the wall section despite the mobility of the coupling part in the recess of the base body, the recess of the base body and the coupling part form a rotary coupling with play, which on the one hand allows a certain adjustment of the spatial orientation of the coupling part relative to the base body and thus a compensation of tolerances, but on the other hand enables a torque transmission between a fastening means for the component to be fixed, such as a screw or a nut, the threaded section of the coupling part and the base body, in order to thereby ensure the relative movement of the base body relative to the clamping ring and the resulting elastic or elastic and plastic expansion of the clamping ring.

[0016] Here, it is provided that the coupling part and the recess of the base body are adapted to one another in such a way that a thread axis of the coupling part, which is determined by the threaded section, can be moved within a movement range determined by the geometry of the recess and the geometry of the coupling part. For example, it is provided that the coupling part can be rotated relative to the base body about the central axis within a predeterminable angular range, for example within a range of + / - 20 degrees, and upon reaching an interval limit of this angular range, it assumes a blocking position relative to the base body, in which blocking position the desired torque transmission about the central axis between the coupling part and the base body can take place. In a similar way, it can be provided that the coupling part is received in the recess so that it can move linearly within a certain, predeterminable interval.In this case, a linear movement of the coupling part relative to the base body can be provided both in spatial directions parallel to the central axis and in spatial directions transverse to the central axis. In addition or alternatively, it can be provided that the coupling part is accommodated in the recess so that it can tilt within a certain, predeterminable interval. Tilting movements of the coupling part relative to the base body preferably take place about tilting axes that are aligned transversely to the central axis. As with the rotational movement of the coupling part about the central axis, maximum deflections are also provided for linear movements and / or tilting movements of the coupling part relative to the base body. For linear movements, it is assumed that the threaded axis of the coupling part cannot exceed a predeterminable maximum distance from the central axis.During tilting movements of the coupling part, it is assumed that the thread axis of the coupling part cannot exceed a predefined maximum angle relative to the central axis.

[0017] The recess and coupling part are adapted to one another in such a way that, in a release position, the coupling part is accommodated in the recess in a tilting and / or linearly movable manner with at least one geometrically limited degree of freedom of movement, and in a functional position, is designed for torque transmission between the threaded section, which is designed in particular as an internal thread, and the base body. It is assumed that, in the release position, no torque transmission takes place between the coupling part and the base body, and that a relative movement of the coupling part relative to the base body can occur with a limited range of motion due to the geometric design of the coupling part and the recess in the base body.Depending on the geometry of the coupling part and the geometry of the recess in the base body, a relative movement between the coupling part and the base body can be exclusively linear, exclusively rotational, or a combination of linear and rotational. When a torque is applied to the threaded portion of the coupling part, as can occur, for example, at the beginning of a screwing process for a screw into a threaded hole in the coupling part or at the beginning of a screwing process for a nut onto a stud bolt of the coupling part, a transition occurs between the release position and the functional position. This transition is typically implemented by a rotational movement of the coupling part relative to the base body around the central axis.In the functional position, the geometry of the coupling part and the geometry of the recess in the base body ensure a positive coupling between the coupling part and the base body, at least with regard to torque transmission around the central axis. This allows torque to be transmitted from the coupling part to the base body, which then also leads to the desired relative movement between the base body and the clamping ring. Depending on the design of the geometries of the coupling part and the recess, a certain centering of the coupling part relative to the base body may occur during the transition from the release position to the rotation position. However, this is neither necessary nor essential for the proper functioning of the fitting.

[0018] Alternatively, it can be provided that the relative movement between the base body and the clamping ring is carried out by a direct introduction of torque onto the base body, for example by means of an open-end wrench which is applied to suitable wrench surfaces of the base body, and a screwing process for the screw with which the component to be fastened is to be fixed into the coupling part is only carried out at a later point in time.

[0019] According to the invention, a partial area of ​​an outer surface of the coupling part defines a first profile section, wherein a partial area of ​​an inner surface of the recess defines a second profile section, wherein the first profile section forms with the second profile section in a functional position a rotary coupling with play for torque transmission between the coupling part and the base body and in a release position for a relative movement between the coupling part and the base body is designed with at least one geometrically limited rotational degree of freedom and / or at least one geometrically limited linear degree of freedom of movement.

[0020] It is expedient if the coupling part, in particular in sections, has a first cross-section in a cross-sectional plane oriented transversely to the central axis and that the recess, in particular in sections, has a second cross-section in the cross-sectional plane, wherein the first cross-section and the second cross-section are geometrically similar, in particular the second cross-section arises from the first cross-section by stretching. Preferably, a first profile section of the coupling part and a second profile section of the recess are designed such that they have geometrically similar cross-sections when the thread axis and the central axis are aligned parallel, in particular coaxially, in a common cross-sectional plane. A geometric similarity exists, for example, when the first cross-section can be converted into the second cross-section by stretching, in particular a centered stretch.Furthermore, for the transmission of a torque between the coupling part and the base body, it is to be provided that a maximum extension of the first cross section of the coupling part is partially larger than a minimum extension of the second cross section of the recess, since this enables a positive-locking torque transmission between the coupling part and the base body.

