Axial tolerance compensation device, connection and connection method between two components based thereon, and method

Abstract

An axial tolerance compensation device for automatically compensating for tolerances between a first component and a second component, comprising: a nut element having a radially outer fastening structure and an inner nut thread in a first direction, the fastening structure being fastenable in an opening of the first component; the head of the hollow screw is located at the first axial end of the hollow screw, the radial outer side of a hollow cylinder shaft of the hollow screw is provided with an adjusting thread matched with a nut thread, and the radial inner side of the hollow cylinder shaft is provided with a fastening thread in the second direction opposite to the first direction. The fastening thread interacts with the fastening screw such that the first part and the second part can be fastened to each other by means of the tolerance compensation device. The fastening thread comprises a towing structure such that the fastening screw can establish a releasable towing connection with the hollow screw by means of the towing structure, a towing torque < = 0.2 Nm such that when the fastening screw is rotated, the hollow screw can be synchronously rotated and moved into abutment with the second component, and after overcoming the towing torque and releasing the towing connection, the hollow screw can be moved into abutment with the second component. The fastening screw can be further screwed into the hollow screw.

Description

Technical Field

[0001] The present invention relates to an axial tolerance compensation device for automatically compensating for axial tolerance between a first component and a second component, the connection of the two components based on the axial tolerance compensation device, the corresponding connection method, and the manufacturing method of the axial tolerance compensation device. Background Technology

[0002] In the prior art, various tolerance compensation devices are known, by means of which two components can be fastened to each other at a certain distance. These tolerance compensation devices follow different technical principles.

[0003] To achieve automatic axial tolerance compensation when two components are connected, existing technologies have proposed tolerance compensation devices that combine threaded mating with different thread directions with a dragging element. These are described, for example, in EP 2 049 807 B1, DE 102020 216 324A1, and EP 1 780 424A1. In particular, integrating the dragging structure into two interconnecting threaded sleeves with different threaded mating increases the manufacturing difficulty of such axial tolerance compensation devices because the dragging structure is typically made of a different material than the threaded sleeves to be connected. Nevertheless, the advantage of these devices is that they can be integrated into the connection process without any additional installation work. When the spaced-apart components are tightened, the tolerance compensation device compensates for the distance between the two components in a supportive, automatic, and subsequently mechanically load-received manner.

[0004] According to German Patent DE 10 2007 037 242A1, a fastening device for fastening a first component to a second component is disclosed, capable of automatically compensating for tolerances in the distance between the two components. The device includes: a base unit comprising a blind rivet nut, an adjusting threaded nut, and a sleeve-shaped cage that abuts against the first component; the sleeve-shaped cage accommodating the adjusting threaded nut and connecting it to the blind rivet nut; an adjusting unit comprising a threaded sleeve, an abutment plate, and a drag bushing connecting the threaded sleeve and the connecting plate, wherein the threaded sleeve of the adjusting unit is screwed into the adjusting threaded nut of the base unit via a first thread in a first thread direction; and a fastening screw, which is screwed into the blind rivet nut abutting against the component via a second thread in the opposite direction to the second thread direction, forming a detachable drag connection with the drag bushing, thereby causing the adjusting unit to rotate in the same direction when the fastening screw is rotated, and thus moving the abutment plate to compensate for tolerances when abutting against the second component.

[0005] The disadvantage of these devices is that, since the towing structure must be treated as a separate component, the overall structure of the tolerance compensation device becomes complex and the manufacturing difficulty increases.

[0006] Therefore, in practical implementation, DE 10 2020 216 324A1 proposes integrating the drag structure into the internal thread of the compensating element, which is adjacent to the connection point. This integration can be achieved by: applying a coating to the internal thread; using a downward tapering thread, a modified internal thread; and / or setting an interruption / defect point on the internal thread.

[0007] Finally, according to European Patent EP 2 980 421A1, an adjusting element for compensating the gap between a carrier and a component to be fixed is disclosed. This adjusting element includes a hollow body with an external thread in a first pitch direction. The hollow body also includes an internal thread with a second pitch direction opposite to the first pitch direction, and the internal thread contains at least two turns, at least one of which is deformed to provide a higher frictional torque than the other turns. A deformed thread refers to a thread in which at least a portion is deformed to bring it closer to an adjacent thread. That is, the distance between the deformed thread and the adjacent thread is less than the pitch of the internal thread.

[0008] By bringing deformed threads close to adjacent threads, a frictional torque is generated that is greater than the torque provided by other undeformed thread rings in the internal thread.

[0009] The drawback of these integrated towing devices is that the torque required to overcome the integrated towing function is typically greater than that of known devices using independent towing structures. Therefore, after tolerance compensation, tightening the fastening screws becomes exceptionally difficult, at least initially. Furthermore, attaching the tolerance compensation device to the first component is time-consuming and complex for the aforementioned devices.

[0010] Therefore, the object of the present invention is to provide a tolerance compensation device to overcome the above-mentioned disadvantages and to optimize it in this respect. Simultaneously, corresponding connections, connection methods, and manufacturing methods should also be provided. Summary of the Invention

[0011] The above-mentioned objectives can be achieved by: the tolerance compensation device according to the present invention; the connection of a first component and a second component using the tolerance compensation device according to the present invention; the method for connecting two components using the tolerance compensation device according to the present invention; and the method for manufacturing the tolerance compensation device according to the present invention. Advantageous configurations and further improvements of the present invention can be derived from the following description, drawings, and embodiments.

[0012] This invention discloses an axial tolerance compensation device for automatically compensating for the tolerance between a first component and a second component. The device features: a nut element (preferably a ring-shaped nut element) with a radially outward fastening structure, particularly a bayonet structure, which can be fastened into the component opening (particularly a keyhole geometry) of the first component and has an internal thread along a first thread direction; a hollow screw with its head located at the first axial end, its hollow cylindrical shaft having an adjusting thread on the radially outer side that matches the nut thread, and a fastening thread on the radially inner side in a second thread direction opposite to the first thread direction, wherein the fastening thread interacts with the fastening screw along the second thread direction, allowing the first and second components to be fastened to each other by the tolerance compensation device. Preferably, the fastening thread has a drag structure near the second axial end of the hollow screw, allowing the fastening screw to establish a releasable drag connection with the hollow screw through the drag structure. The drag torque is preferably ≤0.2 Nm, and more preferably ≤0.1 Nm, so that when the fastening screw is rotated, the hollow screw can rotate in the same direction as the second component and move to abut against it, and after overcoming the drag torque and releasing the drag connection, the fastening screw can be further screwed into the hollow screw.

