Nut

Translation of description of equivalent WO 2013113871 A2

MOTHER

p0002The invention relates to a nut comprising provided a in the region of a bore with an internal thread or imageable nut body having a polygonal portion having a polygonal outer contour, which has a hand edge portions and the other part located between the edge portions of key areas, which extend in conforming to standards extending key face planes.

p0003Such nuts are common, known from the prior art multi-head nuts, wherein the position and orientation and course of key areas, for example, normative bases, for example, DIN EN 1661, 1663, 1664, 1667, DIN EN ISO 4032-4036, ISO 8673-8675 , DIN EN ISO 7040 - 7042, DIN EN ISO 7719, DIN EN ISO 10511-10513 and DIN EN ISO 4759-1 arise.

p0004The nuts can already be provided with an internal thread, or be provided with a bore in which an internal thread, self-forming or self-tapping screws produced when screwing.

p0005In such nuts is a need to reduce the weight in advantageous possible mechanical performance characteristics thereof.

p0006The invention is therefore based on the object to improve a mother of the generic type such that this best possible mechanical properties with minimum weight.

p0007This object is in a mother of the aforementioned type

p0008inventively achieved in that the nut body starting in having several from the respective key area levels in the mother's body in the direction of the bore extending recesses. The advantage of the invention is the fact that a material saving and thus a reduction in weight can be achieved by extending into the nut body into recesses without affecting the mechanical properties of the nut body negatively.

p0009Regarding the arrangement of the recesses, no further details have been made here.

p0010So, an advantageous solution provides that each starting from opposing key face planes recesses extending into the nut body into it.

p0011In the simplest case, this would be two opposing key face planes, starting from which there are recesses extending into the nut body into it.

p0012However, it can also be a number of key face planes, starting from which there are recesses extending into the nut body into it.

p0013Even more advantageous, however, is the weight saving when starting extends into each of the key surface plane of the polygonal section a recess in the nut body.

p0014Regarding the extent of the recess in the nut body into no details have been given in connection with the embodiments described so far.

p0015So, an advantageous solution provides that the recess extends from the respective key area plane to an internal thread stabilizing enclosing thread carrier jacket, that is, that the recess extends only up to the thread carrier jacket, but not beyond it. The thread carrier jacket is a closed circumferential area of ​​the parent body, stabilizing surrounds the internal thread and ensures that the internal thread is not deformed at a stress by a screwed into this threaded bolts or screwed into this screw over a defined amount, in particular widens and hence its loses for the force and / or snapshot required shape or form resistance.

p0016it is particularly advantageous when the thread carrier shell of an outer diameter of the internal thread having starting a minimum radial thickness which is at least 0.05 times the outer diameter of the internal thread.

p0017Here, a minimum radial thickness is measured at the thinnest in the radial direction instead of the thread carrier shell, which is an integral part of the nut body in particular and at each point having the minimum radial thickness so that the minimum radial thickness, the stability of the thread carrier casing is set.

p0018It can be invariant, the minimum radial thickness of the thread carrier shell towards the center line.

p0019but it is also conceivable that the minimum radial thickness of the threaded shell carrier is variable in the direction of the central axis.

p0020In principle it is in the inventive solution conceivable for the nut body such that it extends between a first end and a second end face while each of the faces is adapted a body or element for fixing thereof by means of the mother to apply. However, to optimize the parent invention in view of the introduction of force into the nut body is preferably provided that the mother body has a as a side formed with a pressure surface first end and the print side facing away from second end face, between which extends the nut body.

p0021This solution has the advantage that for the mother to be optimized to the effect that in the pressure side of the occurring forces are applied when applying a body or an element with the nut on the nut body and be absorbed by it, while to go in the second end face thereof is that it does not undergo any direct application of force.

p0022With such a mother, for example, provided that the recess extends to the second end face, there is not expected to force loading of the nut body in the second end face, so that the forces occurring are lowest in the second end face.

p0023Further, it is possible to form the nut body such that the recess extends up to the pressure side, wherein the shape of the pressure side of strength must be sufficiently large in this case that they provided the

p0024Loads receives.

p0025In a further embodiment it is provided that the recess extends only over a part section of the extension of the nut body from the one end side to the other end side, so that the recess does not reach the other end face.

p0026Another advantageous solution provides that the recess extends up to a provided on the pressure side pressure soil and thus ends at the push back, so that the nut body undergoes additional stability in the pressure side by the push back. Alternatively or additionally, it is also provided that the recess to a provided on the pressure side of the pressure flange extends which extends radially beyond the polygonal portion addition.

p0027Also with regard to the minimum thickness of the thread carrier shell, it is advantageous in the presence of a pressure side of the nut body, when the minimum radial thickness of the thread carrier shell in the pressure side is at least as large as in the second end face.

p0028Is even more advantageous if the minimum radial thickness of the thread carrier shell in the pressure side is greater than in the second end face, as higher peripheral loads the thread carrier jacket formed in the pressure side by the force of interaction between pressure side and thread, as in the second end face, characterized so that the nut body with respect to the loads which occur can be optimized.

p0029it when the thread carrier jacket to the pressure side has with increasing extension of the second end face an increasing minimum thickness as this the starting increasing from the second end face of circumferential stresses of thread carrier jacket optimal account can be taken by the force of interaction between pressure side and internal thread is particularly favorable.

p0030Regarding the formation of the key areas were so far no further details.

p0031So, an advantageous solution that are in each key area plane at opposite edge portions subsequent key surface areas between which the respective recess. That is, the respective recess divides at least two key surface areas, which each extend following the edge areas and are at least partially separated from one another by the recess together forming the key face.

p0032With regard to the minimum extension of the key surface areas in a transverse direction between said edge regions, wherein the transverse direction is parallel to a direction of spacing of the edge portions, it is preferably provided that in each plane perpendicular to a central axis of the internal thread cross-sectional plane through the polygonal portion of the sum of the extension of the key surface areas in a transverse direction between any two consecutive edge regions at least 10%, more preferably at least 15%, especially at least 20%, of a distance separating the edge portions in the transverse direction.

