Driving elements

Abstract

The present invention is based on the contour axis P I and defines the contour axis P I The inner driving profile 9 has a plurality of concave driving surfaces 6 arranged in a regular distribution around the axis P, and a planar or convexly curved transition surface 7a is provided between adjacent driving surfaces 6, or A and defines the contour axis P A The present invention relates to a drive element 8 having an outer drive contour 9 with a plurality of concave drive surfaces 10 arranged on the outside in a regularly distributed manner around the drive element 8, and with planar or convexly curved transition surfaces 7a between adjacent drive surfaces 10.

Description

[Technical field]

[0001] The invention relates to a drive element, in particular having at one end of a shaft an inner drive profile, which defines a profile axis and has on its inside a plurality of concave drive surfaces uniformly distributed around the profile axis and with planar or convexly curved transition surfaces between adjacent concave drive surfaces, or an outer drive profile, which defines a profile axis and has on its outside a plurality of concave drive surfaces uniformly distributed around the profile axis and with planar or convexly curved transition surfaces between adjacent concave drive surfaces, In a cross-section, the change or transition points between the drive surface and the transition surface lie on a common inner circle having an inner diameter Di; The drive surfaces are located on an outer circle of diameter Da, uniformly distributed around the contour axis, and relate to drive elements formed symmetrically with respect to a longitudinally extending central plane surrounding the contour axis.

[0002] Furthermore, the invention relates to a method for non-rotatably connecting two components, in particular a screw and a rotary tool, where one component is designed as a drive element with an outer drive profile and the other component is designed as a drive element with an inner drive profile, the drive profiles of the two components being axially inserted into one another to produce a non-rotatable connection of the two components. [Background technology]

[0003] Screws and turning tools are known from the prior art in various designs. The screw comprises a screw shank with an external thread, in the upper end region of which a drive element is provided for coupling with a turning tool, which is usually formed on the screw head. The turning tool is formed, for example, in the form of a ring wrench or spanner or comprises an exchangeable bit, which is connected via a bit holder to a drive, for example in the form of a handle or a cordless screwdriver. Alternatively, the bit holder can be connected via an adapter to a screwdriver handle or angle handle, a ratchet, a torque wrench, a cordless screwdriver or a ratchet screwdriver for alternative use.

[0004] The screw and the turning tool are provided for transmitting the torque from the turning tool to the screw using drive elements designed complementary to each other. For this purpose, one of the two components is provided with an outer driving profile with an outer driving surface at one of its free ends, and the other component is provided with an inner driving profile with an inner driving surface complementary to the outer driving profile at one of its free ends. The driving profiles are, for example, in the form of an inner hexagon, an outer hexagon, a torx profile, and a cross-slot profile or a slot profile. After coupling the inner driving profile to the outer driving profile, both driving profiles contact each other with play. This means that both driving profiles can unintentionally separate from each other, and that the driving profiles cannot be axially aligned with each other either. To simplify handling when screwing and unscrewing the screw with the turning tool, turning tools with magnets or ferromagnetic turning tools that can be magnetized with magnets are provided. However, this entails additional costs. Furthermore, the use of magnetic turning tools does not allow the coaxial alignment of both driving profiles to be achieved either. However, such a coaxial alignment is necessary for the integration of the bolting into an automated manufacturing process.

[0005] To solve this problem, it is known from DE 10 2005 011 734 A1 that the drive faces of the rotary tools for screwing in and loosening so-called Torx screws are inclined at an acute angle to the profile axis, so that when the drive profiles of the rotary tool and the screw engage axially, a tight fit is generated and no additional holding means are required to screw the screw into the thread. Similarly, from WO 2013 / 062895 A1 and US 2010 / 0269644 A1, it is known to form the drive faces of the screw and the rotary tool inclined in order to create a tight fit between the components.

[0006] A recurring problem when screwing and unscrewing is that the drive contour is damaged, especially in the area of ​​the edges, if the torque required for screwing and unscrewing the screw is too high.

[0007] To solve this problem, WO 2019 / 238250 proposes a drive system with a screw and a rotary tool, the drive profile of which is tapered. Furthermore, the outer drive profile has a drive surface that is concave, i.e. curved inwards in the shape of a segment of a circular arc towards the profile axis, and the inner drive profile has a complementary drive surface. This arrangement is such that, when mated, the drive surfaces of the two components come into contact / engage on both sides of the apex of the concave curved surface when viewed in the circumferential direction.