[0021] Preferably, the clamping ring comprises a cantilever extending radially transversely to the central axis, which is provided at its end with a support mandrel extending along the central axis. The function of the cantilever and the support mandrel attached to it is to ensure torque support for the clamping ring relative to the wall section to which the fitting is to be secured.Without the extension arm and the support mandrel attached to it, a frictional connection between an outer peripheral surface of the clamping ring and an inner peripheral surface of the recess, which the clamping ring engages at least partially, is required to secure the fitting part to the wall section. This frictional connection ensures the required torque support between the clamping ring and the wall section when a torque is applied to the coupling part, which is intended to lead to a torque transfer from the coupling part to the base body and thus to a relative movement between the base body and the clamping ring. The extension arm and the support mandrel formed thereon, which engages in a recess in the wall section that is arranged adjacent to the recess formed in the wall section for receiving the clamping ring, enable direct, positive torque support for the clamping ring.Accordingly, the tolerance requirements for the recess in the wall section designed to accommodate the clamping ring are lower. In an alternative embodiment of the invention, the outer peripheral surface of the clamping ring is non-circular, and the recess in the wall section has a geometry corresponding to the outer peripheral surface of the clamping ring, which also ensures a positive fit of the clamping ring in the wall section with regard to torque transmission around the center axis of the fitting.

[0022] In a further development of the invention, it is provided that the first control cam is formed with a wedge-shaped profile on an arcuate, in particular circular-cylindrical, outer surface of the sleeve section, which projects outwards in the radial direction, and that the clamping ring is provided with at least one recess which, in a release position of the clamping ring relative to the base body, is designed to accommodate the first control cam. The wedge-shaped profile of the control cam is visible in the cross-sectional plane oriented transversely to the central axis and is characterized in that, over a section of the circumference of the outer surface of the sleeve section along a circumferential direction of the outer surface, there is a preferably linear increase in the distance between the central axis of the sleeve section and the respective section of the outer surface of the sleeve section.This design of the control cam ensures, during a relative movement between the base body and the clamping ring, an at least largely linear increase in the elastic or elastic and plastic deformation of the clamping ring due to the interaction of the first control cam with the inner surface of the clamping ring. This preferably linear increase in the elastic or elastic and plastic deformation of the clamping ring achieves a substantially proportional relationship between a pivot angle between the base body and the clamping ring and the elastic or elastic and plastic deformation of the clamping ring.Furthermore, it is provided that the first control cam arranged on the sleeve section of the base body projects into a recess of the clamping ring in the release position of the clamping ring relative to the base body, which recess is preferably designed such that the clamping ring in the release position does not have any significant elastic and thus also no plastic deformation due to the interaction with the first control cam.

[0023] In a further embodiment of the invention, the coupling part has a guide section, in particular designed as a plane-parallel plate, which is received between a first axial surface of the base body and a second axial surface of the base body, which is designed opposite, in particular parallel, to the first axial surface, in order to ensure that relative movements of the coupling part with respect to the base body are limited to linear movements in a plane of movement oriented transversely to the central axis. Due to the interaction of the guide section formed on the coupling part and the opposing first and second axial surfaces of the base body, a positive connection is achieved between the coupling part and the base body with regard to tilting movements whose axes of movement are oriented transversely to the central axis of the base body.Accordingly, the coupling part can only perform relative movements in a movement plane oriented transversely to the central axis. Additionally, the guide section of the coupling part and a region of the recess formed between the two axial surfaces of the base body can be profiled in a cross-sectional plane oriented transversely to the central axis in such a way that an additional restriction of the relative mobility between the coupling part and the base body is specified to exactly one spatial direction or a predeterminable movement corridor within the cross-sectional plane.

[0024] It is expedient if the coupling part comprises a first coupling body which is received in the recess so as to be tiltable about at least one, in particular about two tilt axes oriented perpendicular to one another and transverse to the central axis of the base body, and a second coupling body which is provided with the threaded portion and which is mounted on the first coupling body so as to be linearly movable. The first coupling body thus fulfills the task of enabling an angular alignment of the thread axis relative to the central axis at least within a predeterminable angular range. For example, the angular range within which the first coupling body can be aligned relative to the base body can be described as a cone or conical section, wherein the central axis of the base body also forms the central axis of the cone or conical section and the conical surface or conical section surface is determined by the possible orientation of the thread axis.The purpose of the second coupling part is to enable a limited linear movement relative to the first coupling part, in order to enable not only an angular alignment of the thread axis but also a linear adjustment of the position of the thread axis. For this purpose, it is particularly provided that the second coupling body comprises a guide section that is received in a correspondingly designed recess in the first coupling body, thereby achieving the desired limitation of the linear movement between the first and second coupling bodies.Furthermore, the guide section of the second coupling body and the recess in the first coupling body as well as the first coupling body are designed in relation to the recess in the base body for transmitting a torque which is to be transmitted by interaction of a threaded element, in particular a screw or a nut, with the threaded section in the second coupling part via the first coupling part and the base body to the clamping ring and the wall section.