p0033That is, the layer formed from the two key surface areas

p0034Key area was reduced to ten percent of the extension in the transverse direction relative to the extension of the key area in the absence of the recess.

p0035Basically, it is conceivable to select the extension of each individual key surface areas different, the sum of the extensions is 10% of the distance of the edge areas.

p0036This would be possible if an optimized adaptation of the key surface areas of the strains of the nut body when

p0037Tightening or loosening to occur.

p0038For example, it is in a nut body which is to be screwed primarily and is subsequently not usually solved, conceivable that two key surface areas separate roads to choose Edlich, for example, the when tightening the nut body wider perform increasingly loaded key area in the transverse direction, as the less loaded key area.

p0039A simplified embodiment provides that the two spanner flat portions in the transverse direction is approximately the same extension, preferably has the same extension in the transverse direction.

p0040Regarding the formation of the recesses themselves were so far no further details.

p0041The recesses could regard to their extent to the central axis have parallel radially and any desired shapes, that is, having free-form surfaces.

p0042Further, each of the recesses of the nut body differ in their shape and or dimension of the other recesses.

p0043However, for example, are respectively formed on opposite sides of the

p0044Mother body recesses arranged identically configured.

p0045In particular, nothing has been performed over the cross sectional form of the embodiments.

p0046So, an advantageous solution, that the recesses have in each case a perpendicular to a center axis of the internal thread extends through the polygonal portion cross-sectional plane the same cross-sectional shape.

p0047For example, it is conceivable that the cross sectional shape of the recesses is U-like in the respective cross-sectional plane. but it is also conceivable, when the cross sectional shape of the recesses are approximated in the respective cross-sectional plane of a circular segment-like cross-sectional shape or a rectangular or V-shaped cross-sectional shape.

p0048One advantageous solution provides that said recesses have a cross sectional shape which is determined by a bottom portion and adjoining the base region, extending transversely to the respective key surface plane side wall portions.

p0049In this example, it is conceivable that the recesses are formed so that they have a cross sectional shape which is determined by a concave and connects the side wall portions of the floor area.

p0050As regards the variation of the cross-sectional shape of the recess were so far no further details.

p0051Thus, it is provided that the recess parallel to the central axis of constant or varying cross-sectional shape with one of the extension in one direction.

p0052In particular, it is conceivable, for example, which is a distance of the bottom portion of a center axis of the internal thread on the extension of the recess in the direction of the central axis is substantially constant.

p0053Alternatively, but it is also conceivable that the bottom portion with the extension in the direction of the center axis has a varying distance from the central axis.

p0054For example, it is provided that the recess is provided with a sloping floor to the center axis region extending for example to the respective key area plane. Alternatively or in addition to the above described features of the inventive solution, the aforementioned object is achieved by a nut of the type described above according to the invention that the internal thread produced to form the mother as locknut as a standard curve corresponding internal thread, however, by plastic deformation of the nut body is formed by the standard deviation curve.

p0055The advantage of the invention is the fact that only by plastic deformation of the nut body, the possibility to establish a lock nut, which thus has optimum mechanical properties with minimum weight, since no additional elements are provided on the nut body, that of for achieving for a

p0056Locknut required clamping torque are usually necessary.

p0057Thus, the mother of the present invention also has improved or optimized mechanical properties combined with minimum weight.

p0058The required for the function of the invention as a locknut defined clamping torque can be achieved, in particular, that the internal thread due to the deformation of the nut body of a standard course deviating varying radial distances from the center axis and / or deviate from a standard course of distance courses or

p0059has threads so that a screwing in a threaded bolt or screw the plastically deformed nut body again

p0060elastoplastically deformed toward the standard dimensions, whereby the clamping torque.

p0061In the simplest case provision is made such that the internal thread is formed out of round due to the plastic deformation of the nut body relative to the central axis. Another advantageous solution provides that the internal thread with respect to the central axis equiangularly arranged deformed

p0062having threaded regions whose distance is reduced relative from the central axis to a standard curve, that is, that their distance is less than at a sub-standard training.

p0063In the simplest case is a pair of oppositely threaded portions deformed, the distance is reduced from the central axis.

p0064In a further advantageous embodiment may be, the required defined for the lock nut of the present invention clamping torque reach conveniently characterized, that the internal thread has a plurality of twofold or mehrzähliger symmetry with respect to the center axis arranged deformed thread regions whose distance is reduced in relation to a standard curve.

p0065For example, multiple pairs with respect to the central axis has opposed deformed thread regions, whose distance is reduced from the standard size, or for example, three or more evenly distributed circumferentially deformed threaded portions are provided, the distance is reduced relative to a standard curve.

p0066A particularly advantageous design of the mother of the invention provides that the nut body is plastically deformed by a force acting on each other with respect to the central axis opposite edge portions.

p0067Alternatively, provides another solution, that the nut body is plastically deformed by a force acting on each other with respect to the central axis opposite bottom areas and / or side wall portions of the recesses. It is particularly favorable when the force is applied in an upper portion of polygonal section, as the mother body is plastically deformable, preferably in the upper region with less force than the same in the area of ​​a printed page.

p0068Another alternative solution provides that the nut body is plastically deformed by a force acting in the region of an outer edge of the second end face.

p0069In particular, a solution provides that the internal thread has deformed threaded areas with one of a standard curve deviating course, and, for example, the slope of the course is changed with respect to a standard pitch, that is, for example, a distance of the

p0070is threads from each larger or smaller than in a sub-standard figure.

p0071Again, a further advantageous solution provides that the nut body is deformed by a force acting on one of the end faces, and in particular the second end faces, with a component in the direction parallel to the central axis plastically.

p0072In cases in which an outer edge of the second end face of a force is applied directly or indirectly a force is applied to the second end face, preferably a directly subsequent to the second end face thread is deviating plastically deformed by standard course to achieve the required clamping torque.

p0073Regarding the nature of the action of the deformation forces were so far no further details.