[0008] In addition to a secure, torsionally rigid connection, this design also creates a friction or clamping connection between the screw and the rotating tool, through which the components are axially connected and coaxially aligned with each other. Furthermore, the forces or torques are only transmitted via surface contacts that occur on the arc-shaped curved driving surfaces on either side of the apex, and not in the transition areas / surfaces located between the driving parts. In this way, damage to the edge or peripheral areas of the driving surfaces can be completely avoided. [Prior art documents] [Patent documents]

[0009] [Patent Document 1] DE 102005011734 A1 [Patent Document 2] International Publication No. 2013 / 062895 [Patent Document 3] US Patent Application Publication No. 2010 / 0269644 [Patent Document 4] International Publication No. 2019 / 238250 Summary of the Invention [Problem to be solved by the invention]

[0010] The object of the present invention is to further optimize the above-mentioned drive system, in particular to allow high torque transmission and a large number of duty cycles. [Means for solving the problem]

[0011] The problem is solved in a drive element of the above-mentioned type in that the outer diameter Da and the center distance L between the inner and outer circles are selected as a function of the inner diameter Di, and when a torque about the profile axis acts on the drive profile, the normal forces acting at the transition point between each drive surface and its adjacent transition surface act in the tangential direction of one drive surface and the adjacent drive surface or in said adjacent drive surface. In other words, the normal forces are directed towards a central area of ​​the drive profile between the adjacent drive surface and the profile axis. The problem is therefore solved by a method for non-rotatably connecting two components of the initially mentioned type, in particular a screw and a rotary tool, the two components being designed as a drive element according to the invention, the drive profiles of the two drive elements being selected to complement each other in such a way that the drive surfaces of the two components are in surface contact with each other when the components are axially inserted into each other, so that a frictional and / or clamping connection is created between the components, in which the two components are axially connected to each other.

[0012] It has been shown that optimal results are obtained in terms of achievable number of duty cycles and transmittable torque if the normal forces perpendicular to the drive surfaces occurring during torque transmission on the drive surfaces are directed towards the centre of the drive profile, so that the area between the concavely curved drive surfaces is not or only little loaded with bending and / or shear forces. This is achieved by adapting the outer diameter Da, the inner diameter Di and the centre distance L according to the invention. The normal force is understood to be the part of the lever force introduced into the drive profile in order to generate a torque perpendicular to the respective circular segment shaped drive surface and therefore through the centre of the circle.

[0013] According to one embodiment of the present invention, the center distance L is F(L, Di)=0.494e (0,605K) It is prescribed that the running ratio K=Da / Di should be in the range of 0.3 to 2.0.

[0014] According to a further embodiment of the invention, it is provided that the inner driving profile has a driving surface which is inclined with respect to the profile axis and approaches the profile axis from the insertion opening of the inner driving profile towards the rear end of the inner driving profile. A preferred embodiment of this embodiment has a driving surface of the inner driving profile which is inclined with respect to the profile axis at an inclination angle α I is inclined at least 1 degree, in particular at least 1.5 degrees, and / or the driving surface of the inner driving profile is inclined at an inclination angle α I is inclined at a maximum of 5 degrees, in particular at a maximum of 3.5 degrees, and preferably at a maximum of 3 degrees, and said inclination angle α I is specifically characterized by being 2±0.2 degrees or 3±0.2 degrees.

[0015] In a further refinement of this embodiment, it is provided that the transition surface is inclined with respect to the profile axis and approaches the profile axis from the insertion opening of the inner drive profile towards the rear end of the inner drive profile. In this embodiment, the transition surface is inclined with respect to the profile axis at an inclination angle β Iis inclined at least 1 degree, in particular at least 1.5 degrees, and / or the transition surface of the inner driving profile is inclined at an inclination angle β I is inclined at a maximum of 5 degrees, in particular at a maximum of 3.5 degrees, and preferably at a maximum of 3 degrees, and the inclination angle β I Specifically, the inclination angle α of the driving surface relative to the contour axis is 2±0.2 degrees or 3±0.2 degrees. I is the inclination β of the transition surface relative to the contour axis I is exactly the same size as the angle

[0016] In other words, the internal drive profiles are designed to converge conically from their insertion openings.

