DE102019114008A1 - Tolerance compensation fastening system with improved functionality - Google Patents

Abstract

Tolerance compensation fastening system, wherein the tolerance compensation fastening system is set up for tolerance compensation fastening of a first component to a second component, wherein the tolerance compensation fastening system comprises: the components can be pre-assembled using the pre-assembly means, so that the socket opening of the base part is aligned with the opening of the component; - a compensation part with a contact surface for contact with the other of the components and with a shaft made of a first plastic, the shaft being inserted into the thread of the base has a screwable thread and a shaft opening which also extends through the contact surface, the base opening and the shaft opening being aligned with one another when the threads are screwed into one another, a friction element being arranged in the shaft opening et is, wherein the friction element is formed from a second plastic and defines a first inner diameter in a first axial region, wherein the second plastic is softer than the first plastic, and wherein the friction element is injection-molded onto the shaft in the shaft opening; - a transport lock, which has mutually engaging, flexibly evasive stop elements and causes a first torque threshold value which is required to turn the compensation part from the base part from a transport position to an unscrewed compensation position position when the threads are loosely screwed into one another, - a screw with a Outer screw shank diameter which is greater than the first inner diameter, the screw being insertable into the base opening and the shank opening, the first inner diameter being less than or equal to 0.98 times the outer screw shank diameter and greater than or equal to 0, 7 times the outer diameter of the screw shaft, the torque which can be transmitted to the compensation element by means of the screw by simply turning the screw inserted into the shaft opening is greater than the first torque threshold value.

Description

The invention relates generally to tolerance compensation fastening systems.

The state of the art DE 101 17 851 A1 , DE 100 34 968 A1 , DE 10 2015 211798 A1 , WO 2016/105751 A1 , WO 2016/126284 A1 , DE 10 2018 108 830 A1 shows tolerance compensation fastening systems with transport locks.

The inventors found it disadvantageous that the torque required to release the transport lock is not often reproducible or too high or too small.

The object on which the invention is based was to improve this disadvantage. The object is achieved by the invention, in particular as it is defined in the independent claims.

• - ein Basisteil mit einem Vormontagemittel und einem Sockel, wobei der Sockel ein Gewinde und eine Sockelöffnung aufweist, wobei das Basisteil an eine Öffnung einer der Komponenten über die Vormontagemittel, bevorzugt eine Klammer, vormontierbar ist, so dass die Sockelöffnung des Basisteils mit der Öffnung der Komponente fluchtet;
• - ein Kompensationsteil mit einer Anlagefläche zur Anlage an der anderen der Komponenten und mit einem Schaft aus einem ersten Kunststoff, wobei der Schaft ein in das Gewinde des Sockels schraubbares Gewinde und eine Schaftöffnung aufweist, die sich auch durch die Anlagefläche erstreckt, wobei die Sockelöffnung und die Schaftöffnung bei ineinander geschraubten Gewinden zueinander fluchten, wobei in der Schaftöffnung ein Reibelement angeordnet ist, wobei das Reibelement bevorzugt aus einem zweiten Kunststoff gebildet ist, und wobei das Reibelement in einem ersten axialen Bereich einen ersten Innendurchmesser definiert, wobei das Reibelement, bevorzugt das zweite Kunststoffmaterial, weicher ist, als der erste Kunststoff, und wobei das Reibelement bevorzugt durch Spritzguss in der Schaftöffnung an den Schaft angespritzt ist;