p0074So, an advantageous solution provides that the nut body is plastically deformed by punctiform acting deformation forces. Alternatively or additionally, a further solution is that the

p0075Mother body is plastically deformed by linearly acting deformation forces.

p0076Alternatively or in addition, a further expedient solution, that the nut body is plastically deformed by two-dimensionally acting deformation forces.

p0077Regarding the range of deformation of the nut body were so far no further details.

p0078So, an advantageous solution provides that the nut body is primarily deformed globally.

p0079The term global deformed must be understood that a total of the parent body, preferably the polygonal portion of the female body, has a shape that is different relative to a mold at standard-compliant production of the standard curves.

p0080That is, the nut body and in particular the polygonal portion are of the same total deformed.

p0081Alternatively or additionally, it is also likewise possible that the

p0082Mother body is deformed primarily locally.

p0083Under a priority local deformation must be understood that this only locally, ie in the area of ​​the nut body in which it is introduced, impact and therefore does not affect such that the parent body itself or the polygonal portion thereof significantly change its basic shape. As to the material, from the mother's body was made, no details have been given in conjunction with the preceding explanations concerning the inventive solutions.

p0084A mother with at least one of the above-described characteristics can be made "material Smart" from metal, such as steel, ceramic, glass, polymer, composite material or a.

p0085In particular, alternatively or additionally, the object mentioned in the present invention also achieved on the characteristics of the embodiments and versions described thus far, that the nut body is made of steel with a bainitic or ferrite-pearlite microstructure.

p0086A steel having such a structure makes it possible to give the best possible mechanical properties with minimum weight of the nuts, and in particular allows such a structure, a particularly cost-effective production of such a mother.

p0087So, an expedient solution that the bainitic or ferritic-perlite structure having a carbon content of 0.25 wt% or more.

p0088Such carbon content has proved a structure of a mother with optimum mechanical properties as appropriate.

p0089The strength properties of such a bainitic or ferritic-pearlitic structure can be inventively boost that the bainitic or ferritic-perlite structure having through excretions of micro alloying elements increased strength properties.

p0090The shares of such micro-alloying elements are very low.

p0091So, an advantageous solution provides that the bainitic or ferritic-perlite structure at least 0.05 wt% micro-alloying elements having. A particularly expedient solution provides that the bainitic or ferritic-perlite structure at least 0.1 wt% micro-alloying elements having.

p0092In this context, no further details on such micro-alloying elements were made.

p0093Such micro-alloying elements are, for example, Nb, Va, Ti.

p0094Another advantageous solution provides that the bainitic or ferritic-perlite structure having by thermomechanical pretreatment increased strength properties.

p0095These are thermo-mechanical pretreatment steps, which are known from the prior art.

p0096Furthermore, an advantageous solution provides that the bainitic or ferritic-pearlitic structure has a solid solution strengthening by, for example, silicon and / or manganese.

p0097Further, it is possible to form the desired strength of the nut body to achieve particular in the region of the threaded shell by a carrier nachgeschalte heat treatment.

p0098It is particularly advantageous if the desired shape stability of the thread carrier shell can be achieved by cold forming of bainitic or ferritic-pearlitic structures and some regions, production of high dislocation densities without downstream heat treatment, since this method allows significant savings in production costs. An expedient embodiment of a mother provides that the bainitic or ferritic-perlite structure by controlling the microstructure conversion and by forming a hardness in the range 100-370 HV, better 110-360 HV for standard threads and a hardness in the range 170-370 HV, even better 180 to 360 HV for fine threads in the thread carrier jacket thermal aftertreatment is required without.

p0099In addition, the above-mentioned object is also achieved by a method according to any one of claims 48 to 70th

p0100Further features and advantages are subject of the following

p0101Description and the drawings of several embodiments.

p0102In the drawings:

p0103Fig. 1 is a perspective view of a first embodiment of a nut according to the invention;

p0104Fig. 2 is a plan view of the nut in the direction of arrow A in Fig. 1;

p0105Fig. 3 shows a section along line 3-3 in Fig. 2;

p0106Fig. 4 is a view similar to FIG. 1 of a second embodiment of a nut according to the invention;

p0107Fig. 5 is a view similar to FIG. 2 of the second embodiment of the nut according to the invention;

p0108Fig. 6 is a view similar to FIG. 3 of the second embodiment of the nut according to the invention; Fig. 7 is a view similar to FIG. 1 of a third embodiment of the nut according to the invention;

p0109Fig. 8 is a view similar to FIG. 2 of the third embodiment of the nut according to the invention;

p0110Figure 9 is an illustration similar to FIG .3 of the third embodiment of the nut according to the invention.

p0111Fig. 10 is a view similar to FIG. 1 of a fourth embodiment of the nut according to the invention;

p0112FIG. 11 is a view similar to FIG. 2 of the fourth embodiment of the nut according to the invention;

p0113Fig. 12 is an illustration similar to FIG. 3 of the fourth embodiment of the nut according to the invention;

p0114FIG. 13 is an illustration similar to FIG. 1 of a fifth embodiment of the nut according to the invention;

p0115FIG. 14 is an illustration similar to FIG. 2 of the fifth embodiment of the nut according to the invention;

p0116FIG. 15 is a view similar to FIG. 3 of the fifth embodiment of the nut according to the invention;

p0117FIG. 16 is a view similar to FIG. 1 of a sixth embodiment of the nut according to the invention;

p0118FIG. 17 is a view similar to FIG. 2 of the sixth embodiment of the nut according to the invention; FIG. 18 is an illustration similar to FIG. 3 of the sixth embodiment of the nut according to the invention;

p0119FIG. 19 is an illustration similar to FIG. 1 of a seventh embodiment of the nut according to the invention;

p0120FIG. 20 is a view similar to Figure 2 of the seventh embodiment of the parent invention.

p0121FIG. 21 is a view similar to FIG. 3 of the seventh embodiment of the nut according to the invention;

p0122FIG. 22 is a view similar to FIG. 1 of an eighth embodiment of the nut according to the invention;

p0123FIG. 23 is a view similar to Figure 2 of the eighth embodiment of the parent invention.