[0013] This invention provides an axial tolerance compensation device based on two pairs of threads with different thread directions, which can be installed between two spaced-apart components to achieve automatic tolerance compensation. To simplify and expedite the initial connection of the two components, a nut element for accommodating a tolerance-compensating hollow screw is anchored in the keyhole geometry or keyhole of the first component. In this way, a resilient threaded foundation can be formed in the first component by means of the nut element and a bayonet locking structure or bayonet connection used therewith, enabling the second component to be secured at a specific distance. The tightening process of this nut element with a bayonet structure typically requires only a quarter turn, and its manufacturing and application are simpler than, for example, using blind rivet nuts or weld nuts, thereby enabling the connection between the two components.

[0014] In another preferred configuration, the radially outer fastening structure of the nut element is provided by an external thread. In this case, self-forming or thread-grooving external threads are particularly preferred because they establish a reliable connection, especially with the plastic first component. Compared to the bayonet structure described above for anchoring the nut element in a thin-walled component, a nut element with external threads requires a component with a relatively thicker wall for the radially outer fastening structure, or an overhang around the opening of the component. Both solutions ensure sufficient area for the external thread engagement at the opening of the first component.

[0015] In another alternative configuration, the radially outer fastening structure comprises a latching structure with radially resilient locking lugs. Preferably, in this configuration, the nut element includes at least one axially extending rigid web on its radially outer side to prevent rotation of the nut element within the first component during use. For this purpose, the at least one rigid web engages with a corresponding groove at the opening of the first component. In this case, the alternating arrangement of the locking lugs and the rigid web has significant advantages. For example, two locking lugs and two rigid webs can be arranged opposite each other, with the locking lugs forming a 90° angle with adjacent rigid webs. The nut element thus constructed can be anchored in the keyhole geometry or keyhole of the first component, as in the aforementioned bayonet connection. Therefore, preferably, the first component is a thin-walled component.

[0016] If the opening of the first component is located at its edge, for example, in the form of a U-shaped groove, the radially outer fastening structure of the nut element can be achieved by lateral locking lugs. For this purpose, the nut element has a U-shaped body complementary to the U-shaped groove, wherein locking lugs are provided on the radially outer sides of each arm of the U-shape, which engage with corresponding grooves in the opening of the first component. In this case, the nut element is not inserted axially into the component opening, but rather from the side. Similar to the description of external threads as a fastening structure, a hanger or flange must be provided at the component opening to ensure that the nut element can be reliably fastened.

[0017] Finally, in addition to the radially outer fastening structure in each design, the nut element may also include a flange with a sealing lip that extends axially and circumferentially from the flange. In use, the sealing lip surrounds the component opening on the surface of the first component, preventing the medium from entering through the component opening. To further ensure that the medium cannot enter from one side of the component through the component opening, especially not from the other side through the hollow screw, the nut element is preferably configured as a single-sided closed structure.

[0018] The following sections will describe various design options for the radially outer fastening structure with reference to detailed embodiments. This also applies to structures with flanges and sealing lips.

[0019] To compensate for the existing distance between the two components, a hollow screw is provided in the nut element, preferably pre-installed. The fastening threads of this hollow screw constitute a drag structure. Therefore, the drag structure is integrated into the hollow screw. Thus, the separate or independent drag structures commonly found in the prior art are not present here.

[0020] Advantageously, the drag structure is positioned adjacent to the second axial end of the hollow screw. Since the first axial end of the hollow screw forms the screw head, the drag structure is located away from the screw head. When using a tolerance-compensating device, the fastening screw must be screwed into the fastening thread from the first axial end. This means that the fastening screw only engages with the drag structure at the end of the screwing process.

[0021] As described above, the drag structure is integrated into the fastening thread, i.e., located within this portion of the fastening thread. This is particularly important for embodiments where the inner diameter of the second axial end of the hollow screw is larger than the portion of the fastening thread. In such cases, the description immediately adjacent to the second axial end refers to the portion with the fastening thread. This will be clarified in the subsequent description of preferred embodiments and detailed description.

[0022] This drag structure provides drag torque. Preferably, its set value is greater than the release torque between the adjusting thread and the nut thread. Compared to existing technologies using integrated drag structures, the drag torque provided by this drag structure does not result in an excessive increase in the operating force required to release the drag connection, nor does it affect the further screwing of the fastening screw into the hollow screw. This is particularly evident in the preferred set value of the drag torque, which is ≤0.2 Nm, preferably ≤0.1 Nm.

[0023] Therefore, the tolerance compensation device of the present invention has the advantage that, due to the use of a nut element, it can be easily and quickly fixed to the first component. Furthermore, it eliminates the need for a separate dragging structure, thereby reducing the complexity of the tolerance compensation device. Moreover, the dragging torque is set so that the force required to release the dragging connection is not significantly increased, which further facilitates practicality.

[0024] In a preferred embodiment of the tolerance compensation device, the drag structure is located near the second axial end of the hollow screw, particularly within a ≤360° range of the fastening thread path starting from or immediately adjacent to the second axial end. This can be achieved by reducing the depth of the fastening thread, and / or by at least partially interrupting the fastening thread, and / or by constructing the radially inner side of the hollow screw immediately adjacent to the second axial end as partially or completely flat in both the circumferential and axial directions.

[0025] As described above, the phrase "adjacent to the second axial end" primarily refers to embodiments where the hollow screw comprises at least two portions with different inner diameters. For example, the first portion adjacent to the screw head, and thus adjacent to the first axial end, has a first inner diameter and a fastening thread. The second portion adjacent to the second axial end has a larger second inner diameter. Therefore, this portion cannot define the fastening thread and is not considered when analyzing the dragging function.

[0026] Therefore, the statement in the text that "the dragging structure is located within ≤360° of the fastening thread path starting at or immediately adjacent to the second axial end" refers only to the portion with the fastening thread, i.e., the first portion based on the example above, i.e., the fastening portion. This is intended to emphasize that, in the direction of thread insertion, the dragging structure is located at the end of the fastening thread.

[0027] Furthermore, based on the correspondence between the thread path ≤360° and the pitch of the fastening thread 56, the maximum axial extension of this section (where the drag structure exists) can be determined. For example, if the thread pitch is 1.75 mm, the axial extension of the section with the drag structure is 1.75 mm.

[0028] Various preferred configurations of the towing structure can achieve an effective towing connection between the hollow screw and the fastening screw. However, due to the different configurations, the towing torque can be specifically adjusted according to the materials used.

[0029] Based on the above example, a structure where the radial inner diameter is partially or completely flat in both the circumferential and axial directions refers to the first part, i.e., the part with the fastening thread. This does not involve a second part that may have a larger inner diameter, because this construction requires that the fastening thread does not extend to the end of the fastening portion. Instead, a portion of the fastening thread itself needs to be slotted or cut before the fastening screw leaves the threaded portion away from the front end of the head.

[0030] For example, the axial web extends along the portion with shaped fastening threads. For example, three axial webs are provided, which are evenly spaced from each other in the circumferential direction.