[0017] Likewise, the drive faces of the outer drive profile of the drive element according to the invention can be inclined with respect to the profile axis, thereby approaching the profile axis towards the insertion end of the outer drive profile, where the drive faces are inclined with respect to the profile axis by an inclination angle α A is inclined such that the inclination angle α is at least 0.5 degrees, in particular at least 1 degree, and / or at most 1.5 degrees. A is preferably 1.15±0.2 degrees.

[0018] In this case, the transition surface can run parallel to the contour axis. However, according to one embodiment of the invention, the transition surface is inclined at an inclination angle β A is greater than 0 degrees and less than 0.7 degrees, preferably 0.4±0.05 degrees.

[0019] In a further embodiment of this embodiment, the inclination angle β of the transition surface relative to the contour axis A is the inclination angle α of the driving surface relative to the contour axis A is smaller than the inclination angle β A The inclination angle α A is provided that the ratio is ≧2, in particular ≧2.5, preferably 2.8±0.2.

[0020] According to a preferred embodiment of the invention, the outer diameter Da is constant over the entire axial length of the drive profile. Here, it should be taken into account that in the case of conically converging drive profiles, the drive faces can be manufactured differently. On the one hand, a cylindrical cutter can be used, which is adjusted to the desired taper angle. In this case, the drive faces have a true circular shape in a plane perpendicular to the respective flank angle of the tapered drive profile, but this true circular shape is slightly distorted into an ellipse in a cross section perpendicular to the profile axis. Similar distortions can also occur with other manufacturing methods. Such deviations should be considered as manufacturing tolerances.

[0021] Similarly, the inner diameter Di may be constant over the entire axial length of the driving face or may increase continuously in the direction of the insertion opening in the case of the inner driving profile and from the insertion end in the case of the outer driving profile, adapting to the inclination of the transition surface. In the latter case, the claimed conditions and therefore the claimed range of acting normal forces must be present at the tapered end of the outer driving profile, preferably over its entire effective length. As with the screw head, the driving profile preferably has 5 or 6 driving faces. However, a different number of profiles is also possible.

[0022] In a preferred embodiment, the driving element is a screw and the driving profile is formed on the head of the screw. Similarly, the driving element may be a screw bit.

[0023] According to a preferred embodiment of the method according to the invention, it is provided that the drive profiles of the two components have drive surfaces which are inclined relative to the profile axis, and that the drive profiles of the two components are selected to complement each other so that when the drive profiles are inserted axially into each other, the drive surfaces of the two components come into surface contact with each other, so that a friction and / or clamping connection is formed between the two components, which axially connects the components to each other.

[0024] In the method according to the invention, pairs of components which are non-rotatably connected are assigned to one another in a kit-like manner, the components being designed to match and correspond to one another. In one embodiment of the invention, the two components are selected such that the drive profiles of the two components have drive faces which are inclined relative to the respective profile axes. In a preferred embodiment, the inclination angle α, with which the drive face of the inner drive profile is inclined relative to the profile axis, is I is the inclination angle α of the driving surface of the outer driving profile with respect to the profile axis A It is provided that the inclination angle α of the inner driving profile to the profile axis of the driving surface is greater than I is 3±0.2 degrees, and the inclination angle α of the outer driving profile to the profile axis of the driving surface A is 1.15±0.15 degrees, or the inclination angle α of the inner driving profile to the profile axis of the driving surface I is 2±0.2 degrees, and the inclination angle α of the outer driving profile to the profile axis of the driving surface A is provided to be 1.15 ± 0.15 degrees. This design ensures that the two driving profiles engage at the small ends of the taper but have a small gap at the large ends. This has been shown to ensure a secure connection even when forces are applied transverse to the profile axis.

[0025] Similarly, the transition surfaces of the drive profiles of the two components are inclined to their respective profile axes, the inclination angle β of the transition surface of the inner drive profile to the profile axis being >5, in particular >6, preferably >7.5, relative to the inclination angle of the transition surface of the outer drive profile to the profile axis.