p0124FIG. 24 is a view similar to Figure 3 of the eighth embodiment of the parent invention.

p0125FIG. 25 is an illustration similar to FIG. 11 of the fourth embodiment of a nut formed as a first version of a lock nut according to the invention;

p0126FIG. 26 is an illustration similar to FIG. 12 of the first version of a

p0127Locknut invention;

p0128FIG. 27 is a view similar to FIG. 25 of a second version of a

p0129Locknut invention;

p0130FIG. 28 is an illustration similar to FIG. 26 of the second version of the

p0131Locknut invention; FIG. 29 is an illustration similar to FIG. 25 to a third version of a lock nut according to the invention;

p0132FIG. 30 is a view similar to FIG. 26 of the third version of a

p0133Locknut invention;

p0134FIG. 31 is a view similar to FIG. 25 a fourth version of a

p0135Locknut invention;

p0136FIG. 32 is an illustration similar to FIG. 26 of the third version of a

p0137Locknut invention;

p0138FIG. 33 is a view similar to FIG. 25 a fifth version of a

p0139Locknut invention;

p0140FIG. 34 is an illustration similar to FIG. 26 of the fifth version of the lock nut according to the invention;

p0141FIG. 35 is an illustration similar to FIG. 25 a sixth version of a

p0142Locknut invention;

p0143FIG. 36 is a view similar to FIG. 26 of the sixth version of the

p0144Locknut invention;

p0145FIG. 37 is a view similar to FIG. 25 a seventh version of

p0146Locknut invention and

p0147FIG. 38 is an illustration similar to FIG. 26 of the seventh version of the lock nut according to the invention;

p0148Appendix 1 is a compilation of steels with an inventive precipitation hardening ferrite-pearlite microstructure and Appendix 2 is a compilation of properties and compositions of a steel of an inventive Removing divorce curing ferrite-pearlite microstructure with good working properties.

p0149A in Fig. 1 to 3 shown first embodiment of a designated as a whole with 10 mother of the invention comprises a nut body 12 which along a central axis 14 between a first end face 16 and a second end face 18 extends.

p0150The nut body 12 is penetrated by a parallel to the central axis 14 extending from the first end face 16 to the second end 18 threaded bore 20 which has an internal thread 22 having threads 24 extending from a predetermined by an inner contour of the threads 24 core hole diameter DK of up to a predetermined by an outer contour of the threads 24 nominal diameter or outer diameter DA in the nut body 12 extend into, and which from a the threads 24 surrounding thread carrier shell 30, the portion of the nut body 12 is to be worn.

p0151The cylindrical and an integral part of the nut body 12 Performing threaded support sleeve 30 gives the threads 24 the necessary stability to an evasion of the same, in the radial and / or axially to the central axis 14 through its closed in an orbiting around the central axis 14 circumferentially 32 wall 34 wherein the wall 34 of the threaded support sleeve 30, which, starting from the outside diameter DA in the radial direction to the central axis 14 has a thickness which DG

p0152at least 0.05 times the outside diameter DA of the internal thread 22 corresponding to the threads 24 to under a load by a screwed with a corresponding external thread 35 into the threads 24 threaded bolt 36 against movement in the radial and / or axial direction to the center axis 14 stabilize. The nut body 12 is in a polygonal section 38 which extends in the first embodiment of the first face 16 to the second end 18, provided with a polygonal outer contour 40, which lying by edge portions 42 and between the edge portions 42

p0153Key areas is 44, said another relative to the central axis 44 being mutually 14 opposing key surfaces parallel and at a distance, by a customary for the mother 10 standard, for example DIN EN 1661, 1663, 1664, 1667, DIN EN ISO 4032-4036 , DIN EN ISO 8673 - 8675, DIN EN ISO 7040 - 7042, DIN EN ISO 7719, DIN EN ISO 10511-10513 and DIN EN ISO 4759-1, is defined so that the outer contour 40 each having an even number of key areas 44 in pairs parallel to each other, the edge portions 42 each represent a transition between successive in the direction of circulation 32 key areas 44th

p0154In the illustrated nut 10 the polygonal outer contour 40, designed as a hexagon with a cross-sectional shape of a regular hexagon in accordance with "Table book metal", 44th edition, published by Europa Lehrmittel, page 59, so six edge portions 42 and six key areas 44 between each successive edge areas 42 are in the key face planes 46, wherein the key face planes 46 are each parallel to the central axis 14 and oriented so that each opposing key face planes 46 are parallel to therebetween lying central axis 14 and parallel to each other.

p0155In the inventive nut body 12 according to the first embodiment, the key surfaces 44 extend in a plane in the respective key area plane 46 transverse direction 48 between the consecutive edge regions 42 are not contiguous and closed in the key face planes 46 but the flats 44 are formed by key surface areas 52 and 54, which lie in the key face planes 46, wherein preferably the key surface areas 52 and 54 42 respectively extend further to one of the edge portions in the direction of the other edge portion 42, but not into each other.

p0156Rather, between the key surface areas 52 and 54 a, starting from the respective key area plane 46 into the nut body 12 into 14 extending towards the central axis of the recess 60, which, as well as on the key surface regions 52 and 54 then, extending transversely to these side wall portions 62 and 64 a the sidewall areas 62 and 64 connecting bottom portion 66 having formed concave and so far into the nut body 12 that it touches the thread carrier jacket 30th

p0157Preferably, the bottom portion 66 is curved in such a concave, that it passes into the likewise concavely arched side wall portions 62 and 64, so that the recess 60 in a plane perpendicular to the central axis 14 extends, in Fig. 2 incremental level corresponding cross-sectional plane QE a

p0158U-shaped cross-sectional shape, preferably even an arc of a circle segment approximating the cross-sectional shape.