• - eine Transportsicherung, welche gegenseitig in Eingriff gelangende, flexibel ausweichende Anschlagelemente aufweist und einen ersten Drehmomentschwellwert bewirkt, welcher erforderlich ist, um das Kompensationsteil von dem Basisteil bei lose, d.h. bevorzugt ohne Gewindevorspannung, ineinander geschraubten Gewinden von einer Transportposition in eine herausgeschraubte Kompensationspositionsposition zu verdrehen,
• - eine Schraube mit einem Schraubenschaftaußendurchmesser, welcher größer ist als der erste Innendurchmesser, wobei die Schraube in die Sockelöffnung und die Schaftöffnung einführbar ist, wobei der erste Innendurchmesser kleiner oder gleich 0,98 mal der Schraubenschaftaußendurchmesser ist und größer oder gleich 0,7 mal, bevorzugt größer oder gleich 0,8 mal der Schraubenschaftaußendurchmesser ist, wobei das mittels der Schraube auf das Kompensationselement durch reines Drehen der in die Schaftöffnung eingeführten Schraube übertragbare Drehmoment größer ist als der erste Drehmomentschwellwert.

In particular, this object is achieved by a tolerance compensation fastening system, the tolerance compensation fastening system being set up for tolerance-compensating fastening of a first component, preferably a vehicle component, to a second component, preferably a vehicle component, the tolerance compensation fastening system having:

• - A base part with a pre-assembly means and a base, the base having a thread and a base opening, the base part being preassembled to an opening of one of the components via the pre-assembly means, preferably a bracket, so that the base opening of the base part with the opening of the Component aligns;
• - A compensation part with a contact surface for contact with the other of the components and with a shaft made of a first plastic, wherein the shaft has a thread that can be screwed into the thread of the base and a shaft opening which also extends through the contact surface, the base opening and the shaft opening are aligned with one another when the threads are screwed into one another, a friction element being arranged in the shaft opening, the friction element preferably being formed from a second plastic, and the friction element defining a first inner diameter in a first axial region, the friction element, preferably the second Plastic material, is softer than the first plastic, and wherein the friction element is preferably molded onto the shaft by injection molding in the shaft opening;

• - a transport lock, which has mutually engaging, flexibly evasive stop elements and causes a first torque threshold value which is required to rotate the compensation part from the base part with loosely, ie preferably without pre-tensioning, threads screwed into one another from a transport position to an unscrewed compensation position position ,
• - a screw with a screw shank outer diameter which is larger than the first inner diameter, wherein the screw can be inserted into the base opening and the shank opening, the first inner diameter being less than or equal to 0.98 times the screw shank outer diameter and greater than or equal to 0.7 times, is preferably greater than or equal to 0.8 times the outer diameter of the screw shank, the torque which can be transmitted to the compensation element by means of the screw by simply turning the screw inserted into the shank opening is greater than the first torque threshold value.

This simplifies the use of a tolerance compensation fastening system, since the transport lock can be released automatically by turning the screw (which is turned for fastening anyway), but this is also possible with precise reproducibility in the given diameter range.

The soft friction element adapts very flexibly to the properties of the screw used. I.e. Tolerances are not critical and, if necessary, cheaper / imprecise screws can also be used. Furthermore, the system can be adjusted to the surface of the screw by choosing the plastic, e.g. special coating (screw locking varnish, slide coating, anti-corrosion, etc.). In the examples shown here, however, an uncoated screw is assumed.

The base part preferably has a threaded sleeve for the screw.

In a further tolerance compensation fastening system according to the invention it is provided that the friction element has a second inner diameter in a second axial area, the second axial area being offset from the first axial area in the direction of the side opposite the contact surface and the second inner diameter being smaller, than the first inside diameter.

This makes it easier for the screw to be inserted while still being high over the friction element given by the screw on the compensation part transmittable torque.

The compensation part preferably extends over an axial extension and the transverse central plane lies geometrically halfway along this extension, the first axial area and the second axial region being on different sides of the central plane. Preferably one of the and preferably even both axial areas adjoins a respective axial end of the shaft opening. An axial area with an inner diameter that is greater than the outer diameter of the screw shaft is preferably located between the axial areas. The first axial area preferably extends over an axial extent in the range from 0.3 to 0.6 times the outer diameter of the screw shaft.

The second axial area preferably extends over an axial extent in the range of 0.2 to 0.5 times the outer diameter of the screw shank.