[0026] According to a further embodiment of the method of the invention, it is provided to use a drive element whose outer diameter of the inner drive profile is smaller than the outer diameter of the outer drive profile, in particular 1.5-3%, preferably 2% smaller.

[0027] This shows that by slightly undercutting the outer driving contour it is possible to compensate for the wear phenomenon of the cutting insert during the manufacture of the driving surface.

[0028] In a further embodiment of this embodiment, it can be provided that the drive faces of the two components are in surface contact with each other over at least 25% of their total circumferential extent, in particular at least 40%, preferably at least 60%.

[0029] Preferably, the two components come into contact at respective contact surfaces on either side of their longitudinal center plane. Likewise, the drive profiles can be designed such that they do not come into contact in the region of the transition surface.

[0030] Further features and advantages of the present invention will be explained with reference to the accompanying drawings. [Brief description of the drawings]

[0031] [Figure 1] FIG. 1 is a perspective view of a screw having an internal driving profile. [Diagram 2] 2 is a perspective view of a drive element in the form of a screw bit having an outer drive profile according to the invention, which corresponds to the drive profile of the screw in FIG. 1 . [Diagram 3] FIG. 13 is a schematic diagram showing engagement between a screw bit and a screw in a cross-sectional view illustrating the inclination angle α of the drive surface. [Figure 4] FIG. 4 is an enlarged view of a detail of a portion X in FIG. [Diagram 5] FIG. 13 is a schematic diagram of engagement in another cross-sectional view illustrating the inclination angle β of the transition surface. [Figure 6] FIG. 6 is an enlarged view of a portion X in FIG. 5. [Figure 7] FIG. 2 shows the geometry and force transmission paths of the outer drive contour of a drive element according to the invention. [Figure 8] FIG. 13 shows a dimensioned example of an outer driving profile according to the present invention. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0032] 1 shows an example of a drive element in the form of a screw 1. The screw 1 comprises a shank 2 having an external thread 3 and defining a longitudinal axis of the screw 1. At the upper end of the shank 2, a screw head 4 is provided, which opens towards the upper side of the screw head 4, has an inner drive surface 6 and has a profile axis P coaxial with the longitudinal axis of the screw 1. I The inner driving profile 5 defines an insertion opening 5a of the inner driving profile 5 for a screw bit.

[0033] In cross section or in plan view, the inner driving profile 5 has the basic shape of a regular hexagon, the lateral sides of which form driving faces 6 which run along a contour axis P from an insertion opening 5a of the inner driving profile 5 towards the rear end of the inner driving profile 5. A The contour axis P approaches A or the inclination angle α with respect to the longitudinal axis of the screw 1 I 2°. In other words, the driving profile 5 tapers at the screw head 4. In the case of a small screw, the inclination angle α I may be 3°.

[0034] The drive faces 6 of the inner drive profile 5 have a concave cross section, i.e. they are aligned along the profile axis P I In particular, the concave drive faces 6 each have a cross-sectionally arcuate segment shape, whereby the radius of the drive faces 6 is constant over their entire axial length.

[0035] The drive faces 6 are connected to one another at six corners by transition areas or transition faces 7 which are convexly curved and have the shape of a circular arc, so that they protrude outwardly in the shape of a beam. The transition between the transition faces 7 and the drive faces 6 is continuous. The transition faces 7 are aligned along the contour axis P I , so that the transition surface 7 runs from the insertion opening 5a of the inner driving profile 5 towards the rear end of the inner driving profile 5 along the contour axis P I In this case, the contour axis P I The inclination angle β of the transition surface 7 with respect to I is the contour axis P I The inclination angle α of the driving surface with respect toI , and thus 2° in the illustrated embodiment.

