Patent Publication Number: US-2005123376-A1

Title: Tapping assist fastening element and method

Description:
FIELD OF THE INVENTION  
      This invention relates to fasteners and self-tapping fasteners that form internal threads using a swaging or roll forming process. More particularly the invention relates to a fastening element and method capable of forming a fastener assembly by engagement with a self-tapping fastener that reduces the required end load to start the tapping process and assists in the proper alignment of the self-tapping fastener.  
     BACKGROUND OF THE INVENTION  
      Self-tapping fasteners such as self-tapping screws or bolts fall into two broad classes. The first are those which are provided with cutting edges at the work entering end. The second and most common type are those which are so designed to form uniform load carrying internal threads into untapped fasteners or pilot holes with a swaging operation. Fasteners of the first type have numerous disadvantages and one of the most significant being that they all form chips which are cut from the body to which they are driven. As a result, self-tapping fasteners that form threads by deforming a thread pattern within a pilot hole have become the most popular design. Such fasteners are available from a variety of sources and are marketed under the trademark TAPTITE® in connection with a trilobular or three-lobe thread forming blank design.  
       FIGS. 1-2  illustrate a conventional three-lobed fastener according to the prior art. All threads have a characteristic pitch and diameter because of the lobulation of the threads, the radial offset from the axis will vary about the circumference. In general, standard thread diameters and pitches are provided to lobular fasteners, but the lobes tend to have a slightly larger diameter than a standard thread diameter. This enable the lobes to positively form corresponding internal threads as the fastener is driven into an appropriately sized pilot hole into the shape of conforming internal threads.  
      As the fastener is rotated the lobes engage the inner wall of the pilot hole (not shown) and begin to displace material within the pilot hole. In a typical self-tapping fastener, the threaded fastener is provided with a stabilizing zone having stabilizing threads at the end of a fastener shaft and a thread forming zone with corresponding thread forming threads along the shaft of the fastener adjacent the stabilizing zone. The stabilizing zone as illustrated in  FIGS. 1-2  often has a reduced diameter enabling it to fit within an initial untapped hole in a relatively perpendicular fashion. The thread forming zone often has a sloped or tapered shape with a diameter that increases linearly between the stabilizing zone and the full diameter main body of the fastener.  
      Prior known constructions have often provided the thread stabilizing zone and the thread forming zone with a higher out of round than the full diameter main body. In one example, the out of round of the thread forming zone gradually tapers back from the highest out of round adjacent to the stabilizing zone toward the lower out of round that defines the full diameter main body. In another often preferred example, the thread forming zone can define an approximately constant profile high out of round along its entire axial length that transitions step wise at the main body into the characteristic lower out of round. In connection with either example, there is a difference between the high out of round at the stabilizing section and at the main body cross section.  
      As a self-tapping fastener is driven into an untapped pilot hole the thread forming threads encounter the sidewalls of the hole initially. These threads often exhibit an increasing outer diameter and higher out of round. As such, the lobes are able to gradually apply increasing thread forming pressure to the pilot hole until each formed internal thread is contacted by the first full diameter thread. This first full diameter thread often has the out of round profile of the rest of the main body. It provides final formation of each thread in the pilot hole to the desired shape.  
      Self-tapping threaded fasteners are frequently preferred in applications where it is possible to use a metal screw which is harder than the material of a mating element such as a blank or nut through which a threadless bore for the screw has been made. In general, properly forming internal threads in a bore requires several swaging blows from the underlying lobes of the fastener. This process, in essence, forms a shape in the ductile metal of the untapped pilot hole or fastener corresponding to the threads of the self-tapping fastener. A sufficient number of forming threads is necessary to complete the process. Depending upon the nature and hardness of the metal into which a self-tapping fastener is driven, a relatively high driving torque is usually required, particularly in metal having an appreciable thickness. This often results in a stripping torque to driving torque ratio that is relatively low. The requirement of high driving torque not only creates problems with respect to drivability but a low driving torque to stripping torque ratio can restrict the usage of automated power drivers in assembly lines.  
