Securing assembly, component comprising the securing assembly, corresponding connecting structure, method for producing same, and connecting method

Abstract

The invention relates to a securing assembly (10; 12; 14) for connecting a first component (A) to a second component (B) with a tolerance compensation between the first component (A) and the second component (B), said securing assembly consisting of an outer sleeve (20; 80; 82; 84; 86) and an inner sleeve (50; 90). The outer sleeve (20; 80; 82; 84; 86) comprises a first through-channel (26), which is concentric to a central longitudinal axis (L) and which is designed to be conical at least in some parts, and at least one axially running first slot (28), which extends from one axial end (24) in the direction of the other axial end (22). The inner sleeve (50; 90) likewise has two axial ends (52, 54) and a second through-channel (56), which is concentric to the central longitudinal axis (L) and which is preferably designed to be thread-free, wherein the radial exterior is designed to be conical at least in some parts. The inner sleeve (50; 90) is received in the outer sleeve (20; 80; 82; 84; 86) in a movable manner along the central longitudinal axis (L) such that in a securing state, the position of the first component (A) can be fixed between the axial ends (22, 24) of the outer sleeve (20; 80; 82; 84; 86) by means of a frictional engagement on the outer sleeve (20; 80; 82; 84; 86), and the frictional engagement is achieved on the basis of the expansion of the outer sleeve (20; 80; 82; 84; 86) by means of the inner sleeve (50; 90).

Description

[0001] Fastening arrangement, component with the fastening arrangement, associated connection structure and manufacturing and connection methods

[0002] 1. Field of the invention

[0003] The present invention relates to a fastening arrangement for connecting a first component to a second component with a tolerance compensation between the first component and the second component, a first component with the fastening arrangement, a connecting structure comprising the first component and a second component as well as a manufacturing method of the fastening arrangement and a connecting method of a first component to a second component using the fastening arrangement.

[0004] 2. Background of the invention

[0005] Fastening arrangements with tolerance compensation in the radial or axial direction are known in the prior art. An example of a radial compensation element for compensating tolerances between a first component and a second component to be connected to this first component by means of a connecting bolt can be found, for example, in DE 10 2019 211 757 A1.

[0006] The radial compensation element comprises a base body having a receiving channel in which the connecting bolt can be received. The receiving channel is designed to receive the connecting bolt. Furthermore, the radial compensation element comprises a number of elastic elements designed to radially compensate for tolerances between the connecting bolt and the first component. An alternative embodiment for compensating radial tolerances is described in DE 10 2018 109 520 A1. The device for connecting and adjusting two components comprises an outer bearing body and an inner bearing body, each with a coaxial center axis. The outer bearing body can be fastened to a first component, and the inner bearing body can be fastened to a second component.The outer bearing body has an at least partially conical inner surface arranged concentrically to the central axis and an at least partially cylindrical outer surface arranged concentrically to the central axis. The inner bearing body has an at least partially conical outer surface arranged concentrically to the central axis. The inner bearing body is at least partially inserted into the outer bearing body, with its outer surface resting against the inner surface of the outer bearing body. To enable diverse adjustments and at the same time improved fastening in the axial direction and at the same time in all directions perpendicular to the axial direction, the inner bearing body has an elongated hole. The elongated hole runs from the center of the inner bearing body in a radial direction towards the central axis outwards.

[0007] DE 102 15 314 A1 discloses a device for clamping a first and a second component at a distance from one another. A fastening shaft is assigned to the first component, and the second component has a fastener insertion opening. The device comprises a spacer consisting of an expansion sleeve and an expansion body inserted therein. The spacer is initially axially displaceable and can be inserted into the fastening shaft at a distance from the second component, and can be displaced into a contact position with the second component by actuating a fastener inserted into the fastener insertion opening. Once the contact position is reached, the spacer is clamped to the shaft wall by further actuation of the fastener and the resulting relative displacement of the expansion body to the expansion sleeve, by means of an expansion of the expansion sleeve.In order to achieve a design which is advantageous in terms of manufacturing technology, this document proposes that the spacer is manufactured in one piece, in particular as an injection-molded part, whereby the expansion sleeve is connected to the expansion body inserted therein at several points which break off after the contact position is reached.

[0008] Another device for connecting two components arranged at a distance subject to tolerance, comprising a support part which can be fastened to the first component and a spacer element which is assigned to the support part and which can be displaced in the direction of the second component when a connecting screw is screwed in, said spacer element having restraining means which, once the spacer element has reached a stop position on the second component, axially fasten the spacer element to the support part in a restraining position relative to the axis of rotation of the connecting screw, wherein an axial force is required to displace the spacer element into the stop position, is known from DE 102011 056 465 A1. In order to specify a spacer screw connection in which a preload can be applied using simple means, the spacer element is coupled to the support part in such a way that the axial force must be applied at a predetermined strength over the entire displacement path up to the contact position.

[0009] Also known from EP 1 200 745 B1 is a device for clamping spaced-apart components by means of a spacer arranged in the space and a clamping piece that clamps the two components against each other. The fastening actuation of the clamping piece first displaces the spacer from a spacing position to a contact position with the second component and subsequently secures the device to the first component by means of clamping elements that press against the wall of an insertion cavity in the first component. The expansion elements are assigned to the spacer.

[0010] Finally, WO 2019 / 046079 A1 discloses a tolerance-compensating fastening device for fastening a first vehicle component to a second vehicle component by means of a screw. The fastening device is configured to compensate for a tolerance within a tolerance compensation range. Furthermore, a fastening system comprising such a fastening device and a method for fastening a first vehicle component to a second vehicle component by means of a screw are described.

[0011] A disadvantage of known devices is that often only one type of tolerance can be compensated, i.e., an axial or a radial tolerance. In cases where both a radial and an axial tolerance can be compensated, the device has a complex structure consisting of a multitude of different components.

[0012] The object of the present invention is therefore to provide a fastening arrangement with which both axial and radial tolerances can be compensated when fastening a first component to a second component, while simultaneously having a simpler design compared to known devices. Likewise, it is an object of the invention to provide a corresponding first component, a connecting structure, a manufacturing method for the fastening arrangement, and an associated connecting method.

[0013] 3. Summary of the invention

[0014] The above object is achieved by a first alternative of a fastening arrangement for connecting a first component to a second component with a tolerance compensation between the first component and the second component according to independent patent claim 1, a second alternative of a fastening arrangement for connecting a first component to a second component with a tolerance compensation between the first component and the second component according to independent patent claim 2, a first component according to independent patent claim 13, a connecting structure consisting of the first component, a second component and a fastening screw according to independent patent claim 14, a connecting structure consisting of the first component, a second component and a nut according to independent patent claim 15, a manufacturing method of the first alternative of the fastening arrangement according to independent patent claim 16,a manufacturing method of the second alternative of the fastening arrangement according to independent claim 17 and a connecting method according to independent claim 18. Advantageous embodiments and further developments emerge from the following description, the drawings and the appended claims.

[0015] A first alternative of a fastening arrangement according to the invention for connecting a first component to a second component with tolerance compensation between the first component and the second component has the following features: an outer sleeve with a first and a second axial end, which defines a central longitudinal axis of the fastening arrangement, has a first through-channel formed concentrically to the central longitudinal axis, which is at least partially conical, and comprises at least one axially extending first slot extending from the second axial end towards the first axial end of the outer sleeve, and an inner sleeve with a third and a fourth axial end, the radial outer side of which is at least partially conical and has a second through-channel formed concentrically to the central longitudinal axis, which is preferably thread-free,wherein the inner sleeve is movably received along the central longitudinal axis in the outer sleeve such that, in an initial state of the fastening arrangement, the fourth axial end of the inner sleeve is arranged adjacent to the first axial end of the outer sleeve and, in a fastening state, the fourth axial end of the inner sleeve is arranged adjacent to the second axial end of the outer sleeve, whereby, in the fastening state, a position of the first component between the first and second axial ends of the outer sleeve can be fixed by means of frictional engagement on the outer sleeve, the frictional engagement being achieved due to the spreading of the outer sleeve.

[0016] For greater clarity, the first alternative of the fastening arrangement according to the invention is explained below in the context of its use for connecting the first component to the second component. For this purpose, the first component has a first opening into which the fastening arrangement is inserted.

[0017] Depending on the material of the first component, the outer sleeve is preferably made of plastic, in particular PA66, PA 12, PA66-GF15, or PA66-GF30. The inner sleeve is preferably made of metal or plastic, in particular PA66-GF30 or PPA-GF50.