[0031] Between the axial webs, the walls of the fastening portion spring back radially. In other words, the axial webs protrude radially from the walls of the fastening portion. Here, the radial protrusion is sized to allow the fastening screw to engage with the axial web. However, since the axial web is flat, the fastening screw must be threaded onto the axial web. In this configuration, and referring to the above description, the radially inner side is constructed to be partially flat in both the circumferential and axial directions.

[0032] Preferably, the cross-section of the axial web is trapezoidal. The longer base of the trapezoid is arranged radially outward, and the shorter base is arranged radially inward, forming the part that engages with the fastening screw during use.

[0033] Specifically, the axial web of this configuration provides a drag force for the automatic dragging of the hollow screw. Only when the drag torque is overcome can the fastening screw form threads on the axial web. Furthermore, the axial web can also serve as a drive mechanism for manually adjusting the hollow screw. The drag torque can be adjusted by changing the number of webs and / or their circumferential extension length. This will be further explained in the detailed description.

[0034] In an advantageous embodiment of the tolerance compensation device, the device further includes a transport safety structure to prevent the hollow screw from accidentally unscrewing from the nut element during transport. Preferably, the transport safety structure also provides a first anti-reverse safety structure between the hollow screw and the nut element. Particularly advantageously, for this purpose, the nut element has an axially projecting lug that combines with a transport safety profile radially outward of the abutment surface of the hollow screw head facing the axis, forming the transport safety structure. In this regard, preferably, the transport safety profile does not radially extend beyond the screw head in a first circumferential portion, does not radially extend beyond the encompassing circle of the screw head shape in a second circumferential portion, and radially extends beyond the encompassing circle in a third circumferential portion.

[0035] In particular, the combination of the axially projecting lug and the transport safety structure on the hollow screw not only provides a transport safety function (i.e., preventing the hollow screw from accidentally unscrewing from the nut), but also prevents counter-rotation between the hollow screw and the nut element. This is due to the width of the lug (i.e., its circumferential extension) and the resulting contact surface at the transport safety profile. When the hollow screw is screwed into the nut element, the lug preferably contacts the transport safety profile, but radial offset is preferably avoided.

[0036] Here, radial offset refers to the state in which the lug is further pushed radially outward relative to its initial state due to the action of the transport safety contour. This is predicated on the first, second, and third circumferential portions being arranged sequentially circumferentially. For example, when the hollow screw is in the screw-in position, the lug is radially adjacent to or abuts against the transport safety contour. This may occur, for example, in the second circumferential portion of the transport safety contour or the transition between the second and third circumferential portions, depending on the radial position of the lug. Preferably, in this state, the lug does not undergo radial offset, i.e., the transport safety contour does not push the lug radially outward.

[0037] If the hollow screw is then unscrewed from the nut element, the lug will engage with the third circumferential portion. This causes the lug to shift radially or push outward, making the unscrewing process more difficult. During subsequent unscrewing, the lug will reach the area of ​​the first circumferential portion. However, this area is sized to prevent it from pushing the lug radially outward. Therefore, the lug can return to its initial state. Due to the matching dimensions of the pitch and the lug in the axial direction, continuing to unscrew the hollow screw will not cause the screw head to engage with the transport safety profile in the axial direction. Therefore, the axial extension length of the lug is preferably such that the transport safety profile no longer engages with the lug at least after the hollow screw has been fully rotated or completed one full rotation.

[0038] In another preferred embodiment of the tolerance compensation device with a transport safety profile, a second anti-reverse safety structure is provided between the hollow screw and the nut element. Preferably, this second anti-reverse safety structure is formed in such a way that the adjusting thread terminates discontinuously near the first axial end of the hollow screw; and / or the thread of the nut element terminates discontinuously near the first axial end of the nut element. Preferably, this second anti-reverse safety structure provides a resistance torque greater than the drag torque. Thus, this second anti-reverse safety structure provides additional anti-reverse safety assurance.

[0039] According to another preferred embodiment of the tolerance compensation device, the annular nut element and the hollow screw are made of plastic material, preferably containing a glass fiber content in the range of 25% to 65%, more preferably 45% to 55%, and even more preferably 50%.

[0040] To achieve a low-cost design for the axial tolerance compensation device, it is preferably manufactured using injection molding with plastic materials. Known plastic materials, such as thermoplastics, possess sufficient mechanical elasticity to be used as tolerance compensation devices. By adding a certain proportion of glass fiber to the thermoplastic, its mechanical load-bearing capacity can be further improved. Thus, since the production cost of plastic tolerance compensation devices is lower than that of tolerance compensation devices made of metal or a combination of plastic and metal, production and transportation costs can be reduced. Furthermore, the weight of plastic tolerance compensation devices is also lower than that of metal tolerance compensation devices of the same structure. This not only affects subsequent transportation and delivery costs but also the final weight after connecting two components using the axial tolerance compensation device.

[0041] Regarding the tolerance compensation device, it has further advantages when it includes a disassembly protection structure, as described in German patent application DE 10 2024 132 374.4, filed on the same day as this application.

[0042] Furthermore, the present invention also discloses a connection between a first component and a spaced-apart second component, which is achieved by means of a tolerance compensation device and a fastening screw configured according to at least one of the above.

[0043] According to another preferred configuration of the connection, the first component has a keyhole geometry in which a nut element is arranged.

[0044] Furthermore, the present invention discloses a connection method for connecting a first component having a keyhole geometry to a spaced second component, the second component having a component opening, using any of the above configurations or combinations of tolerance compensation devices. The method includes the following steps: fixing an annular nut element pre-loaded with a hollow screw in the keyhole geometry of the first component; aligning the component opening of the second component with the fastening thread of the hollow screw; screwing the fastening screw through the component opening into the fastening thread; rotating the fastening screw and thereby causing the hollow screw to rotate until the hollow screw abuts against the second component; and tightening the fastening screw in the fastening thread when the head of the hollow screw abuts against the second component.