      It is well known that the driving torque of individual fasteners can vary considerably due to the presence of any lubricant, slight variations in the material hardness into which the fastener is driven, in the hole size, in the fastener diameter, as well as dullness of cutting edges or from misformed or damaged threads (especially the lead threads) from handling or processing such as plating. Similarly, failure torque, including stripping torque of the mating threads as well as the failure torque of the fasteners themselves can vary somewhat considerably from one fastener to the next. The clutch or related mechanisms of the power drivers cannot be relied upon to disengage at precisely the same torque value each time. If the driver is set just above the normal driving torque, and any of these variations causes an increase driving torque, conventional tapping fasteners will not be driven in fully and loose assemblies could result. If the driver clutch is so adjusted to give a greater driving torque so as to overcome any such difficulty, a conventional tapping fastener can then be overdriven, resulting in stripped threads or broken fasteners, either of which will result in costly delays of the assembly line while repair or replacement is made.  
      It is also known, that in many cases the efficiency and thus the usefulness of self-tapping operation can be problematic, particularly because at the beginning of each operation considerable pressure or end load must be applied by means of a conventionally used power driven tool to cause the self-tapping screw to properly start winding itself into the material adjacent the cylindrical surface defining the threadless bore. Such forces can make proper alignment difficult. Difficulties may be encountered when the bore is originally, or thereafter becomes oriented at an angle relative to a driven self-tapping fastener such that the fastener is not in perfect alignment with the axis of the bore. As a result, the fastener may become permanently askew and not seat properly. This can be where the lead thread of the fastener is initially slightly misformed or thereafter becomes distorted.  
      Such problems have been acute where for example, the bore axis extends horizontally and the self-tapping fastener is driven from a position relatively higher than or relatively lower than the axis. In many such instances, the threads of the self-tapping fastener which are designed to form threads within the bore upon proper engagement then are mangled or otherwise distorted. If the resulting assembly is formed at all, it may have significantly impaired holding characteristics since the underside of the fastener itself may be damaged and thus weakened. Additionally, the entire fastening assembly may be weakened and put in jeopardy. Moreover, the cocked or askew fastener head may have roughened the surface of the structural element containing the bores such that it would not hold paint, or such that the thickness of such element may be reduced and consequently the entire assembly may become weak. The askew screw head appearance also is undesirable. Frequently, in such situations a new fastener must be driven into the bore, new bore formed, or the part must be scrapped entirely.  
      In order to try and overcome these drawbacks and to make the process go more quickly, a high out of round, which concentrates the force of the blows generated by the underlying lobes of the fastener has often been utilized. Use of a high out of round within the main full diameter threads, reduces the amount of torque that must be applied to form threads. However, this lower torque comes at a price, since it results in less diametrical material remaining in contact with the internal thread once it is formed. Hence, such fasteners will not hold as much load as a more round fastener. This increases the chances of failure occurring in such a fastener system. Such failure in general results from axial pull out, or when thicker nut members are used, fracture. Also, since area varies by the square of the radius, the use of a higher out of round cross-section results in a significantly reduced cross-sectional area, which lowers the screws failure limit. Hence, self-tapping screws typically use an out of round dimension that is a compromise between the optimum value for thread forming efficiency and the optimum value for resistance to failure.  
      Another drawback of self-tapping fasteners is that in order to engage a pilot hole and begin forming threads, they necessarily are initially pulled somewhat out of proper alignment. If the thread forming fastener does not start in a straight line like a normal threaded bolt and nut combination for example, then the threads can be improperly formed and can pose further problems if the fastener is ever removed and then reinserted, since cross threading or additional thread cuts will then likely result. It is the inherent nature of a thread forming fastener to start out of alignment and subsequently straighten up. In order to accomplish this, the undesirable application of significant additional torque to drive the fastener is often required. In some castings with unthreaded bores this has lead to cracking of the casting itself.  
      To date, great effort has been placed into modifying the geometry construction of self-tapping fasteners such as screws or bolts in order to try to overcome these above stated problems, but they have still left significant issues or compromises. Since most all self-tapping fasteners are designed to create uniform load carrying internal threads into untapped nut members or other similar bores upon installation, the structure and the geometry of the untapped bore has not been given equal attention as a potential solution to these problems. Most modifications to unthreaded nuts or mating type fasteners have been directed to nuts that have a particular structure that assists in aligning the screw or bolt that is to be mated with the self-tapping fastener. Known solutions directed to threadless nut type fasteners have generally involved extensive and complicated geometries that project inwardly from the untapped sidewalls and have not decreased the required driving torque and are cumbersome and expensive to form.  
      Several solutions involving a fastening element designed to form a fastener assembly by engagement with a self-tapping screw have been proposed. One such construction provides a threadless bore having a varied diameter and an inwardly protruding rib that has at least one interruption therein. This rib, however, extends substantially around the 360° circumference. Such a construction involves considerable complication and expense in forming the rib and also requires the self-tapping fastener to remove or form an internal thread through the rib itself.  