p0159In the nut body 12 according to the invention the edge portions 42, the key surface areas 52 and 54 and the side wall portions 62 and 64 and to the part of the bottom portion 66 of the outer contour of the carriers 70 are

p0160Nut body 12 is supported, which are also an integral part of the nut body 12 and therefore also formed integrally with the threaded support sleeve 30 and, starting in each case radially to the central axis 14 extending from the threaded support sleeve 30 to the outside and are responsible for the above-mentioned areas. Starting from the edge regions 42, the key surface 44 forming key surface areas 52 and 54 extend in the respective perpendicular to the central axis 14 extending transverse plane QE, for example, the drawing plane in FIG. 2, a width B₅₂ and a width B₅₄ in a transverse direction 48, which together amount to at least 10% of a distance AK adjacent edge portions 42 so that, conversely, the recess 60 a in the direction perpendicular to the central axis 14 extending transverse plane QE a width BA having the maximum of 90% of the distance AK of the consecutive edge portions 42 is.

p0161Into conformity trained only by the key surface areas 52 and 54 and the edge portions defined 42 and in these areas outside contour 40 is identical with the first embodiment in the area of ​​the polygonal section 38 of the nut body 12 in each perpendicular to the central axis 14 extending transverse plane QE, so that at the polygonal section can attack 38 standard provided for such standardized polygonal tools with the respective wrench width SW to screw the nut 10 with the internal thread 22 on a threaded bolt and to tighten.

p0162In the in Fig. 1 illustrated embodiment, a nut 10 according to the invention extends the nut body 12 does not have the polygonal section 38 also, that is, the nut body 12 is only formed by the polygonal section 38 so that, for example, the end face 16 a pressure surface is 82, which enables festzuschraubendes element or a festzuschraubender body is to act upon.

p0163Further, the cross-sectional shape of the nut body 12 perpendicular to the central axis 14 extending in any throughout the polygonal portion 38 cross-sectional plane QE is the same, so that it has the identical cross-sectional shape over the entire extension of the nut body between the first end face 16 and the second end face 18th Thus, in the first embodiment, a total of the nut body 12 is formed so that this 22 has a six-fold rotational symmetry about the central axis 14 to the course of the internal thread.

p0164If acted upon by the pressure side 82 with a pressure surface 84 an item, so are the near the pressure side 82 acts in the circumferential direction 32 in the thread carrier jacket 30 forces acting in the sense of a widening of the thread carrier shell 30, maximum and decrease with increasing distance from the pressure side 82 , so that the thread carrier jacket is 30 in total to be dimensioned such that the radial thickness DG is sufficient from the wall 34 to receive the 12 acting on the pressure side 82 at the intended load on the nut body following load spectrum of forces and moments (Fig. 3).

p0165In a second embodiment, illustrated in FIGS. 4-6, the polygonal portion 38 extends also over the entire nut body 12 'of the first end face 16 to the second end 18 along the central axis 14, however, the recess 60' extends from the second end face 18 is not until the first end face 16, but up to an integral part of the nut body 12 'print depicting floor 90 in the region of the pressure side 82' which extends between successive edge areas 42 radially to the central axis 14 to the key face planes 46, so that a key area 56 is formed in the region of the pressure base 90, which extends continuously in the transverse direction 48 between the edge regions 42nd

p0166In the second embodiment, 'thus from the second end face 18 toward the first face 16 only until the pressure bottom 90, and thus over a portion TA of the extension of the nut body 12', the recess 60 extends in the direction of the central axis 14 and ends with a

p0167End wall 92, which is aligned parallel to a perpendicular to the central axis 14 extending transverse plane QE and represents a pressure face 84 'opposite upper side of the soil pressure 90th Because of the pressure bottom 90 radially extends further in the second embodiment in the pressure side 82 'outwardly, the radial thickness of DG in the first end face 16 is 1 of the thread carrier belt 30 is greater than in the second end face, in which the radial thickness DG 2 of the thread carrier shell 30 is limited by the bottom portion 66 'of the recess 60'.

p0168Thus, the thread carrier shell 30 'in the pressure side 82' has a greater radial thickness DG1 and thus gives the internal thread 22 in

p0169the same region of the pressure side 82 'a greater stability against radial and / or axial expansion.

p0170The push back 90 thus takes place in the pressure side 82 'an additional stiffening of the thread carrier belt 30 to an expansion in the circumferential direction 32nd

p0171In addition, effected by the pressure bottom 90, a stiffening of the outer contour of the carrier 70 relative to one another so that thereby a total of the nut body 12 'is able to take up large loads.

p0172In a third embodiment, shown in Figs. 7 to 9, those parts which are identical to those of the first embodiment, are also provided with the same reference numerals, so can be that fully incorporated to the comments on the preceding embodiments reference.

p0173Unlike the second embodiment, the third embodiment in the range of pressure bottom 90 a radially over the polygonal body 38 projecting pressure flange is still 100 provided that with respect to the central axis 14 a circular outer contour 102, such that in the region of the pressure side 82 "of the nut body an enlarged pressure surface 84 "is present, the cross-sectional area of ​​the polygonal portion 38, which in this embodiment parallel to the central axis 14 raises in direction to the pressure flange 100, projects radially beyond. The polygonal section 38 is similarly formed as in the second embodiment, since the recess 60 'in the same manner as in the second embodiment from the second end face 18 toward the first end face 16 "only to push back 90 extends and in the area of ​​pressure soil 90 ends with the final wall 92nd

p0174The end wall 92 extends in the same manner as described in the second embodiment, parallel to the perpendicular to the central axis 14 extending cross-sectional planes QE.

p0175In a fourth embodiment, shown in FIGS. 10, 11 and 12 of the nut body 12 '' so far found as the same reference numerals used, formed identically as in the preceding embodiments, so that the designs can be made in full at the moment.

p0176In particular, the nut body comprising 12 ' "the polygonal portion 38, with the pressure bottom 90, and the pressure flange 100 according to the third embodiment.

p0177In contrast to the third embodiment, however, runs the

p0178End wall 92 " 'of the recess 60"' is not parallel to a transverse plane QE, but at an angle α to it, and is therefore, starting from the bottom portion 66 " 'of the recess 60'" with increasing radial

p0179Extension inclined with respect to the central axis 14 to the outside so that the end wall 92 '' radially falls outwards to the pressure flange 100 down. In a fifth embodiment, illustrated in FIGS. 13 to 15, those parts that the preceding embodiments are identical to those that are also provided with the same reference numerals and so with respect to the description thereof will be made in full to the comments on the preceding embodiments reference can.