[0045] Furthermore, the present invention includes a method for manufacturing a tolerance compensation device according to one of the above configurations, the method comprising the steps of: providing an injection mold for a nut element and a hollow screw, injection molding the nut element and the hollow screw, demolding the nut element and the hollow screw, and pre-installing the hollow screw in the nut element. Attached Figure Description

[0046] The invention will now be described in detail with reference to the accompanying drawings. In the drawings, the same reference numerals denote the same parts and / or elements. They are shown as follows: Figure 1 This is an exploded perspective view of a preferred configuration of the tolerance compensation device of the present invention. Figure 2 According to Figure 1 The diagram shows a three-dimensional view of a hollow screw. Figure 3 According to Figure 1 The cross-sectional view of the hollow screw shown is shown. Figure 4 According to Figure 1 The top view of the hollow screw shown. Figure 5 According to Figure 1 The 3D view of the nut component shown. Figure 6 for Figure 1 The diagram shown is a perspective view of the tolerance compensation device in its pre-installation state. Figure 7 According to Figure 6 The sectional view of the tolerance compensation device shown is shown. Figure 8 A perspective view of the first component with a keyhole geometry, used to receive and fasten a nut element. Figure 9 According to Figure 8 The perspective view of the first component shown, wherein the tightness is based on Figure 1 The tolerance compensation device shown Figure 10 According to Figure 9 The diagram shows the first component and tolerance compensation device connected to the fastening screw and the second component. Figure 11 This is a side view showing the two components connected by a tolerance compensation device and fastening screws. Figure 12 for Figure 11 sectional view, Figure 13a According to Figure 1 The diagram shows a top view of the tolerance compensation device, with the hollow screw fully screwed in. Figure 13b for Figure 13a A 3D diagram showing the state. Figure 14a According to Figure 1 The diagram shows a top view of the tolerance compensation device, with the hollow screw in its initial, untightened state. Figure 14b According to Figure 14a A 3D diagram showing the state. Figure 15a According to Figure 1 The top view of the tolerance compensation device shown indicates that the hollow screw is in a further loosened state. Figure 15b According to Figure 15a A 3D diagram showing the state. Figure 16a According to Figure 1 The top view of the tolerance compensation device shown indicates that the hollow screw is further loosened. Figure 16b for Figure 16a The diagram shows a 3D representation of this state. Figure 17 This is a perspective view of a tolerance compensation device with a disassembly protection structure. Figure 18 for Figure 17 The enlarged view of the second axial end of the hollow screw shown. Figure 19 A flowchart illustrating a preferred embodiment of the connection method using an axial tolerance compensation device. Figure 20 This is a flowchart of a preferred embodiment of the manufacturing method of the axial tolerance compensation device of the present invention. Figure 21 A perspective view of optional configurations for hollow screws. Figure 22 For the belt Figure 21 The diagram shows a cross-sectional view of an embodiment of the tolerance compensation device of the present invention for hollow screws. Figure 23 This is an exploded perspective view of another preferred configuration of the tolerance compensation device and the first component of the present invention. Figure 24 According to Figure 23 The cross-sectional view of an embodiment of the tolerance compensation device of the present invention shown is shown below. Figure 25 This is an exploded perspective view of another preferred configuration of the tolerance compensation device and the first component of the present invention. Figure 26 According to Figure 25 The figure shown is a cross-sectional view of an embodiment of the tolerance compensation device of the present invention. Figure 27 This is an exploded perspective view of another preferred configuration of the tolerance compensation device and the first component of the present invention. Figure 28 According to Figure 27 The figure shown is a cross-sectional view of an embodiment of the tolerance compensation device of the present invention. Figure 29 This is an exploded perspective view of another preferred configuration of the tolerance compensation device and the first component of the present invention. Figure 30 for Figure 29 The perspective view of the tolerance compensation device embodiment of the present invention used in the first component, and... Figure 31 According to Figure 30 The figure shown is a cross-sectional view of an embodiment of the tolerance compensation device of the present invention. Detailed Implementation

[0047] First, refer to Figures 1 to 7 The structure of an embodiment of the tolerance compensation device 1 of the present invention will be described below. Figure 1 This is an exploded view of the axial tolerance compensation device 1, which consists of a nut element 10 and a hollow screw 40. To fasten the first component A and the second component B together using the tolerance compensation device 1, a fastening screw 80 with a washer 86 is used, the washer 86 being positioned below the head of the fastening screw 80.

[0048] The nut element 10 and the hollow screw 40 are preferably manufactured from plastic material using an injection molding process. The fastening screw 80 and the washer 86 are preferably manufactured from metal material. To improve the mechanical strength of the plastic parts in the axial tolerance compensation device 1, 25% to 65% glass fiber, preferably 45% to 55%, and more preferably 50%, is added to the plastic material used during the injection molding process.

[0049] Preferably, the nut element 10 has a ring-shaped structure so as to secure it into the fitting opening O1 of the first component A. Figure 1In the preferred configuration shown, the nut element 10 has a bayonet structure as described in the following detailed description, which allows it to be secured in the keyhole geometry 90 of the first component A. For this purpose, the keyhole geometry 90 is provided with at least two circumferentially evenly distributed slits 92 in a known manner. The slits 92 are adapted to the nut element 10 such that two bayonet webs 12 extending radially outward from the nut element 10 can pass through the slits 92, thereby enabling the nut element 10 to be locked onto the first component A by rotation. In the secured state, the first component A is fixed by friction between the bayonet webs 12 of the nut element 10 and the bottom surface of the retaining flange 14, wherein the retaining flange 14 is axially spaced from the bayonet webs 12. Figure 8 A first component A is shown with a component opening O1 having a cutout 92 of a keyhole geometry 90. Figure 9 The first component A is shown, with the axial tolerance compensation device 1 fastened inside it.

[0050] At least one locking web 16 is preferably offset by 90° relative to the two snap-fit ​​webs 12. When there are two snap-fit ​​webs 12, it is preferable to provide two locking webs 16. The locking web 16 is preferably positioned in the insertion direction R of the nut element 10. E The arrangement is inclined. When the nut element 10 is inserted into the keyhole geometry 90, the bayonet web 12 passes through the cut 92. At the same time, the locking web 16 abuts against the surface of the first component A between the cuts 92, and in the insertion direction R E The reverse force generates a preferred elastic preload on the nut element 10.

[0051] Once the nut element 10 rotates about its longitudinal axis, the bayonet web 12 locks onto the side of the first component A away from the retaining flange 14. When the bayonet web 12 is rotated out of the notch 92 (the notch for securing the nut element 10 to the keyhole 90), the locking web 16 is preferably screwed into the notch 92. Because the locking web 16 is preferably of an inclined construction, its engagement with the notch 92 prevents the nut element 10 from rotating again along its longitudinal axis.

[0052] For rotating the nut element 10, the flange 14 is preferably broken at least in two places to provide engagement points 15 for rotating tools.

[0053] Preferably, the nut element 10, together with the bayonet web 12 and the locking web 16, forms a ring structure.

[0054] According to another preferred embodiment (not shown) of the nut element 10, it includes radially outward external threads instead of the bayonet web 12 and locking web 16, so as to be secured in the threaded opening of the first component A.

[0055] Therefore, the annular nut element 10 is screwed into the threaded hole of the first component A until the retaining flange 14 abuts against the surface of the first component A. Thus, the external thread and the retaining flange 14 together form a friction-based anti-rotation safety structure. Figure 1 In one embodiment, the anti-rotation safety structure is achieved by combining the bayonet web 12 and the locking web 16 to form a mating anti-rotation safety structure.