      Another known self threading fastener device for use with a threaded member utilizes a generally helical rib formed from the material of the side wall protruding inwardly from the side wall. The rib is helically inclined so its angle of inclination corresponds generally to the angle of inclination of the threads on the threaded member. The rib must span the entire circumference of a section of the unthreaded bore. This design is quite complicated and therefore, expensive to form and again necessitates the thread forming fastener to engage and cut threads through the inwardly projecting helical member. This has often lead to increasing the required end load or force required to start the tapping process and cracking the fastening device.  
      It is apparent from the drawbacks of the prior known constructions set forth above that there exists a need for an improved threadless fastening element for use with a self-tapping fastener that overcomes these drawbacks and provides additional benefits and advantages.  
     SUMMARY OF THE INVENTION  
      In accordance with a first aspect of the invention, there is provided fastening element and method for forming a fastener assembly by engagement with a self tapping fastener comprising a solid body having a threadless internal substantially cylindrical surface defining a bore having an axis and extending through all or a portion of a solid body, and at least one indentation, preferably of a substantially elliptical configuration extending inwardly from a portion of the top of the bore or a lead in to the bore. The indentation extends around the circumference of the cylindrical inner surface from about 1° to greater than 360° and in some preferred embodiments from about 15° to about 360° in accordance with certain aspects of the invention. The helix angle or pitch of the indentation of the threadless bore can be specially dimensioned for engagement by a standard size self tapping fastener. More specifically, the indentation of the threadless bore may take the form of a narrow scribe like line having a flat, notched, rounded or angled base or a wider notch that is approximately equal to or greater than the distance between threads of the self tapping fastener.  
      A further aspect of certain embodiments is to provide a plurality of indentations which in total extend less than the entire 360° circumference of the threadless bore. Regardless of the type or number of indentations used, all the indentations can extend only a very slight depth into the internal surface of the thread bore, and in most all cases, significantly less than the depth of the thread to be formed by the self tapping fastener.  
      The indentation provided in the internal surface of the threadless bore can also initially act as a guide and alignment device for the self tapping fastener. Upon assembly, the end load or force required to start the tapping process is significantly reduced as the self tapping fastener passes the indentation and engages the portion of the threadless bore without the indentation forming threads in the bore. As a result the differential between the driving torque and the failure torque of the self tapping fastener is significantly altered, thereby resulting in fewer failures and significantly reducing the risk thereof while assisting in monitoring proper alignment.  
      It is therefore a primary object of the present invention to provide a new and improved fastening element for forming a fastener assembly by engagement with a self tapping fastener as set forth above that assists in aligning the fastener and/or decreases the end load required to start forming threads in the element. 
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS  
      These and other aspects and objects of the invention will become better understood from the following detailed description of various embodiments thereof, when taken in conjunction with the drawings wherein:  
       FIG. 1 , already described, is a side view of a self tapping fastener according to the prior art;  
       FIG. 2 , already described, is a front end view of the fastener of  FIG. 1 ;  
       FIG. 3  is a perspective view of one embodiment of the present invention;  
       FIG. 4  is a cross-section taken along line  4 - 4  of  FIG. 3 ;  
       FIG. 4A  is a cross-section taken along line  4 A- 4 A of  FIG. 3 ;  
       FIG. 5  is a perspective view of an alternative embodiment of the present invention;  
       FIG. 6  is a cross-section taken along line  6 - 6  of  FIG. 5 ;  
       FIG. 6A  is an exploded view of a portion of  FIG. 6 ;  
       FIG. 7  is a perspective view of another alternative embodiment of the invention;  
       FIG. 7A  is an exploded view of a portion of  FIG. 7 ;  
       FIG. 8  is a cross-section of an alternative embodiment of the present invention;  
       FIG. 9A  is a partial cross-section of an embodiment of the invention shown in combination with a self-tapping fastener;  
       FIG. 9B  is an exploded view of a portion of  FIG. 9A ;  
       FIG. 9C  is a partial cross-section of an embodiment of the invention shown in combination with a self-tapping fastener;  
       FIG. 9D  is an exploded view of an alternative embodiment to the one illustrated in  FIG. 9B ;  
       FIG. 10  is a test apparatus utilized to measure end load and drive torque values for various embodiments of the present invention;  
       FIG. 11  is a cross-section of another alternative embodiment of the present invention;  
       FIG. 11A  is an exploded view of a portion of  FIG. 11 ;  
       FIG. 12  is a partial cross-sectional view of another alternative embodiment of the present invention;  
       FIG. 13  is a cross-section of another alternative embodiment of the present invention;  
       FIG. 13A  is an exploded view of a portion of  FIG. 13 ;  
       FIG. 14  is a cross-section of another alternative embodiment of the present invention;  
       FIG. 15  is a cross-section of another alternative embodiment of the present invention;  
       FIG. 15A  is an exploded view of an alternative embodiment geometry to that shown in  FIG. 15 ;  
       FIG. 15B  is an exploded view of another alternative embodiment geometry to that shown in  FIG. 15 ;  
       FIG. 16A  is a partial perspective view of an alternative embodiment of the present invention;  
       FIG. 16B  is a partial perspective view of another alternative embodiment of the present invention;  
       FIG. 16C  is a partial perspective view of another alternative embodiment of the present invention. 