[0025] It is advantageous if the recess has a smaller cross-section than the coupling part in some sections, and the resulting undercut for the coupling part ensures positive force transmission between the coupling part and the base body along the central axis. This ensures axial force transmission between the coupling part and the base body along the central axis.

[0026] In an alternative embodiment of the fitting, the clamping ring at least almost completely, in particular completely, surrounds the outer surface of the base body. This embodiment of the fitting can be mounted in workpieces that are only provided with blind holes and therefore only allow access to the fitting from one side. The torque for the elastic deformation of the clamping ring, which largely or completely covers the outer surface of the base body, is applied by a torque that is either introduced into the coupling element via a suitable fastening element such as a screw or via a tool that can be attached to the base body in a torque-transmitting manner. This torque can be supported by the clamping ring being inserted into the recess or hole during assembly.the blind hole comes into frictional contact with the workpiece in such a way that sufficient torque transmission between the fitting and the workpiece is ensured.

[0027] Additionally or alternatively, it can be provided that a suitable tool is attached to the clamping ring in order to achieve the desired torque support without involving the workpiece. Accordingly, it can be provided that a tool coupling for receiving a tool is formed on an axially oriented end face of the base body and / or on an axially oriented end face of the clamping ring.

[0028] In the simplest case, however, the fitting is inserted into the recess or blind hole or even into a through hole in the workpiece, possibly with the aid of a hammer or purely manually or mechanically. Then, with the aid of additional tools, the torque is introduced simply by screwing the component to be fastened using the screw used for this purpose. This leads to the desired relative movement between the base body and the clamping ring in order to ensure the force-fitting fixation of the fitting element in the workpiece. Depending on the material selected for the workpiece into which the fitting is to be inserted, an outer surface of the clamping ring can be provided with a profile, in particular with longitudinal grooves or knurling and / or with a friction-increasing coating, for example a rubber coating.

[0029] In a further embodiment of the invention, the outer surface of the base body and an inner surface of the clamping ring are each designed in the shape of a conical segment. Preferably, the two conical segment-shaped geometries of the base body and the clamping ring taper towards an opening of the recess in the base body. As a result, when tensile forces are applied to the fitting part, an additional wedge effect is created between the base body and the clamping ring, which leads to an improvement in the force-fitting fastening of the fitting part in the workpiece. Preferably, the outer surface of the base body and the inner surface of the clamping ring are designed with a cone angle in the range of 0 degrees to 5 degrees with respect to the central axis of the recess.

[0030] In an advantageous development of the invention, it is provided that a control edge determined by the control cam is aligned at an acute angle to an edge of a recess in the clamping ring. It is advantageous if the control cam or a plurality of control cams are arranged on the outer surface of the base body and are each designed to interact with an edge of a recess in the clamping ring. It is preferably provided that the clamping ring is designed as a slotted ring in order to facilitate the desired elastic deformation through interaction of the control cam(s) with the corresponding edge(s), in particular formed on recesses in the clamping ring. It is preferably provided that the clamping ring is provided with a number of recesses whose size is equal to the number of control cams.The acute-angled arrangement of the control cams relative to the edges ensures that the complete deformation of the clamping ring does not have to occur in a short distance when the control cam first hits the edge, which would require the introduction of a high torque. Purely as an example, the edge intended for interaction with the control cam is aligned parallel to the center axis of the recess. In this case, the control cam is also aligned at an acute angle to the center axis of the recess.Additionally or alternatively, it can be provided that a plurality of control cams and associated recesses are arranged in a phase-shifted manner, so that in the event of a rotational relative movement between the base body and the clamping ring, a cascaded engagement of the individual control cams is ensured in order to avoid an excessive torque between the base body and the clamping ring even with such a structural design.

[0031] Advantageous embodiments of the invention are illustrated in the drawing. Figure 1 is a perspective view of a first embodiment of a fitting part, Figure 2 is a view from below of the fitting part according to the Figure 1 , Figure 3 a sectional view of the fitting part according to the Figures 1 and 2 , Figure 4 a partially sectioned plan view of the fitting part according to the Figures 1 to 3, Figure 5 a perspective view of a second embodiment of a fitting part, Figure 6 a sectional view of the second embodiment of the fitting part according to the Figure 5 , Figure 7 a variant of the fitting according to the Figures 5 and 6 , Figure 8 a partially sectioned plan view of the fitting part according to the Figure 7 , Figure 9 is a perspective view of a third embodiment of a fitting part, and Figure 10 is a sectional view of the fitting part according to the Figure 9 .

[0032] One in the Figures 1 to 4The first embodiment of a fitting part 1 shown is designed purely as an example for connecting a screw (not shown) to a wall section 2 shown purely schematically in Figure 3. For example, such a fitting part 1 can be used in aircraft construction to fasten components such as, for example, paneling parts to an inner wall of an aircraft fuselage. The fitting part 1 should, if possible, be fastened to the wall section 2 in such a way that it is not necessary to absorb a torque using a tool such as an open-end wrench when screwing in the screw (not shown).Such a two-sided torque application is necessary, for example, in a classic screw connection with a screw and a nut, since a torque must be applied to both the screw head and the nut into which the screw is screwed. Alternatively, the screw can be screwed directly into a thread in the wall section, but the wall thickness of the wall section is often too thin to ensure reliable fastening of the screw.