[0036] In Fig. 2, a driving element / rotating tool 8 in the form of a screw bit designed to manipulate the screw 1 shown in Fig. 1 is shown. The rotating tool 8 has an outer driving contour 9, the lower end of which is provided on the shaft of a screw bit, not shown, and which is designed to correspond to the driving contour of the screw 1, thereby having a contour axis P A The outer driving profile 9 therefore also has a basic shape that is hexagonal in cross section, the driving face 10 of the driving profile 9 being concave, i.e. the profile axis P A Curved in the direction of the contour axis P A Specifically, the driving surface 10 of the screw bit is inclined with respect to the contour axis P A Angle α of 1.15° A and inclines toward the free insertion end of the outer driving profile 9 (the upper end in FIG. 2) along the profile axis P A , with the outer driving profile 9 being inserted into the inner driving profile 5 of the screw 1. The driving face 10 of the screw bit is therefore somewhat steeper than the driving face 9 of the screw (see figures 3 and 4). The driving face 10 has a cross section in the shape of a circular arc segment, the radius of which is constant over its entire axial length and which has the same value as the radius of curvature of the driving face 6 of the screw 1.

[0037] The drive faces 10 are continuously connected to one another by a convex transition region or surface 7a which is tapered and has an arcuate shape.

[0038] Like the inner driving profile 5, the transition surface 7a of the outer driving profile 9 is aligned with the profile axis P A and towards the insertion end of the outer driving profile 9, the profile axis P A As a result, the contour axis P of the transition surface 7a approaches A The inclination angle β A The angle of the contour axis P is 0.4°. A The inclination angle β of the transition surface 7a with respect to A is the contour axis P A The inclination angle α of the drive surface 10 with respect to AThis means that the inclination angle α A The inclination angle β A Ratio α to A / β A is approximately 3. Furthermore, the inclination angle β of the transition surface 7a of the outer driving profile 9 relative to the profile axis P A is the transition surface of the inner driving profile along the profile axis P I The inclination angle β I (see Figures 5 and 6). In this case, the inclination angle β I The inclination angle β A Ratio to β I / β A is 7.5. This configuration ensures that the transition regions of the screw 1 and the corresponding screw bit 8 do not come into contact with each other. Thus, the radius of curvature of the transition region 7a of the bit 8 is greater than the radius of curvature of the transition region 7 of the screw 1.

[0039] In other words, the surface contact / engagement between the drive contours 5,9 takes place only in the region of the drive faces 6,10 and not in the intermediate transition region 7,7a, and the contact zone is configured to extend, in the circumferential direction, on both sides of the apex of the concavely curved drive faces 6,10, respectively. A surface contact between the drive faces 6,10 of the two components 1,8 in the mated state is desirable, so that the two components 1,8 are precisely coaxially aligned with each other in the axial direction when their two drive contours 5,9 are inserted into each other until a clamping connection is created between the two components 1,8 due to the conical nature of the drive contours 5,9 of the drive faces 6,10. Furthermore, the surface contact creates a frictional connection that can transmit high torques.

[0040] FIG. 7 shows the shape of the outer driving contour 5 of a bit 8 at its free tapered end according to the invention.

[0041] It can be seen that the transition surfaces 7 lie on a common circle (the inner circle) having an inner radius Da. However, the transition surface 7 does not have to have a continuous arc shape, but may for example be flat. It is essential that the transition point between the drive surface 6 and the adjacent transition surface 7 (here indicated by arrow P1) lies on the above mentioned common inner circle.

[0042] Furthermore, the driving surface 6 has a contour axis P A are arranged on an outer circle of diameter Da uniformly distributed around the contour axis P A It is shown that the axial direction of the slit 10 is symmetrically formed about a longitudinal center plane that encircles the slit 10 .

[0043] Contour axis P A Torque M centered on D The outer diameter Da and the center distance L between the center points of the inner and outer circles are selected as a function of the inner diameter Di such that, when is introduced into the driving profile 5, the normal force acting on the transition point between the driving surface 6 and the adjacent transition surface 7 is applied in the tangential direction of one driving surface 6 and the adjacent driving surface. N1 is shown in FIG. 7 as an example of a transition point P1 between the upper drive surface 6 and the adjacent transition surface 7 on the left side.

[0044] Desired torque M D To generate this force, the lever force F H1 must act on point P1. This is due to the normal force F, which is directed perpendicular to the outer circle on which the driving surface 6 is located and passes through its center. N1 and the tangential force F perpendicular to it T1 As is clear from FIG. 3, this configuration is N1 acts tangentially on the drive face 6 arranged adjacent to the left side of the upper drive face 6. According to the invention, the normal force F N1 Also, in Figure 3, the dashed arrow F NB As illustrated in the figure, the normal force F N1 and contour axis P A The normal force F N1 is introduced in the central region of the component 8, which is designed as a drive profile 9 or screw bit, so that the beam-shaped transition region 7 between the two drive surfaces 6 is not or only very little subjected to bending or shear.