    
    
     DETAILED DESCRIPTION OF CERTAIN PREFERRED EMBODIMENTS  
      Referring to the drawings, and in particular  FIGS. 3-4A  and  9 A-D thereof, there is illustrated one embodiment of the fastening element of the present invention designated generally at  10 . In this particular embodiment, the fastening element of the present invention, is in the form of a weld nut  12  with a pilot  14 . It should be understood that the construction and principles of the present invention are not restricted to weld nuts, fasteners with pilots or nuts in general but rather this embodiment is only exemplary of the present invention which can be utilized with all manner of threadless bores contained in fasteners or castings that are susceptible of having internal threads formed therein by engagement with a self-tapping fastener or a tap in a nut tapping process. The fastening element of the present invention is also capable of forming a fastener assembly by engagement with all manner of self-tapping fasteners such as, screws, bolts, studs and the like having a variety of different constructions. The illustrations and descriptions herein of both the fastening element and self-tapping fastener are meant to be exemplary and not limiting.  
      The fastening element  10  as illustrated in  FIG. 3  has a pilot  14  extending upwardly from its top  15 . The pilot  14  features an angled lead in area  16  located around its internal circumference. The non-pilot end  18  of the element  10  also has an angled or rounded lead in area  20  located between the respective lead in areas  16  and  20  is a bore  22  that extends through the entire body  24  of the element  10 . In the case of a blind hole in a casting for example, the bore would not extend through the entire body. The internal surface  26  of the bore  22  is non-threaded. The diameter of the bore  22  is continuous and uninterrupted except for a small portion of the circumference thereof that is adjacent the lead in area  16  of the pilot  14 .  
      To facilitate the entrance of a self-tapping fastener into the bore  22  of the element  10  and reduce the end load required to begin the tapping process, one or more indentations  28  are provided in the bore  22  adjacent the lead in area  16 . In the embodiment illustrated in  FIGS. 3-4A  the element  10  utilizes a single indentation  28  that extends less than the entire circumference of the bore  22 . The indentation  28  is tapered in an axial direction with the thinnest portion being adjacent the lead end  30  and the thickest portion being adjacent the trailing end  32  of the indentation  28  for a normal right handed threaded fastener. The ends  30  and  32  terminate preferably on a helix. Likewise, the bottom edge  34  preferably has a helix angle or pitch that prefereably corresponds to the pitch of the thread on the fastener with which the element is intended to be used. The edge  34  may be flat or angled as illustrated in  FIGS. 9B and 9D . The edge may also have a helix angle or pitch that does not correspond to the pitch of the thread on the fastener with which the element is intended to be used. In such cases, similar beneficial results in the reduction of end load are achievable, however, the benefits in aligning the self-tapping fastener are usually not as high.  
      The depth of the indentation can vary from a small fraction of the ultimate depth of the threads to be formed in the bore  22  to a maximum depth that equals the depth of the threads or the difference between the major and minor diameter of the fastener. Preferably, the depth of the indentation  28  is greater than zero but less than and in most preferred cases substantially less than the depth of the ultimate thread that is to be formed in the bore  22 . Regardless of its depth the overall indentation is always smaller in one or more dimensions than the ultimately formed thread. The depth of the indentation in the bore is preferably, although not necessarily, substantially constant along its length. It has been found that even such slight indentations permit a significantly reduced end load required to start the self-tapping fastener in the element. It has also been found that the indentations allow a low end load even for a slightly misformed or damaged lead threads on a self-tapping fastener that could adversely effect the alignment and further guide the fastener to start and therefore finish in a straighter alignment within the element.  