[0056] According to another preferred embodiment (not shown), the nut element 10 is triangular or polygonal in the circumferential direction so as to be inserted into the component opening of the complementary first component A. This angular structure of the nut element 10 ensures its anti-rotation safety relative to the first component A within the component opening O1.

[0057] To secure the angle nut element 10 in the component opening O1, it is inserted axially in the direction R below the retaining flange 14. E A snap-fit ​​structure (not shown) is provided. The preferred snap-fit ​​structure preferably engages the nut element 10 in the component opening O1 by means of friction fit and form fit.

[0058] The nut element 10 includes a passage 18, the radially inner side 20 of which is provided with an internal thread or internal nut thread 22 in a first thread direction.

[0059] In the illustrated embodiment, the nut element 10 further includes a lug 24 projecting axially. In the illustrated embodiment, the lug 24 is disposed on one of the two locking webs 16. Alternatively, the lug 24 may also be disposed on the retaining flange 14.

[0060] In conjunction with the hollow screw 40, the lug 24 provides transport safety, preventing the hollow screw 40 from being accidentally unscrewed or detached from the nut element 10 during transport, as will be described later.

[0061] In addition to providing transport safety, lug 24 has an additional function: when used in conjunction with hollow screw 40, it prevents the hollow screw 40 from reversing with the nut element 10. This is due to the circumferential extension of lug 24, which will be explained later when discussing hollow screw 40.

[0062] In addition to the first anti-reverse safety structure formed by the lug 24, the nut element 10 also includes a second anti-reverse safety structure formed by the abrupt end 26 of the nut thread 22. The abrupt end 26 is located near the axial end of the nut element 10 having the retaining flange 14. Therefore, the nut thread 22 of the nut element 10 does not extend continuously near the first axial end of the nut element 10.

[0063] The hollow screw 40 includes a hollow cylindrical shaft 42 having a first axial end 62 and a second axial end 64. A head 44 is provided at the first axial end 62 of the shaft 42, the head 44 having a drive feature 46 (particularly hexagonal) and an abutment surface 48 facing the shaft.

[0064] The hollow cylindrical shaft 42 includes a radial outer edge 50 with an adjusting thread 52. The adjusting thread 52 mates with the nut thread 22 of the nut element 10, and is therefore an adjusting thread 52 in the first thread direction. It is particularly advantageous when the adjusting thread 52 also includes a stop end 78, which mates with the stop end 26 of the nut thread 22, forming an effective second anti-reverse safety structure between the hollow screw 40 and the nut element 10. Therefore, the stop end 78 of the adjusting thread 52 is positioned immediately adjacent to the first axial end 62.

[0065] The hollow cylindrical shaft 42 includes an inner channel 54 with openings on both sides, such as... Figure 3 The axial sectional view is shown. A second threaded fastening thread 56 is provided on the radially inner side of the channel 54, with its thread direction opposite to the first thread direction. The portion with the fastening thread 56 is also referred to as the first portion or fastening portion 58. It has a first inner diameter that matches the corresponding fastening screw 80.

[0066] like Figure 3 As shown, the fastening portion 58 extends axially to a second portion 60 with a larger inner diameter. The second portion 60 is located at the second axial end 64 and is unthreaded.

[0067] like Figure 17 and Figure 18 As shown, in a particularly preferred configuration, a disassembly protection structure 79 for the hollow screw 40 is provided on the second axial end 64 opposite to the head 44. For clarity, the lug 24 is not shown in the figure.

[0068] For example, the disassembly protection structure 79 consists of two axial webs, and is achieved by the thermal expansion of the second axial end 64 of the hollow screw 40, such that the radial expansion of the second axial end 64 exceeds the inner diameter D of the nut element 10. i In addition to the axial web, an annular wall is also a preferred option. Thermal expansion is preferably achieved by applying heat or ultrasound using a tool W. After expansion, the hollow screw 40 will be unable to be removed from the nut element 10 without damage. For information on this disassembly protection structure and other structures, please refer to German patent application DE 10 2024 132 374.4, filed on the same day.

[0069] Returning to the fastening portion 58, which includes the fastening thread 56, this fastening portion also includes a drag section 66 with a drag structure. Therefore, this drag structure is integrated into the hollow screw 40. Thus, there is no separate or independent drag structure as known in the prior art here.

[0070] The drag section 66 and the drag structure are adjacent to the second axial end 64 of the hollow screw 40. Since the first axial end 62 of the hollow screw 40 has a screw head 44, the drag section 66 and the drag structure are located away from the screw head. When using the tolerance compensation device 1 (see below), the fastening screw 80 is screwed into the fastening thread 56 starting from the first axial end 62. Therefore, the fastening screw 80 only engages with the fastening thread 56 of the hollow screw 40 with the drag section 66 and the drag structure at the end of the screwing process.

[0071] This towing structure provides a towing torque. Preferably, this torque is set to a value greater than the release torque between the adjusting thread 52 and the nut thread 22 of the nut element 10. Compared to prior art using integrated towing structures, the towing torque provided by this towing structure does not result in an excessive increase in the operating force required to release the towing connection, nor does it affect the further rotation of the fastening screw 80 into the hollow screw 40. This is particularly evident in the preferred value of the towing torque, which is ≤0.2 Nm, preferably ≤0.1 Nm.

[0072] In the illustrated embodiment, the drag structure is positioned adjacent to the second axial end 64 of the hollow screw 40, within a range of ≤360° of the fastening thread 56 path starting from or near the second axial end 64. This constitutes the drag section 66. Figure 3 As shown, the phrase "at or near the second axial end 64" refers to the fastening portion 58 with the fastening thread 56. Therefore, the second portion 60 with a larger inner diameter is not considered here. This emphasizes that the drag structure is located in the tightening direction of the fastening screw 80 and is located at the end of the fastening thread 56.

[0073] Furthermore, based on the correspondence between the thread path ≤360° and the pitch of the fastening thread 56, the maximum axial extension length of the drag section 66 (in which the drag structure exists) can be determined. For example, if the pitch is 1.75 mm, the maximum axial extension length of the drag section 66 is 1.75 mm.

[0074] The dragging structure in the dragging section 66 can be achieved by reducing the depth of the fastening thread 56; and / or by making the fastening thread 56 at least partially interrupted; and / or by making the radial inner surface of the hollow screw 40 adjacent to the second axial end 64 partially or completely flat in both the circumferential and axial directions. As mentioned above, since the second portion 60 with a larger inner diameter is not considered, the flat structure of the radial inner surface refers to the fastening portion 58. Figure 17 and Figure 18 A partially flat circumferential structure is shown. Here, the flat structure is particularly evident at the end of the fastening portion 58 toward the second axial end 64, which extends in the axial direction no more than one turn of the fastening thread 56.