[0033] For fitting part 1 according to the Figures 1 to 4 as well as in the other embodiments according to the Figures 5 to 8On the other hand, it is intended to create a frictional connection between the wall section 2 and the fitting part 1 or the alternative embodiments, without the need for counter-holding with a second tool or complex preparation of the wall section, for example by cutting threads.

[0034] To ensure this function, the fitting part 1 comprises a base body 3 which extends along a central axis 4. Purely as an example, the base body 3 is provided on an outer surface 14 in sections with a hexagonal profile 5, which comprises key surfaces 6 arranged in pairs symmetrically to the central axis 4. As can be seen from the illustration of the Figure 2 can be removed, the base body 3 is penetrated by a recess 7 extending along the central axis 4. For example, the recess 7 comprises a total of three recess sections 8, 9 and 10. As can be seen from the illustrations of the Figures 1 ,3 and 4 can be removed, the first recess section 8 is in a only symbolic in the Figure 3 drawn cross-sectional plane 15, which is aligned transversely to the central axis 4, with a circular cross-section. As the sectional view of the Figure 3 can be seen, the upper recess section 8 can be realized, for example, as a conical section, which tapers along the central axis 4 to an upper side 11 of the base body 3. In the upper recess section 8, for example, a circular cover plate 16 designed as a plane-parallel plate is accommodated, which delimits the recess 7 in the base body 3 in the axial direction. Adjacent to the upper recess section 8 is a central recess section 9, the profile of which is shown in the illustration of the Figure 4can be seen. Purely by way of example, the central recess section 9 has a profile that essentially corresponds to the outer contour of the number 8. Adjoining the central recess section 9 along the central axis 4 is a lower recess section 10, which is purely exemplary and circularly cylindrical and opens out at an underside 12 of the base body 3.

[0035] A coupling part 20 is received in the recess 7, which coupling part 20 has, purely by way of example, a sleeve 21 and a guide section 22 formed on the end of the sleeve 21 and extending outwards in the radial direction. The coupling part 20 is penetrated by a threaded section designed as an internally threaded bore 23, wherein an axis of symmetry of the internally threaded bore 23 is also referred to as the thread axis 24. By way of example, the sleeve 21 is designed to be rotationally symmetrical to the thread axis 24. Furthermore, the guide section 22, which can also be referred to as the first profile section, is realized in a cross-sectional plane aligned parallel to the cross-sectional plane 15 and not shown in detail, which is geometrically similar to the profiling of the central recess section 9, which can also be referred to as the second profile section, and which essentially corresponds to the outer contour of the number 8.

[0036] Purely by way of example, the guide section 22 and the central recess 9 can be converted into one another by stretching in two spatial directions not shown, which are perpendicular to one another and are aligned transversely to the central axis 4. As can be seen from the illustration of the Figure 4 can be removed, a minimum extension 25 of the central recess 9 is smaller than a maximum extension of the guide section 22. As a result, when the coupling part 20 is rotated about the central axis 4 from the release position according to the Figure 4 into a functional position not shown, due to the positive engagement occurring with respect to the central axis 4, a torque transmission about the central axis 4 between the coupling part 20 and the base body 3 is enabled. In this respect, the coupling part 20 has a rotational degree of freedom about the central axis 4 with respect to the base body 3, which is limited by the pivot angle.

[0037] Furthermore, it is provided that an upper side 27 of the guide section 22 is arranged opposite a first axial surface 29, which is defined by an underside of the cover plate 16. It is assumed that the cover plate 16 is received in the upper recess section 8 of the base body 3, at least by elastic, and possibly also by plastic, deformation, in a force-fitting or possibly also form-fitting manner, and can thus be considered a component of the base body 3.

[0038] A lower side 28 of the guide section 22 rests against an axial end face of the base body 3, which is also referred to as the second axial surface 30 and which is created by the transition between the middle recess section 9 and the lower recess section 10.

[0039] Purely by way of example, it is provided that both the first axial surface 29 and the second axial surface 30 are each flat. Furthermore, it is provided that the first axial surface 29 and the second axial surface 30 are arranged parallel to one another and spaced apart. Furthermore, it is provided that the upper side 27 and the lower side 28 of the guide section 22 are designed in the manner of a plane-parallel plate. These measures limit the relative mobility of the coupling part 20 with respect to the base body 3 to linear movements in a movement plane (not shown) that is oriented transversely to the central axis 4.Together with the pivoting mobility of the coupling part 20 relative to the base body 3, which is not impaired by the above measures, it follows that relative movements between the coupling part 20 and the base body 3 can take place as linear movements in the plane of movement oriented transversely to the central axis 4 as well as as rotational movements about the central axis 4, whereby due to the profiling of the central recess section 9 and the guide section 22, both a limitation of the linear movements and a limitation of the pivoting movement is ensured.