      The trailing end  32  of the indentation  28  can terminate so as to create a notch  36  as illustrated in  FIGS. 3 and 4 A. In the alternative, the indentation may be tapered at the trailing end  32  from the full depth of the indentation back to the diameter of the non-threaded bore. The indentation extends circumferentially around the element as described, for a distance of about at least about 1° to greater than 360°, and most preferably about 15° to just under 360°. The base  38  of the indentation is preferably flat as illustrated although an angled, tapered or rounded construction (See  FIGS. 6A, 11A  and  12 ) could also be provided. Additionally, the lead end  30  of the indentation  28  preferably begins in the lead in area  16 . In certain alternative embodiments, the lead end  30  can instead begin adjacent the lead in area  16  in the bore  22  or in a bore without a lead in area. The axial length of the widest portion of the indentation  28  at the trailing end  32  can extend up to a distance equal to the distance between respective thread crests of the self-tapping fastener or greater in some embodiments. The indentations may be formed in the bore  22  by a variety of known processes such as cold forming or cutting or tapping dies.  
      Use of the embodiment of the fastening element  10  illustrated in  FIGS. 3-4A  will now be discussed with particular reference to FIGS.  9 A-D. The element  10  is illustrated in combination with a self-tapping bolt designated generally as  40 . Such trilobular self-tapping bolts are well known and are commercially available from a variety of sources under the trademark TAPTITE®. The fastener  40  has an out of round diameter with three lobes each having an increased radius measured from the center of the fastener similar to the design illustrated in  FIGS. 1-2 .  
      Referring particularly to  FIG. 9A , two such lobes  42  and  44  respectively are visible. The fastener  40  is provided with a stabilizing section  46  at the end of its shank. The diameter of the fastener  40  in this section is smaller than the diameter on the remainder of the shank  48 . The reduced diameter of the stabilizing section  46  enables it to fit within an untapped pilot hole in a relatively perpendicular fashion without having its outer diameter contact the element  10 . The fastener  40  is also provided with a continuous thread  54  along substantially its entire length beginning at the end of the shaft and continuing virtually the entire length of the shank  48 . Moving along the fastener shank  48  away from the stabilizing section  46  and towards the head  52 , a thread forming section  50  is provided. The thread forming section  50  has a tapered shape with a diameter that increases between the stabilizing section  46  and the full diameter main body  51 . The thread has a continuous helix angle or pitch angle indicated as A.  
      As the fastener  40  is driven, it moves axially through the pilot  14  and partially into the bore  22 . This axial movement into the bore  22  continues until the diameter of the fastener increases sufficiently in the thread forming section  50  until a portion of the thread  54  encounters the bottom edge  34  of the indentation  28 . As previously indicated, the bottom edge  34  of the indentation  28  preferably has the same helix angle or pitch as the fastener  40 . As a result, once the thread  54  of the rotating fastener  40  contacts the edge  34 , the edge  34  acts as a guide properly aligning the fastener in an appropriate helical path to form the mating threads in the element  10 . As the fastener  40  continues to rotate this thread  54  in engagement with the indentation, one of the lobes such as a lobe  42  will encounter the trailing end  32  of the indentation  28 . At this point the fastener  40  will begin forming threads by deforming the bore  22  and the indentation  28 .  
      As will later be discussed in detail, it has been found that provision of the indentation  28  with either a notch or a taper at the trailing end  32 , ensures that the fastener  40  is properly aligned as it begins to form threads in the bore. It has also been found that such an indentation also significantly reduces the end load force required to form threads with the fastener since the first cut by the thread  54  of the fastener  40  is made into a notched or tapered sidewall  33 , as illustrated for example in  FIG. 4A , as opposed to a sidewall having a completely flat surface as in the prior art. This has proven to be even more advantageous where the lead thread is even slightly misformed or damaged. Once the threads begin to be formed by the fastener  40  in the element  10 , the indentation  28  is replaced by a fully formed mating thread  56  as indicated in  FIG. 9C . The reduction of required end load torque had proven to be so significant that the self-tapping fastener may usually be hand turned into an element to a point where the fastener is properly aligned and sufficiently engages the element to resist uncoupling. It has also been found that use of one or more indentations as described in the various embodiments of this invention, has not adversely effected the performance of the lead threads ultimately formed in the fastening element by the self-tapping fastener.  