[0075] Therefore, the fastening thread 56 is not fully formed. Instead, a portion of the fastening thread 56 itself must be slotted or cut before the tip of the fastening screw 80 leaves the fastening portion 58. Here, all different configurations of component dragging can achieve an effective dragging connection between the hollow screw 40 and the fastening screw 80. Due to the different configurations, the dragging torque can be specifically adjusted according to the material used.

[0076] Having discussed the internal structure of the hollow screw 40, we will now explore its external structure.

[0077] The axial abutment surface 48 has a transport safety profile 68 on its radially outer side. This transport safety profile 68 is constructed such that: in the first circumferential portion 70, its radial extension does not exceed the head 44; within the second circumferential portion 72, its radial extension does not exceed the envelope circle of the head shape; and within the third circumferential portion 74, its radial extension exceeds the envelope circle. The first circumferential portion 70, the second circumferential portion 72, and the third circumferential portion 74 are arranged sequentially circumferentially. A transition portion 76 exists between the second circumferential portion 72 and the third circumferential portion 74. In the circumferential radial direction, the shape of the transition portion 76 remains unchanged and transitions to the second circumferential portion 72 and the third circumferential portion 74 respectively via inclined surfaces. In the illustrated embodiment, when the hollow screw is fully screwed into the nut element 10, the lug 24 abuts against the transition portion 76. This state is as follows... Figure 6 , Figure 13a and Figure 13b As shown.

[0078] By engaging with the lug 24 of the nut element 10, the transport safety profile 68 provides transport safety assurance, thereby preventing the hollow screw 40 from accidentally unscrewing from the nut element 10 during transport of the tolerance compensation device 1. As described above regarding the lug 24, this structure also provides a first anti-reverse safety structure between the hollow screw 40 and the nut element 10. This is due to the width of the lug 24, i.e., its circumferential extension length, and the abutment surface thus formed at the transport safety profile 68.

[0079] In this context, the aforementioned term "radial offset" refers to the state in which the lug 24 is further radially pushed outward relative to its initial state due to the action of the transport safety contour 68. For example, if... Figure 6 , Figure 13a and Figure 13bBased on the initial state shown, when the hollow screw 40 is unscrewed from the nut element 10, the lug 24 contacts the third circumferential portion 74 through the inclined surface. This causes the lug 24 to shift radially or be pushed outward, thus increasing the difficulty of unscrewing the hollow screw 40. Figure 14a and 14b As shown.

[0080] During further loosening, lug 24 reaches position 70 of the first circumferential portion, such as... Figure 15a and 15b As shown. However, the dimensions of this part are designed so that the lug 24 is no longer pushed outward radially. Therefore, the lug 24 can return to its initial state.

[0081] Due to the matching design of the thread pitch and the axial dimensions of the lug 24, further loosening of the hollow screw 40 will not cause the lug 24 to engage with the transport safety profile 68, which is evident from... Figure 16a and 16b As is clearly shown in the illustration. Therefore, the extension length of the lug 24 in the axial direction is preferably such that the transport safety profile no longer engages with the lug after the hollow screw has been fully rotated or rotated one full turn at the latest.

[0082] Furthermore, the adjusting thread 52 of the hollow screw 40 has a stop end 78 near its first axial end 62. Therefore, the adjusting thread 52 does not terminate continuously near its first axial end 62. In particular, this, combined with the stop end 26 of the nut thread 22 of the nut element 10, forms a second anti-reverse safety structure. The resisting torque provided by this second anti-reverse safety structure is preferably greater than the drag torque. Therefore, additional anti-reverse safety is provided by this second anti-reverse safety structure. Moreover, it is this second anti-reverse safety structure that ensures a certain distance is maintained between the abutting surface 48 of the hollow screw 40 and the upper side of the retaining flange 14 of the nut element 10 when the hollow screw 40 is fully screwed into the nut element 10. For this, see [reference needed]. Figure 7 An exemplary description.

[0083] The tolerance compensation device 1 has the advantage that, due to the use of the nut element 10, it can be quickly and easily fixed to the first component A. It also eliminates the need for a separate towing structure, thus reducing the structural complexity of the tolerance compensation device 1. Furthermore, the towing torque is set to ensure that no significant increase in force is required when releasing the towing connection, further enhancing ease of use.

[0084] Figures 10 to 12The connection process of the first component A and the second component B is illustrated, while the axial tolerance between components A and B is compensated using the tolerance compensation device 1. In the first preferred step A, the nut element 10, pre-installed with a hollow screw 40, is fixed into the keyhole geometry 90 of the first component A. For details, please refer to the above description and... Figure 9 .

[0085] Subsequently, the second component B with the opening O2 is positioned such that the opening O2 is aligned with the channel 54 of the hollow screw 40 in the nut element 10. Here, "alignment" preferably means that the center point of the opening O2 is located on or near the central longitudinal axis of the channel 54. Figure 10 As shown.

[0086] Then, the fastening screw 80 is inserted through the component opening O2 of the second component B into the channel 54 of the hollow screw 40 and rotated in the second thread direction, because the thread 82 of the fastening screw 80 has the same thread direction as the fastening thread 56 of the hollow screw 40.

[0087] Since the fastening threads 56 and 82 are geometrically matched, the fastening screw 80 can be screwed into the fastening thread 56 until the end of the screw 84 facing away from the screw head reaches the drag section 66. This section increases the frictional resistance between the rotating fastening screw 80 and the hollow screw 40 compared to the thread engagement between the thread 82 and the fastening thread 56 (step B).

[0088] Due to the increased friction between the fastening screw 80 and the hollow screw 40, the hollow screw 40 rotates together with the fastening screw 80. When the fastening screw 80 drives the hollow screw 40 to rotate along the second thread direction, the hollow screw 40 is guided by the nut thread 22 in the first thread direction through the adjusting thread 52. The rotation of the fastening screw 80 causes the hollow screw 40 to unscrew from the nut element 10 in the direction of the second component B (step C).

[0089] When the head 44 of the hollow screw 40 abuts against the second component B, the rotation of the fastening screw 80 overcomes the force of the drag section 66 and tightly engages with the hollow screw 40. This state is as follows: Figure 11 and Figure 12 As shown.

[0090] Furthermore, the present invention also includes the connection between components A and B established by means of axial tolerance compensation device 1. Figure 11 and Figure 12 This type of connection is illustrated in a specific embodiment of the axial tolerance compensation device 1.

[0091] like Figure 19 As shown, the connection method of connecting two components A and B by means of axial tolerance compensation device 1 is summarized.

[0092] First, (step a) the nut element 10 pre-loaded with a hollow screw is fastened into the opening O1 of the first component, preferably the keyhole geometry opening of the first component A. Then, (step b) the component opening O2 of the second component B is aligned with the fastening thread 56 of the hollow screw 40, and (step c) the fastening screw 80, passing through the component opening O2, is screwed into the fastening thread 56. Next, (step d) the tolerance compensation device 1 is extended axially by rotating the fastening screw 80, causing the hollow screw 40 to rotate accordingly, until the tolerance compensation device 1 abuts against the second component B through the head 44 of the hollow screw 40. Finally, in step e, when the head 44 of the hollow screw 40 abuts against the second component B, the fastening screw 80 is screwed into the fastening thread of the hollow screw 40.