p0180In contrast to the preceding embodiments is the fifth embodiment of the bottom portion 66 '' of the recesses 60 "" designed, that it has a maximum depth at the second end 18, that is a maximum distance from the key surface plane 46 with it increasing extension of the bottom portion 66 "" is increasingly reduced toward the first end face 16, that is, the bottom portion 66 "" a total of at an acute angle to the central axis 14 extends and upon reaching the pressure base 90 also reaches the key surface plane 46th

p0181An extension of the recess 60 " 'of the second end face 18 toward the first end face 16 is, for example, limited to a section of TA of the nut body 12" ", the extension of which less than half of the extension of the nut body 12" "of the first end face 16 is at this second face 18th

p0182In this embodiment, therefore, the radial thickness Dg of the wall is also 34 "" of the threaded support sleeve 30 "" is already at about half the extension of the nut body 12 of the second end face 18 to the first end face 16 is significantly greater than in the region of the second end face 18 and receives further to the radial thickness DG 1 in the first end face 16 and the present in this area compression flange 100th In a sixth embodiment, illustrated in FIGS. 16 to 18, is in contrast to the fifth embodiment of the bottom portion 66 "" 'of the recess 60 ""' is not formed straight running, but extends from the second end face 18 toward the first end face 16 of a concave shape until reaching the respective key surface plane 46th

p0183Incidentally, the sixth embodiment is configured in the same manner as the fifth embodiment, so that can be taken for further details in full to the explanations concerning the fifth embodiment and the preceding embodiments reference.

p0184In a seventh embodiment, illustrated in FIGS. 19 to 21, the recesses 60 are "" "so formed that they do not have a roughly U-shaped cross section, as shown in connection with the embodiments described so far, but an approximately rectangular shaped cross-section, wherein the side wall portions 62" "" and 64 "" "initially be approximately perpendicular to the key surface plane 46 into the nut body 12" "" in extending and then "pass, which up to the rounded transitions to the side wall portions 62" with slight curves in the bottom portion 66 "" "" and 64 " "" running in the transverse direction 48 approximately parallel to the key surface plane 46 between the side wall portions 62 and 64 and also from the second face 18 with increasing extent in the direction parallel to the central axis 14 with respect to the central axis 14 extends outwardly and consequently to the pressure flange 100 toward radially falls outwards.

p0185Thus, the bottom portion 66 "" extending ", starting from the second end face 18 of the nut body in the direction of the first end face 16 at an acute angle A" "" to the central axis 14 to the first end face 16 to slope radially outwardly and thus achieved by the extension over the part TA key surface plane 46th Incidentally, the other elements of the nut 10 according to the invention are in the seventh embodiment so far as those with which the above embodiments are identical, with the same reference characters, so can be that fully incorporated to the comments on the preceding embodiments reference.

p0186In an eighth embodiment, illustrated in FIGS. 22 to 24, the recess 60 "" " 'irregularly shaped, so that for example, the bottom portion 66" ""' is partially curled irregularly, both in the direction of extension of the second end face 18 toward the first end face 16 of the nut body 12 " " '" and also in the cross direction 48 between the edge portions 42, so that both the whole of the side wall portions 62 "" "' and 64" "" 'in conjunction with the bottom portion 66 "" "' any irregular shape may have, wherein the maximum distance of the bottom portion 66 "" " 'of the respective key area plane 46 the radial thickness DG of the wall 34 of the thread carrier shell 30" ""' sets.

p0187The recesses 60 '' can '' of the second end 18 extending toward the first end face 16 to the pressure flange 100, but optionally also comprise only an extension over a portion of TA, so that between the respective recess 60 "" " 'and the pressure flange 100 yet in the formation of a pressure soil 90th

p0188In connection with all of the preceding embodiments, it is possible to carry out the parent invention than conventional mother, that is, as a mother whose internal thread onto the threaded bolt 36 is 22 possible smoothly screwed and in particular no clamping torque when screwing or unscrewing has thus had no captive has ,

p0189Alternatively, however, but it is also possible according to the invention the nuts 10, and in particular the nuts 10 in accordance with all embodiments described above, be designed as locking nuts 10S, that is, these Nuts in such a way that when screwing on the internal thread 22 of the threaded bolt 36, a clamping torque occurs, which prevents the mother may separate from the one screwed into position due to a prevailing collective load automatically, whereby the clamping torques preferably should be predetermined depending on the application.

p0190Based on the fourth above embodiment shown below different alternatively or additionally inventive possibilities are shown as polygonal nuts in general, but in particular also according to the first to eighth embodiments trained polygonal nuts, in a simple manner a defined clamping torque can be specified.

p0191In a first, in FIGS. 25 and 26 version of a nut according to the invention 10S, whose parent body 12 having the polygonal section 38, there is a deformation of the polygonal section 38 by the action of a point deformation force DKP, for example, on opposite edge portions 42, for example, only two opposing edge portions 42 of opposite outer contour beams 70 such that under deformation of the polygonal portion 38, plastic deformation of the inner thread 22 is carried out such that, for example, lying in the region of applied by the point-like acting deformation forces outer contour carrier 70 threaded portions GBD that face each other with respect to the central axis 14 opposite one another, a smaller distance AGD from one another, than outside the threaded portions GBD lying threaded portions GB, so that on screwing this nut 10S according to the first version of the deformed thread portions GBD whose distance AGD is less than specified by the standard, when the threaded bolt 36 with the external thread 35 into the internal thread 22 the internal thread 22 is expanded again to the dimension of the thread to be screwed bolt 36 by elasto-plastic deformation of the polygonal portion 38, so that the polygonal portion 38 having a global elastoplastic mold strength, primarily as a whole undergoes a shape change, and therefore elastoplastic thereto, a reaction force is generated, with which press the deformed thread portions GBD onto the external thread 35 of the threaded bolt to be screwed 36 and thus produce the desired clamping torque.