[0018] After the first component has been equipped with the first alternative of the fastening arrangement according to the invention, it is brought into alignment with the second component. In the first example, the second component has a second opening. The second opening has an internal thread either itself or adjacent thereto. An internal thread adjacent to the second opening can be provided, for example, by a weld nut. It should be noted that the second axial end of the outer sleeve faces the second component. In addition, the conical shape of the inside of the outer sleeve is oriented such that the smaller inside diameter is adjacent to the second axial end. The conical shape of the outside of the inner sleeve is correspondingly oriented so that the smaller outside diameter is adjacent to the fourth axial end.In order to achieve effective expansion in this respect, the outer diameter of the cone shape of the inner sleeve is larger than the corresponding inner diameter of the cone shape of the outer sleeve. This definition refers to the smallest diameter and / or the largest diameter of the respective cone shape being arranged in the same plane transverse to the central longitudinal axis. Following alignment, a fastening screw is inserted from the first axial end of the outer sleeve through the fastening assembly such that it can engage with the internal thread of the second component. Since the smallest inner diameter of the inner sleeve is larger than the outer diameter of the shank of the fastening screw, the fastening screw can move radially within the fastening assembly and thus compensate for radial tolerances between the first opening in the first component and the second opening in the second component.

[0019] The axial tolerance is compensated for by appropriately positioning the first component between the first and second axial ends of the outer sleeve of the fastening assembly. The axial length of the outer sleeve therefore limits the axial tolerance compensation. In particular, the outer sleeve rests against the second component with its second axial end.

[0020] Once the correct positioning has been achieved, the fastening screw is tightened. Before tightening the screw, the fastening assembly is still in its initial state. The fourth axial end of the inner sleeve is thus adjacent to the first axial end of the outer sleeve. In other words, the fastening assembly has its greatest possible axial length in this state.

[0021] When the fastening screw is tightened, the inner sleeve is driven into the outer sleeve. This causes the outer sleeve to expand, generating a circumferential radial force on the first component. In this way, the position of the first component in the fastening state is fixed between the first and second axial ends of the outer sleeve by means of frictional engagement on the outer sleeve.

[0022] According to a second example, the second component has a threaded shaft. As in the previous example, the second axial end of the outer sleeve faces the second component. As in the first example, the conical shapes are aligned such that the smaller inner diameter of the conical shape on the inside of the outer sleeve is adjacent to the second axial end. Analogously, the conical shape on the outside of the inner sleeve is aligned such that the smaller outer diameter is adjacent to the fourth axial end. Once aligned, the threaded shaft is inserted through the fastening arrangement from the second axial end of the outer sleeve. Since the smallest inner diameter of the inner sleeve is larger than the outer diameter of the threaded shaft, the threaded shaft can move radially within the fastening arrangement, thus compensating for radial tolerances between the first opening in the first component and the second component.

[0023] As in the first example, the axial tolerance is compensated for by appropriately positioning the first component between the first and second axial ends of the outer sleeve of the fastening assembly. The axial length of the outer sleeve limits the axial tolerance compensation, since the outer sleeve must rest against the second component with its second axial end in the final state.

[0024] Once the correct positioning is achieved, a nut is placed on the threaded shaft and tightened. Before tightening the nut, the fastening assembly is still in its initial state. The fourth axial end of the inner sleeve is thus adjacent to the first axial end of the outer sleeve. In other words, the fastening assembly has its greatest possible axial length in this state.

[0025] When the nut is tightened, the inner sleeve is driven into the outer sleeve. This causes the outer sleeve to expand, generating a circumferential radial force on the first component. In this way, the position of the first component, when fastened, is fixed between the first and second axial ends of the outer sleeve by frictional engagement with the outer sleeve.

[0026] An advantage of the first alternative of the fastening arrangement according to the invention is that no additional stresses are generated between the first and second components. Furthermore, the fastening arrangement has a compact design with few separate parts. This makes the fastening arrangement particularly cost-effective to manufacture and easy to use. Furthermore, as described above,both axial and radial tolerances between the first and second components are compensated. Finally, in addition to use in combination with a fastening screw, the fastening arrangement can also be used in conjunction with a threaded shaft provided on the second component. This makes the fastening arrangement particularly versatile. A second alternative of a fastening arrangement according to the invention for connecting a first component to a second component with tolerance compensation between the first component and the second component has the following features: an outer sleeve with a first and a second axial end, which defines a central longitudinal axis of the fastening arrangement, has a first through-channel formed concentrically to the central longitudinal axis, which is conical at least in sections, and comprises at least one axially extending first slot,which extends from the second axial end towards the first axial end of the outer sleeve, and an inner sleeve with a third and a fourth axial end, the radial outer side of which is at least partially conical and which has a second through-channel formed concentrically to the central longitudinal axis, which is preferably thread-free, and a hollow screw with an external thread and a third through-channel formed concentrically to the central longitudinal axis, in which the outer sleeve is at least partially arranged, wherein the inner sleeve is movably received along the central longitudinal axis in the outer sleeve such that, in an initial state of the fastening arrangement, the fourth axial end of the inner sleeve is arranged adjacent to the first axial end of the outer sleeve and, in a fastening state, the fourth axial end of the inner sleeve is arranged adjacent to the second axial end of the outer sleeve,whereby, in the fastening state, a position of the hollow screw can be fixed by means of frictional engagement on the outer sleeve, the frictional engagement being achieved due to the expansion of the outer sleeve.

[0027] In comparison to the first alternative, the second alternative of the fastening arrangement according to the invention additionally has a hollow screw. The above-described arrangement comprising an outer sleeve and an inner sleeve inserted therein is arranged inside the hollow screw in the third through-channel. Analogous to the inner and outer sleeve, the hollow screw has a fifth and a sixth axial end. The third through-channel has a smaller diameter on the side facing the second component, i.e. adjacent to the sixth axial end, compared to the remaining area of ​​the through-channel, which is adjacent to the fifth axial end. The outer sleeve with the inner sleeve arranged therein is provided in the area with the smaller diameter. The fastening arrangement in the first component is mounted via the external thread of the hollow screw. The use of a hollow screw in particular enables the compensation of larger axial tolerances.In particular, further axial compensation can be achieved by rotating the hollow screw before tightening the fastening screw or nut. In contrast to the first alternative, the position of the hollow screw is therefore determined by frictional engagement on the outer sleeve in the fastening state, rather than the position of the first component. Otherwise, the use of this fastening arrangement is similar to the first alternative, so reference is made to the above explanations.

[0028] In a preferred embodiment of the fastening arrangement, the conical shape in the first through-channel is oriented such that the larger diameter is arranged adjacent to the first axial end of the outer sleeve, and the conical shape of the radial outer side of the inner sleeve is oriented such that the larger outer diameter is arranged adjacent to the third axial end of the inner sleeve, wherein in use the second and fourth axial ends face the second component. The inner sleeve thus moves in the direction of the second component. This in particular, in conjunction with the threadless design of the inner sleeve, results in a versatile application of the respective fastening arrangement. In this context, it is particularly preferred that the conical angle of the respective conical shapes is the same.This is precisely how a parallel expansion of the outer sleeve is ensured, so that sliding of the first component in a preferred direction can be avoided.

[0029] Preferably, the outer side of the outer sleeve comprises a flange adjacent to the first axial end. The flange is particularly dimensioned to limit movement of the outer sleeve in the first component or in the hollow screw toward the second component. The flange thus prevents the outer sleeve from being moved through the opening in the first component or in the hollow screw in the insertion direction of the fastening arrangement.

[0030] Furthermore, the outer side of the outer sleeve preferably has a plurality of locking lugs adjacent to the second axial end, which are evenly distributed around the circumference. The use of locking lugs limits movement of the fastening arrangement in the axial direction opposite to the direction of insertion of the fastening arrangement into the first opening or into the hollow screw. This advantage is particularly evident in conjunction with the flange, since the combination of flange and locking lugs provides an axial loss protection for the fastening arrangement in the first opening in the first component or in the hollow screw.

[0031] In a further advantageous embodiment of the fastening arrangement, the outer side of the outer sleeve comprises a profile, in particular in the form of one or a plurality of ribs or a thread profile. This is particularly advantageous if the first component or the hollow screw is made of a softer material than the outer sleeve. This is because, in this case, the profile of the outer sleeve can dig into the material of the first component in the first opening or into the material of the hollow screw when the fastening screw or the nut is tightened. Of course, the reversal of this principle is also possible and is preferred, particularly with regard to the first component according to the invention described later, but also with regard to the fastening arrangement with a hollow screw, i.e.a profiling in the first opening of the first component or in the area of ​​the hollow screw with a smaller inner diameter, which digs into the outer sleeve when the fastening screw or nut is tightened.