In a further tolerance compensation fastening system according to the invention it is provided that the second inside diameter is less than or equal to 0.97 times the screw shaft external diameter and greater than or equal to 0.69 times, preferably greater than or equal to 0.79 times the screw shaft external diameter.

The desired torque is achieved particularly well in these areas. The outer diameter of the screw shank is preferably 6mm (M6). However, other diameters are also possible.

In a further tolerance compensation fastening system according to the invention, it is provided that the first and / or the second inner diameter is defined by at least two, preferably three, jaw elements projecting radially inward into the shaft opening, the jaw elements taken together only having a circumferential angle of less than or equal to 240 ° , preferably less than or equal to 180 °, of the inner diameter and otherwise gaps are present.

This in turn allows the screw to be easily inserted while still having good torque transmission properties.

In a further tolerance compensation fastening system according to the invention it is provided that a first of the stop elements is arranged on the base, preferably on an end face of the base facing the contact surface, and a second of the stop elements is arranged on the compensation part on the rear side of the contact surface The second stop element consists of the second plastic, and was preferably formed in the same injection molding shot as the friction element, the second stop element being designed as a prism with a rounded prism tip and the first stop element as a cylinder sector, preferably a hemi or half cylinder, with one of the back of the contact surface facing lateral surface, so that the rounded prism tip with flexible deformation of the prism must rub over the lateral surface in order to release the transport lock.

This provides a transport lock with a reliable and reproducible loosening torque. The "hardness" can be adjusted via the size and nature of the second stop element. This allows you to react very flexibly to the intended use, the transport conditions and the size (M3, M10, ...), type and possibly also coating (e.g. screw locking varnish) of the screw.

In a further tolerance compensation fastening system according to the invention it is provided that the base angles of the prism are in the range from 60 ° to 70 °, the ratio of prism height to prism base in the range from 0.7 to 0.9, preferably from 0.75 to 0, 85, and the ratio of the radius of curvature of the prism tip to the prism base in the range from 0.1 to 0.3, preferably from 0.15 to 0.25.

An even more desirable torque results in these areas.

The prism base or the length of the prism base in the case of an M6 screw is preferably in the range from 1.3 mm to 1.6 mm.

In a further tolerance compensation fastening system according to the invention it is provided that the ratio of the cylinder sector radius to the prism base is in the range from 0.3 to 0.5, preferably from 0.35 to 0.45, and in the transport position there is a distance between the cylinder sector and the The prism base is 0.3 to 0.5 times the prism height.

An even more desirable torque results in these areas.

In a further tolerance compensation fastening system according to the invention it is provided that the prism depth is greater than or equal to the maximum cylinder sector height.

An even more desirable torque results in these areas.

In a further tolerance compensation fastening system according to the invention It is provided that the cylinder sector has the maximum cylinder sector height on its base side, the cylinder sector having a second cylinder sector height on its side facing the contact surface, which is smaller than the maximum cylinder sector height, and the cylinder sector height thus from the base side to that facing the contact surface Side of the cylinder sector becomes smaller.

As a result, a torque for releasing the transport lock that is more uniform over a certain range of rotation is obtained, so that inadvertent release becomes less likely despite the torque that is not too high. This is based on the fact that the friction surface between the stop elements decreases, but the pressure on the friction surfaces increases as the deformation of the prism increases and vice versa.

In a further tolerance compensation fastening system according to the invention it is provided that the maximum cylinder sector height is in the range of 1.1 and 1.3 times the prism base and the second cylinder sector height is in the range of 0.7 and 0.9 times the prism base.

An even more desirable torque results in these areas.

In a further tolerance compensation fastening system according to the invention it is provided that the first plastic has a Shore hardness in the range of at least D65, preferably at least D72, and the friction element, preferably the second plastic, has a Shore hardness of less than D65, preferably e.g. of A60.

An even more desirable torque results in these areas.