[0045] Given a given inner diameter Di, the outer diameter Da and the center-to-center distance L between the center of the inner circle and the center of the outer circle can be calculated according to the following formula: L = F(L, Di)Di The effective ratio K=Da / Di can be selected between 0.3 and 2.0.

[0046] A calculation example is shown in Figure 8. The parameters are selected as follows:

[0047] Di=5.6mm K=0.8 (select freely within the above range) From this, Da = Di x K = 5.6 x 0.8 = 4.48.

[0048] F(L, Di) = 0.494e (0.605K) =0.494e (0.605× 0.8) = 0.8479, and L is calculated.

[0049] L=(L,Di)Di=0.8479×5.6=4.748 From these parameters, the geometry shown in FIG. 4 can be constructed.

[0050] The shape of the inner driving contour 5 is such that the outer diameter D of the outer driving contour A Diameter D of the inner drive contour 5 into which A is selected accordingly, provided that it is approximately 2% smaller than 0. This takes into account the fact that when the drive surface is formed by the cutting insert, the greatest wear occurs in the central region of the drive surface, since the cutting insert has to remove most of the material. With increasing wear, less material is removed in the central region of the drive surface, and therefore the smallest curvature is formed here to compensate for the undersizing.

[0051] It should be noted that the inclination angle α of the drive surface and the inclination angle β of the transition surface are measured circumferentially about the respective surfaces, and therefore the angles are measured at the midplane of the respective surfaces that intersects with the profile axis of the respective drive profile. [Explanation of symbols]

[0052] 1: Screw 2: Shaft 3: Male thread 4: Screw head 5: Inner driving contour 5a: Insertion opening 6: Drive surface 7: Transition area 7a: Transition surface 8: Drive elements / rotary tools / bits 9: Outer driving contour 10: Drive surface Da: Outer diameter L: Distance between centers M D :torque P I :Contour axis P A :Contour axis

Claims

1. Contour axis (P Ｉ ) and a contour axis (P Ｉ an inner driving profile (5) having on its inside a plurality of concave driving surfaces (6) evenly distributed around the driving surface (5) and having planar or convexly curved transition surfaces (7) between adjacent concave driving surfaces (6); or the contour axis (P Ａ ) and a contour axis (P Ａ the outer driving contour (9) having on its outer side a number of concave driving surfaces (10) uniformly distributed around the driving surface (10) and having planar or convexly curved transition surfaces (7a) between adjacent concave driving surfaces (10), In the cross section, the transition point (P) between the drive surface (6) and the transition surface (7) of the inner drive profile (5) １ ) are located on a common inner circle with diameter Di and are also the transition points (P １ ) lie on a common inner circle having a diameter Di, The driving surface (6) of the inner driving profile (5) is located on an outer circle of diameter Da along the profile axis (P Ｉ ) and are uniformly distributed around the contour axis (P Ｉ ) and the driving surface (10) of the outer driving contour (9) is formed symmetrically with respect to a central plane extending in the longitudinal direction and including the contour axis (P Ａ ) and are uniformly distributed around the contour axis (P Ａ A drive element (1, 8) formed symmetrically with respect to a longitudinally extending central plane including the The diameter Da of the outer circle and the center distance L between the inner and outer circles are selected as a function of the diameter Di of the inner circle, and the contour axis (P Ｉ , P Ａ ) acting on the drive contours (5, 9), the center of the outer circle on which each drive surface (6, 10) is located and the transition point (P １ ) acts in the tangential direction of the adjacent driving surface (6, 10) of each of the driving surfaces (6, 10), or acts in the tangential direction of the adjacent driving surface (6, 10) of each of the driving surfaces (6, 10) and the contour axis (P Ｉ , P Ａ ) .

2. 2. The drive element according to claim 1, characterized in that the running ratio K=Da / Di is in the range of 0.3 to 2.

0.