[0032] The inner side of the outer sleeve preferably has an undercut adjacent to the first axial end. The undercut on the inner side of the outer sleeve serves to secure the inner sleeve in the outer sleeve. This function arises precisely in conjunction with the preferred design of the inner sleeve, in which the outer side of the inner sleeve adjacent to the fourth axial end comprises at least one locking lug, preferably two locking lugs that are evenly spaced around the circumference, which engages with the first slot in the outer sleeve. This is because this locking lug, in conjunction with the undercut preferably formed by the first slot, limits the movement of the inner sleeve in the direction opposite to the insertion direction, i.e. in the extraction direction. In this way, the inner sleeve is arranged captively in the outer sleeve. This also means that the first slot in the outer sleeve does not extend as far as the first axial end of the outer sleeve.

[0033] In a further preferred embodiment of the fastening arrangement, the outer sleeve has at least two axially extending second slots which extend from the second axial end to the first axial end of the outer sleeve, wherein a web for bridging the second slot is preferably present in each of the second slots. In order to further ensure the stability of the outer sleeve, this embodiment is particularly preferred in conjunction with the use of a flange which is continuous in the circumferential direction. Furthermore, this embodiment is particularly preferred in conjunction with a preferred embodiment of the inner sleeve, in which the outer side of the inner sleeve adjacent to the fourth axial end has at least two circumferentially evenly spaced guide projections which engage in particular with the second slots of the outer sleeve. An advantage of this procedure is that the shape of the outer sleeve is stabilized.Especially when the outer sleeve is manufactured by injection molding, warpage during the injection molding process is prevented. Furthermore, the webs provide a defined stop for the inner sleeve, especially when it has the guide projections. In this context, it is preferred that, if both guide projections and one or more locking lugs are provided, these are each evenly spaced from one another and arranged alternately. If two locking lugs are provided, these are therefore arranged opposite one another. Likewise, if two guide projections are provided, these would also be arranged opposite one another. In addition, an angle of 90° would exist between each locking lug and each guide projection.

[0034] Furthermore, the outer side of the inner sleeve preferably comprises at least two radially outwardly projecting webs adjacent to the third axial end, which provide anti-rotation protection for the inner sleeve within the outer sleeve. Particularly advantageously, the webs are provided at the same circumferential position as the locking lugs. This prevents the webs from being located in the area of ​​the guide projections, since this is where the second slots are located, extending to the first axial end.

[0035] According to an advantageous embodiment of the fastening arrangement, a limiting bushing is further arranged in the inner sleeve, which limits compression of the fastening arrangement during use. The limiting bushing is preferably made of metal or plastic, in particular PA6-GF50, PPA-GF50, PPA-GF60. The use of the limiting bushing depends on the material of the inner sleeve, since the limiting bushing prevents the inner sleeve from being damaged when tightening the fastening screw or nut. This is especially true when the inner sleeve also rests against the second component in the fastened state.

[0036] If this is not the case and the inner sleeve is merely adjacent to the second component, the preload of the fastening arrangement can also be limited by the torque of the fastening screw or nut. Precisely in these cases, a limiting bushing is not required. A first component according to the invention has a first opening in which the first or second alternative of the fastening arrangement according to the invention is arranged, in particular in a captive manner. Since the first component according to the invention has one of the fastening arrangements according to the invention, reference is made to the above explanations to avoid repetition.

[0037] A first alternative of a connecting structure according to the invention consists of an alternative of the first component and a second component, as well as a fastening screw, wherein a thread is provided on or adjacent to a second opening of the second component, so that the components are fastened to one another via the fastening screw, which extends through the fastening arrangement and engages the thread. To avoid repetition, reference is also made to the above explanations.

[0038] A second alternative of a connecting structure according to the invention consists of an alternative of the first component and a second component, as well as a nut, wherein the second component has a threaded shaft that extends through the fastening arrangement and engages with the nut. With regard to the resulting technical effects and advantages, reference is again made to the above statements regarding the alternatives of the fastening arrangement according to the invention.

[0039] A manufacturing method according to the invention for the first alternative of the fastening arrangement according to the invention comprises the steps of: providing the outer sleeve, in particular by injection molding, providing the inner sleeve, in particular by injection molding, inserting the inner sleeve into the outer sleeve. Accordingly, a manufacturing method according to the invention for the second alternative of the fastening arrangement according to the invention comprises the steps of: providing the outer sleeve, in particular by injection molding, providing the inner sleeve, in particular by injection molding, providing the hollow screw, in particular by injection molding,Inserting the inner sleeve into the outer sleeve and inserting the outer sleeve with the inner sleeve arranged therein into the hollow screw. The respective alternative of the fastening arrangement according to the invention can be produced using the manufacturing methods according to the invention. Therefore, in this context, reference is also made to the above explanations with regard to the resulting technical effects and advantages. A method according to the invention for connecting a first component to a second component using an alternative of the fastening arrangement according to the invention comprises the following steps: Inserting the first alternative of the fastening arrangement according to the invention into a first opening in the first component or screwing the hollow screw of the second alternative of the fastening arrangement according to the invention into a first opening in the first component, then, if the second component has a thread at or adjacent to a second opening,Aligning the fastening arrangement in the first component with the second opening, inserting a fastening screw into the fastening arrangement, and fastening the second component to the first component by means of the fastening screw extending through the fastening arrangement and engaging the thread at or adjacent to the second opening in the second component, or, if the second component has a threaded shaft, aligning the fastening arrangement in the first component with the threaded shaft of the second component, inserting the threaded shaft into the fastening arrangement, and fastening the second component to the first component by means of a nut. The respective alternative of the connecting structure according to the invention can be produced using the connecting method according to the invention. To avoid repetition, reference is therefore made to the above explanations with regard to the resulting technical effects and advantages.

[0040] 4. Brief summary of the drawings

[0041] The present invention is described in detail below with reference to the drawings. Like reference numerals in the drawings denote like components and / or elements. They show:

[0042] Figure 1 is a first perspective view of a first embodiment of a fastening arrangement according to the invention,

[0043] Figure 2 is a second perspective view of the first embodiment of the fastening arrangement according to Fig. 1,

[0044] Figure 3 is a first perspective view of a first embodiment of an outer sleeve of the fastening arrangement according to Fig. 1, Figure 4 is a second perspective view of the first embodiment of the outer sleeve according to Fig. 3,

[0045] Figure 5 is a third perspective view of the first embodiment of the fastening arrangement according to Fig. 1,

[0046] Figure 6 is a perspective view of a first embodiment of an inner sleeve of the fastening arrangement according to Fig. 1,

[0047] Figure 7 is an enlarged view of an end portion of the inner sleeve according to Fig. 6,

[0048] Figure 8 is a side view of the fastening arrangement according to Fig. 1 inserted into a first component,

[0049] Figure 9 is a perspective view of the first component with the fastening arrangement according to Fig. 8 inserted therein,

[0050] Figure 10 is a side view of an embodiment of a connecting structure according to the invention with the fastening arrangement according to Fig. 1, wherein the distance between the first and the second component corresponds to the greatest possible distance,

[0051] Figure 11 is a side view of an embodiment of the connecting structure according to the invention with the fastening arrangement according to Fig. 1, wherein the distance between the first and the second component corresponds to the smallest possible distance,

[0052] Figure 12 is a side view of a first embodiment of the connecting structure according to the invention with the fastening arrangement according to Fig. 1, wherein the first component is in an end position,

[0053] Figures 13a to 13g show different states during the fastening of the first component to the second component in side view and in sectional view,

[0054] Figures 14a to 14d show different states during the fastening of the first component to the second component in a perspective view, Figure 15 shows a perspective view of a second embodiment of an outer sleeve of the fastening arrangement,

[0055] Figure 16 is a perspective view of a third embodiment of an outer sleeve of the fastening arrangement,

[0056] Figure 17 is a side view of a second embodiment of a fastening arrangement according to the invention,

[0057] Figure 18 is a perspective view of the second embodiment of the fastening arrangement according to the invention according to Fig. 17,

[0058] Figure 19 is an enlarged view of an end portion of a second embodiment of an inner sleeve,

[0059] Figure 20 is a side view of a third embodiment of a fastening arrangement according to the invention,

[0060] Figure 21 is a perspective view of a fourth embodiment of a fastening arrangement according to the invention,

[0061] Figure 22 shows a first perspective view of a fifth embodiment of a fastening arrangement according to the invention,

[0062] Figure 23 is a second perspective view of the fifth embodiment of the fastening arrangement according to the invention according to Fig. 22,

[0063] Figure 24 is a sectional view of the fifth embodiment of the fastening arrangement according to the invention according to Fig. 22,