The invention will now be further illustrated by way of example with reference to drawings.

• 1 bis 5: eine erste Ausführungsform eines erfindungsgemäßen Befestigungssystems aus verschiedenen Perspektiven und Ausschnitten, wobei in 3 nur das Reibelement separat darstellt ist und insgesamt die Schraube des Systems nicht dargestellt ist.

Here show:

• 1 to 5 : a first embodiment of a fastening system according to the invention from different perspectives and sections, wherein in 3 only the friction element is shown separately and overall the screw of the system is not shown.

• - ein Basisteil 10 mit einem Vormontagemittel 11 und einem Sockel 12, wobei der Sockel 12 ein Gewinde 13 und eine Sockelöffnung 14 aufweist, wobei das Basisteil 10 an eine Öffnung einer der Fahrzeugkomponenten über die Vormontagemittel 11, hier eine Klammer, vormontierbar ist, so dass die Sockelöffnung 14 des Basisteils 10 mit der Öffnung der Fahrzeugkomponente fluchtet;
• - ein Kompensationsteil 20 mit einer Anlagefläche 21 zur Anlage an der anderen der Fahrzeugkomponenten und mit einem Schaft 22 aus einem ersten Kunststoff, wobei der Schaft 22 ein in das Gewinde 13 des Sockels 12 schraubbares Gewinde 23 und eine Schaftöffnung 24 aufweist, die sich auch durch die Anlagefläche 21 erstreckt, wobei die Sockelöffnung 14 und die Schaftöffnung 24 bei ineinander geschraubten Gewinden 13, 23 zueinander fluchten, wobei in der Schaftöffnung 24 ein Reibelement 25 angeordnet ist, wobei das Reibelement 25 aus einem zweiten Kunststoff gebildet ist und in einem ersten axialen Bereich 25.1 einen ersten Innendurchmesser 25.91 definiert, wobei der zweite Kunststoff weicher ist, als der erste Kunststoff, und wobei das Reibelement 25 durch Spritzguss in der Schaftöffnung 24 an den Schaft 22 angespritzt ist;
• - eine Transportsicherung 30, welche gegenseitig in Eingriff gelangende, flexibel ausweichende Anschlagelemente 16, 26 aufweist und einen ersten Drehmomentschwellwert bewirkt, welcher erforderlich ist, um das Kompensationsteil 20 von dem Basisteil bei lose, d.h. hier ohne Gewindevorspannung, ineinander geschraubten Gewinden 13, 23 von einer Transportposition in eine herausgeschraubte Kompensationspositionsposition zu verdrehen,
• - eine Schraube mit einem Schraubenschaftaußendurchmesser, welcher größer ist als der erste Innendurchmesser 25.91, wobei die Schraube in die Sockelöffnung 14 und die Schaftöffnung 24 einführbar ist, wobei der erste Innendurchmesser 25.91 kleiner oder gleich 0,98 mal der Schraubenschaftaußendurchmesser ist und größer oder gleich 0,7, hier größer oder gleich 0,8 mal der Schraubenschaftaußendurchmesser ist, wobei das mittels der Schraube auf das Kompensationselement 20 durch reines Drehen der in die Schaftöffnung 24 eingeführten Schraube übertragbare Drehmoment größer ist als der erste Drehmomentschwellwert.

A more detailed description of 1 to 5 . The design is such that the tolerance compensation fastening system 1 is set up for the tolerance-compensating fastening of a first vehicle component to a second vehicle component, the tolerance compensation fastening system 1 having:

• - a basic part 10 with a pre-assembly agent 11 and a base 12 , with the base 12 a thread 13 and a socket opening 14th having, the base part 10 to an opening of one of the vehicle components via the pre-assembly means 11 , here a clamp, can be pre-assembled, so that the base opening 14th of the base part 10 aligned with the opening of the vehicle component;
• - a compensation part 20th with a contact surface 21st to rest on the other of the vehicle components and with a shaft 22nd made of a first plastic, the shaft 22nd one in the thread 13 of the base 12 screwable thread 23 and a shaft opening 24 has, which is also through the contact surface 21st extends, the base opening 14th and the shaft opening 24 with threads screwed into one another 13 , 23 aligned with each other, in the shaft opening 24 a friction element 25th is arranged, wherein the friction element 25th is formed from a second plastic and in a first axial area 25.1 a first inside diameter 25.91 defined, wherein the second plastic is softer than the first plastic, and wherein the friction element 25th by injection molding in the shaft opening 24 to the shaft 22nd is molded on;
• - a transport lock 30th , which mutually engaging, flexibly evasive stop elements 16 , 26th and causes a first torque threshold value, which is required to the compensation part 20th of the base part with loosely, ie here without pre-tensioning, threads screwed into one another 13 , 23 to rotate from a transport position to an unscrewed compensation position position,
• - A screw with an outer screw shank diameter which is larger than the first inner diameter 25.91 with the screw in the socket opening 14th and the shaft opening 24 is insertable, the first inner diameter 25.91 is less than or equal to 0.98 times the outer diameter of the screw shank and is greater than or equal to 0.7, here greater than or equal to 0.8 times the outer diameter of the screw shank, this being done by means of the screw on the compensation element 20th by simply turning the into the shaft opening 24 Introduced screw transmittable torque is greater than the first torque threshold.

In this example, the base part has a threaded sleeve 17th for the screw on. The design is such that the friction element 25th in a second axial area 25.2 a second inside diameter 25.92 having the second axial portion 25.2 compared to the first axial area 25.1 in the direction of the contact surface 21st opposite side is offset and wherein the second inner diameter 25.92 is smaller than the first inner diameter 25.91 . In this example the compensation part extends 20th The transversal central plane lies geometrically over an axial extension and halfway through this extension 27 , the first axial range 25.1 and the second axial section 25.2 on different sides of the median plane 27 lie. In this example, one of the, and here even both, axial areas borders 25.1 , 25.3 to a respective axial end of the shaft opening 24 at.

In this example is between the axial areas 25.1 , 25.2 an axial area 28 with an inner diameter that is larger than the outer diameter of the screw shank. The first axial area 25.1 extends here over an axial extent in the range of 0.3 to 0.6 times the screw shaft outer diameter.

The second axial area 25.2 extends here over an axial extent in the range of 0.2 to 0.5 times the screw shaft outer diameter. The configuration is such that the second inside diameter is less than or equal to 0.97 times the screw shaft external diameter and is greater than or equal to 0.69, here greater than or equal to 0.79 times the screw shaft external diameter. The outer diameter of the screw shaft is 6mm (M6).

The configuration is such that the first and / or the second inner diameter through at least two, here three, radially inward into the shaft opening 24 protruding jaw elements 25.3 , 25.4 , 25.5 is defined, the jaw elements 25.3 , 25.4 , 25.5 Taken together, only limit the inner diameter to a circumferential angle of less than or equal to 240 °, here less than or equal to 180 °, and otherwise the spaces 25.6 , 25.7 , 25.8 available.

The configuration is such that a first of the stop elements 16 on the base 12 , here on one of the contact surfaces 21st facing face of the base 12 , is arranged, and a second of the stop elements 26th on the compensation part 20th on the back of the contact surface 21st is arranged, the second stop element 26th consists of the second plastic, and was formed here in the same injection molding shot as the friction element 25th , wherein the second stop element 26th as a prism with a rounded prism tip 26.1 is formed and the first stop element 16 as a cylinder sector, here a hemi or half cylinder, with one of the back of the contact surface 21st facing lateral surface, so that the rounded prism tip 26.1 with flexible deformation of the prism must touch the outer surface to secure the transport 30th to solve.