[0093] As previously mentioned, the components of the axial tolerance compensation device 1 are preferably made of plastic material, particularly the nut element 10 and the hollow screw 40. Furthermore, it is preferable to add a certain proportion of glass fiber (see above) to the plastic material used to manufacture the nut element 10 and the hollow screw 40 to improve their mechanical elasticity and stability.

[0094] According to a preferred embodiment of the present invention, the nut element 10 and the hollow screw 40 are manufactured by injection molding. Therefore, the manufacturing method can be summarized as follows: Figure 20 As shown: (Step S1) Provide an injection mold for the nut element 10 and the hollow screw 40; (Step S2) Inject the nut element 10 and the hollow screw 40 into shape; (Step S3) Demold the nut element 10 and the hollow screw 40; and (Step S4) Pre-assemble the hollow screw 40 into the nut element 10.

[0095] The pre-installation step (step S4) is not a mandatory step in the manufacturing process and can be postponed according to the installation process of the axial tolerance compensation device 1.

[0096] Figure 21 and Figure 22 An alternative structure for the hollow screw 140 is shown. The basic structure of the hollow screw 140 is the same as that of the hollow screw 40, and therefore the hollow screw 140 also includes a first axial end 62 and a second axial end 64. The second portion 60 is located at or adjacent to the second axial end 64.

[0097] Unlike the previous hollow screw 40, the hollow screw 140 has axial webs 167 in the drag section 66. These axial webs 167 extend along the portion having shaped fastening threads 56.

[0098] In the illustrated embodiment, three axial webs 167 are provided, evenly spaced from each other in the circumferential direction. Between the axial webs 167, the walls of the fastening portion 58 spring back radially. In other words, the axial webs 167 protrude radially from the walls of the fastening portion 58. The radial protrusion dimension allows the fastening screw 80 to engage with the axial webs 167. However, since the axial webs 167 have a flat construction, the fastening screw 80 must be threaded onto the axial webs 167. Therefore, in this configuration, the radially inner side is partially flat in both the circumferential and axial directions. The number of axial webs 167 and / or their circumferential extension length can be adjusted to suit the desired application.

[0099] In the structure shown, the cross-section of the axial web 167 is trapezoidal. The longer base of the trapezoid is arranged radially outward, and the shorter base is arranged radially inward, forming the portion that engages with the fastening screw 80 during use. Therefore, the circumferential extension length or width of the axial web 167 adjacent to the wall is greater than its radial extension length away from the wall.

[0100] The axial web 167 constitutes the dragging structure for automatically dragging the hollow screw 140, because the fastening screw 80 can only form threads on the axial web 167 after the dragging torque is overcome. Furthermore, the trapezoidal axial web 167, in particular, can also serve as an additional drive structure for manually moving the hollow screw 140. Therefore, for example, rotation can be achieved by engaging the hollow screw 140 from the second axial end 64 with a special tool.

[0101] like Figure 23 and Figure 24 As shown, this paper discusses another preferred configuration of the radially outer fastening structure of nut element 110. The difference between nut element 110 and nut element 10 lies only in the change of its radially outer fastening structure.

[0102] For nut element 110, the radially outer fastening structure is formed by external thread 128. In this case, self-tapping or self-slotted external thread 128 is particularly preferred because it establishes a reliable connection, especially with the first plastic component A.

[0103] like Figure 11 and Figure 12 As shown, when the nut element 110 with this design is fastened to the first component A, a flange or wall portion 494 needs to be provided near the opening. This is especially important for the thin-walled first component A, because only in this way can a sufficiently large meshing surface be formed between the external thread 128 and the first component A.

[0104] Figure 25 and Figure 26A nut element 210 with an alternative radially outward fastening structure is shown. This nut element 210 differs from the embodiment of nut element 10 only in the radially outward fastening structure.

[0105] In this embodiment, the radially outward fastening structure is formed by a snap-fit ​​structure with radially resilient locking lugs 230. Two opposing locking lugs 230 are provided here. Figure 25 As shown, the nut element 210 designed in this way can also be inserted into the keyhole geometry 90 in the first component A.

[0106] In the illustrated embodiment, the nut element 210 is further provided with two axially extending rigid webs 232 on its radially outer side to prevent the nut element 210 from rotating within the first component A during use. For this purpose, the two rigid webs 232 engage with corresponding grooves 294 in the keyhole geometry 90.

[0107] The locking lugs 230 and the rigid webs 232 are arranged alternately in the circumferential direction. Therefore, the two locking lugs 230 and the two rigid webs 232 are arranged opposite to each other, and the locking lugs 230 form a 90° angle with the adjacent rigid webs 232.

[0108] Figure 27 and Figure 28 A nut element 310 with a flange 334 and a sealing lip 336 is shown. The basic structure of the nut element 310, especially in terms of the radially outer fastening structure, corresponds to the structure of the nut element 10.

[0109] Flange 334 is located axially above the radially outer fastening structure. Sealing lip 336 extends continuously axially from the outer end of flange 334 to the bottom, i.e., along the direction of the radially outer fastening structure. Therefore, in use, sealing lip 336 surrounds the component opening O1 on the surface of the first component A, preventing the medium from entering through the component opening O1. To further ensure that the medium cannot enter from one side of the component through the component opening O1, particularly through the hollow screw 140, the nut element 310 is preferably configured to be closed on one side. This can be illustrated by the closed end 338.

[0110] The sealing function associated with nut element 310 can be applied by analogy to other nut elements 10, 110, 210, and nut element 410, which will be discussed below.

[0111] Finally combined Figures 29-31 We will now discuss another construction of the nut element 410. This construction is particularly suitable for cases where the component opening O1 of the first component A is located at the edge of the first component A.

[0112] The component opening O1 shown in the example is in the form of a U-shaped groove. Therefore, the radially outer fastening structure of the nut element 410 is achieved by lateral locking lugs 413. For this purpose, the nut element 410 includes a U-shaped nut body 411 formed complementary to the U-shaped groove, wherein the locking lugs 413 are provided radially outer on each arm of the U-shape. Each locking lug 413 engages with a corresponding groove 496 on the wall 494 of the component opening O1 in the first component A. Here, as with the case where the external thread 128 is used as the radially outer fastening structure, for the thin-walled first component A, an enlarged abutment surface is also required to securely fasten the nut element 410.