[0064] Figure 25 is a sectional view of the hollow screw of the fastening arrangement according to Fig. 22, Figures 26a to 26j show different states during the fastening of the first component to the second component with a fastening arrangement with a hollow screw in partial section and section view,

[0065] Figure 27 is a perspective view of a sixth embodiment of a fastening arrangement according to the invention,

[0066] Figure 28a is an exploded view of the fastening arrangement according to Fig. 27,

[0067] Figure 28b shows the fastening arrangement according to Fig. 28a in partial section,

[0068] Figure 29a shows the fastening arrangement according to Fig. 27 in connection with a second component in a partial sectional view,

[0069] Figure 29b shows the fastening arrangement according to Fig. 27 in connection with a first and a second component in a partial sectional view,

[0070] Figures 30a to 30d are perspective views of different embodiments of a hollow screw for use in a fastening arrangement,

[0071] Figure 31 is a side view of a second embodiment of the connecting structure according to the invention with the fastening arrangement, wherein the first component is in an end position,

[0072] Figure 32 is a flow chart of an embodiment of a manufacturing method according to the invention for producing a first embodiment of a fastening arrangement according to the invention,

[0073] Figure 33 is a flow chart of an embodiment of a manufacturing method according to the invention for producing a second embodiment of a fastening arrangement according to the invention,

[0074] Figure 34 shows a flowchart of an embodiment of a joining method according to the invention. 5. Detailed Description of the Preferred Embodiments

[0075] A first embodiment of a fastening arrangement 10 according to the invention is discussed below with reference to Figures 1 to 7.

[0076] The fastening arrangement 10 comprises an outer sleeve 20, which defines a central longitudinal axis L of the fastening arrangement 10, and an inner sleeve 50. Depending on the respective application, a limiting bushing 70 is provided inside the inner sleeve 50, which will be explained later. The outer sleeve 20 is preferably made of plastic, in particular PA66, PA 12, PA66-GF15 or PA66-GF30. With regard to the inner sleeve 50, this is preferably made of metal or plastic, in particular PA66-GF30 or PPA-GF50. The limiting bushing 70 is preferably made of metal or plastic, in particular PA6-GF50, PPA-GF50, PPA-GF60.

[0077] As can be seen in Figures 3 and 4, the outer sleeve 20 comprises a first axial end 22 and a second axial end 24. Two axially extending first slots 28 extend from the second axial end 24 in the direction of the first axial end 22 of the outer sleeve 20. In addition, the outer sleeve 20 has two axially extending second slots 42. In contrast to the first slots 28, which do not extend completely along the axial direction of the outer sleeve 20, the second slots 42 extend from the second axial end 24 to the first axial end 22 of the outer sleeve 20. In each of the second slots 42, a web 44 is provided to bridge the second slot 42. This prevents distortion in the injection molding process, especially when the outer sleeve 20 is manufactured by injection molding. Furthermore, the webs 44 provide a defined stop for the inner sleeve 50, which will be explained later.

[0078] The first 28 and second slots 42 are each evenly spaced from one another and arranged alternately. Thus, the first slots 28 are arranged opposite one another. The second slots 42 are also arranged opposite one another. As a result, there is an angle of 90° between a first 28 and a second slot 42. Adjacent to the first axial end 22, the outer side of the outer sleeve 20 comprises a flange 30 that is continuous in the circumferential direction. The flange 30 is dimensioned such that it limits movement of the outer sleeve 20 in a first component A toward a second component B. The flange 30 thus prevents the outer sleeve 20 from being moved through an opening 120 in the first component A in the insertion direction of the fastening arrangement 10. Furthermore, the flange 30 increases the stability of the outer sleeve 20, especially with regard to the second slots 42.

[0079] In the illustrated embodiment, the flange 30 comprises two opposing tabs 32. The tabs 32 are provided in the region of the second slots 42. In principle, other configurations of the flange 30 are also possible, which will be explained below using corresponding embodiments.

[0080] Furthermore, the outer side of the outer sleeve 20 adjacent to the second axial end 24 has a plurality of locking lugs 36 that are evenly distributed around the circumference. The locking lugs 36 are each provided adjacent to a first slot 28 and a second slot 42. As an alternative to a plurality of locking lugs 36, the use of a locking lug 36 extending circumferentially between two adjacent slots 28, 42 is also possible.

[0081] The use of locking lugs 36 has the effect of limiting movement of the fastening arrangement 10 in the axial direction opposite to the direction of insertion of the fastening arrangement 10 into the first opening 120 in the first component A. The advantage becomes particularly clear in conjunction with the flange 30, since the combination of flange 30 and locking lugs 36 provides axial loss protection for the fastening arrangement 10 in the first opening 120 in the first component A.

[0082] The inner side of the outer sleeve 20 has an undercut 40 adjacent to the first axial end 22. The undercut 40 serves to secure the inner sleeve 50 in the outer sleeve 20, which will be explained later in the description of the structure of the inner sleeve 50.

[0083] Furthermore, the outer sleeve 20 has a first through-channel 26 which is concentric with the central longitudinal axis L and is conical in shape at least in sections. The conical shape in the first through-channel 26 is oriented such that the larger inner diameter is arranged adjacent to the first axial end 22 of the outer sleeve 20. The inner sleeve 50 has a third 52 and a fourth axial end 54. The radial outer side of the inner sleeve 50 is conical in shape at least in sections. The conical shape of the radial outer side of the inner sleeve 50 is oriented such that the larger outer diameter is arranged adjacent to the third axial end 52 of the inner sleeve 50.As explained in detail later, the inner sleeve 50 is movably received in the outer sleeve 20 along the central longitudinal axis L such that, in an initial state of the fastening arrangement 10, the fourth axial end 54 of the inner sleeve 50 is arranged adjacent to the first axial end 22 of the outer sleeve 20. In a fastening state in which the inner sleeve 50 has been pushed further into the outer sleeve 20, the fourth axial end 54 of the inner sleeve 50 is therefore adjacent to the second axial end 24 of the outer sleeve 20. Therefore, the inner sleeve 50 has an axial length that is equal to or greater than the axial length of the outer sleeve 20. This is particularly useful in the case of a block screw connection, since the outer sleeve 20 is not subjected to an axial force in this way.

[0084] The cone angle of the respective conical shapes, i.e., the conical shape in the first through-channel 26 of the outer sleeve 20 and the conical shape of the outer side of the inner sleeve 50, is identical. This ensures parallel expansion of the outer sleeve 20, preventing the first component A from sliding in a preferred direction. It is important to ensure that the conical angle is neither too steep nor too shallow to ensure proper functioning of the fastening arrangement 10.

[0085] In the illustrated embodiment, the outer side of the inner sleeve 50, adjacent to the fourth axial end 54, has two circumferentially evenly spaced locking lugs 58. These engage with the first slots 28 of the outer sleeve 20. Thus, the locking lugs 58 of the inner sleeve 50, in conjunction with the undercut 40, which in this case is formed by the first slots 28, limit the movement of the inner sleeve 50 in the direction opposite the insertion direction, i.e., in the withdrawal direction. In this way, the inner sleeve 50 is arranged captively in the outer sleeve 20. This also means that the first slots 28 in the outer sleeve 20 do not extend to the first axial end 22 of the outer sleeve 20. Furthermore, the outer side of the inner sleeve 50, adjacent to the fourth axial end 54, comprises two circumferentially evenly spaced guide projections 60.When the inner sleeve 50 is used in the outer sleeve 20, these engage with the second slots 42 of the outer sleeve 20. The webs 44 provided in the second slots 42 therefore provide a defined stop for the inner sleeve 50. As already shown for the first 28 and second slots 42 of the outer sleeve, the locking lugs 58 and guide projections 60 of the inner sleeve 50 are each evenly spaced from one another and arranged alternately. If there are two locking lugs 58, these are arranged opposite one another. Likewise, if there are two guide projections 60, these are also arranged opposite one another. In addition, there is an angle of 90° between each locking lug 58 and each guide projection 60.

[0086] Inside, the inner sleeve 50 has a second through-channel 56, which is concentric with the central longitudinal axis L and is designed without a thread. In the illustrated embodiment, a limiting bushing 70 is also arranged in the inner sleeve 50, which limits compression of the fastening assembly 10 during use. The limiting bushing 70 is also designed without a thread inside.

[0087] The use of the limiting bushing 70 depends, on the one hand, on the material of the inner sleeve 50. This is because the limiting bushing 70 prevents the inner sleeve 50 from being damaged when tightening a fastening screw 130 or a nut 142. This is especially true if the inner sleeve 50 is intended to bear against the second component B, which will be explained later. If this is not the case and the inner sleeve 50 is merely arranged adjacent to the second component B, the preload of the fastening arrangement 10 can be limited via the torque of the fastening screw 130 or the nut 142.