      In  FIGS. 5 and 6  there is illustrated a modification of the fastening element designated generally at  10   a , which is generally similar to that shown in  FIGS. 3-4A  with the suffix a added to the referenced numerals to indicate like parts. In this embodiment the indentation  28   a  has a slightly different form and geometry than that previously described. In this embodiment, the indentation  28   a  again extends to the same circumferential extent and depth as previously described. It also preferably, although not necessarily, has the same helix angle or pitch as the threads on the self-tapping fastener utilized to form threads therein. The indentation  28   a , however, extends in a helical line and preferably has a substantially constant width along its entire circumferential length. As such, the indentation  28   a  of this embodiment does not create a notched cross-section that extends along the entire length of the indentation  28   a  from the top of the lead in area  16   a  or bore  22   a  to the bottom edge  34   a . Instead, the indentation  28   a  forms a groove along a portion of the circumference of the bore that moves increasingly away from the lead in area  16   a  as the helical path between the lead end  30   a  and trailing end  32   a  is traversed. The width or axial length of the indentation  28   a  is preferably greater than zero and is less than that of an ultimately formed thread.  
      As illustrated in  FIG. 6A  the base  38   a  of the indentation  28   a  is preferably pointed and can also be angled to approximate the shape of the ultimate mating thread, illustrated in dotted lines as  56   a  that will be formed in the bore  22   a . In the alternative, the base can also be rounded or flat (See  FIGS. 4A and 12 ). Likewise, the trailing end  32   a  may terminate at the same depth as the remainder of the indentation  28   a  or may taper back to the surface of the bore  22   a . In all of the embodiments illustrated and described with respect to  FIGS. 5 and 6 , the element  10   a  functions the same way in use as previously described with respect to the embodiments illustrated in  FIGS. 3-4A  and  9 A-D and similar beneficial results have been achieved.  
      In  FIGS. 7 and 7 A there is illustrated another modification of the fastening device designated generally at  10   b , which is generally similar to that shown in  FIGS. 3-4A  and  9 A-D with the suffix b added to the reference numerals to designate like parts. In this embodiment the indentation  28   b  does not have a substantially constant depth over its length between the lead end  30   b  and the trailing end  32   b . Instead the base  38   b  of the indentation  28   b  is provided with two separate sections, a tapered section  58  that extends from the lead end  30   b  and a constant depth section  60  that extends from the tapered section  58  to the trailing end  32   b . The transition between the section  58  and the section  60  is designated by the line X-X in  FIG. 7A .  
      In the illustrated example the tapered section  58  would be the first encountered by the self-tapping fastener, although the relative position of this section with the tapered section could be reversed. Likewise, the dividing line between the two sections  58  and  60  respectively, could occur virtually anywhere along the indentation  28   b  or the constant section  58  could be eliminated entirely and the depth of the indentation could be tapered or constant along its entire length. In certain preferred embodiments, the constant depth section  60  begins at a maximum depth and tapers toward the surface  26   b  of the bore  22   b  at the end of this section. This emdodiment can utilize the construction details of the other embodiments described herein. The use, performance and characteristics of the embodiment illustrated in  FIGS. 7-7A  are the same or substantially similar to those previously described with respect to the embodiments illustrated in  FIGS. 3-6  and  9 A-D.  
       FIG. 8  illustrates another modification of the fastening element  10   c , which is generally similar to that shown in  FIGS. 3-4A  and  9 A-D with the suffix c added to the reference numbers in order to designate like parts thereof. In this particular embodiment multiple indentations are provided around the circumference of the bore  22   c , although two indentations are illustrated in this embodiment, it should be understood that more than two could also be provided. In most preferred embodiments the indentations  28   c  do not overlap. The indentations  28   c  are preferably equally spaced about the circumference of the bore  22   c . By using multiple indentations in this embodiment, the thread of a self-tapping fastener is provided with multiple points of engagement and alignment around the circumference of the bore  22   c . It is further preferred that when multiple indentations are used that the total circumference of all indentations not exceed 360°. The construction and configuration of the indentations  28   c  can take any of the forms that have been previously described. Likewise, the indentations  28   c  contained on the element  10   c  can take the form of any of the constructions described herein and yield similar results and advantages to those previously described.  