[0113] The nut element 410 is inserted into the opening O1 of the component not axially, but laterally. To prevent axial displacement of the nut body 411 during and after insertion, the U-shaped nut element 411 is provided with guide protrusions 415. These guide protrusions are located at the two axial ends of the U-shaped nut element body, namely the top and bottom, and preferably mate with corresponding grooves in the wall portion 494, such as... Figure 29 and Figure 31 As shown.

[0114] List of reference numerals 1. Axial tolerance compensation device 10 Nut Components 12-gauge web 14. Maintain the flange 15. Tool engagement 16 locking webs Pathway in 18-nut component 20 channels 18 radial inner side 22 Nut thread in the first thread direction 24 protruding ears 26. The protruding stop end of the nut thread 22. 40 Hollow Screws 42 Hollow cylindrical shaft 44 Head 46 driving features 48 contact surfaces Radial outer side of shaft 42 (50) 52 Adjusting thread in the first thread direction 54 channels 56 Fastening threads in the second thread direction 58 Fastening parts 60 Part Two 62 First Axial End 64 Second Axial End 66 Towing Section 68. Transportation Safety Profile 70 First Weekly Section 72 Second week to part 74 Third week to part 76 Transition Section 78. Adjusting thread 52's protruding stop end 79. Disassembly of protective structure 80 Fastening screws 82 thread 84 Screw Shaft 86 Washer 90 keyhole geometry 92 incisions 110 Nut Component (Second Embodiment) 128 external thread 140 Hollow Screw (Second Embodiment) 167 Axial Web 210 Nut Component (Third Embodiment) 230 locking lug 232 Rigid Web 294 grooves 310 Nut Component (Fourth Embodiment) 334 flange 336 Sealing Lip 338 Closed End 410 Nut Component (5th Embodiment) 411 U-shaped nut body 413 Locking Lug 415 guide protrusion 494 wall section 496 groove in wall 494 A First Component B Second Component D i Inner diameter of nut element 10 O1 First component opening O2 Second Component Opening R E Insertion direction W Tools

Claims

1. An axial tolerance compensation device (1) for automatically compensating the tolerance between a first component (A) and a second component (B), having the following features: a. A nut element (10) having a radially outer fastening structure (12) and an internal nut thread (22) in a first thread direction, the radially outer fastening structure (12) being fastened into the component opening (O1) of the first component (A). b. A hollow screw (40) having a head (44) and a hollow cylindrical shaft (42), the head (44) being located at its first axial end (62), the hollow cylindrical shaft having an adjusting thread (52) on its radially outer side that mates with a nut thread (22), and a fastening thread (56) in a second thread direction on its radially inner side, the second thread direction being opposite to the first thread direction, wherein... c. The fastening thread (56) interacts with the fastening screw (80) in the second thread direction, such that the first component (A) and the second component (B) can be fastened to each other by the tolerance compensation device, wherein d. The fastening thread (56) includes a drag structure, such that the fastening screw (80) can establish a releasable drag connection with the hollow screw (40) through the drag structure, wherein the drag torque is ≤0.2 Nm, so that when the fastening screw (80) is rotated, the hollow screw (40) can rotate synchronously and move to abut against the second component (B), and after overcoming the drag torque and releasing the drag connection, the fastening screw (80) can be further screwed into the hollow screw (40).

2. The tolerance compensation device (1) according to claim 1, wherein, The drag structure is positioned near the second axial end (64) of the hollow screw (40) in the following manner: a) Reduce the depth of the fastening thread (56), and / or b) Configure the fastening thread (56) to be at least partially interrupted, and / or c) The hollow screw (40) is constructed to be partially or completely flat in the circumferential and axial directions on the radially inner side adjacent to the second axial end (64).

3. The tolerance compensation device (1) according to claim 1 further includes a transport safety structure to prevent the hollow screw (40) from accidentally unscrewing from the nut element (10) during transport of the tolerance compensation device (1).

4. The tolerance compensation device (1) according to claim 3, wherein the transport safety structure further provides a first anti-reverse safety structure between the hollow screw (40) and the nut element (10).

5. The tolerance compensation device (1) according to claim 3 or 4, wherein the nut element (10) includes an axially projecting lug (24) which, together with a transport safety profile (68) radially outward of the abutment surface (48) of the head (44) of the hollow screw (40) facing the shaft, constitutes the transport safety structure.

6. The tolerance compensation device (1) according to claim 3 or 4, wherein the nut element (10) includes an axially projecting lug (24) that combines with a transport safety profile (68) radially outward of the abutment surface (48) of the head (44) of the hollow screw (40) facing the shaft, forming the transport safety structure, wherein, The transport safety profile (68) does not extend radially beyond the head (44) in the first circumferential portion (70); does not extend radially beyond the envelope circle of the head shape in the second circumferential portion (72); and extends radially beyond the envelope circle in the third circumferential portion (74).

7. The tolerance compensation device (1) according to claim 4, wherein, A second anti-reverse safety structure is also provided between the hollow screw (40) and the nut element (10).

8. The tolerance compensation device (1) according to claim 7, wherein, The second anti-reverse safety structure is formed in: a) Near the first axial end (62) of the hollow screw (40), the adjusting thread (52) terminates discontinuously, and / or b) Near the first axial end of the nut element (10), the nut thread (22) of the nut element (10) terminates discontinuously.

9. The tolerance compensation device (1) according to any one of claims 1, 2, 3, 4, 7 or 8, wherein the annular nut element (10) and the hollow screw (40) are made of plastic material.

10. A connection between a first component (A) and a spaced-apart second component (B) is achieved based on a tolerance compensation device (1) and a fastening screw (80) according to any one of the preceding claims.

11. The connection according to claim 10, wherein the first component (A) has a keyhole geometry (90) and a nut element (10) is provided therein.

12. A method for connecting a first component (A) and a spaced-apart second component (B) using a tolerance compensation device (1) according to any one of claims 1 to 9, the first component (A) having a keyhole geometry (90) and the second component (B) having a component opening (O2), the method comprising the steps of: a. Tighten the nut element (10) pre-installed with a hollow screw (40) into the opening (O1) of the first component (A). b. Align the component opening (O2) of the second component (B) with the fastening thread (56) of the hollow screw (40), and c. Screw the fastening screw (80) that passes through the opening (O2) of the component into the fastening thread (56). d. Rotate the fastening screw (80), thereby causing the hollow screw (40) to rotate synchronously until the hollow screw (40) abuts against the second component (B), and e. When the head (44) of the hollow screw (40) abuts against the second component (B), the fastening screw (80) is tightened in the fastening thread (56).

13. A method for manufacturing a tolerance compensation device (1) according to any one of claims 1 to 9, comprising the following steps: a. (S1) Provides an injection mold for the nut element (10) and the hollow screw (40), b. (S2) Injection molding the nut element (10) and the hollow screw (40), and c. (S3) Demold the nut element (10) and the hollow screw (40), and d. (S4) Pre-install the hollow screw (40) into the nut element (10).

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