[0088] Initially, the fastening assembly 10 is present, which consists of the outer sleeve 20 and the inner sleeve 50 inserted therein, as well as optionally the limiting bushing 70. The fourth axial end 54 of the inner sleeve 50 is arranged adjacent to the first axial end 22 of the outer sleeve 20.

[0089] When in use, this fastening arrangement 10 is first inserted with the second axial end 24 of the outer sleeve 20 facing forward into the first opening 120 in the first component A and latches there. The fastening arrangement 10 is thus arranged captively in the first component A. An example representation of this state can be found in Figures 8 and 9. Figures 10 and 11 show the extreme positions of the first component A between the first 22 and the second axial end 24 of the outer sleeve 20, in particular between the flange 30 and the locking lugs 36. If the first component A is arranged adjacent to the locking lugs 36, the distance to the second component B is minimal. The distance to the second component B is maximum when the first component A is arranged adjacent to the flange 30. Thus, by setting the desired distance, tolerance compensation between the first component A and the second component B in the axial direction can be achieved.

[0090] Figure 12 shows a possible final state of an embodiment of a connecting structure 1, wherein the second component B here has a nut 132 for engagement with a fastening screw 130. As can be seen from these figures, the second axial end 24 of the outer sleeve 20 faces the second component B. In addition, the conical shape of the inner side of the outer sleeve 20 and the outer side of the inner sleeve 50 is aligned such that the smaller inner diameter is provided adjacent to the second 24 and the fourth axial end 54, respectively.

[0091] For the case of a desired block screw connection, an inner diameter of the opening 120 in the first component A is selected such that, relative to a maximum expansion of the outer sleeve 20 by the inner sleeve 50, it is at least 1% and at most 6%, preferably between 2% and 3%, smaller than an outer diameter of the outer sleeve 20 in the maximally expanded state. The elastic deformation of the outer sleeve 20 creates an interference fit with sufficient friction and therefore adhesive strength against twisting and displacement of the outer sleeve 20 in the opening 120 of the first component A.

[0092] Referring now to Figures 13a to 14d, the different steps in the connection between the first component A and the second component B are explained using a second embodiment of a connecting structure 3. In this embodiment, the second component B has an opening with a blind rivet nut arranged therein as nut 132. Figure 14a shows a corresponding exploded view at the beginning.

[0093] After the first component A has been equipped with the fastening arrangement 10, as shown in Figures 13a and 14b, it is brought into alignment with the second component B. In use, the second 24 and the fourth axial end 54 thus face the second component B. Subsequent movement of the inner sleeve 50 within the outer sleeve 20 thus occurs in the direction of the second component B. In the embodiment shown, the second component B has a second opening. The second opening has an internal thread, either itself or adjacent thereto, here provided by a blind rivet nut as nut 132.

[0094] Once aligned, the fastening screw 130 is inserted from the first axial end 22 of the outer sleeve 20 through the fastening assembly 10 such that it can engage with the internal thread of the second component B, i.e. the nut 132. Since the smallest inner diameter of the inner sleeve 50 is larger than the outer diameter of the shank of the fastening screw 130, the fastening screw 130 can move radially in the fastening assembly 10 and thus compensate for radial tolerances between the first opening 120 in the first component A and the second opening in the second component B. If a limiting bushing 70 is used in the inner sleeve 50, the limiting bushing 70 accordingly also has an inner diameter that is larger than the outer diameter of the shank of the fastening screw 130. Otherwise, the radial tolerance compensation would not be guaranteed.This can be seen in Figure 13b in the side view and in Figure 13c in the sectional view.

[0095] The axial tolerance is compensated for by appropriately positioning the first component A between the first 22 and the second axial end 24 of the outer sleeve 20 of the fastening arrangement 10. Typically, the axial length of the outer sleeve 20 limits the axial tolerance compensation, since the outer sleeve 20 in the final state rests with its second axial end 24 on the second component B. If the outer sleeve 20 and / or the inner sleeve 50 rest on the second component and a preload force and therefore a clamping force is generated between the fastening arrangement 10 and the second component B by the fastening screw 130, a block screw connection results.

[0096] If a limiting bushing 70 is used, it is at least advantageous that the limiting bushing 70 also rests against the second component B. The state in which the outer sleeve 20 already rests against the second component B is shown in Figures 13d in the side view, in Figure 13e in the sectional view, and in Figure 14c in the perspective view.

[0097] Once the correct positioning has been achieved, the fastening screw 130 is tightened. Before tightening the fastening screw 130 begins, the fastening assembly 10 is still in its initial state. The fourth axial end 54 of the inner sleeve 50 is thus adjacent to the first axial end 22 of the outer sleeve 20. In other words, the fastening assembly 10 has its greatest possible axial length in this state.

[0098] If the fastening screw 130 is now tightened, the inner sleeve 50 is driven into the outer sleeve 20. As a result, the webs 44 in the second slots 42 are sheared off by the guide projections 60, the outer sleeve 20 is spread open, and a circumferential radial force is generated towards the first component A. In this way, the position of the first component A in the fastening state between the first 22 and the second axial end 24 of the outer sleeve 20 is fixed by means of frictional engagement on the outer sleeve 20. The corresponding fastening state is shown in Figures 13f in a side view, in Figure 13g in a sectional view, and in Figure 14d in a perspective view.

[0099] In order to achieve this effect, the inner sleeve 50 is dimensioned relative to the outer sleeve 20 such that it has an outer diameter at least at the fourth axial end 54 and at least partially in the region of the conical shape that is larger than the inner diameter of the outer sleeve 20 at the second axial end 24 and in the region of the conical shape of the first through-channel 26.

[0100] An advantage of this fastening arrangement 10 is that no additional stresses are generated between the first component A and the second component B. Furthermore, the fastening arrangement 10 has a compact design with few individual parts. This makes the fastening arrangement 10 particularly cost-effective to manufacture and easy to use. Furthermore, as described above, both axial and radial tolerances between the first component A and the second component B can be compensated.

[0101] Referring now to Figure 15, an alternative embodiment of an outer sleeve 80 is shown. Here, the outer side of the outer sleeve 80 comprises a profile 38 in the form of a plurality of ribs. This is particularly advantageous when the first component A is made of a softer material than the outer sleeve 20. In this case, when the fastening screw 130 is tightened, the profile 38 of the outer sleeve 20 can dig into the material of the first component A in the first opening 120. Of course, this principle can also be reversed, so that the first component A has a profile in the first opening 120, which digs into the respective outer sleeve 20, 80 when the fastening screw 132 is tightened.

[0102] Figure 16 shows a further embodiment of an outer sleeve 82. This is similar to the first embodiment 20, but has a differently configured flange 30. In particular, the flange 30 does not have the two tabs 32, but rather is provided with two webs 34 radially spaced at the first axial end 22. The webs 34 are provided in alignment with the first slots 28.

[0103] Figures 17 and 18 show a further possible design of an outer sleeve 84 in a further embodiment of a fastening arrangement 12. This design represents a combination of the designs of Figures 15 and 16. On the one hand, the flange 30, as shown in Figure 16, is provided with two webs 34 at the first axial end 22. On the other hand, the outer side of the outer sleeve 84 has a profile 38 in the form of several ribs, as shown in Figure 15.

[0104] With regard to the inner sleeve, Figure 19 shows an alternative embodiment of the inner sleeve 90. This essentially corresponds to the inner sleeve 50, but additionally has two radially outwardly projecting webs 62 on the outer side adjacent to the third axial end 52. These webs 62 form a rotation lock of the inner sleeve 90 in the outer sleeve 20, 80, 82 or 84. The webs 62 are provided at the same circumferential position as the locking lugs 58 of the inner sleeve 50, 90. In this way, it is particularly prevented that the webs 62 are present in the region of the guide projections 60, since this is where the second slots 42 are present in the outer sleeve 20, 80, 82 or 84, which extend to the first axial end 22.

[0105] Figure 20 shows the fastening arrangement 12 in conjunction with a modified first opening 120 in the first component A. This is because the first component A has a circumferential projection 122 as a profile in the opening 120. This further improves the connection between the outer sleeve 84 and the first component A and provides a stepped adjustment option.

[0106] In an analogous manner, Figure 21 shows a further embodiment of the fastening arrangement 14.

[0107] Here, the outer sleeve 86 has a profile 36 in the form of a thread. Similarly, a matching thread profile 124 is provided in the opening 120 in the first component A. This allows for continuous adjustment.