      In  FIGS. 11 and 11 A a modification of the fastening element designated generally at  10   d , which is generally similar to that shown in  FIGS. 3-4A  with the suffix d added to the referenced numerals to indicate the like parts. In this embodiment the indentation  28   d  has a slightly different form and geometry but is otherwise similar to those constructions previously described. In this embodiment, the indentation  28   d  is an angled groove that extends for more than the 360 degree circumference of the element  10   d . Although the indentation  28   d  is illustrated as beginning in the lead in area  16   d , it could instead begin in the internal surface  26   d  of the bore  22   d.    
      As with other previously described embodiments, the shape and length of the indentation can vary considerably because the self-tapping fastener will form over or reform and replace the indentation to match the thread profile. As a result, as illustrated in  FIGS. 11, 11A  and  12 , the shape or profile of the indentation  28   d  can vary from the normal 60 degree angled thread profile to a rounded or virtually any other shape. The dashed lines designated  72  are the boundry areas which a full form thread will occupy when self-tapping is complete.  
      In  FIGS. 13-13A  a modification of the fastening element designated generally at  10   e , which is generally similar to that shown in  FIGS. 3-4A  with the suffix e added to the referenced numerals to indicate like parts. In this embodiment the indentation  28   e  has a slightly different form and geometry but is otherwise similar to those constructions previously described. In this embodiment, one or more indentations  28   e  are provided with a generally rectangular notch-type configuration. The sidewalls  74  preferably extend at an angle of about 90 degrees (or greater or less than 90 degrees) from the lead in area  16   e  and/or the internal surface  26   e  of the bore  22   e . The depth of the indentation  28   e  is no greater than, and preferably less than, the depth of the ultimately formed thread in the bore  22   e.    
      The angle of the bottom edge  34   e  may either be the same as the helix angle of the self-tapping fastener or different. Either such design provides at least some beneficial effect on alignment of the self-tapping fastener and allows it to start tapping with reduced end load. The previous descriptions regarding the use, performance, characteristics and construction of this embodiment are the same or substantially similar to those embodiments previously described.  
      In  FIG. 14 a  modification of the fastening element designated generally at  10   f , which is generally similar to that shown in  FIGS. 3-4A  with the suffix f added to the referenced numerals to indicate like parts. In this embodiment the indentation  28   f  has a slightly different form and geometry but is otherwise similar to those constructions previously described. In this embodiment the indentation  28   f  takes the form of a scuffed or scratched surface along a portion of the inner surface  26   f  of the bore  22   f . The indentation  28   f  can take the form of a circular or angular grain or have a plurality of different angles, edges and/or voids in the surface  26   f . The indentation  28   f  could also extend into the lead in area  16   f . The roughened surface of the indentation  28   f  permits similar benefits regarding the alignment and reduced end load required for the self-tapping fastener. The use, performance, characteristics and construction of the embodiment illustrated in  FIG. 14  are similar to those in the other embodiments described herein.  
      Referring now to FIGS.  15 ,  15 A-B and  16 A-C, various alternative constructions of indentations  28  are illustrated that have been cold formed into a fastening device  10 . Although these embodiments illustrate the indentations as beginning in the respective lead in areas, it should be understood that the indentations could also begin in the respective inner surface  26  of the bores  22 .  
      As illustrated in  FIGS. 15A and 15B  the profile of an indentation having a substantially flat base  38  can vary from a substantially square configuration to one that has a flatter rectangular configuration. Similarly FIGS.  16 A-C illustrate indentations  28  having an angled base  38 . Such a configuration may vary from having an upper angle designated as X that is either less than, equal to or greater than 90 degrees. The lower angle designated as Y can be similarly varied.  
     EXAMPLES  
      The following examples will serve to illustrate some of the novel features and advantages of the present invention. While these examples show one skilled in the art how to operate within the scope of this invention, they are not to serve as a limitation on the scope of the invention. A series of tests were conducted to evaluate the performance of various configurations of the fastening element of the present invention.  
      Referring to  FIG. 10 , the test fixture that was utilized is illustrated and generally referred to at  62  to determine the load required to start. Each fastening element  10  that was tested was placed in a nut fixture  64  that was slidably connected along two rails  66  to permit engagement with a force gauge  68 . A self-tapping fastener  40  was placed in a socket or on a drive bit collectively referred to as  69  mounted on a torque gun  70 . The torque gun was then started and moved into engagement with the fastening element in order to form mating threads therein. The required end load was measured for each fastening element. The alignment of the self-tapping fastener in the resulting formed threads of the fastening element was also inspected.  