[0040] As the representation of the Figure 3can be seen, adjacent to the hexagonal profile 5 of the base body 3 is a bearing section 35, which also belongs to the outer surface 14 of the base body 3 and is designed purely as an example rotationally symmetrical to the central axis 4, which is designed for a rotatable reception of a clamping ring 17. By way of example, the bearing section 35 is designed as a circular cylinder, wherein immediately adjacent to the hexagonal profile 5 of the base body, a circumferential groove 36 is introduced into the bearing section 35, which purely as an example has a rectangular cross-section in the representation plane according to the Figure 3is formed. In an extension of the bearing section 35 along the central axis 4, a sleeve section 37 is formed, which also belongs to the outer surface 14 of the base body 3 and, purely by way of example, has a circular cross-section in a cross-sectional plane (not shown) oriented transversely to the central axis 4. As will be explained in more detail below, the sleeve section 37 is provided at its end with a plurality of control cams 38, each extending radially outward.

[0041] In order to ensure the desired rotatable mounting of the clamping ring 17 on the base body 3, the clamping ring 17 comprises a ring part 42 which, purely by way of example, is rotationally symmetrical to the central axis 4 and which, as shown in Figure 3, is designed with a U-shaped profile. A shorter U-leg 43 of the ring part 42 engages in the groove 36. A longer leg 44 of the ring part 42 bears against an axially aligned end face 39 of the bearing section 35. Accordingly, the ring part 42 encompasses the bearing section 35 in a manner that ensures a positive connection between the clamping ring 17 and the base body 3 with respect to linear movements and tilting movements transverse to the central axis. Furthermore, the desired rotational mobility of the clamping ring 17 relative to the base body 3 about the central axis 4 is ensured due to the design of the ring part 42 and the bearing section 35.

[0042] The clamping ring 17 further comprises, purely by way of example, on an axial end face 45 facing away from the hexagonal profile 5 of the base body 3, three axial projections 46 each formed in the shape of a circular ring and arranged coaxially to the central axis, the inner surfaces 47 of which are designed for a mechanical interaction with the control cam 38.

[0043] As the detailed representation of the Figure 2 can be seen, the control cams 38 in the representation plane according to the Figure 2 , which is aligned parallel to the cross-sectional plane 15 according to Figure 3, has a wedge-shaped profile. This profile is characterized by the fact that when viewing the control cam 38 in a, according to the illustration of the Figure 2in the clockwise direction, a distance 41 between the central axis 4 and an outer surface 55 of the control cam 38 increases, in particular, a substantially proportional increase in distance is provided. Adjacent to the wedge-shaped profiling of the control cam 38 is a concavely rounded profiling, wherein the distance of the outer surface 55, when viewed in the circumferential direction 40, initially decreases sharply in the area of ​​the rounded profiling, before then transitioning back into a weaker curvature, which in turn then transitions into the opposite, convexly curved outer surface of the sleeve section 37.

[0044] Furthermore, it is provided, by way of example, that the inner surfaces 47 of the axial projections 46 are convexly rounded at the ends at the transitions to the respective outer surfaces in order to achieve, during a relative movement between the base body 3 and the clamping ring 17, a displacement effect by the control cam 38 with respect to the clamping ring 17 that increases as evenly as possible and thus a force or torque increase that is as uniform as possible for the relative movement between the base body 3 and the clamping ring 17, in the course of which an increase in the diameter of the clamping ring 17 is to be achieved by elastic or elastic and plastic deformation. In order to facilitate this increase in the diameter of the clamping ring 17, the clamping ring 17 is provided, purely by way of example, with a relief slot 48 extending radially outwards, as shown in the Figures 2 and 4 is recognizable.

[0045] In principle, torque transmission between the fitting part 1 and a recess in the wall section 2 is provided exclusively by frictional engagement. For this purpose, it is advantageous if the outer diameter of the axial projections 46 is selected to be only slightly smaller than the inner diameter of a recess formed in the wall section 2. For additional torque support, a radially projecting arm 18 is provided on the clamping ring 17, purely as an example. This arm is provided in a radially outer end region with a support mandrel 19 extending along the central axis 4. This support mandrel 19 is provided until it engages in a second recess provided away from the recess designed to accommodate the axial projection 46, thereby enabling positive torque support between the clamping ring 17 and the wall section 2.To increase the friction effect between the fitting part 1 and the recess in the wall section 2, a film section, in particular a self-adhesive film section, can be arranged between the fitting part 1 and the recess in the wall section 2. Such a film section can also create a sealing effect between the fitting part 1 and the recess in the wall section 2.

[0046] In the Figures 5 and 6 The second embodiment of a fitting part 61 shown differs from the first embodiment according to the Figures 1 to 4 It is provided that the coupling part 62 has a first coupling body 63 and a second coupling body 64 firmly connected thereto. By way of example, it is provided that the first coupling body 63 is essentially designed as a pyramid section, which has a total of four side walls each aligned in a wedge shape. In the illustration of the Figure 6The first side wall 65 and the second side wall 66 are two of the four side walls of the first coupling body 63. By way of example, it is provided that the first coupling body 63 is made of a plastic material, for example a dimensionally stable plastic material such as PEEK (polyetheretherketone), which on the one hand ensures advantageous force and torque transmission between the coupling part 62 and the base body 67 and on the other hand, due to the material pairing with the base body 67, which is typically made of steel, is associated with self-lubricating properties. The second coupling body 64 is received in the first coupling body 63, for example, overmolded in the course of a plastic injection molding process. The second coupling body 64 is preferably made of metal, in particular steel, and its outer surface 68 is designed to be rotationally symmetrical to the thread axis 69.