[0108] An embodiment of an alternative fastening arrangement 16 is shown in Figures 22 to 25. In the example shown, this consists of the outer sleeve 82 according to Figure 16 and the inner sleeve 50 according to Figure 6, wherein no limiting bushing 70 is provided. In contrast to the previous embodiments, however, the outer sleeve 82 with the inner sleeve 50 arranged therein is not arranged directly in the first component A, but rather in a hollow screw 100 belonging to the fastening arrangement 16. The above statements regarding the fastening of the combination of outer sleeve 20, 80, 82, 84 or 86 and inner sleeve 20 or 90 in the first component A therefore apply analogously to the fastening of this combination in the hollow screw 100.

[0109] The hollow screw 100 has a fifth 102 and a sixth axial end 104. A third through-channel 106 is provided inside the hollow screw, concentric with the central longitudinal axis L. The third through-channel 106 has a first region 108 with a first inner diameter adjacent to the fifth axial end 102 and a second region 108 with a second inner diameter adjacent to the sixth axial end 104. The second inner diameter is smaller than the first inner diameter and serves to at least partially accommodate the outer sleeve 20, 80, 82, 84, or 86. Thus, the outer sleeve 20, 80, 82, 84, or 86 is at least partially arranged in the third through-channel 106. To strengthen the connection between the hollow screw 100 and the respective outer sleeve 20, 80, 82, 84 or 86, a profile 112 is provided in the second area 110.

[0110] On the outside, the hollow screw 100 has an external thread 114. This external thread 114 secures the fastening assembly 16 in the opening 120 in the first component A. The external thread 114 enables continuous adjustment of the fastening assembly 16.

[0111] In the fastening state, a position of the hollow screw 100 can thus be fixed by means of frictional engagement on the outer sleeve 20, 80, 82, 84 or 86, wherein the frictional engagement is achieved due to the expansion of the outer sleeve 20, 80, 82, 84 or 86. Analogous to the fastening in the first component A, in this embodiment an inner diameter of the second region 110 of the hollow screw 100 is selected for the case of a desired block screw connection such that, based on a maximum expansion of the outer sleeve 20, 80, 82, 84 or 86 by the inner sleeve 50, 90, it is at least 1% and at most 6%, preferably between 2% and 3%, smaller than an outer diameter of the outer sleeve 20, 80, 82, 84 or 86 in the maximally expanded state.The elastic deformation of the outer sleeve 20, 80, 82, 84 or 86 creates an interference fit with sufficient friction and therefore adhesive strength against twisting and displacement of the outer sleeve 20, 80, 82, 84 or 86 in the second region 110 of the hollow screw 100.

[0112] In this variant, the fastening arrangement 16 additionally has a hollow screw 100 compared to the fastening arrangements 10, 12, and 14. The above-described arrangement of outer sleeve 20, 80, 82, 84, or 86 and the inner sleeve 50 or 90 inserted therein is arranged inside the hollow screw 100 in the third through-channel 106.

[0113] The use of a hollow screw 100 in particular enables the compensation of larger axial tolerances. In particular, further compensation in the axial direction can be achieved by turning the hollow screw 100 before tightening the fastening screw 130. In contrast to the fastening arrangements 10, 12, and 14, in the fastening state, a position of the hollow screw 100 is determined by frictional engagement with the outer sleeve 20, 80, 82, 84, or 86, and not a position of the first component A. Otherwise, the use of this fastening arrangement 16 is similar to the previously described fastening arrangements 10, 12, and 14, so reference is made to the above explanations.

[0114] Referring now to Figures 26a to 26j, the different steps in the connection between the first component A and the second component B are explained. Figures 26a and 26b show the fastening arrangement 16 in connection with the first component A, wherein the first component A is located in different axial positions of the hollow screw 100.

[0115] In this embodiment, the second component B has an opening with a weld nut arranged thereon as nut 132. The further figures discuss the connection structure 5, in which the fastening arrangement 16 with hollow screw 100 is used. After the first component A has been equipped with the fastening arrangement 16, it is brought into alignment with the second component B. In use, the second 24, the fourth 54, and the sixth axial end 104 thus face the second component B. Subsequent movement of the inner sleeve 50 or 90 in the outer sleeve 20, 80, 82, 84, or 86 thus occurs in the direction of the second component B. In the embodiment shown, the second component B has a second opening. The second opening has an internal thread, either itself or adjacent thereto, provided here by the weld nut as nut 132.

[0116] After alignment has been achieved, the fastening screw 130 is inserted from the first axial end 22 of the outer sleeve 20, 80, 82, 84 or 86 through the fastening assembly 16 such that it can engage the internal thread of the second component B, i.e., the nut 132. Since the smallest inner diameter of the inner sleeve 50 or 90 is larger than the outer diameter of the shank of the fastening screw 130, the fastening screw 130 can move radially in the fastening assembly 16 and thus compensate for radial tolerances between the first opening 120 in the first component A and the second opening in the second component B. This can be seen in Figure 26c.

[0117] The axial tolerance is compensated for by appropriately positioning the first component A between the fifth 102 and the sixth axial end 104 of the hollow screw 100 of the fastening arrangement 16. In addition, axial tolerance compensation is achieved by positioning the second region 110 of the hollow screw 100 between the first 22 and the second axial end 24 of the outer sleeve 20, 80, 82, 84 or 86. The axial tolerance compensation is therefore limited on the one hand by the axial length of the hollow screw 100 and on the other hand by the axial length of the outer sleeve 20, 80, 82, 84 or 86, since the outer sleeve 20, 80, 82, 84 or 86 rests against the second component B with its second axial end 24 in the final state. This can also be seen from a comparison of Figures 26c and 26d.

[0118] After the fastening screw 130 is initially screwed into the nut 132, with the fastening assembly 16 still in its initial state, a distance between the first component A and the second component can be adjusted using the hollow screw 100. This is shown in Figures 26e and 26f. Furthermore, the distance can be adjusted by moving the hollow screw 100 relative to the outer sleeve 20, 80, 82, 84, or 86, as shown in Figures 26g and 26h.

[0119] Once the correct positioning has been achieved, the fastening screw 130 is tightened. Before tightening the fastening screw 130, the fastening assembly 16 is still in its initial state (see also Figure 26i). The fourth axial end 54 of the inner sleeve 50 or 90 is thus adjacent to the first axial end 22 of the outer sleeve 20, 80, 82, 84, or 86.

[0120] If the fastening screw 130 is now tightened, the inner sleeve 50 or 90 is driven into the outer sleeve 20, 80, 82, 84 or 86. This spreads the outer sleeve 20, 80, 82, 84 or 86 and generates a circumferential radial force to the first component A. In this way, the position of the hollow screw 100 in the fastening state between the first 22 and the second axial end 24 of the outer sleeve 20, 80, 82, 84 or 86 is determined by means of frictional engagement on the outer sleeve 20, 80, 82, 84 or 86. The corresponding fastening state is shown in Figure 26j.In order to achieve this effect, the inner sleeve 50 or 90 is dimensioned relative to the outer sleeve 20, 80, 82, 84 or 86 such that it has an outer diameter at least at the fourth axial end 54 and at least partially in the region of the conical shape that is larger than the inner diameter of the outer sleeve 20, 80, 82, 84 or 86 at the second axial end 24 and in the region of the conical shape of the first through-channel 26.

[0121] An advantage of this fastening arrangement 16 is that, due to the hollow screw 100, larger axial tolerances can be compensated for compared to the fastening arrangement 10, 12, or 14 without the hollow screw 100. Furthermore, reference is made to the explanations regarding the previously discussed fastening arrangements 10, 12, and 14.

[0122] Referring now to Figures 27 to 29b, a further fastening arrangement 18 with hollow screw 150 and the associated connecting structure 7 is shown. The hollow screw 150 differs from the hollow screw 100 in the profile 112 used. Otherwise, the hollow screw 150 corresponds to the hollow screw 100. Accordingly, the outer sleeve is preferably the outer sleeve 86 shown in Figure 21. Reference is made to the corresponding explanations to avoid repetition. Figures 30a to 30d show further embodiments of the hollow screw 152, 154, 156 and 158. In their basic structure, the hollow screws 152, 154, 156 and 158 correspond to the hollow screws 100 and 150. Only the profile 112 is designed differently. For example, the hollow screw 152 has a circular profile, while the hollow screw 154 has a plurality of projections forming the profile 112.In the hollow screw 156, the profile 112 is formed by a zigzag shape and in the hollow screw 158 by a plurality of elongated and obliquely arranged projections.