3. The center distance L is F(L,D ｉ ) = 0.494e (0.605K) In the formula L = F (L, D ｉ ) D ｉ 3. The drive element according to claim 2, characterized in that it is calculated according to:

4. The inner driving profile (5) has a driving surface (6) on the inner driving profile (5) and the driving surface (6) on the inner driving profile (5) is aligned with the profile axis (P Ｉ ) and extends from the insertion opening (5a) of the inner driving profile (5) towards the rear end of the inner driving profile (5) along the profile axis (P Ｉ 10. The drive element according to claim 9, wherein the rotational speed of the drive element is approximately 100 rpm.

5. The driving surface (6) of the inner driving profile (5) is aligned with the profile axis (P Ｉ ) with an inclination angle α Ｉ is inclined such that the inner driving profile (5) has a driving surface (6) which is inclined such that the inner driving profile (5) has a driving axis (P Ｉ ) with an inclination angle α Ｉ 5. The drive element according to claim 4, characterized in that it is inclined by a maximum of 5 degrees.

6. The transition surface (7) of the inner driving profile (5) is aligned with the profile axis (P Ｉ ) and extends from the insertion opening (5a) of the inner driving profile (5) towards the rear end of the inner driving profile (5) along the profile axis (P Ｉ 6. The drive element according to claim 4 or 5, characterized in that the rotational speed of the drive element approaches 0.5 mm.

7. The transition surface (7) of the inner driving profile (5) is aligned with the profile axis (P Ｉ ) with an inclination angle β Ｉ is inclined at least 1 degree, and the transition surface (7) of the inner driving profile (5) is inclined to the contour axis (P Ｉ ) with an inclination angle β Ｉ 7. The drive element according to claim 6, characterized in that it is inclined by a maximum of 5 degrees.

8. The contour axis (P Ｉ ) the inclination angle α of the drive surface (6) relative to Ｉ is the contour axis (P Ｉ ) the inclination angle β of the transition surface (7) relative to Ｉ A drive element according to any one of claims 5 to 7, characterized in that it is of the order of magnitude of

9. The outer driving profile (9) has a driving surface (10) on the outer driving profile (9) and the driving surface (10) on the outer driving profile (9) is aligned with the profile axis (P Ａ ) towards the insertion end of the outer driving profile (9) Ａ 10. The drive element according to claim 9, wherein the rotational speed of the drive element is approximately 100 rpm.

10. The driving surface (10) of the outer driving profile (9) is aligned along the profile axis (P Ａ ) with an inclination angle α Ａ is inclined such that the contour axis (P Ａ ) with an inclination angle α Ａ 10. The drive element according to claim 9, characterized in that it is inclined by a maximum of 1.5 degrees.

11. The transition surface (7a) of the outer driving contour (9) has an inclination angle β greater than 0 degrees and less than 0.7 degrees. Ａ The contour axis (P Ａ 11. The drive element according to claim 9 or 10, characterized in that it is inclined with respect to the axis of rotation of the drive element.

12. The contour axis (P Ａ ) the inclination angle β of the transition surface (7a) relative to Ａ is the contour axis (P Ａ ) the inclination angle α of the drive surface (10) relative to Ａ is smaller than the inclination angle α Ａ The inclination angle β Ａ 12. The drive element according to claim 11, characterized in that the ratio to is ≧2.

13. 10. A drive element according to claim 9, characterized in that the diameter Da of the outer circle on which the drive faces (6) of the inner drive profile (5) lie is constant over the entire axial length of the inner drive profile (5) and the diameter Da of the outer circle on which the drive faces (10) of the outer drive profile (9) lie is constant over the entire axial length of the outer drive profile (9).

14. The change point (P) between the drive surface (6) and the transition surface (7) of the inner drive contour (5) １ The diameter Di of the inner circle on which the inner driving profile (5) is located is constant over the entire axial length of the inner driving profile (5) or the ... driving profile (5) is constant over the entire axial length of the inner driving profile (5) or the diameter Di of the inner driving profile (5) is constant over the entire axial length of the inner driving profile (5) or the Ｉ ) and increases continuously towards the insertion opening (5a) so as to match the inclination of the transition surface (7) relative to the driving surface (10) of the outer driving contour (9) and the transition surface (7a) at the change point (P １ The diameter Di of the inner circle on which the outer driving profile (9) is located is constant over the entire axial length of the outer driving profile (9) or the ... Ａ Starting from the insertion end of the outer driving profile (9), the profile axis (P Ａ 5. A drive element according to claim 1, characterized in that the inclination of the transition surface (7a) relative to the axial direction of the drive shaft (1) increases continuously to match the inclination of the transition surface (7a) relative to the axial direction of the drive shaft (1).