[0047] The recess 70 in the base body 67 has a substantially square cross-section in a cross-sectional plane (not shown) oriented transversely to the central axis 71. In combination with the pyramid-shaped design of the first coupling body 63, a rotary coupling is thus created which enables torque transmission about the central axis 71 between the coupling part 62 and the base body 67. Furthermore, the pyramid-shaped design of the first coupling body 63 in conjunction with the square cross-section of the recess 70 enables tilting of the coupling part 62 about tilt axes (not shown), which are oriented perpendicular to the thread axis 69 and perpendicular to one another and which each intersect the side walls 65, 66 and the other side walls (not visible) at a minimal angle to the respective surface normal of the corresponding side wall.

[0048] To ensure the transmission of axial forces along the central axis 71 between the coupling part 62 and the base body 67, the recess 70 is partially convex and subsequently transitions into a conically widened opening 72. The opening 72 creates the mounting space for a screw (not shown), which can be tilted relative to the fitting part 61 in a movement space limited by the geometries of the coupling part 62 and the recess 70, also shaped like a cone segment.

[0049] The design of the fitting part 61 with regard to the clamping ring 73 is identical to the design of the fitting part 1, so that a more detailed description of the clamping ring 73 is unnecessary.

[0050] In the Figures 7 and 8 The third embodiment of a fitting part 81 shown is a variant of the second embodiment of the fitting part 61 according to the Figures 5 and 6, so that the same reference symbols are assigned to components with the same function and these are not described again.

[0051] In contrast to the fitting part 61, the coupling part 82 of the fitting part 81 is formed from two separate coupling bodies 83, 84 that are movable relative to each other. The first coupling body 83 has the same external geometry as the first coupling body 63 and is intended for reception in a base body 87, which is identical to the base body 67. From the illustration of the Figure 8 In particular, the essentially square profiling of the recess 90 in the base body 87 can be seen, which is formed in the same way as the recess 70 in the base body 67 of the second embodiment of the fitting part 61.

[0052] The second coupling body 84 is designed in an identical manner to the coupling part 20 of the first embodiment of the fitting part 1, so that the same reference numerals are used for the second coupling body 84 as for the coupling part 20 and a new description is unnecessary.

[0053] The first coupling body 83 is provided with a recess 85 which is designed identically to the recess 7 of the base body 3, so that a new description is unnecessary here too and the same reference numerals are used.

[0054] Accordingly, the third embodiment of the fitting part 81 represents a hybrid version of the first embodiment of the fitting part 1 and the second embodiment of the fitting part 61, in which both a tilting of the coupling part 82 within a limited angular range relative to the central axis 86 is possible, as well as a translational displacement of the second coupling body 84 relative to the first coupling body 83 in a movement plane not shown, which is oriented transversely to the threaded axis 88 of the second coupling body 84. Accordingly, the third embodiment of the fitting part 81 enables both a compensation of angular deviations and a compensation of translational deviations between a recess in a wall section and a component to be attached thereto, such as a trim part.

[0055] The design of the fitting part 81 with regard to the clamping ring 89 is identical to the design of the fitting part 1, so that a more detailed description of the clamping ring 89 is unnecessary.

[0056] A functional principle for the fitting part 81 can be described as follows: First, the fitting part 81 with the axial projections 46 is inserted into a recess (not shown in detail) in a wall section 2. It is assumed that the recess in the wall section 2 is circular and has an inner diameter slightly larger than an outer diameter of the axial projections 46. Subsequently, a screw (not shown), which, for example, penetrates a trim part (also not shown), is screwed into the internally threaded bore 23 of the second coupling body 84.Due to the geometric design of the first coupling body 83 and the geometric design of the second coupling body 84, the coupling part 82 can advantageously align itself both with regard to an angular alignment with respect to the central axis 86 and with regard to a linear alignment between the thread axis 88 and the first coupling body 83. As the screwing-in process continues, torque is transmitted from the screw via the coupling part 82 to the base body 87, whereby due to the geometric design of the first coupling body 83 and the second coupling body 84, a positive torque transmission with respect to the central axis 86 is ensured between the coupling part 82 and the base body 87.Due to this torque transmission, a relative movement occurs between the base body 87 and the clamping ring 89, particularly taking into account the torque support through friction between the axial projections 46 and the inner surface of the recess in wall section 2 as well as the support mandrel 19 in a second recess in wall section 2. During this relative movement, the control cams 38 interact with the inner surfaces 47 of the axial projections 46 and therefore lead to an elastic or elastic and plastic expansion of the clamping ring 89 in the radial direction. This increases the normal forces transmitted outward in the radial direction by the axial projections 46 onto the inner surface of the recess in wall section 2 and thus also the resulting frictional forces, so that both a rotationally fixed and a tensile-resistant force-locking coupling is created between the fitting part 81 and the wall section 2.