[0123] A further embodiment of a connecting structure 9 is shown in Figure 31 and consists of the first component A with the fastening arrangement 10, 12, 14, 16 or 18 and a second component B and a nut 142. In comparison to the previously discussed embodiments of the connecting structure 1, 3, 5 and 7, here the second component B has a threaded shaft 140. This extends through the fastening arrangement 10, 12, 14, 16 or 18 and engages with a nut 142.

[0124] As in the previous example, in use, the second axial end 24 of the outer sleeve 20, 80, 82, 84 or 86 faces the second component B. In addition, the conical shape of the inner side of the outer sleeve 20, 80, 82, 84 or 86 and the outer side of the inner sleeve 50 or 90 is aligned such that the smaller inner diameter is adjacent to the second 24 or the fourth axial end 54.

[0125] After alignment, the threaded shaft 140 is inserted from the second axial end 24 of the outer sleeve 20, 80, 82, 84, or 86 through the fastening assembly 10, 12, 14, 16, or 18. Because the smallest inner diameter of the inner sleeve 50 or 90 is larger than the outer diameter of the threaded shaft 140, the threaded shaft 140 can move radially within the fastening assembly 10, 12, 14, 16, or 18, thus compensating for radial tolerances between the first opening 120 in the first component A and the second component B.

[0126] As in the previous examples, the axial tolerance is compensated for by appropriately positioning the first component A and / or the hollow screw 100, 150, 152, 154, 156, or 158. Once the correct positioning has been achieved, a nut 142 is placed on the threaded shaft 140 and tightened. Before tightening the nut 142, the fastening arrangement 10, 12, 14, 16, or 18 is still in its initial state.

[0127] When the nut 142 is now tightened, the inner sleeve 50 or 90 is driven into the outer sleeve 20, 80, 82, 84, or 86. This spreads the outer sleeve 20, 80, 82, 84, or 86, and a circumferential radial force is generated toward the first component A or the hollow screw 100, 150, 152, 154, 156, or 158. In this way, the position of the first component A and, if present, the hollow screw 100, 150, 152, 154, 156, 158 is determined in the fastened state. With regard to the resulting technical effects and advantages, reference is again made to the above explanations regarding the fastening arrangements 10, 12, 14, 16, and 18.

[0128] Referring now to Figure 32, an embodiment of a manufacturing method for the fastening arrangement 10, 12, or 14 is explained. For this purpose, in a first step a, the outer sleeve 20, 80, 82, 84, or 86 is provided, in particular by injection molding. Before, at the same time, or afterward, in step b, the inner sleeve 50 or 90 is provided, in particular by injection molding. In step c, the inner sleeve 50 or 90 is subsequently inserted into the outer sleeve 20, 80, 82, 84, or 86.

[0129] Figure 33 shows a flow diagram of an embodiment of a manufacturing method for a fastening arrangement 16 or 18 with a hollow screw 100, 150, 152, 154, 156 or 158. As in the previous method, the outer sleeve 20, 80, 82, 84 or 86 is provided in a first step A, in particular by injection molding. Before, at the same time, or after, in step B, the inner sleeve 50 or 90 is provided, in particular by injection molding. In step C, which can take place before, after, or simultaneously with steps A and / or B, the hollow screw 100, 150, 152, 154, 156 or 158 is provided, likewise in particular by injection molding. In step D, the inner sleeve 50 or 90 is then inserted into the outer sleeve 20, 80, 82, 84 or 86, while in the following step E, the outer sleeve 20, 80, 82, 84 or 86 with the inner sleeve 50 or 90 arranged therein is inserted into the hollow screw 100, 150, 152, 154, 156 or 158.A schematic flow diagram of a method of joining a first component A to a second component B using a fastening arrangement 10, 12, 14, 16 or 18 is shown in Figure 34.

[0130] First, in step A1, the fastening arrangement 10, 12 or 14 is inserted into a first opening 120 in the first component A.

[0131] Alternatively, and when using a fastening arrangement 16 or 18 with hollow screw 100, 150, 152, 154, 156 or 158, in step A2 the hollow screw 100, 150, 152, 154, 156 or 158 is screwed into the first opening 120 in the first component A.

[0132] If the second component B has a thread, for example in the form of a nut 132, at or adjacent to a second opening, step B1 involves aligning the fastening arrangement 10, 12, 14, 16 or 18 in the first component A with the second opening, inserting a fastening screw 130 into the fastening arrangement 10, 12, 14, 16 or 18 and fastening the second component B to the first component A by means of the fastening screw 130, which extends through the fastening arrangement 10, 12, 14, 16 or 18 and engages the thread of the nut 132 at or adjacent to the second opening in the second component B.

[0133] If the second component B has a threaded shaft 140, in step B2 the fastening arrangement 10, 12, 14, 16 or 18 in the first component A is aligned with the threaded shaft 140 of the second component B, the threaded shaft 140 is inserted into the fastening arrangement 10, 12, 14, 16 or 18 and the second component B is fastened to the first component A by means of a nut 142.

[0134] 6. List of reference symbols

[0135] A first component

[0136] B second component

[0137] L central longitudinal axis

[0138] 1 Connection structure (1st embodiment of the first alternative)

[0139] 3 Connection structure (2nd embodiment of the first alternative) 5 Connection structure (3rd embodiment of the first alternative)

[0140] 7 Connection structure (4th embodiment of the first alternative)

[0141] 9 Connection structure (1st embodiment of the second alternative)

[0142] 10 Fastening arrangement (1st embodiment of the first alternative)

[0143] 12 Fastening arrangement (2nd embodiment of the first alternative)

[0144] 14 Fastening arrangement (3rd embodiment of the first alternative)

[0145] 16 Fastening arrangement (1st embodiment of the second alternative)

[0146] 18 Fastening arrangement (2nd embodiment of the second alternative)

[0147] 20 Outer sleeve (1st embodiment)

[0148] 22 first axial end

[0149] 24 second axial end

[0150] 26 first through channel

[0151] 28 first slots

[0152] 30 flange

[0153] 32 tab

[0154] 34 jetty

[0155] 36 locking lug

[0156] 38 Profile

[0157] 40 undercut

[0158] 42 second slot

[0159] 44 Bridge in the second slot 42

[0160] 50 inner sleeve (1st embodiment)

[0161] 52 third axial end

[0162] 54 fourth axial end

[0163] 56 second through channel

[0164] 58 locking lug

[0165] 60 lead

[0166] 62 jetty

[0167] 70 Limit bushing 80 Outer sleeve (2nd design)

[0168] 82 Outer sleeve (3rd embodiment)

[0169] 84 Outer sleeve (4th embodiment)

[0170] 86 Outer sleeve (5th embodiment)

[0171] 90 inner sleeve (2nd version)

[0172] 100 hollow screw (1st version)

[0173] 102 fifth axial end

[0174] 104 sixth axial end

[0175] 106 third through channel

[0176] 108 first area

[0177] 110 second area

[0178] 112 Profile

[0179] 114 external thread

[0180] 120 Opening in the first component A

[0181] 122 projection in the opening 120

[0182] 124 Thread profile in the opening 120

[0183] 130 fixing screw

[0184] 132 mother

[0185] 140 threaded shaft

[0186] 142 Mother

[0187] 150 Hollow screw (2nd version)

[0188] 152 Hollow screw (3rd design)

[0189] 154 Hollow screw (4th version)

[0190] 156 Hollow screw (5th design)

[0191] 158 Hollow screw (6th design)

Claims

Patent claims 1. A fastening arrangement (10; 12; 14) for connecting a first component (A) to a second component (B) with tolerance compensation between the first component (A) and the second component (B), wherein the fastening arrangement (10; 12; 14) has the following features: a) an outer sleeve (20; 80; 82; 84; 86) with a first (22) and a second axial end (24), which defines a central longitudinal axis (L) of the fastening arrangement (10; 12; 14), has a first through-channel (26) which is conical at least in sections and comprises at least one axially extending first slot (28) which extends from the second axial end (24) in the direction of the first axial end (22) of the outer sleeve (20; 80; 82; 84; 86), and b) an inner sleeve (50;90) with a third (52) and a fourth axial end (54), the radial outer side of which is at least partially conical and which has a second through-channel (56) which is formed concentrically to the central longitudinal axis (L), which is preferably threaded, wherein c) the inner sleeve (50; 90) is movably received along the central longitudinal axis (L) in the outer sleeve (20; 80; 82; 84; 86) such that in an initial state of the fastening arrangement (10; 12; 14) the fourth axial end (54) of the inner sleeve (50; 90) is adjacent to the first axial end (22) of the outer sleeve (20; 80; 82; 84; 86) and in a fastening state the fourth axial end (54) of the inner sleeve (50; 90) is adjacent to the second axial end (24) of the outer sleeve (20; 80; 82; 84; 86) is arranged, whereby d) in the fastening state a position of the first component (A) between the first (22) and the second axial end (24) of the outer sleeve (20; 80; 82; 84;86) can be fixed to the outer sleeve (20; 80; 82; 84; 86) by means of frictional engagement, the frictional engagement being achieved due to the spreading of the outer sleeve (20; 80; 82; 84; 86).