      In all of the tests, both unthreaded fastening elements without indentations and those with various indentations in accordance with the present invention were tested. In general, in the case of the unthreaded nuts without any indentation, the bolt just spun and did not start threading until a gradual load or force was applied. This is what has been referred to previously as end load. The fastening elements that had an indentation of the type of one of the embodiments described above, allowed the bolt to start threading immediately as the torque gun started with virtually no end load required. The alignment of all of the self-tapping fasteners used in the examples was likewise consistently straighter than those driven into nuts without indentations.  
     Example 1  
      In this example, the force required to start the tapping process for unthreaded nuts having a central bore without any indentations was compared against nuts having a single indentation and multiple indentations in accordance with the present invention. The indentations had a depth less than the ultimate thread formed by the self-tapping fastener and had the same helix angle or pitch as the threads of the self-tapping fastener. All bolts used were M12 TAPTITE® trilobular bolts. The nuts were untapped with 11.2 mm diameter holes. The results were as follows:  
                                                       No Indentation   Single Indentation   Dual Indentation           Force/Lbs.   Force/Lbs.   Force/Lbs.                          14.5   .5   .5           14.5   .5   .5           16.5   .5   .5           19.0   .5   .5           13.0   .5   Ave. .5 Lbs.           18.5   .5           10.0   .8           10.0   .2           18.0   Ave. .5 Lbs.           19.0           14.5           Ave. 15.5 Lbs.                      
 
      As illustrated in these results, the nuts having one or more indentations in accordance with the present invention continuously exhibited a dramatically reduced required force or end load to start the tapping process as compared to those that did not have any such indentations.  
     Example 2  
      In this test, all bolts utilized were again M12×1.75 TAPTITE® trilobular bolts. All nuts used were untapped with 11.2 mm diameter holes. Various types of indentations were made in the nuts as indicated below and measured against nuts without any such indentations. The results were as follows:  
                                       No.   Circumferential Length   End Load (Lbs.)                                    Nuts With Indentations Cut In Nut With Standard       M12 TAPTITE ® Bolt                         1    90°   0.5       2    90°   0.5*       3    90°   0.5       4    90°   1.0*       5    90°   0.5                 Nuts With Thread Indentation Rolled In Nut With Captive Point Bolt                         1   180°   .5       2   180°   .5*       3   180°   .5       4   180°   1.0                 Nuts With No Indentation                         1       13.0       2       5.0       3       9.5*       4       12.0       5       9.5*                 Nuts With Machined Indentation                         1   270°   .5       2   360°   1.0*       3   360°   .5       4   180°   .5*                 *Denotes Bolts That Had Flattened Lead Threads             
 
      The results indicated that all of the nuts having indentations in accordance with the present invention regardless of the type and circumferential extent of the indentation required a dramatically reduced end load to start the tapping process compared to nuts without any such indentations. This was likewise true for bolts that had flattened lead threads.  
     Example 3  
      A third example was conducted to attempt to measure the effect of a single notched type indentation made in an unthreaded nut to compare the effect of various circumferential lengths of such indentations on the performance of the fastening element. All of the indentations had a depth that was less than the ultimate thread formed by the self-tapping fastener. TAPTITE® trilobular bolts were again used. The results were as follows:  
                              Nuts With Single Indentation                                                                                     30°   60°   90°   120°   180°   270°   360°                                                         Circumferential   1   1.5   0.5   0.5   0.5   1   0.5       Length-No.:       1   1   1.5   0.5   0.5   0.5   1   0.5       2   1.5   2   0.5   0.5   0.5   2.5   0.5       3   1   0.5   0.5   0.5   0.5   0.5   0.5       4       0.5   1   1   0.5   0.5   0.5       5       0.5   0.5   0.5   1   0.5   0.5       Nut With No           Indentations No.:           1   13.5       2   9.5       3   6.5                  
 
      All of the values above are pounds of force required to start the self-tapping bolts, also referred to as end load. In this example the nuts with an indentation consistently required an end load many times lower than those nuts without indentations to start the self-tapping bolts. This was true regardless of the circumferential length of the indentation.  
      While the principles of the invention have been made clear in illustrative embodiments, it will be obvious to those skilled in the art that many modifications of structure, arrangement, proportions, the elements, materials and components can be used in the practice of the invention, which are particularly adapted to specific environments and operative requirements without departing from those principles. The appended claims are intended to cover and embrace any and all such modifications, within the spirit and scope of the invention.