[0057] Alternatively, it can be provided that the fitting part 81 is fastened by a direct introduction of torque onto the base body 87, for example by means of an open-end wrench which is applied to the hexagonal profile 5 of the base body 87, and a screwing process for the screw with which the component to be fastened is to be fixed into the coupling part 82 is only carried out at a later time.

[0058] To detach the fitting part 81 from the wall section 2, it is intended to first remove the component attached to the fitting part 81 and the associated screw. This may already result in a rotational relative movement between the base body 87 and the clamping ring 89 in a direction that reduces the interaction between the control cams 38 and the axial projections 46.If this is not the case, after removing the component and the associated screw, a torque can be applied to the hexagonal profile 5 of the fitting part 81 using a suitable tool, for example an open-end wrench, in order to apply a loosening torque to the base body 87 about the central axis 86, which results in the control cams 38 being able to be disengaged from the inner surfaces of the axial projections 46 and being arranged in spaces 49 between the axial projections 46, whereby an elastic expansion of the clamping ring 89 is reduced to a minimum.

[0059] In the Figures 9 and 10 In the third embodiment of a fitting part 101 shown, a repeated complete description of structures that are already known from the embodiments described above is omitted.

[0060] In the fitting part 101, it is provided that the base body 107 is provided with a recess 109 in the same way as in the previously described embodiments of fitting parts 1, 61 and 81. In this recess 109, a coupling part 102 is accommodated, which in the Figure 10 is shown in more detail and which has a first coupling body 103 and a second coupling body 104, wherein the first coupling body 103 is pivotally received in the recess 109 and wherein the second coupling body 104 is mounted linearly movable relative to the first coupling body 103. Accordingly, in the embodiment of the fitting part 101, as shown in the Figures 9 and 10 As shown, a pivoting mobility and a linear mobility for the second coupling body 104 relative to the base body 107 and thus a variable spatial orientation of the thread axis 124 can be assumed.

[0061] As the representation of the Figures 9 and 10 As can also be seen, the base body 107 is, purely by way of example, completely surrounded by a clamping ring 113, wherein the clamping ring 113 is rotatably mounted on an outer surface 114 of the base body 107. By way of example, it is provided that the outer surface 114 of the base body and an inner surface 115 of the clamping ring 113 are each designed in the shape of a cone section, wherein the geometries of the outer surface 114 and the inner surface 115 are selected such that the inner surface 115 lies flat against the outer surface 114.

[0062] The clamping ring 113 is provided purely by way of example with three control openings 116, each of which is slit-shaped and extends essentially in the direction of a central axis 111 of the recess 109, wherein two of the control openings 116 extend only over a partial area of ​​the length of the clamping ring 113, while only the third control opening 116 extends over the entire length of the clamping ring 113 and thereby contributes to a considerable improvement in the elastic deformability of the clamping ring 113. At each of the control openings 116, a purely exemplary rounded edge 117 is provided, which is intended for interaction with a control cam 118, which is formed on the outer surface 114 of the base body 107. As can be seen from the detailed illustration of the Figure 9As can be seen, a control edge 121 of the control cam 118, which results from the radius jump between a radius of the outer surface 114 of the base body 107 and a radius of the control cam 118, is aligned at an acute angle to the edge 117. Due to this acute-angled alignment of the control edge 121 with respect to the central axis 111, which also serves as the axis of rotation for the relative movement of the clamping ring 113 with respect to the base body 107, a gradual overlap between the control cam 118 and the inner surface 115 of the clamping ring 113 is achieved during this rotational movement. This ensures a slowly rising torque curve for a torque that is required for the relative movement between the clamping ring 113 and the base body 108.

[0063] On an axially aligned end face 119 of the base body, three bores 120 are formed, purely by way of example, arranged at equal angular pitch to the central axis 111. These bores can be used for engagement with a tool (not shown) equipped with pins that correspond to the bores 120. Such a tool can provide torque support for the base body. Furthermore, it can be provided for another tool, also not shown, to engage the continuous slot of the control opening 116 in order to thereby provide torque support for the clamping ring 113.For example, it can be provided that the fitting part 101 is inserted into a blind hole in a workpiece (not shown) and is then locked in the workpiece by a relative rotational movement between the base body 107 and the clamping ring 113 using tools (not shown) that engage in the bores 120 of the base body 107 and the slot in the clamping ring 113. In a subsequent step, a body (not shown) can then be secured to the workpiece equipped with the fitting part 101 using a screw that is screwed into the coupling part 102.