2. A fastening arrangement (16; 18) for connecting a first component (A) to a second component (B) with tolerance compensation between the first component (A) and the second component (B), the fastening arrangement (16; 18) having the following features: a) an outer sleeve (20; 80; 82; 84; 86) with a first (22) and a second axial end (24), which defines a central longitudinal axis (L) of the fastening arrangement (16; 18), has a first through-channel (26) which is concentric with the central longitudinal axis (L), is conical in shape at least in sections, and comprises at least one axially extending first slot (28) which extends from the second axial end (24) in the direction of the first axial end (22) of the outer sleeve (20; 80; 82; 84; 86), and b) an inner sleeve (50;90) with a third (52) and a fourth axial end (54), the radial outer side of which is at least partially conical and which has a second through-channel (56) which is formed concentrically to the central longitudinal axis (L), which is preferably designed to be thread-free, and c) a hollow screw (100; 150; 152; 154; 156; 158) with an external thread (114) and a third through-channel (106) which is formed concentrically to the central longitudinal axis (L), in which the outer sleeve (100; 150; 152; 154; 156; 158) is at least partially arranged, wherein d) the inner sleeve (50; 90) is received in the outer sleeve (20; 80; 82; 84; 86) so as to be movable along the central longitudinal axis (L) such that in an initial state of the fastening arrangement (16; 18) the fourth axial end (54) of the inner sleeve (50; 90) adjacent to the first axial end (22) of the outer sleeve (20; 80; 82; 84; 86) and in a fastening state the fourth axial end (54) of the inner sleeve (50;90) is arranged adjacent to the second axial end (24) of the outer sleeve (20; 80; 82; 84; 86), whereby e) in the fastening state, a position of the hollow screw (100; 150; 152; 154; 156; 158) can be fixed by means of frictional engagement on the outer sleeve (20; 80; 82; 84; 86), wherein; the frictional engagement is achieved due to the spreading of the outer sleeve (20; 80; 82; 84; 86).

3. The fastening arrangement (10; 12; 14; 16; 18) according to one of the preceding claims, wherein the conical shape in the first through-channel (26) is oriented such that the larger diameter is arranged adjacent to the first axial end (22) of the outer sleeve (20; 80; 82; 84; 86), and the conical shape of the radial outer side of the inner sleeve (50; 90) is oriented such that the larger outer diameter is arranged adjacent to the third axial end (52) of the inner sleeve (50; 90), wherein in use the second (24) and the fourth axial end (54) face the second component (B).

4. The fastening arrangement (10; 12; 14; 16; 18) according to one of the preceding claims, wherein the outer side of the outer sleeve (20; 80; 82; 84; 86) comprises a flange (30) adjacent to the first axial end (22).

5. The fastening arrangement (10; 12; 14; 16; 18) according to one of the preceding claims, wherein the outer side of the outer sleeve (20; 80; 82; 84; 86) adjacent to the second axial end (24) comprises a plurality of locking lugs (36) which are arranged in a circumferentially uniformly distributed manner.

6. The fastening arrangement (10; 12; 14; 16; 18) according to one of the preceding claims, wherein the outer side of the outer sleeve (80; 84; 86) comprises a profile, in particular in the form of one or a plurality of ribs or a thread profile.

7. The fastening arrangement (10; 12; 14; 16; 18) according to one of the preceding claims, wherein the inner side of the outer sleeve (20; 80; 82; 84; 86) has an undercut (40) adjacent to the first axial end (22).

8. The fastening arrangement (10; 12; 14; 16; 18) according to one of the preceding claims, in which the outer sleeve (20; 80; 82; 84; 86) has at least two axially extending second slots (42) which extend from the second axial end (24) to the first axial end (22) of the outer sleeve (20; 80; 82; 84; 86), wherein in each of the second slots (42) there is preferably a web (44) for bridging the second slot (42).

9. The fastening arrangement (10; 12; 14; 16; 18) according to one of the preceding claims, wherein the outer side of the inner sleeve (50; 90) adjacent to the fourth axial end (54) comprises at least one locking lug (58), preferably two circumferentially evenly spaced locking lugs (58), which engage with the first slots (28) of the outer sleeve (20; 80; 82; 84; 86).

10. The fastening arrangement (10; 12; 14; 16; 18) according to one of the preceding claims, in which the outer side of the inner sleeve (50; 90) adjacent to the fourth axial end (54) has at least two circumferentially evenly spaced guide projections (60) which in particular engage with the second slots (42) of the outer sleeve (20; 80; 82; 84; 86) are engaged.

11. The fastening arrangement (10; 12; 14; 16; 18) according to one of the preceding claims, wherein the outer side of the inner sleeve (50; 90) adjacent to the third axial end (52) comprises at least two radially outwardly projecting webs (62) which provide an anti-rotation device for the inner sleeve (50; 90) in the outer sleeve (20; 80; 82; 84; 86).

12. The fastening arrangement (10; 12; 14; 16; 18) according to one of the preceding claims, further comprising a limiting bushing (70) arranged in the inner sleeve (50; 90) which limits compression of the fastening arrangement (10; 12; 14; 16; 18) during use.

13. A first component (A) having a first opening (120) in which a fastening arrangement (10; 12; 14; 16; 18) according to one of the preceding claims is arranged, in particular in a captive manner.

14. A connecting structure (1; 3; 5) comprising a first component (A) according to claim 13 and a second component (B) as well as a fastening screw (130), wherein a thread is provided on or adjacent to a second opening of the second component (B), so that the fastening of the components (A, B) to one another takes place via the fastening screw (130), which extends through the fastening arrangement (10; 12; 14; 16; 18) and engages with the thread.

15. A connecting structure (7; 9) comprising a first component (A) according to claim 13 and a second component (B) and a nut (142), wherein the second component (B) has a threaded shaft (140) which extends through the fastening arrangement (10; 12; 14; 16; 18) and engages with the nut (142).

16. A method of manufacturing a fastening arrangement (10; 12; 14) according to one of claims 1 or 3 to 12 in conjunction with claim 1, comprising the steps of: a) providing the outer sleeve (20; 80; 82; 84; 86), in particular by means of injection molding, b) providing the inner sleeve (50; 90), in particular by means of injection molding, c) inserting the inner sleeve (50; 90) into the outer sleeve (20; 80; 82; 84; 86).

17. A manufacturing method of a fastening arrangement (16; 18) according to one of claims 2 or 3 to 12 in conjunction with claim 2, comprising the steps of: a) providing the outer sleeve (20; 80; 82; 84; 86), in particular by means of injection molding, b) providing the inner sleeve (50; 90), in particular by means of injection molding, c) providing the hollow screw (100; 150; 152; 154; 156; 158), in particular by means of injection molding, d) inserting the inner sleeve (50; 90) into the outer sleeve (20; 80; 82; 84; 86) and e) inserting the outer sleeve (20; 80; 82; 84; 86) with the inner sleeve (50; 90) arranged therein into the hollow screw (100; 150; 152; 154; 156; 158).

18. A method of joining a first component (A) to a second component (B) using a fastening arrangement (10; 12; 14; 16; 18) according to one of claims 1 to 12, comprising the following steps: a1) inserting the fastening arrangement (10; 12; 14) according to claim 1 or according to one of claims 3 to 12 in conjunction with claim 1 into a first opening (120) in the first component (A) or a2) screwing the hollow screw (100; 150; 152; 154; 156; 158) of the fastening arrangement (16; 18) according to claim 2 or according to one of claims 3 to 12 in conjunction with claim 2 into a first opening (120) in the first component (A), then bl) if the second component (B) has a thread at or adjacent to a second opening, aligning the fastening arrangement (10; 12; 14; 16; 18) in the first component (A) with the second opening, inserting a fastening screw (130) into the fastening arrangement and fastening the second component (B) to the first component (A) by means of the fastening screw (130) which is formed by the fastening arrangement (10; 12; 14; 16;18) and engages the thread at or adjacent to the second opening in the second component (B), or b2) if the second component (B) has a threaded shank (140), aligning the fastening arrangement (10; 12; 14; 16; 18) in the first component (A) with the threaded shank (140) of the second component (B), inserting the threaded shank (140) into the fastening arrangement (10; 12; 14; 16; 18) and fastening the second component (B) to the first component (A) by means of a nut (142).;

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