15. 10. A drive element according to claim 1, characterized in that the drive contour (5, 9) has five or six drive faces (6, 10).

16. 10. A drive element according to any one of the preceding claims, characterized in that the drive element (1) is a screw, and the drive contour (5) is formed in the screw head (4).

17. Driving element according to any one of the preceding claims, characterized in that the driving element (8) is a screw bit.

18. A method for non-rotatably connecting two components, one of which is designed as a drive element (8) with an outer drive profile (9) and the other as a drive element (1) with an inner drive profile (5), in which the drive profiles (5, 9) of the two components (1, 8) are interdigitated axially with one another to produce a non-rotatable connection between the two components (1, 8), The two components are a drive element (1, 8) according to any one of the preceding claims, characterized in that the inner drive contour (5) has a transition point (P １ ) is located at the inner circle diameter Di of the outer driving contour (9) change point (P １ ) is designed to be larger than the diameter Di of the inner circle on which it is located, 1. A method according to claim 1, wherein the drive contours (5, 9) of the drive elements (1, 8) are selected to complement each other in such a way that when the drive contours (5, 9) are axially inserted into each other, the drive surfaces (6, 10) of the two components (1, 8) come into surface contact with each other, so that a friction and / or clamping connection is formed between the two components (1, 8) which axially connects them to each other.

19. The drive contours (5, 9) of the two components (1, 8) are aligned along the respective contour axes (P Ｉ , P Ａ 19. The method according to claim 18, characterized in that the drive faces (6, 10) are inclined relative to the drive shaft (10).

20. The driving surface (6) of the inner driving profile (5) is aligned with the profile axis (P Ｉ ) with respect to the inclination angle α Ｉ However, the driving surface (10) of the outer driving profile (9) is aligned with the profile axis (P Ａ ) with respect to the inclination angle α Ａ 20. The method for non-rotatably connecting two components according to claim 19, wherein the connecting member is greater than .

21. The inclination angle α of the driving surface (6) of the inner driving contour (5) Ｉ is 3±0.2 degrees and the inclination angle α of the driving surface (10) of the outer driving contour (9) Ａ is 1.15±0.15 degrees, or the inclination angle α of the driving surface (6) of the inner driving contour (5) ｉ is 2±0.2 degrees and the inclination angle α of the driving surface (10) of the outer driving contour (6) Ａ 21. The method for non-rotatably connecting two components according to claim 20, characterized in that the angle is 1.15±0.15 degrees.

22. The transition surfaces (7, 7a) between adjacent drive faces (6, 10) of the drive contours (5, 9) of the two components (1, 8) are aligned along the respective contour axes (P Ｉ , P Ａ ) and the profile axis (P Ｉ ) with respect to the inclination angle β Ｉ The transition surface (7a) of the outer driving profile (9) is aligned with the profile axis (P Ｉ ) with respect to the inclination angle (β Ａ ) to the ratio β Ｉ / β Ａ The method for non-rotatably connecting two components according to any one of claims 18 to 21, characterized in that is 5 or more.

23. Method according to any one of claims 18 to 22, characterized in that drive elements (1, 8) are used, the diameter Da of the outer circle on which the drive surface (6) of the inner drive contour (5) is located being smaller than the diameter Da of the outer circle on which the drive surface (10) of the outer drive contour (9) is located.

24. Method according to any one of claims 18 to 23, characterised in that the drive faces (6, 10) of the two components are in surface contact with each other over at least 25% of their total circumferential extent.

25. The two components are aligned along a contour axis (P Ｉ , P Ａ 25. The method according to claim 18, characterized in that the driving surfaces (6, 10) are contacted on either side of a longitudinally extending central plane that includes a center line (11) and a center line (12).

26. Method according to any one of claims 18 to 25, characterized in that the inner driving profile (5) and the outer driving profile (9) are designed to be non-contact in the area of ​​the transition surfaces (7, 7a).

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