Claims

1. Fitting (1; 61; 81; 101) for fixing a threaded element to a wall section (2), comprising a base body (3; 67; 87; 107) which is penetrated by a recess (7; 70; 90; 109), which recess is extended along a central axis (4; 71; 86; 111), further comprising a clamping ring (17; 73; 89; 113) which is rotatably movable mounted on an outer surface, in particular on a sleeve section (37) arranged coaxially to the central axis (4; 71; 86; 111), of the base body (3; 67; 87; 107), wherein a first cam (38; 118) is assigned to the outer surface (14; 114), in particular to the sleeve section (37), and / or wherein a second cam is assigned to the to the clamping ring (17; 73; 89; 113), which effectuates a change in diameter of the clamping ring (17; 73; 89; 113) during a rotary movement of the clamping ring (17; 73; 89; 113) relative to the base body (3; 67; 87; 107), characterized in that a coupling part (20; 62; 82; 102) is movably received in the recess (7; 70; 90; 109) and forms with the base body (3; 67; 87; 107) a rotary coupling for a transmission of a torque between the coupling part (20; 62; 82; 102) and the base body (3; 67; 87; 107) about the central axis (4; 71; 86; 111), wherein a threaded portion (23) of the coupling part (20; 62; 82; 102) determines a thread axis (24; 124), which is aligned with a variable orientation within a predetermined angular interval and / or within a predetermined distance interval to the central axis (4; 71; 86; 111), wherein a region of an outer surface of the coupling part (20; 62; 82; 102) defines a first profile (22) and wherein a region of an inner surface of the recess (7; 70; 90; 109) defines a second profile (9), wherein the first profile (22) forms with the second profile (9) a rotary coupling for a torque transmission between the coupling part (20; 62; 82; 102) and the base body (3; 67; 87; 107) in a functional position and is designed for a relative movement between the coupling part (20; 62; 82; 102) and the base body (3; 67; 87; 107) with at least one geometrically limited rotational degree of freedom and / or at least one geometrically limited linear degree of freedom of movement.

2. Fitting (1; 61; 81; 101) according to claim 1, characterized in that the coupling part (20; 62; 82; 102) has, in particular in sections, a first cross-section in a cross-sectional plane (15) aligned transversely to the central axis (4; 71; 86), and that the recess (7; 70; 90; 109) has, in particular in sections, a second cross-section in the cross-sectional plane, wherein the first cross-section and the second cross-section are geometrically similar, wherein in particular the second cross-section is obtained by stretching the first cross-section.

3. Fitting (1; 61; 81) according to any preceding claim, characterized in that the clamping ring (17; 73; 89) comprises a cantilever (18) projecting transversely to the central axis (4; 71; 86) in the radial direction, which cantilever (18) is provided at the end with a supporting mandrel (19) extending along the central axis (4; 71; 86).

4. Fitting (1; 61; 81) according to any preceding claim, characterized in that the first cam (38) is formed with a wedge-shaped profiling on the outer surface (14; 114), in particular on an arcuate, in particular circular cylindrical, outer surface of the sleeve section (37), which wedge-shaped profiling projects outwards in the radial direction, and that the clamping ring (17; 73; 89) is provided with at least one recess (49) which, in a release position of the clamping ring (17; 73; 89) relative to the base body (3; 67; 87), is designed to receive the first cam (38).

5. Fitting (1; 61; 81; 101) according to any preceding claim, characterized in that the coupling part (20; 62; 82; 102) has a guide section (22), in particular being configured as a plane parallel plate, which is arranged between a first axial surface (29) of the base body (3; 67; 87; 107) and a second axial surface (30) of the base body (3; 67; 87; 107), which second axial surface (30) is formed opposite, in particular parallel, to the first axial surface (29), in order to ensure a limitation of relative movements of the coupling part (20; 62; 82; 102) with respect to the base body (3; 67; 87; 107) to linear movements in a movement plane (15) aligned transversely to the central axis (4; 71; 86; 111).

6. Fitting (1; 61; 81; 101) according to any of claims 1 to 4, characterized in that the coupling part (82; 102) comprises a first coupling body (83; 103) which is accommodated in the recess (90; 109) such that it can be tiltably moved about at least one axis, in particular about two axes being perpendicular to each other, oriented transverse to the central axis (86; 111) of the base body (87; 107), and a second coupling body (84; 104) which is provided with the threaded portion (23) and which is mounted on the first coupling body (83; 103) such that it can move linearly with respect to the first coupling body (83; 103).

7. Fitting (1; 61; 81; 101) according to any preceding claim, characterized in that a region of the recess (7; 70; 90; 109) has a smaller cross-section than the coupling part (20; 62; 82; 102) to provide an undercut for the coupling part (20; 62; 82; 102) which undercut enables a positive transmission of force between the coupling part (20; 62; 82; 102) and the base body (3; 67; 87; 107) along the central axis (4; 71; 86; 111).

8. Fitting (1; 61; 81; 101) according to any preceding claim, characterized in that the clamping ring (113) surrounds the outer surface (114) of the base body (107) at least almost entirely, in particular entirely.

9. Fitting (1; 61; 81; 101) according to claim 8, characterized in that the outer surface (114) of the base body (107) and an inner surface (115) of the clamping ring (113) are each formed in the shape of cone sections.

10. Fitting (1; 61; 81) according to claim 8 or 9, characterized in that a control edge (121) determined by the cam (118) is oriented at an acute angle to an edge (117) of a recess (116) in the clamping ring (113).