The design is such that the base angle 26.2 of the prism lie in the range of 60 ° to 70 °, the ratio of the prism height 26.3 to prism base 26.4 in the range from 0.7 to 0.9, here from 0.75 to 0.85, and the ratio of the radius of curvature 26.5 the prism tip 26.1 to prism base 26.4 in the range from 0.1 to 0.3, of which 0.15 to 0.25. In this example, the prism base or the length of the prism base in the case of an M6 screw is in the range from 1.3 mm to 1.6 mm.

The configuration is such that the ratio of the cylinder sector radius 16.1 to the prism base 26.4 in the range from 0.3 to 0.5, here from 0.35 to 0.45, and a distance in the transport position 16.2 between the cylinder sector and the prism base 26.4 from 0.3 to 0.5 times the prism height 26.3 present.

The design is such that the prism depth 26.6 greater than or equal to the maximum cylinder sector height 16.3 is. The configuration is such that the cylinder sector on its base side 16.5 the maximum cylinder sector height 16.3 having, the cylinder sector on its the contact surface 21st facing side a second cylinder sector height 16.4 which is smaller than the maximum cylinder sector height 16.3 , and where the cylinder sector height is thus from the base side 16.5 towards that of the contact surface 21st facing side of the cylinder sector becomes smaller.

The design is such that the maximum cylinder sector height 16.3 in the range of 1.1 and 1.3 times the prism base 26.4 and the second cylinder sector height 16.4 in the range of 0.7 and 0.9 times the prism base 26.4 lies. The configuration is such that the first plastic has a Shore hardness of more than D72 and the second plastic has a Shore hardness in the range of A60.

List of reference symbols

1

Tolerance compensation fastening system

10

Base part

11

Pre-assembly means

12

base

13

thread

14th

Base opening

16

Stop element

16.1

Cylinder sector radius

16.2

distance

16.3

maximum cylinder sector height

16.4

second cylinder sector height

16.5

Base page

17th

Threaded sleeve

20th

Compensation part

21st

Contact surface

22nd

shaft

23

thread

24

Shaft opening

25th

Friction element

25.1

axial area

25.2

axial area

25.3

Jaw element

25.4

Jaw element

25.5

Jaw element

25.6

Space

25.7

Space

25.8

Space

25.91

first inside diameter

25.92

second inside diameter

26th

Stop element

26.1

Prism tip

26.2

Base angle

26.3

Prism height

26.4

Prism base

26.5

Rounding radius

26.6

Prism depth

27

transverse median plane

28

axial area

30th

Transport lock

QUOTES INCLUDED IN THE DESCRIPTION

This list of the documents listed by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Patent literature cited

• DE 10117851 A1 [0002]
• DE 10034968 A1 [0002]
• DE 102015211798 A1 [0002]
• WO 2016/105751 A1 [0002]
• WO 2016/126284 A1 [0002]
• DE 102018108830 A1 [0002]

Claims (11)