p0192Since in this embodiment generated by the point-like deformation forces DKP plastic deformation of the polygonal portion 38 is primarily a global deformation of the polygonal portion 38, the forces generated by the elasto-plastic change in shape, with which the deformed screw portions GBD act on the external thread 35 of the to be screwed the threaded bolt 36, also primarily determined by global elastoplastic form strength of the polygonal portion 38th

p0193The action of the dot-shaped deformation forces DKP on the edge portions 42 is preferably carried out in a close to the second end face 18 lying upper portion 112 of the edge portions 42, since in this upper portion 112 of the polygonal section 38 a larger plastic deformation than in the region of the pressure base 90 or the pressure flange 100 so that the path that the external thread 68 of the threaded bolt 36 travels through the deformed with minimal distance AGD range, is lower.

p0194Preferably, the upper portion 112 thereby extends from the second end face 18 to a maximum of one half of the extent of the recess 60 " 'of the second end face 18 toward the first face 16 or the pressure side 82, preferably up to one third of the extent of the recess 60 " 'from the second end face 18 toward the first end side sixteenth

p0195In the first version of the lock nut according to the invention the 10S punctiform deformation forces acting DKP are aligned so that they radially and transversely to the central axis 14, preferably perpendicular to this act. but there is also the possibility of acting punctiform

p0196Deformation forces DKP either to let interact with a component in the direction of the first end face 16, or both with a component toward the second end face 18th

p0197The point-like forces acting DKP left on the nut body 12 punctate pressure points 114, where the action can be seen.

p0198In a second version of an inventive locknut 10S ', shown in Fig. 27 and 28, the action of which takes place

p0199not deformation forces in the form of point-like acting

p0200Deformation forces DKP, but acting in the form of Iinienförmig deformation forces DKL on the edge portions 42 in the upper section 112, which is also similar to lead to deformations of the polygonal section 38 the manner described in connection with the first version, which applied to the Iinienförmig deformation forces DKL also in essentially there is a deformation of the polygonal section 38 as a whole.

p0201In the same way as in the first version of the Iinienförmig acting deformation forces DKL may be two pairs with respect to the central axis 14 oppositely acting deformation forces DKL or more preferably each at regular angular intervals with respect to the central axis 14 disposed acting deformation forces DKL, wherein approximately similar deformation of the polygonal section 38 occur as in the first version and the deformation forces DKL line- shaped bruises 116 on the nut body 12 behind.

p0202acting also in the use of deformation forces Iinienförmig DKL according to the second version, the deformation forces acting Iinienförmig DKL directed so that they extend transversely to the central axis 14, for example perpendicular to this. but there is also the possibility of the linearly acting

p0203either to allow both interact with a component in the direction of the first end face 16, or both with a component toward the second end 18 deformation forces DKL.

p0204In a third version of a lock nut, shown in FIGS. 29 and 30 according to the invention a nut body will also be 12 used in accordance with the fourth embodiment and there is an effect not in this case in the region of the outer contour of the carrier 70, but in the base area 66 '' of the recesses 60 " ', wherein in the third version also punctiform acting deformation forces DKP be used in the upper part 112, which primarily lead to a deformation of the point-shaped pressure points 114 adjacent portions of the threaded support sleeve 30 and thus produce deformed threaded portions GBD ", the deformation is more localized as also already the threaded support sleeve 30 as opposed to the outer contour of carriers 70 undergoes a primarily local elasto-plastic deformation due to a smaller thickness, which is also in a local elasto-plastic deformation of the internal thread thus leads to 22 and to a localized deformed thread portion GBD ".

p0205When screwing of such a lock nut 10S acting force generated by the elasto-plastic deformation "according to the third version of the external thread 35 of a threaded bolt 36 on the deformed screw portions GBD is" generated in that primarily the local plastic deformation of the thread carrier shell 30 by local elastoplastic rear deformation of the thread carrier shell 30 is at least partially regressed when screwing the threaded bolt 36th

p0206Here also the local elastoplastic reshaping can additionally be superimposed, with a total deformation of the polygonal section 38, which allows the deformed thread regions GBD "time again to move apart, that the threaded bolt 36 can be screwed into the internal thread 22, however, to produce the desired clamping torque.

p0207The deformation '' 60 of the recess '' primarily locally produced by action on the bottom portion 66 but can also be additionally combined with a priority global deformation of the polygonal section 38 through complementary action of deformation forces DKP or DKL on the edge portions 42 as in connection described with the first or second version.

p0208The version according to the third effective point-like deformation forces DKP are also preferably directed transversely to the central axis 14, in particular perpendicular thereto.

p0209However, it is also possible, these acting punctiform

p0210Deformation forces DKP to impart a component toward the first end face 16 or the second end face 18th

p0211In a fourth version of a lock nut according to the invention 10S ' "shown in FIG. 31 and FIG. 32 is carried out in the base region 66 no point-like action, but there are linearly acting

p0212Deformation forces DKL used which are, in this version, for example, in all floor areas 66 of the polygonal section 38 operates to 66 several times around corresponding to the number of floor areas around the central axis 14, for example, the deformed thread regions GBD " 'i to GBD'"₆Caused primarily by local deformation of the threaded support sleeve 30, to produce, so that these six arranged about the central axis 14 deformed threaded portions GBD " 'i to GBD'"₆ for the clamp to be generated torque of the internal thread 22 when screwing it onto a threaded bolt 36 are responsible. The measures provided for in the fourth version linear acting

p0213Deformation forces DKL example, extend transverse to the central axis 14, preferably perpendicular to this or also with a component in the direction of the first end face 16 or the second end 18, and leave the linear bruising 116th

p0214Basically, the amount and direction can deformed linearly

p0215Threaded portions GBD " 'i to GBD'"₆ pairwise different.