Tolerance compensation fastening system (1), wherein the tolerance compensation fastening system (1) is set up for tolerance-compensating fastening of a first component to a second component, wherein the tolerance compensation fastening system (1) has: a base part (10) with a pre-assembly means (11) and a base (12) wherein the base (12) has a thread (13) and a base opening (14), wherein the base part (10) can be preassembled to an opening of one of the components via the pre-assembly means (11), so that the base opening (14) of the base part (10) is aligned with the opening of the component; - A compensation part (20) with a contact surface (21) for contact with the other of the components and with a shaft (22) made of a first plastic, the shaft (22) being screwable into the thread (13) of the base (12) Has thread (23) and a shaft opening (24) which also extends through the contact surface (21), wherein the base opening (14) and the shaft opening (24) are aligned with one another when the threads (13, 23) are screwed into one another, wherein in the A friction element (25) is arranged in the shaft opening (24), the friction element (25) defining a first inner diameter (25.91) in a first axial region (25.1), the friction element (25) being softer than the first plastic; - A transport lock (30) which has mutually engaging, flexibly evasive stop elements (16, 26) and causes a first torque threshold value which is required to remove the compensation part (20) from the base part when the threads (13, 23) are loosely screwed into one another ) to rotate from a transport position to a screwed-out compensation position position, - a screw with a screw shaft outer diameter which is larger than the first inner diameter (25.91), the screw being insertable into the base opening (14) and the shaft opening (24), characterized in that, that the first inner diameter (25.91) is less than or equal to 0.98 times the outer diameter of the screw shank and is greater than or equal to 0.7 times the outer diameter of the screw shank, this being done by means of the screw on the compensation element (20) by simply turning the screw shaft opening (24) Introduced screw, the transmittable torque is greater than the first e torque threshold. Tolerance compensation fastening system (1) according to Claim 1 , the friction element (25) having a second inner diameter (25.92) in a second axial area (25.2), the second axial area (25.2) being offset from the first axial area (25.1) in the direction of the side opposite the contact surface (21) and wherein the second inner diameter (25.92) is smaller than the first inner diameter (25.91). Tolerance compensation fastening system (1) according to Claim 2 , wherein the second inner diameter is less than or equal to 0.97 times the screw shank outer diameter and greater than or equal to 0.69 times the screw shank outer diameter. Tolerance compensation fastening system (1) according to one of the Claims 1 to 3 , the first and / or the second inner diameter being defined by at least two jaw elements (25.3, 25.4, 25.5) projecting radially inward into the shaft opening (24), the jaw elements (25.3, 25.4, 25.5) taken together only having a circumferential angle of less or equal to 240 ° of the inner diameter and otherwise gaps (25.6, 25.7, 25.8) are present. Tolerance compensation fastening system (1) according to one of the Claims 1 to 4th , wherein a first of the stop elements (16) is arranged on the base (12), and a second of the stop elements (26) is arranged on the compensation part (20) on the rear of the contact surface (21), the second stop element (26) consists of the second plastic, the second stop element (26) being designed as a prism with a rounded prism tip (26.1) and the first stop element (16) as a cylinder sector with a lateral surface facing the back of the contact surface (21), so that the rounded prism tip ( 26.1) with flexible deformation of the prism must touch the outer surface in order to release the transport lock (30). Tolerance compensation fastening system (1) according to Claim 5 , the base angle (26.2) of the prism being in the range from 60 ° to 70 °, the ratio of prism height (26.3) to prism base (26.4) being in the range from 0.7 to 0.9 and the ratio of the radius of the rounding (26.5) the prism tip (26.1) to the prism base (26.4) is in the range from 0.1 to 0.3. Tolerance compensation fastening system (1) according to one of the Claims 5 to 6th , the ratio of the cylinder sector radius (16.1) to the prism base (26.4) being in the range from 0.3 to 0.5 and, in the transport position, a distance (16.2) between the cylinder sector and the prism base (26.4) of 0.3 to 0, 5 times the prism height (26.3) is available. Tolerance compensation fastening system (1) according to one of the Claims 5 to 7th , wherein the prism depth (26.6) is greater than or equal to the maximum cylinder sector height (16.3). Tolerance compensation fastening system (1) according to Claim 8 , the cylinder sector having the maximum cylinder sector height (16.3) on its base side (16.5), the cylinder sector having a side facing the contact surface (21) second cylinder sector height (16.4), which is smaller than the maximum cylinder sector height (16.3), and the cylinder sector height is thus smaller from the base side (16.5) to the side of the cylinder sector facing the contact surface (21). Tolerance compensation fastening system (1) according to Claim 9 , the maximum cylinder sector height (16.3) being in the range of 1.1 and 1.3 times the prism base (26.4) and the second cylinder sector height (16.4) being in the range of 0.7 and 0.9 times the prism base (26.4). Tolerance compensation fastening system (1) according to one of the Claims 1 to 10 wherein the first plastic has a Shore hardness in the range of at least D65 and the friction element (25) has a Shore hardness of less than D65.

Images