p0216As with a fifth version of a lock nut of the invention 10S "" in FIGS. shown 33 and 34, also areally forces acting DKF can be used as an alternative to point-like forces acting DKP or linear forces acting DKL, the sheet-like " 'of the recesses 60 act in the fifth version in the base region 66' 'to produce sheet-like pressure points 118 and thus according to the sheet-like action of a still primarily local but distributed over a larger surface area elastoplastic

p0217"Generate deformation of the thread carrier shell 30 and thus large-scale trained deformed threaded portions GBD".

p0218Even such areally 'acting in the bottom portions 66 "

p0219Deformation forces DKF can either '' be effective or each in three or more a pair of opposing bottom portions 66 '' in a pair of opposing bottom portions 66 or else combined with acting in the edge areas 42

p0220Deformation forces, be they punk shaped deformation forces DKP or linear deformation forces DKL or optionally area- shaped deformation forces DKF.

p0221In the fifth version, the sheet-like acting deformation forces DKF are primarily oriented so that they cross act to the center axis 14, wherein the surface fastener applied deformation forces DKF but also both one component in the direction of the first end face 16 or in the direction the second end face may comprise 18 to the region of a partial area of ​​its action still a reinforced plastic deformation, in particular a mainly local plastic deformation in the thread carrier body 30 and thus also the corresponding deformed thread portion GDB "" of the internal thread to be able to produce the 22nd

p0222In a sixth version of a lock nut 10S '' 'according to the invention, shown in FIGS. 35 and 36, an action is performed on the edge portions 42 is not in the upper portion 112, but for example the linearly acting deformation forces DKL adjacent to a second of the end face 18 upper outer edge 122 between the second end face 18 and, for example, two opposite edge regions 42 or more pairs of opposing edge portions 42, so that each of the outer contour of the carrier 70, the deformation forces DKL act and thus to be a priority global deformation of the polygonal section 38 immediately following the second face 18 leads so that especially deformed threaded portions GBD ' "" occur in the immediately subsequent to the second end 18 threads of the internal thread 32nd

p0223The linearly acting deformation forces DKL are preferably directed so that they act on the one hand in the direction of the central axis 14 and the other part towards the first end side 16 or pressure side 82nd

p0224Also in this embodiment, only two, each to be relative to the central axis 14 opposite deformation forces DKL effective or even several pairs of opposed deformation forces DKL.

p0225In a seventh version of a lock nut according to the invention 10S "" ", shown in FIGS. 37 and 38 act in parallel to the central axis 14 aligned axial deformation forces DKAL line shape, namely oriented radially to the center axis 14 on the second end face 18 in the region of the Thread carrier belt 30 to produce linear pressure points 120 and lead to an orbiting around the central axis 14 of the plastic deformation subsequent to the second end face 18 first

p0226Thread 24 of the internal thread 22, which thus, for example, a total of a constriction with respect to its core hole diameter DK undergoes, and in the direction of the central axis 14 has with respect to a standard curve deformed thread regions whose distance is reduced with respect to the standard pitch. This deformation, which in total leads when screwing in the threaded bolt 36 into the internal thread 22 to a elastoplastic expansion of the polygonal portion 38 in particular close to the second end face 18, which elastoplastic widening again to the first

p0227Threads against the external thread 35 of the screwed threaded bolts 36 oppressive reaction forces resulting which is thus responsible for the desired clamping torque.

p0228Generally it is possible, which can be generated by the deformation forces DK plastic deformations which affect each other on the distance from threaded portions of the central axis 18 and the course of the threads relative to combine with each other at the first to seventh version of the invention thereby, for example, by multiple deformations the polygonal portion 38 to achieve the desired clamping torque during screwing and unscrewing of the female thread on a threaded bolt.

p0229A nut 10 according to the invention can preferably be produced from a material having a bainitic or ferritic-pearlitic structure according to Enclosure 1. For both types of materials, an advantageous combination of tensile strength and ductility is achieved through a targeted control of the structure conversion.

p0230There are generated by alloying micro alloying elements and thermomechanical properties pretreatment process prior to the actual forming process, the result of the actual conversion (cooling run the blacksmith heat at Warmumformvorgängen or increasing the displacement in Kaltumformvorgängen) in defined structural mechanical properties that would be set by a separate heat treatment process after the actual shaping process, for example, when using conventional cold heading grades.

p0231Starting from a material having such a bainitic or ferritic-pearlitic structure is, for example, cold forming or extrusion of a raw material, such as a wire or rod material in at least one forming stage or in several forming to a shape of the nut body 12 of any of the embodiments described above and / or one of the above described versions.

p0232In this forming process of the above-mentioned material by formation of dislocations and / or increasing the dislocation density is carried out a hardening of the material due to the non-homogeneous cross-sectional configuration in different thicknesses, in particular in the area of ​​thinner cross section, a greater deformation occurs than in regions with correspondingly thicker cross-section.

p0233In particular, leading the transformation to an increase in strength of at least 5% compared to the starting material, even better to

p0234at least 10% or more preferably at least 20% starting from strength If the starting material.

p0235For example, there is a stronger solidification of the threaded support sleeve 30 of the nut body 12 in the region of the recesses 60, which contributes to improved stabilization of the internal thread 22 against deformation when loaded with the threaded bolt 36th Here, due to the Versetzungsdichtegradienten generated by the conversion on the basis of the key faces 44 becoming the thread carrier shell 30 to a possible subsequent to the forming process heat treatment, dispensed Because in the higher structural and mechanical requirements, such as the thread carrier shell 30, by the combination of higher dislocation density and material with bainitic or ferritic-pearlitic basic structure sufficient hardness can be achieved.

p0236For example, the hardness of the thread carrier belt 30 is for fine threads in the range of 180 to 360 HV, for coarse thread in the range 110-360 HV.

p0237As an example of a precipitation-hardening ferritic-pearlitic material or precipitation hardening ferritic-perlitic steel having good cold formability, is made for example to the material 24MnSiV5 or to the material 27MnSiV6 40, wherein the latter material are listed in Appendix 2 properties and in investment 2 having said chemical composition.

p0238Here the resistance is achieved by solid-solution strengthening with Si, Mn and / or precipitation with Va, Nb, Ti.